Abstract:
A printing group of a printing machine is comprised of a pair of cylinders each having a circumference that corresponds essentially to a length of a section of a side to be printed. The effective generated surface of at least one of the cylinders comprises, at the most, one break in the circumferential direction. The surface forms, in the longitudinal direction, a plurality of adjacently arranged breaks which, when viewed in the circumferential direction, are arranged in a staggered manner with respect to each other.

Description:
FIELD OF THE INVENTION 
   The present invention is directed to a printing group of a printing press, a method for placing a cylinder against or away from another, as well as a method for producing a printed product. 
   BACKGROUND OF THE INVENTION 
   A linearly arranged printing group is disclosed in DE 100 08 216 A1. A plane through the rotating shafts of the cylinders and the paper web form an obtuse angle. The cylinders are seated in guide devices in the lateral frame in a linearly movable manner. 
   A printing group is known from DE 198 03 809 A1. A forme cylinder has one printing plate in the circumferential direction on its circumference, and several printing plates in the longitudinal direction. A transfer cylinder working together with the forme cylinder has double the circumference and is embodied for having one printing blanket in the circumferential direction and two in the longitudinal direction which two printing blankets, however, are arranged offset from each other in the circumferential direction. 
   JP 10-071 694 discloses printing group cylinders with four grooves arranged next to each other and offset in the circumferential direction in respect to each other. The printing group cylinders have a so-called double circumference. 
   An arrangement for a joint-free printing press is known from CH 345 906. The joints of four dressings which are arranged next to each other on transfer cylinders of double circumference, and the joints of four dressings which are arranged next to each other on a forme cylinder, are arranged offset from each other. 
   A double printing group is known from DE 198 15 294 A1, wherein the rotating shafts of the printing group cylinders are arranged on one level. The cylinders have four times the width of a newspaper page, double width and a circumference of one height of a newspaper page. The transfer cylinders have endless sleeves, which can be laterally exchanged through openings in the lateral wall. 
   Printing group cylinders of single circumference are known from U.S. Pat. No. 4,125,073, which have an oscillation damper. In the case of wider printing presses, the forme cylinder has a double circumference and two printing plates arranged one behind the other. The grooves, which are arranged in the longitudinal direction next to each other and which receive the printing plates, are additionally offset in respect to each other in the circumferential direction. 
   A double printing group is known from DE 44 15 711 A1. For the purpose of improving the print quality, a plane which extends perpendicularly to the paper web is inclined by approximately 0° to 10° in relation to a plane connecting the two rotating shafts of the transfer cylinders. 
   JP 57-131 561 discloses a double printing group wherein the shafts of the printing group cylinders are arranged in one plane. The phases of the printing group cylinders are arranged with each other in such a way that grooves for fastening the dressings roll off on each other, and simultaneously on the two printing groups which are working together. 
   A double printing group is also disclosed in DE 34 12 812 C1. The cylinder shafts are arranged in a common plane, which extends inclined in relation to the web to be imprinted. The placement of the transfer cylinders against, or away from other cylinders takes place along an almost straight movement direction by the use of double eccentric cams. 
   EP 0 862 999 A2 discloses a double printing group with two transfer cylinders which are working together and which are seated in eccentric, or double eccentric bushings, for the purpose of being placed against or away from other cylinders. In another embodiment, the two transfer cylinders are seated on levers, which are seated eccentrically in respect to the forme cylinder shaft and are pivotable. 
   A double printing group, in which the shafts of the printing group cylinders are arranged in one plane, is known from EP 1 075 945 A1. Several printing group cylinders are seated in carriages and are embodied so that their distance from each other can be changed by the use of guide elements arranged in a support wall for the purpose of being placed against or away from other cylinders. 
   Printing group cylinders are known from DE 199 37 796 A1, which can be moved along a linear actuation path in order to place them against or away from each other. A drive motor, which is moved simultaneously with the cylinder, is assigned to each cylinder. Movement takes place in a direction extending parallel in respect to a common plane of the printing group cylinders. 
   For the purpose of the transfer cylinders in U.S. Pat. No. 5,868,071 being placed against or away from other cylinders, these transfer cylinders are seated in carriages. 
   These carriages are linearly displaceable in the lateral frame along parallel movement directions in linear guide elements having linear bearings. 
   SUMMARY OF THE INVENTION 
   The object of the present invention is directed to providing a compact, low oscillation printing group for a printing press, which can be produced in a simple manner, and on a method for placing a cylinder against or away from another cylinder, as well as to a method for producing a printed product. 
   In accordance with the present invention, this object is attained by providing a printing group of a printing press having at least a pair of cylinders. Each cylinder can have several sections in its longitudinal direction, which sections are offset in the cylinder circumferential direction. The cylinder shafts can be in a common plane when the cylinders are in a print-on position. These shafts can be of the forme cylinder and the transfer cylinder in a print-on position. The plane extends at an angle with respect to a web passing through the printing group. The shafts can be moved along a linear actuating path. 
   The advantages which can be gained by the present invention lie, in particular, in that a printing press is provided which is constructed in a compact, low-oscillating and rugged manner, provides a large production variety and requires a comparatively low production and maintenance outlay. 
   Minimizing the number of parts which must be designed to be movable for normal operations and during setup, for example omitting the movement of all cylinders, frame walls, bearings etc., assures a rugged and cost-effective construction. 
   The cylinders support each other by the linear arrangement of the printing group cylinders, i.e. by the arrangement of the rotating shafts of the printing group cylinders in the print-on position in substantially one plane. This prevents relative sagging of the cylinders. Even a compensation of the bending static line of the forme and of the transfer cylinders, in respect to each other, can be achieved. 
   Since the dressings on the cylinders are not secured in grooves extending continuously over the length of the cylinders, but instead in grooves which are offset in respect to each other in the circumferential direction, a groove beating, in the course of the passage of the groove during the roll-off of two cylinders on each other, is considerably reduced. In an advantageous embodiment, in the case of two grooves arranged next to each other in the longitudinal direction, the grooves are arranged offset by 180° from each other. 
   The arrangement of the printing group cylinders and their grooves in such a way that the grooves of each cylinder, which are offset in respect to each other, roll off in the area of the opposite, offset groove of the cylinder working together with it, is particularly advantageous. A compensation of the dynamic forces can occur in this way. At a fixed offset angle of 180°, and with a linear arrangement of the cylinders, destructive interference occurs at all production rates, i.e. angular speeds, without an offset angle of the grooves needing to be changed as a function of the number of revolutions or the frequency. 
   The arrangement of printing group cylinders of single circumference is particularly advantageous for printed products of a small and/or of a variable number of pages and/or for print shops with restricted space availability. In comparison with the production of the same product on a printing press of double circumference (without assembling), no “double” plate change is required. In contrast to a printing press of double circumference, during assembling operations it becomes possible to create a page jump of two pages and in this way to provide increased flexibility in the printed product. 
   The type of construction, with all of the printing groups cylinders being of a single circumference, permits a much more compact and easier construction, in comparison with printing groups having one or several cylinders of double circumference. Also, rubber blankets, which would have to be replaced in case of damage are smaller and therefore more cost-effective. 
   The use of printing blankets and printing plates makes it possible to seat the cylinders stably at both ends, which makes possible a simple, rugged and cost-effective construction of the frame receiving the printing group cylinders. 
   Also, in view of a rugged and simple construction, it is advantageous if only the transfer cylinders need to be moved for bringing the printing group into or out of contact with others. Although the forme cylinders can be movably seated for adjusting the distance to the associated transfer cylinder as well as to a possible inking system and, if provided, a dampening system, the placement against or away from each other of the transfer cylinders and the associated forme cylinders takes place in an advantageous manner only by a movement of the transfer cylinders. 
   The linear arrangement of the cylinders is made possible by a specially selected movement in the area of the printing position. At the same time, devices for movement into and out of contact, or movements into and out of contact of the forme cylinders are avoided. This, too, contributes to a rugged and simple construction. 
   In one embodiment, the transfer cylinders are seated in carriages, for example, in linear guide devices, or on the lateral frame, which makes possible a movement which is substantially perpendicular in respect to the plane of the axes of the cylinders. If the guide devices are arranged in specially designed inserts on the lateral frame, the journals are shortened and make possible a simple construction of an encapsulated lubricant chamber. A special arrangement of the movement direction makes possible the rapid and assured separation between the forme and counter-pressure cylinders, as well as from the web. 
   For this purpose, the transfer cylinders are arranged, in another embodiment, on levers, which levers are seated eccentrically pivotable in respect to the forme cylinder axis. By the special placement of the pivot points and the size of the eccentric, in respect to the rotating shaft of the forme cylinder, together with the selected inclination in relation to the plane of the cylinders constituting the printing position, or between the web and the plane of the cylinders, the rapid separation of associated cylinders, or access to the web, are possible. The movement into and out of contact during operation takes place only by the transfer cylinders and, in a preferred embodiment, by use of only a single actuating movement. 
   In a third embodiment, the transfer cylinders are seated in double-eccentric bushings, which makes possible a movement which is almost linear and to a large extent which is perpendicular to the plane of the cylinder axes, at least in the area near the printing position. 
   By the dressings being embodied in the form of so-called metallic printing blankets on the transfer cylinders, the effective groove width is reduced, because of which, an excitation of oscillations is further reduced in an advantageous manner. The non-printing area on the cylinders, i.e. the “white edge” on the product, as well as paper waste, are also reduced. 
   An embodiment of the printing group with cylinders of single circumference, and the arrangement in one plane, with offset grooves which, however, alternatingly roll off on each other, and with dressings which are embodied as metallic printing blankets on the transfer cylinders, is particularly advantageous. 
   Cylinders, or rollers, of printing groups must be moved away from each other, out of an operating state designated as “print on”, i.e. a print-on position, and then back into contact with each other, particularly for washing, changing of dressings, and the like. The radial movement of the rollers required for this also contains a movement component in a tangential direction, whose size is a function of the structural design; i.e. the design of the eccentric cam, lever, linear guide device, as well as their angle in respect to the nip point of the actuating device. If a speed difference is created on the active jacket surfaces at the nip point because of the actuation in relation to the operational state, this implies, because of the surface friction of the roller materials used, a tangential frictional force component which is directed opposite to the actuating movement. Therefore, the actuating movement is slowed by this, or its speed is limited. This is important in particular with printing group cylinders in case of so-called “windings”, since there large frictional forces also result from the high pressures which are also occurring. 
   It is therefore advantageous, in a method for bringing cylinders into and out of contact with each other, that a relative tangential speed in the area near the contact, i.e. in the area of the nip point, of two cylinders or rollers working together, is reduced, correlated with the movement, by the intentional rotation, or turning, of at least one of the affected cylinders or rollers. Besides a reduction of the slowing of the actuation, an unnecessarily high load, such as caused by friction or deformation on the dressings and/or the jacket surfaces of the involved cylinders or rollers, is prevented. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
     Preferred embodiments of the present invention are represented in the drawings and will be described in greater detail in what follows. 
     Shown are in: 
       FIG. 1 , a schematic representation of a double printing group, 
       FIG. 2 , a schematic representation of a three-cylinder offset printing group, 
       FIG. 3 , a schematic representation of a double-wide double printing group, 
       FIG. 4 , a schematic representation of a double-wide double printing group, which is highly symmetrical, 
       FIG. 5 , a schematic representation of a double printing group in a section taken along line B—B in  FIG. 1 , and with a linear actuating path, 
       FIG. 6 , a schematic representation of a non-linear double printing group with linear actuating paths, 
       FIG. 7 , a schematic representation of an H-printing group with a linear actuating path, 
       FIG. 8 , a side view of a first embodiment of a linear guide device for transfer cylinders, 
       FIG. 9 , a cross-section through the linear guide device in  FIG. 8 , 
       FIG. 10 , a side elevation view of a second embodiment of a linear guide device for transfer cylinders, 
       FIG. 11 , a section through the linear guide device shown in  FIG. 10 , 
       FIG. 12 , a schematic representation of a linear double printing group in a section taken along line B—B in accordance with  FIG. 1 , and with a curved actuating path, 
       FIG. 13 , a schematic representation of an angled double printing group in a section taken along line B—B in accordance with  FIG. 1 , and with a curved actuating path, 
       FIG. 14 , a schematic side elevation representation of an H-printing group with a curved actuating path, 
       FIG. 15 , a lateral view of the seating of the cylinders, 
       FIG. 16 , a cross-section through the seating in  FIG. 15 , 
       FIG. 17 , a partial view of a drive mechanism for pairs of transfer cylinders, 
       FIG. 18 , a schematic front view of the linear guide device of  FIG. 10 , 
       FIG. 19 , a schematic end view of a double printing group with cylinders of differing circumference, 
       FIG. 20 , the coverage of a forme cylinder with four newspaper pages, 
       FIG. 21 , the coverage of a forme cylinder with eight tabloid pages, 
       FIG. 22 , the coverage of a forme cylinder with sixteen vertical pages in book format, and in 
       FIG. 23 , the coverage of a forme cylinder with sixteen horizontal pages in book format. 
   

   DESCRIPTION OF THE PREFERRED EMBODIMENTS 
   Referring initially to  FIG. 1 , there may be seen a first preferred embodiment of a printing group of a printing press in accordance with the present invention. A first printing group  01  of a printing press, in particular a rotary printing press, has a first cylinder  02 , for example a forme cylinder  02 , and an associated second cylinder  03 , for example a transfer cylinder  03 . Their rotating shafts R 02 , R 03  define a plane E in a print-on position AN, as seen in  FIG. 5 . 
   On their circumferences, the forme cylinder  02  and the transfer cylinder  03  each have at least one interference in the circumferential direction on the jacket surface, for example a disruption  04 ,  06  in the jacket surface which is active during roll-off. This disruption  04 ,  06 , which is also shown in  FIG. 5 , can be a joint between leading and trailing ends of one or several dressings, which are arranged on the circumference, for example by use of a magnetic force or by material-to-material contact. However, as represented in what follows in the preferred embodiments, these can also be grooves  04 ,  06 , or slits  04 ,  06 , which receive ends of dressings. The interferences, called grooves  04 ,  06  in what follows, are equivalent with other interruptions  04 ,  06  on the active jacket surface, i.e. the outward pointing face of the cylinders  02 ,  03  provided with dressings. 
   Each of the forme cylinders  02  and transfer cylinders  03  has at least two grooves  04 ,  06 , or interruptions  04 ,  06 . These two grooves  04 ,  06  are respectively arranged one behind the other in the longitudinal direction of the cylinders  02 ,  03 , and are offset in respect to each other in the circumferential direction. 
   If the cylinders  02 ,  03  only have a length L 02 , L 03 , which substantially corresponds to two widths of a newspaper page, only two grooves  04  and  06  are provided, which are offset in respect to each other in the circumferential direction and are arranged one behind the other in the longitudinal direction. 
   The grooves  04 ,  06  are arranged on the two cylinders  02 ,  03  in such a way that, in the course of a rotation of the two cylinders  02 ,  03 , they roll off on respectively one of the grooves  06 ,  04  of the other cylinder  03 ,  04 . The offset of the grooves  04 ,  06  of each cylinder  02 ,  03  in the circumferential direction is preferably approximately 180°. Therefore, after respectively one 180° rotation of the cylinders  02 ,  03 , at least one pair of grooves  04 ,  06  rolls off on each other, while on a longitudinal section “a” of the cylinders  02 ,  03 , as seen in  FIG. 1 , the cylinders  02 ,  03  roll off unimpeded on each other. 
   The transfer cylinder  03  of the first printing group  01  forms a printing position  09 , together with a third cylinder  07 , on a web  08 , for example a web  08  of material to be imprinted. This third cylinder  07  can be embodied as a second transfer cylinder  07 , as shown in  FIG. 1 , or as a counter-pressure cylinder  07 , as shown in  FIG. 2 , for example as a steel cylinder or a satellite cylinder  07 . In the print-on position AN, the rotating shafts R 03  and R 07  of the cylinders  03 ,  07  forming the printing position  09  define a plane D. See, for example,  FIG. 6  or  FIG. 13 . 
   In the embodiment of  FIG. 5 , in the print-on position AN the rotating shafts R 02 , R 03 , R 07  of the three cylinders  02 ,  03 ,  07  working together are substantially located in a common plane E which, in this case, coincides with the plane D, and which planes D and E extend parallel with each other, as seen in  FIGS. 5 ,  12 . If the satellite cylinder  07  has two printing positions on its circumference, a second printing group, not represented, is preferably also arranged in the common plane E. However, it can also define a plane E of its own, which is also different from the plane D associated with it. 
   As represented in the preferred embodiment in  FIG. 1 , the third cylinder  07 , embodied as the second transfer cylinder  07 , works together with a fourth cylinder  11 , in particular a second forme cylinder  11  with an rotating shaft R 11  and constitutes a second printing group  12 . The two separate printing groups  01 ,  12  constitute a combined printing group  13 , a so-called double printing group  13 , which imprints both sides of the web  08  simultaneously. 
   As seen in  FIG. 5 , during printing, i.e. in the print-on position AN, all rotating shafts R 02 , R 03 , R 07 , R 11  of the four cylinders  02 ,  03 ,  07 ,  11  are located in the common plane E or D and extend parallel with each other.  FIGS. 6 and 13  show a corresponding printing group  13 , wherein respective pairs of forme and transfer cylinders  02 ,  03 ,  11 ,  07  form one plane E, and the transfer cylinders  03 ,  07  form the plane D, which differs from the plane E. 
   In the case of the double printing group  13 , shown in  FIG. 1 , the cylinders  07 ,  11  of the second printing group  12  have grooves  04 ,  06  with the properties regarding the number and offset in respect to each other already described above in connection with the first printing group  01 . Now the grooves  04 ,  06  of the four cylinders  02 ,  03 ,  07 ,  11  are preferably arranged in such a way that respectively two grooves  04 ,  06  of two cylinders  02 ,  03 ,  07 ,  11  which work together roll off on each other. 
   In an advantageous embodiment, the forme cylinder  02  and the transfer cylinder  03  each have a length L 02 , L 03 , which corresponds to four or more widths of a printed page, for example a newspaper page, for example 1,100 to 1,800 mm, and in particular to 1,500 to 1,700 mm, and a diameter D 02 , D 03 , for example 130 to 200 mm, and in particular of 145 to 185 mm, whose circumference U substantially corresponds to the length of a newspaper page, “single circumference” in what follows. The device is also advantageous for other circumferences, wherein the ratio between the circumferences D 02 , D 03  and the length L 02 , L 03  of the cylinders  02 ,  03  is less than or equal to  0 ,  16 , in particular less than  0 ,  12 , or even less than or equal to  0 ,  08 . 
   In an advantageous embodiment, each of the two cylinders  02 ,  03  has two grooves  04 ,  06 , each of which extends continuously at least over a length corresponding to two widths of a newspaper page. 
   More than two grooves  04 ,  06  can be arranged per cylinder  02 ,  03 . In this case, respectively two grooves  04 ,  06  arranged next to each other can be arranged aligned, or respectively alternatingly. However, for example with four grooves  04 ,  06 , the two grooves  04 ,  06  adjoining the front ends of the cylinders  02 ,  03  can be arranged in a common alignment, and the two grooves  04 ,  06  located on the “inside” can be arranged in a common alignment, but offset in the circumferential direction in respect to the first mentioned ones, as depicted in  FIG. 4 . 
   If the interruptions  04 ,  06  are actually embodied as grooves  04 ,  06 , or as slits  04 ,  06 , the grooves  04 ,  06  schematically represented in  FIGS. 1 to 4  can be slightly longer than the width, or twice the width of the printed page. Possibly two grooves  04 ,  06  adjoining each other in the longitudinal direction can also slightly overlap in the circumferential direction. This is not shown in detail in  FIGS. 1 to 4 , which are only schematic representations. 
   In view of the excitation, or the damping of oscillations caused by groove beating, it is particularly advantageous if the grooves  04 ,  06  on the respective cylinders  02 ,  03 ,  07 ,  11  are offset by 180° from each other. In this case, the grooves  04 ,  06  between the forme cylinders  02 ,  11  and the transfer cylinders  03 ,  07  of the two printing groups  01 ,  12  roll off simultaneously and in the area of the same section in the longitudinal direction of the cylinders  02 ,  03 ,  07 ,  11 , in one stage of the cycle for example on the same side, for example a side I, as seen in  FIGS. 1 ,  3  and  4  of the double printing group  13 , and in the other phase on a side II or, with more than two grooves  04 ,  06  per cylinder  02 ,  03 ,  07 ,  11 , for example in the area of the center of the cylinders  02 ,  03 ,  07 ,  11 . 
   The excitation of oscillations is considerably reduced by the offset arrangement of the grooves  04 ,  06  and the roll-off of all grooves  04 ,  06  in the described manner, and possibly also by the linear arrangement of the cylinders  02 ,  03 ,  07 ,  11  in one plane E. Because of the synchronous, and possibly symmetrical roll-off on the two printing groups  01 ,  12 , a destructive interference with the excitation occurs which, with the selection of the offset by 180° of the grooves  04 ,  06  on the cylinders  02 ,  03 ,  07 ,  11 , takes place independently of the number of revolutions of the cylinders  02 ,  03 ,  07 ,  11 , or of the frequency. 
   If the interruptions  04 ,  06  are actually embodied as grooves  04 ,  06 , in an advantageous embodiment they are embodied with a gap of only little width, for example less than or equal to 3 mm, in the area of a jacket surface of the forme cylinders  02 ,  11 , or of the transfer cylinders  03 ,  07 , which gap receives ends of one or several dressings, for example one or several rubber blankets on the transfer cylinder  03 ,  07 , or ends of one or several dressings, for example one or several printing plates, on the forme cylinders  02 ,  11 . The dressing on the transfer cylinder  03 ,  07  is preferably embodied as a so-called metallic printing blanket, which has an ink-conducting layer on a metallic base plate. In the case of the transfer cylinders  03 ,  07 , the beveled edges of the dressings are secured by clamping and/or bracing devices, and in the case of forme cylinders  02 ,  11  by clamping devices, in the grooves  04 ,  06 . 
   A single, continuous clamping and/or bracing device can be arranged in each one of the grooves  06  of the transfer cylinder  03  or, in case of grooves extending over several widths of newspaper pages, several clamping and/or bracing devices can be arranged one behind the other in the longitudinal direction. The grooves  04  of the forme cylinder  02 , for example, also have a single, or several clamping devices. 
   A “minigap technology” is preferably employed in the grooves  04  of the forme cylinders  02 ,  11 , as well as in the grooves  06  of the transfer cylinders  03 ,  07 , wherein a leading dressing end is inserted into a groove with an inclined extending suspension edge, the dressing is wound on the cylinders  02 ,  03 ,  07 ,  11 , the trailing end is also pushed into the groove  04 ,  06 , and the ends are clamped, for example by use of a rotatable spindle or a pneumatic device, to prevent them from sliding out. 
   However, it is also possible to arrange a groove  04 ,  06  embodied as a narrow slit  04 ,  06  for the dressing on the forme cylinders  02 ,  11 , as well as for the dressing, embodied as a metallic printing blanket, of the transfer cylinders  03 ,  07 , which receives the ends of the dressings. In this case, the plate or blanket ends are secured in the slit  04 ,  06  by their shaping and/or by the geometry of the slit  04 ,  06 . 
   For example, in an advantageous embodiment as depicted in  FIG. 3 , the transfer cylinders  03 ,  07  have only two dressings, which are offset by 180° from each other in the circumferential direction, each of which dressings has at least a width corresponding to two widths of a newspaper page. In this case, the dressings, or the grooves  04  of the forme cylinders  02 ,  11 , extending complementary thereto must have either, as represented, two continuous grooves  04 , each of the length of two widths of a newspaper page, or grooves  04  which adjoin in pairs and are arranged aligned, each of the length of two widths of a newspaper page. In the first case, in an advantageous embodiment, each interruption  04  of the forme cylinder  02 ,  11  actually embodied as a groove  04  which has two clamping devices, each of a length substantially corresponding to the width of a newspaper page. 
   In an advantageous embodiment, the forme cylinders  02 ,  11  are covered with four flexible dressings, which adjoin each other in the longitudinal direction of the forme cylinders  02 ,  11  and which have a length of slightly greater than the length of a printed image of a newspaper page in the circumferential direction, and in the longitudinal direction have a width of approximately one newspaper page. With the arrangement of continuous grooves  04  and with only one clamping device per groove  04 ,  06 , which has a length of two widths of a newspaper page, it is also possible to apply dressings of a width of two newspaper pages, which dressings are so-called panoramic printing plates. 
   In connection with printing groups for which the need for a setup with panoramic printing plates can be excluded, an arrangement can also be of advantage in which the “outer” dressings, which respectively adjoin the side I and the side II, are aligned with each other, and the “inner” dressings are aligned with each other and are arranged offset by 180° from the first mentioned ones, as seen in  FIG. 4 . This highly symmetrical arrangement makes it additionally possible to minimize, or to prevent, the danger of an oscillation excitation in the plane E, which might result from the non-simultaneous passage of the grooves  04 ,  06  on the sides I and II. The alternating tensing and relaxation of the web  08  occurring alternatingly on the sides I and II, and oscillations of the web  08  caused thereby, can also be avoided by this. 
   In a further development, the above-mentioned arrangement of the interruptions  04 ,  06  on the respective cylinders  02 ,  03 ,  07 ,  11 , as well as between the cylinders  02 ,  03 ,  07 ,  11 , and the possibly linear arrangement of the cylinders  02 ,  03 ,  07 ,  11 , can be applied in particular to cylinders of a length L 02 , L 03  substantially corresponding to six times the width of a newspaper page. However, in this case, it can be advantageous to embody the transfer cylinders  03 ,  07  and/or the forme cylinders  02 ,  11  with a diameter D 02 , D 03  which results in a circumference which substantially corresponds to double the length of a newspaper page. 
   In an advantageous embodiment, for a mechanically simple and rugged embodiment of the double printing group  13 , the forme cylinders  02 ,  11  are arranged fixed with respect to their axes of rotation R 02 , R 11 . For bringing the printing groups  01 ,  12  in and out of contact, the transfer cylinders  03 ,  07  are embodied to be movable by shifting their rotating shafts R 03 , R 07 , and can each be simultaneously moved away from their associated forme cylinders  02 ,  11  and transfer cylinders  03 ,  07  working together with them, or can be placed against them. In this embodiment, only the transfer cylinders  03 ,  07  are moved in the course of normal operation of the printing press, while the forme cylinders  02 ,  11  remain in their fixed and possibly previously adjusted position. However, the forme cylinders  02 ,  11  can also be seated in appropriate devices, for example in eccentric or double eccentric bushings, in linear guide devices or on levers, for adjustment, if necessary. 
   As represented schematically in  FIGS. 5 to 7 , and as depicted in greater detail in  FIGS. 8 to 11 , the transfer cylinders  03 ,  07  can be movable along a linear actuating path  16 , or, as represented schematically in  FIGS. 12 and 13 , and in detail in  FIGS. 14 and 15 , they can be movable along a curved actuating path  17 . The actuating paths  16  and  17 , as well as the transfer cylinders  03 ,  04  in a print-off position AB, are represented in dashed lines in  FIGS. 5 ,  6  and  12 . 
   In a further embodiment, which is not specifically represented, the actuating paths  16 ,  17  are determined by seating the transfer cylinders  03 ,  07  in eccentric bushings, not specifically represented, and in particular in double eccentric bushings. It is possible, by the use of double eccentric bushings, to provide a substantially linear actuating path  16  in the area of the print-on position AN. However, in the area remote from the printing position  09 , a curved actuating path  17  when required, is provided, which curved actuating path  17  allows a more rapid, or greater removal of the transfer cylinders  03 ,  07  from the transfer cylinders  07 ,  03  working together with them, than from the associated forme cylinders  02 ,  11 , or vice versa. The seating on the side I and on the side II of the double printing group  13  is also of advantage for the use of eccentric cams. 
   In the discussion of  FIGS. 5 to 11 , as follows, preferred embodiments of the printing groups  01 ,  12  are represented, wherein at least one of the transfer cylinders  03 ,  07  can be moved along a linear actuating path  16 , as shown in  FIG. 5 : 
   The linear actuating path  16  is accomplished with the aid of linear guide devices, which are not represented in  FIG. 5 , and which are arranged in or on the lateral frame, that is also not represented in  FIG. 5 . Seating in a linear guide device is provided for a rugged and low-oscillation construction, preferably on the side I and the side II of the double printing group  13 . 
   The course of the web  08  through the printing position  09 , which is in the print-on position AN, is represented in  FIG. 5 . The plane E of the double printing group  13 , shown in  FIG. 5 , or of the respective printing group  01 ,  12  shown in  FIG. 6 , and the plane of the web  08  intersect in an advantageous embodiment at an angle α of 70° to 85°. If the transfer cylinders  03 ,  07  have a circumference approximately corresponding to the length of one newspaper page, the angle α is approximately 75° to 80°, preferably approximately 77°, but if the transfer cylinders  03 ,  07  have a circumference approximately corresponding to two newspaper pages, the angle α is approximately 80 to 85°, preferably approximately 83°. For one, this selection of the angle a takes into account the assured and rapid access to the web  08  and/or the moving apart from each other of the transfer cylinders  03 ,  07  over a minimized actuating path  16 , and also minimizes negative effects, such as mackling or smearing, on the result of printing, which are decisively affected by the amount of a partial looping of the web about the transfer cylinder(s)  03 ,  07 . In an optimal arrangement, the required linear actuating path  16  of each transfer cylinder  03 ,  07  is less than or equal to 20 mm for bringing the transfer cylinders  03 ,  07  into and out of contact with each other, but up to 35 mm for affording free access to the web  08  during imprint operations. 
   When arranging the rotating shafts R 02 , R 03 , R 07  of the forme, transfer and counter-pressure cylinders  02 ,  03 ,  07  in the plane E, as seen in  FIG. 5 , the direction of the linear actuating path  16  forms an angle Δ with the plane E, which here coincides with the plane D, which essentially is 90°. The direction of the linear actuating path  16  forms an angle γ with a plane of the incoming or outgoing web  08  in the area of an obtuse angle β between the web  08  and the plane E. In case of a straight course of the web  08 , β=180°−α applies, wherein γ lies around 5 to 20°, in particular around 7 to 13°. In that case, with a linear printing group  01  and straight-running web  08 , the obtuse angle β preferably lies between 95° and 110°. 
   In the case where only one of the forme cylinders and the associated transfer cylinders  02 ,  03 ,  11 ,  07  define the plane E in the contact position, as seen in  FIG. 6 , the angle γ between the actuating path  16  and the plane of the web  08  preferably should be selected to be greater than or equal to 5°, preferably between 5° and 30°, and in particular between 5° and 20°. In particular, for forme cylinders  02 ,  03 ,  07 ,  11  of single circumference, the angle γ is greater than or equal to 10°. However, the angle γ is upwardly limited in such a way that the angle γ between the portion of the plane E pointing in the direction toward the forme cylinders  02 ,  11  and the direction of the contact-release path  16  is at least 90°. The rapid and dependable removal of the transfer cylinders  03 ,  07  simultaneously from the web  08  and the associated forme cylinders  02 ,  11  is assured in this way. 
   The relationships mentioned are to be correspondingly applied to a “non-linear” course of the web  08 , taking into consideration the respective obtuse angle between the web  08  and the plane E. 
   The direction of the actuating path  16 , in the direction toward contact release is selected, regardless of the relative course of the web  08 , in such a way, that an angle φ between the plane E and the actuating path  16  in the direction toward contact release lies by at least 90° and at most 120°, in particular between 90° and 115°. However, the angle φ is again upwardly limited in such a way that the angle Δ is at least 90°. 
   The double printing group  13  can be multiply employed, for example twice, as represented in  FIG. 7 , in a printing unit  19 , for example a so-called H-printing unit  19 , in a common lateral frame  20 . In  FIG. 7 , a separate identification of the respective parts of the lower located double printing group  13 , which parts are identical to those in the upper double printing group  13 , is omitted. With an arrangement of all cylinders  02 ,  03 ,  07 ,  11  whose circumference substantially corresponds to the length of a newspaper page, it is possible to save structural space, i.e. a height “h” of the printing unit  19 . This, of course, also applies to individual printing groups  01 ,  12  for double printing groups  13 , as well as for otherwise configured printing units having several printing groups  01 ,  12 . However, a priority can also be an improved accessibility of the cylinders  02 ,  03 ,  07 ,  11 , for example for changing dressings, for cleaning work and washing, and for maintenance and the like, in place of for accomplishing a savings in height “h”. 
   The print-on, or print-off positions AN, AB have been drawn bold in all drawing figures for the purpose of clarity. In  FIG. 7 , the transfer cylinders  03 ,  07  are indicated in dashed lines in a second possible position along the linear actuating path  16 , wherein here, for example, the upper double printing group  13  is operated in the print-off AB position, shown in solid lines, for example for a printing forme change, and the lower double printing group  13  is operated in the print-on position AN, shown in solid lines, for example for continued printing. 
   In an advantageous embodiment, each one of the printing groups  01 ,  12  has at least one drive motor  14  of its own, which is only indicated in dashed lines in  FIG. 7 , for the rotatory driving of the cylinders  02 ,  03 ,  07 ,  11 . 
   In a schematically represented embodiment, shown at the top in  FIG. 7 , this can be a single drive motor  14  for the respective printing group  01 ,  12  which, in an advantageous embodiment, in this case initially drives the forme cylinders  02 ,  11 , and power is transferred from there via a mechanical drive connection, for example spur wheels, toothed belts, etc., to the transfer cylinders  03 ,  07 . However, for reasons of space and for reasons of the flow of torque or moments, it can also be of advantage to transfer power from the drive motor  14  to the transfer cylinders  03 ,  07 , and from there to the forme cylinders  02 ,  11 . 
   In an alternate embodiment, each printing group  01 ,  12  has one separate drive motor  14  for each cylinder  02 ,  03 ,  07 ,  11 , as shown in  FIG. 7  bottom, which motor  14  is mechanically independent of the remaining drive mechanisms and has a large degree of flexibility in the various operating situations, such as production runs, registration, dressing changes, washing, web draw-in, etc. 
   The type of drive mechanism in  FIG. 7 , in the top and bottom is represented by way of example and can therefore be transferred to every other example. 
   In an advantageous embodiment, driving by use of the drive motor  14  takes place coaxially between the rotating shafts R 02 , R 03 , R 07 , R 11  and the motor shaft, if required with a coupling for compensating for angles and/or offset, which will be explained in greater detail below. However, it can also take place via a pinion, in case the “moving along” of the motor  14 , or a flexible coupling between the drive motor  14  and the cylinders  02 ,  03 ,  07 ,  11 , which are to be moved when required, is to be avoided. 
   A first preferred embodiment for providing the linear actuating path  16  by the use of a linear guide device is represented in  FIGS. 8 and 9 . 
   The journals  23  of at least one of the transfer cylinders  03 ,  07  are rotatably seated in radial bearings  27  which are, for example, positioned in bearing housings  24  that are embodied as carriages  24 . In  FIGS. 8 and 9 , only the arrangement in the area of the front faces of the cylinders  02 ,  03 ,  07 ,  11  is represented. The bearing housings  24 , or carriages  24 , are movable in linear guide devices  26 , which are connected with the lateral frame  20 . 
   For the linear arrangement of the double printing group  13 , the linear guide devices are oriented in an advantageous embodiment almost perpendicularly in respect to the plane E, or D, i.e. Δ=90°, see  FIG. 5 . In a preferred embodiment, two linear guide devices  26 , which extend parallel with each other, are provided for guiding each bearing housing  24 , or carriage  24 . The linear guide devices  26  of two adjacent transfer cylinders  03 ,  07  also preferably extend parallel with each other. 
   In an embodiment which is not specifically represented, the linear guide devices  26  can be arranged directly on the walls of the lateral frame  20 , and in particular on walls of openings in the lateral frame  20  which extend almost perpendicularly to the front faces of the cylinders  02 ,  03 ,  07 ,  11 . 
   In the preferred embodiment in accordance with  FIGS. 8 and 9 , the lateral frame  20  has an insert  28 , for example a so-called bell  28 , in an opening. The linear guide devices  26  are arranged on, or in this bell  28 . 
   In an advantageous embodiment, the bell  28  has an area which projects in the direction toward the cylinders  02 ,  03 ,  07 ,  11  out of the aligned lateral frame  20 . The linear guide devices  26  are arranged in, or on this area of the bell  28 . 
   The distance between the two oppositely-located lateral frames  20 , only one of which is represented is, as a rule, set in accordance with the widest unit, for example the wider inking system  21  and, as a rule, leads to a correspondingly longer journal of the cylinders  02 ,  03 ,  07 ,  11 . With the above mentioned arrangement, it is advantageous that it is possible to keep the journals of the cylinders  02 ,  03 ,  07 ,  11  as short as possible. 
   In a further development, the bell  28  has a hollow chamber  29 , which is, at least partially arranged at the height of the alignment of the lateral frame  20 . As schematically represented in  FIG. 9 , the rotatory drive mechanisms of the cylinders  02 ,  03 ,  07 ,  11  are connected with the journals of the cylinders  02 ,  03 ,  07 ,  11  in this hollow chamber  29 . 
   With paired driving of the cylinders  02 ,  03 ,  07 ,  11 , see for example  FIG. 11 , drive connections, such as cooperating drive wheels  30 , for example, can be particularly advantageously housed in this hollow chamber  29 . In an advantageous embodiment shown in  FIG. 9 , with the drive motor  14  fixed in place on the frame, a coupling  61 , which compensates for angles and offset, can be arranged on the transfer cylinders  03 ,  07  between the transfer cylinders  03 ,  07  and the drive motor  14  in order to even out the movements into and out of contact of the transfer cylinders  03 ,  07 . Coupling  61  can be designed to be double-jointed or, in an advantageous embodiment, as an all-metal coupling  61  with two multi-disk packets, which are rotationally rigid, but axially deformable. The all-metal coupling  61  can even out the offset and the positional change caused by this at the same time. It is important that the rotatory movement is transmitted without play. 
   In case of the coaxial driving of the forme cylinders  02 ,  11  in particular, the drive mechanism of the forme cylinders  02 ,  11  has a coupling  62  between the journal  51  and the drive motor  14 , which takes up at least an axial relative movement between the cylinders  02 ,  11  and the drive motor  14  for setting the lateral register. In order to also take up production tolerances and possibly required movements of the forme cylinders  02 ,  11  for adjusting purposes, the coupling  62  is designed as a coupling  62  which evens out at least small angles and offsets. It is also designed, in an advantageous embodiment, as an all-metal coupling  62  with two multi-disk packets, which are rotationally rigid, but which are axially deformable. The linear movement is taken up by the multi-disk packets, which are positively connected in the axial direction with the journal  51 , or with a shaft of the drive motor  14 . 
   If lubrication, for example a lubricant or oil chamber, is required, the hollow chamber  29  can be bordered in a simple manner by the use of a cover  31 , shown in dashed lines, without it increasing the width of the press, or protruding from the frame  20 . In that case the hollow chamber  29  can be designed to be encapsulated. 
   Thus, the arrangement of the bell  28  shortens the lengths of the journals, which has a reduction of oscillations as a result, and makes possible a simple and variable construction, which is suitable for the most varied driving configurations and, along with a large degree of structural uniformity, allows the changing between configurations, with or without drive connections, with or without lubricants, with or without additional couplings. 
   In the embodiment schematically represented in  FIG. 8 , driving of the respective bearing housings  24 , or carriages  24  in the linear guide devices  26  is performed, for example, by the use of linear drives  32 , for example by respective threaded drives  32 , for example a threaded spindle driven by an electric motor, not represented. In this case, the rotary position of the electric motor can be controllable. For limiting the travel in the print-on position AN, a stop which is fixed in place on the frame but which is adjustable, can be provided for the bearing housing  24 . 
   However, driving of the bearing housing  24  can also take place by use of a lever mechanism. The latter can also be driven by an electric motor, or by a cylinder which can be charged with a pressure medium. If the lever mechanism is driven by means of one or by several cylinders, which can be charged with a pressure medium, the arrangement of a synchronizing spindle which synchronizes the actuating movements on both sides I and II is advantageous. 
   The attachment of the transfer cylinders  03 ,  07  to be moved to the lateral frame  20 , or to the bell  28 , is provided as follows in the preferred embodiment in accordance with  FIG. 9 : the bell  28  has support walls  33  on both sides of the carriage  24  to be guided, which receive one of the two corresponding parts of the linear guide device  26 . This part can possibly also already be a component of the support wall  33 , or can be worked into it. The other corresponding part of the linear guide  26  is arranged on the carriage  24 , or has been worked into it, or has it. In an advantageous embodiment, the carriage  24  is guided by two such linear guide devices  26 , which are arranged on opposite sides of the carriage  24 . 
   The parts of the guide devices  26  arranged on the support walls  33 , or without a bell  28  directly on the lateral frame  20  in this way engage or partially enclose the carriage  24  arranged between them. The active surface of the parts of the linear guide device  26  connected with the lateral frame  20 , or the bell  28 , point into the half space facing the journal  23 . For reducing the friction between the parts of the guide devices  26  which work together, bearings  34  are arranged in an advantageous embodiment, for example, linear bearings  34 , and in particular rolling bearing cages  34 , which make possible a linear movement, are provided. 
   In the ideal case, the respective two parts of the two guide devices  26  permit a movement of the carriage  24  only in one degree of freedom in the form of a linear movement. For this purpose, the entire arrangement is clamped together essentially free of play in a direction extending perpendicularly in respect to the rotating shafts R 03 , R 07  and perpendicularly in respect to the movement direction of the carriage  24 . For example, the respective part of the guide device close to the forme cylinder, shown in  FIG. 9  with larger dimensions has a clamping device, which is not specifically represented. 
   The carriage  24  seated in the described manner has the radial bearing  27 , which receives the journal  23 , for example on a radially inward directed side of a recess facing the transfer cylinders  03 ,  07 . 
   In a second preferred embodiment, as shown in  FIGS. 10 and 11 , which is advantageous in particular with respect to structural space and to a rugged construction, the active surfaces of the parts of the linear guide device  26 , which are connected with the lateral frame  20 , or with the bell  28 , point into the half space facing away from the journal  23 . For this purpose, the parts of the linear guide device are arranged on a support  36  connected with the bell  28  or with the lateral frame  20 . The carriage  24  has the parts of the linear guide device  26  which are assigned to it in a recess facing the lateral frame  20 , or the bell  28 . These parts can be arranged in the recess of the component, or can be already worked into an inward directed surface of the recess of the carriage  24 . As in the preferred embodiment in accordance with  FIG. 9 , the carriage  24  has a recess pointing toward the transfer cylinders  03 ,  07 , in which the radial bearing  27  for receiving the journal  23  is arranged. In the present preferred embodiment, a bearing face for rolling elements of the radial bearing  27  embodied as a rolling bearing  27  has already been worked into an inward directed face of the recess. 
   Thus, the parts of the guide device  26  arranged on the carriage  24  comprise the support  36 , or the parts of the guide devices  26  arranged on the support  36 , on the lateral frame  20 , or on the bell  28 . 
   In an advantageous embodiment, at least one of the supports  36  assigned to the transfer cylinders  03 ,  06  has an elongated hole, which is not visible in the drawing figures, and which is matched to the movement direction of the carriage  24 , for passing the journal  36  through, which is to be linearly moved. This elongated hole is aligned, at least in part, with an elongated hole, also not visible, which is arranged in the bell  28 , or in the associated lateral frame  20 . The journal  23 , or a shaft connected with the journal  23 , passes through these elongated holes, and is in a driven connection with a drive wheel  30 , as seen in  FIG. 9  or with the drive motor  14  for the rotatory driving of the transfer cylinders  03 ,  07 . 
   Driving of the carriage  24  can take place in a manner already described in connection with the first preferred embodiment.  FIG. 11  shows the embodiment by use of an actuating device embodied as a lever mechanism. The carriage  24  is hingedly connected, via a connector  37 , with a lever  38 , which lever  38  can be pivoted around an axis which extends substantially parallel with the rotating shafts R 03 , R 07  of the transfer cylinders  03 ,  07 . In the preferred embodiment, the connectors  37  of the two adjoining carriages  24  of the cooperating transfer cylinders  03 ,  07  are hingedly connected with the lever  38 , here embodied as a three-armed lever  38 , for the purpose of synchronizing the actuating movements of both transfer cylinders  03 ,  07 . Driving of the lever  38  is performed by the use of at least one actuating drive  39 , for example by use of one, or by use of two, as in  FIG. 10  cylinders  39 , which can be charged with a pressure medium. In the course of actuating the actuating drive  39  and pivoting of the lever  38  in one direction, here in a clockwise direction, the rotating shafts of the two transfer cylinders  03 ,  07  are moved into the plane E, wherein they are simultaneously placed against each other and against the respective forme cylinders  02 ,  11 . By pivoting in the other direction, the two transfer cylinders  03 ,  07  are brought out of contact with each other and with the associated forme cylinders  02 ,  11 . 
   In particular in the case wherein the actuating drive  39  is embodied as a cylinder  39  which can be charged with a pressure medium, the arrangement of stops  41  is advantageous, against which stops  41  the respective carriage  24  is placed in the print-on position AN. These stops  41  have been configured to be adjustable in order to make possible the setting of the end position of the transfer cylinders  03 ,  07 , in which the rotating shafts R 03 , R 07  come to lie in the plane E. The system becomes very rigid if the carriage  24  is pushed with a large force against the stop  41 , or respectively the two stops  41  shown in  FIG. 10 . 
   If, as in the present case, the carriages  24  of the two adjoining transfer cylinders  03 ,  07  are actuated by a common actuating device, it is advantageous, in a further development of the preferred embodiments, if the actuating device between the respective carriages  24  and the first common part of the actuating device are embodied to be resilient, at least within narrow limits. To this end, each connector  37  has a multi-disk packet  42 , for example a plate spring packet  42 , in the manner of a shock-absorbing leg. While in the print-on position AN, the spring packet  42  of the one transfer cylinder  03 ,  07  is compressed, the spring packet  42  assigned to the other transfer cylinder  07 ,  03  is under tensile strain. 
   For synchronizing the linear movement of both sides of the transfer cylinders  03 ,  07 , a shaft  43 , for example a synchronized shaft  43 , is connected with the actuating device arranged on both sides of the transfer cylinders  03 ,  07 . For this purpose, the shaft  43  in the example is connected, fixed against relative rotation, with the two levers  38  which are respectively arranged on a lateral frame  20  on the sides I and II. In this case, this represents the pivot axis for the levers  38  at the same time. 
   An adjusting device can be provided in the preferred embodiments in  FIGS. 8 to 11 , which adjusting device makes possible the basic setting of the spacings between the rotating shafts R 02 , R 03 , R 07 , R 11 , in particular during assembly and/or if the configurations and/or conditions have changed. For this purpose, individual ones of the cylinders  02 ,  03 ,  07 ,  11 , for example the forme cylinder  02 ,  11 , can be seated in an eccentric bushing, if desired. At least one of the transfer cylinders  03 ,  07  can also be adjustable in a radial direction for this adjustment. For example, the parts of the linear guide device  26  assigned to the lateral frame  20 , or to the bell  28 , or those of the support  38 , can be connected with the lateral frame  20 , or the bell  28 , through elongated holes which are sufficient for adjusting purposes. An eccentric position, which can be fixed in place, of the radial bearings  27  in the carriage  24  is also possible. 
   Preferred embodiments of the printing group  01 ,  12  are explained in what follows and as depicted in  FIGS. 12 to 18 , wherein at least one of the transfer cylinders  03 ,  07  can be moved along a curved actuating path  17 , as shown in  FIG. 12 . 
   One of the transfer cylinders  03  is seated, pivotable around a pivot axis S, in the lever  18 , as schematically represented in  FIG. 12 . In this case, the pivot axis S is located in the plane E, for example. The lever  18  here is of a length, between the seating of the rotating shafts R 03 , R 07  of the transfer cylinders  03 ,  07 , which is greater that the distance of the rotating shafts R 03 , R 07  of the transfer cylinders  03 ,  07  from the rotating shafts R 02 , R 11  of the associated forme cylinders  02 ,  11  in the print-on position AN. With this, the simultaneous taking out of contact of transfer cylinders  03 ,  07  working together and the associated forme cylinders  02 ,  11  takes place, and vice versa for putting them into contact. 
   However, in particular as described in greater detail below, the pivot axis S can also be eccentrically arranged with respect to the rotational shafts R 02 , R 11  of the associated cylinders  02 ,  11  in a different way, for example at a distance from the plane E. Seating in a lever  18  preferably takes place on side I and on side II of the double printing group  13 . 
   The course of the web  08  through the printing position  09  located in the print-on position AN is also represented in  FIGS. 12 and 13 . The plane E of the double printing group  13  shown in  FIG. 12 , or of the respective printing groups  01 ,  12  shown in  FIG. 13 , and the plane of the web  08  here also intersect in an advantageous embodiment at an angle a of 70° to 85°. If the transfer cylinders  03 ,  07  have circumferences corresponding to the length of one newspaper page, the angle a is, for example, approximately 75° to 80°, preferably approximately 77°, but if the transfer cylinders  03 ,  07  have circumferences approximately corresponding to two newspaper pages, the angle a is, for example, 80 to 85°, preferably approximately 83°. Here, too, the selection of the angle a contributes to assured and rapid separation of the web  08  and/or the movement out of contact of the transfer cylinder  03 ,  07  from each other with a minimized actuating path  16 . Furthermore, it minimizes negative effects on the result of printing, such as mackling or smearing, which is decisively affected by the amount of a partial looping of the transfer cylinder(s)  03 ,  07  by the web  08 . 
   The double printing group  13 , depicted here in a linear embodiment can be multiply employed, for example twice, as represented in  FIG. 14 , in a printing unit  19 , for example a so-called H-printing unit  19 , in a common lateral frame  20 . In  FIG. 14 , a separate identification of the respective parts of the lower located double printing group  13 , which are identical to the upper double printing group  13 , has been omitted. Regarding the advantages of this arrangement, reference is made to the remarks previously set forth in connection with  FIG. 7 . 
     FIG. 14  indicates in dashed lines, which are however drawn bold for more clarity the transfer cylinders  03 ,  07  in a second possible position along the actuating path  17 , wherein here the upper printing group  13 , for example, is operated in the print-off position AB, for example for changing the printing formes, and the lower printing group  13  is operated in the print-on position AN, for example for continued production printing. 
   In an advantageous embodiment, every one of the printing groups  01 ,  12  here also has at least one drive motor  14  of its own for rotatory driving of the cylinders  02 ,  03 ,  07 ,  11 . 
   In an embodiment which is schematically represented at the bottom of  FIG. 14 , this motor can be a single drive motor  14  for each of the respective printing group  01 ,  02 , which, in an advantageous embodiment, in this case first drives the forme cylinders  02 ,  11 , and from there the power is transferred via a mechanical drive connection, for example spur wheels, toothed belts, etc. to the transfer cylinders  03 ,  07 . 
   However, as in the previously described embodiment, in one embodiment with its own drive motor  14  for each cylinder  02 ,  03 ,  07 ,  11 , and which motor  14  is mechanically independent of the remaining drive mechanisms, the printing group  01 ,  12  has a large degree of flexibility. This is shown in  FIG. 14  for an upper double printing group  13 . 
   The type of drive mechanism in  FIG. 14 , either top or bottom is represented by way of example and can therefore be transferred to the respectively other printing groups  01 ,  12 , or to the other double printing group  13 . 
   In an advantageous embodiment, the driving by operation of the drive motor  14  takes place coaxially between the rotating shafts R 02 , R 03 , R 07 , R 11  and the motor shaft, if required via the couplings  61 ,  62  for compensating for angles and/or offset, as was already explained in greater detail previously. It can also take place via a pinion in case the “moving along” of the motor  14  or of a flexible coupling between the drive motor and the cylinders  02 ,  03 ,  07 ,  11 , which are to be moved when required, is to be avoided. 
   A preferred embodiment for providing the curved actuating path  17  by use of the lever  18  is represented in  FIGS. 15 and 16 . 
     FIG. 15  shows a lateral view, in which only one of two journals  23  which are arranged on the fronts of the transfer cylinders  03 ,  07 , shown in dashed lines is visible. 
   The lever  18  is seated, pivotable around the pivot axis S, which is preferably fixed in place, but which can be adjustable, if required with respect to the lateral frame  20 . In the embodiment represented, in a print-on position AN, the rotating shafts R 02 , R 03 , R 07 , R 11  of the cylinders  02 ,  03 ,  07 ,  11  shown in dashed lines, are again located in a plane E, which, in this case, coincides with the plane D between the cylinders  03 ,  07  which form printing positions  09 . 
   The pivot axis S of the lever  18  is arranged eccentrically with respect to the rotating shafts R 02 , R 11  of the forme cylinders  02 ,  11  and is located outside the plane E or D. Pivoting of the lever  18  around the pivot axis S by use of a drive mechanism  44 , for example by use of a pressure medium cylinder  44 , via an actuating assembly  44 , for example a single- or multi-part connector  46 , for example a lever or toggle lever mechanism  46 , causes the transfer cylinders  03 ,  07  to be simultaneously brought out of and into contact with the assigned forme cylinders  02 ,  11 , or with the respectively other transfer cylinders  07 ,  03 . The toggle lever mechanism  46  is hingedly connected with the lever  18  and with a pivot fixed on the frame. The advantageously double-acting pressure medium cylinder acts, for example, on a movable joint of the toggle lever mechanism. The rotating shafts R 02 , R 11  of the forme cylinders  02 ,  11  remain at rest for this process. So that the movement of the two levers  18  for the transfer cylinder  03 ,  07 , which are arranged on the front face, takes place synchronously, the actuating assembly  44  can have a shaft  47 , for example a synchronous shaft  47 , which connects the two actuating assemblies  44 , or can be connected with such a one. To assure the desired, for example linear, arrangement of the cylinders  02 ,  03 ,  07 ,  11 , a stop  48 , which is preferably embodied to be adjustable, is provided for each lever  18 . 
   The driving and actuating assemblies  44 ,  46  are structured and arranged in such a way that the move out of contact of the transfer cylinders  03 ,  07  takes respectively place in the direction of the obtuse angle β for a straight web run 180°−α between the web  08  and the plane D or E. 
   The eccentricity e−S of the pivot axis S, with respect to the rotating shafts R 02 , R 11  of the forme cylinders  02 ,  11  lies between 7 and 15 mm, and in particular approximately is 9 to 12 mm. In the contact position of the transfer cylinders  03 ,  07 , i.e. the rotating shafts R 03 , R 07  lie in the above mentioned plane D, the eccentricity ε−S is oriented in such a way, that an angle ε−S between the plane D of the cylinders  03 ,  07  forming the printing position  09  and the connecting plane V of the pivot axis S and the rotating shafts R 02 , R 11  lies between 25° and 65°, advantageously between 32° and 55°, and in particular lies between 38° and 52°, wherein the pivot axis S is preferably in the area of an obtuse angle β between the plane D and the incoming or outgoing web  08 , and is farther apart from the printing position  09  than the rotating shaft R 02 , R 11  of the associated forme cylinders  02 ,  11 . In case of a vertical and, except for a possible offset caused by the partial looping around, straight path of the web, as well as an angle of 77° between the plane D and the plane of the web  08 , the eccentrics ε−S have an angle of, for example 120 to 520, advantageously 19° to 42°, and in particular between 25° to 39°, with respect to a horizontal line H. 
   In the ideal case, i.e. with never-changing conditions and with a tolerance-free production, the arrangement as described so far meets the demands made on putting the printing groups  01 ,  12 , or the double printing group  13 , into and out of contact without further actuating mechanisms. 
   However, for compensating for possibly occurring production tolerances, and/or for being able to perform a base positioning of the dressings, materials to be imprinted, etc., further actuating options for adjusting purposes are provided. 
   The rotating shafts R 02 , R 11  on the forme cylinders  02 ,  11  are seated adjustably, for example also eccentrically in respect to their fastening on the lateral frame  20 , in this case with respect to a bore  49 . In the present case, a journal  51  of the forme cylinders  02 ,  11  is arranged in an eccentric bearing  52 , or in an eccentric bearing bushing  52 , which is pivotably seated in the bore  49 . 
   A pivot axis S 51  of the forme cylinders  02 ,  11  is eccentrically arranged by an eccentricity of 5 to 15 mm, in particular an eccentricity of approximately 7 to 12 mm, in respect to the rotating shafts R 02 , R 11  of the forme cylinders  02 ,  11 , and is located outside of the plane E. 
   In the contact position between the forme cylinders and the associated transfer cylinders  02 ,  03 ,  07 ,  11 , in which the rotating shafts R 0 , R 03 , or R 11 , R 07  are located in the plane E, the eccentricity e−S 51  is oriented in such a way that an angle ε−S 51  between the plane E of the pair of cylinders  02 ,  03 , or  02 ,  11 , lies between 25° and 65°, advantageously between 32° and 55°, and in particular lies between 38° and 52°. The pivot axis S 5  is preferably located in a half plane which is farther removed from the rotating shafts R 03 , R 07  of the associated transfer cylinders  03 ,  07  than the rotating shafts R 02 , R 11  of the associated forme cylinders  02 ,  11 . 
   In the preferred embodiment, the pivot axis S 51  for the eccentric seating of the forme cylinder  02 ,  11  coincides with the pivot axis S of the lever  18 . 
   The coincidence of the pivot axes S and S 51  is not absolutely necessary, but is practical. In particular, the pivot axis S, which is stationary with respect to the lateral frame  20  and is not affected by the pivoting of the forme cylinders  02 ,  11 , permits a simple and exact adjustment. In principle, the lever  18  could also be arranged on an eccentric flange of the bearing bushing  52  which receives the journals  51 , but during turning, this would result in a simultaneous displacement of the distances between the forme cylinders  02 ,  11  and the transfer cylinders  03 ,  07 , as well as between the transfer cylinders  03 ,  07 . 
   In an advantageous embodiment, the two pivot axes S 51  (and/or S) and S 23  of the pairs of forme and transfer cylinders  02 ,  03 ,  11 ,  07  are arranged on two different sides of the plane E in the print-on position AN. 
   The position of the forme cylinders  02 ,  11  can be adjusted by the provision of a second adjusting assembly  53  in accordance with the desired position in respect to the plane E, or in regard to the required distance from the transfer cylinders  03 ,  07  for the print-on position AN, by a slight twisting of the eccentric bearing  52 . After it has been adjusted, this position is set, for example, by an assembly which is not represented. 
   For placing the printing gap at the printing position  09  into the print-on position AN, at least the journals  23  of one of the two transfer cylinders  03 ,  07 , in this case the transfer cylinder  07 , can be adjusted. For example, they are also seated in assigned levers  18 . The eccentricity e−s 23  of a pivot axis S 23 , with respect to the rotating shafts R 03 , R 07  of the transfer cylinder lies between 1 and 4 mm, and in particular at 2 mm. In the contact position of the cylinders  03 ,  07  forming the printing position  09 , i.e. when the rotating shafts R 03 , R 07  are located in the plane D, the eccentricity e−S 23  is oriented in such a way that an angle ε−S 23  between the plane D and the connecting plane of the pivot axis S 23  and the rotating shaft R 07  (R 03 ) lies between 70° and 110°, advantageously between 80° and 100°, and in particular lies between 85° and 95°. In the example, the angle ε−S 23  should be approximately 90°. 
   An embodiment in accordance with  FIG. 15  is represented in  FIG. 16  in a section taken along the plane E of  FIG. 15 . Each of the journals  51  of the forme cylinders  02 ,  07  is rotatably seated in bearings  54 , for example rolling bearings  54 . In order to be able to provide a setting, or a correction of the lateral register, this bearing  54 , or an additional axial bearing, not represented, makes possible the movement of the forme cylinders  02 ,  11 , or their journals  51 , in the axial direction. The bearings  54  are arranged in eccentric bearings  52 , or in eccentric bearing bushings  52 , which, in turn, are arranged pivotably in the bore  49  in the lateral frame  20 . Besides the eccentric bearing bushing  52  and the bearing  54 , further bearing rings and friction bearings or rolling bearings can be arranged between the bore  49  and the journals  51 . The lever  18  is seated on a part of the bearing bushing  52  projecting from the lateral frame  20  in the direction toward the forme cylinders  02 ,  11 , and is pivotably seated in relation to it. On its end remote from the pivot axis S, the lever  18  receives the journal  23  of the transfer cylinders  03 ,  07 , which is arranged, rotatable in a bearing  56 , and the latter, in the case of the transfer cylinder  07 , is arranged, pivotable around the pivot axis S- 23 , in an eccentric bearing  57 , or in an eccentric bearing bushing  57 . If required, a bearing bushing which is pivotable in such a way can also be arranged for both transfer cylinders  03 ,  07 . 
   The lateral frame  20  advantageously has recesses  58 , at least on the drive side of the printing press, in which the journals  23  of the transfer cylinders  03 ,  07  can be pivoted. The actuating assemblies  46 ,  53 , or the drive assemblies  44 , are not represented in  FIG. 16 . 
   The rotatory drive of the cylinders  02 ,  03 ,  07 ,  11  is provided by respectively individual drive motors  14 , which are mechanically independent from the drive mechanisms of the respectively other cylinders  02 ,  03 ,  07 ,  11  and which are preferably arranged fixed in place on the frame. The latter has the advantage that the drive motors  14  need not be moved. 
   For compensating for the pivot movement of the transfer cylinders  03 ,  07 , the coupling  61 , which compensates for the angles and the offset, is arranged between the transfer cylinders and the drive motor  14 , and is embodied as a double joint  61  or, in an advantageous embodiment, can be embodied as an all-metal coupling  61 . The all-metal coupling simultaneously compensates for the offset and for the position change caused by this, wherein the rotatory movement is transmitted free of play. 
   Between the journal  51  and the drive motor  14 , the drive mechanism of the forme cylinders  02 ,  11  also has a coupling  62 , which absorbs at least an axial relative movement between the cylinders  02 ,  11  and the drive motor  14  and which, to also be able to absorb production tolerances and possibly required adjusting movements of the forme cylinders  02 ,  11  for adjusting purposes, can be embodied to compensate for at least minute angles and offsets. In an advantageous embodiment, it is also embodied as an all-metal coupling  62 , which absorbs the axial movement by the provision of multi-disk packets, which are positively connected in the axial direction with the journal  51 , or with a shaft of the drive motor  14 . 
   In a variation which is represented in  FIGS. 17 and 18 , a drive in pairs can also take place from the drive motor  14 , and if required, via further gear elements, not represented, via a pinion  59  to a drive wheel  61  of the transfer cylinders  03 ,  07 , for example if it is intended to achieve a special flow of moments or torque. 
   In that case, a rotating shaft R 59  of the pinion  59  is then arranged fixed on the frame in such a way that a straight line G 1  determined by the rotating shaft R 59  of the pinion  59  and the pivot axis S of the lever  18 , together with a plane E 18 , determined by the pivot axis S of the lever  18  and the rotating shafts R 03 , R 07  of the transfer cylinders  03 ,  07 , defines an opening angle η in the range between +20° to −20°. 
   In a further development, a straight line G 2  determined by the rotating shafts R 02 , R 11  of the forme cylinders  02 ,  11  and the rotating shaft R 59  of the pinion  59 , together with the straight line G 1  determined by the rotating shaft R 59  of the pinion  59  and the pivot axis S of the lever  18  defines an opening angle λ in the range between 160° and 200°. 
   The above mentioned embodiments for driving, as well as for moving, the transfer cylinders  03 ,  07 , as well as the embodiment of the lever  18 , or of the linear guide device  26  can be applied in the same way to printing groups in which the cylinders  02 ,  03 ,  07 ,  11  do not all have the same circumference, or diameter, as seen in  FIG. 19 . For example, the forme cylinder(s)  02 ,  11  can have a circumference U which has one printed page, for example the longitudinal page of a newspaper, a “single circumference” in what follows. The cooperating transfer cylinders  03 ,  07  have, for example, a circumference or diameter, which corresponds to a whole number multiple greater than 1 of that of the forme cylinders  02 ,  11 , i.e. it has a circumference, for example, of two or even three printed pages of newspaper format, or is correspondingly matched to other formats. 
   If the printing position is constituted by a transfer cylinder  03 ,  07  and a counter-pressure cylinder  07 ,  03 , embodied as a satellite cylinder  07 ,  03 , the forme and the transfer cylinders  02 ,  11 ,  03 ,  07  can also have a single circumference, and the assigned counter-pressure cylinder  07 ,  03  can be designed larger by a multiple. 
   By the use of the mentioned embodiments, an increased stiffness of the printing groups is also achieved, in an advantageous manner. This has a particular advantage in connection with cylinders  02 ,  03 ,  07 ,  11  which have a length that corresponds to at least four, or even six, vertical printed pages, in particular newspaper pages. 
   By utilization of the measures explained in the preferred embodiments, it is possible to construct, or to operate a printing group  01 ,  12  with long, slim cylinders  02 ,  03 ,  07 ,  11 , which have the above mentioned ratio of diameter to length of approximately 0.008 to 0.16, in a rugged and low-oscillation manner, while at the same time requiring little outlay regarding space, operation and frame construction. This applies, in particular, to forme cylinders  02 ,  11  of “single circumference”, i.e. with one newspaper page at the circumference, but of double width, i.e. with four newspaper pages on the length of the cylinders  02 ,  03 ,  07 ,  11 . 
   In the preferred embodiments mentioned, at least one of the transfer cylinders  03 ,  07  can be advantageously brought out of contact sufficiently far so that, during printing operations, the drawn-in web  08  can be moved through the printing position  09  without touching it. 
   As described, in all of the preferred embodiments, the cylinders  02 ,  03 ,  07 ,  11  can be driven either in pairs or individually by respectively one drive motor  14  of their own. For special requirements, for example for only one-sided imprinter operations, or merely for the requirement for changing the relative angle of rotation position of the forme cylinders  02 ,  11  in relation to each other, driving is also possible wherein one of the forme cylinders  02 ,  11  of a printing group  01 ,  12  has its own drive motor  14 , and the remaining cylinders  02 ,  03 ,  07 ,  11  of the printing group  01 ,  12  have a common drive motor  14 . A configuration of four or five cylinders  02 ,  03 ,  07 ,  11  with three drive motors  14  can be advantageous, in the case of a double printing group  13 , for example, in which, respectively, one drive motor  14  is provided for each of the forme cylinders  02 ,  11  and a common one is provided for the transfer cylinders  03 ,  07 . In the case of a five-cylinder or of a satellite printing unit, for example, one drive motor  14  is provided for each pair of forme and transfer cylinders  02 ,  03 ,  07 ,  11 , and the satellite cylinder has its own drive motor  14 . 
   As represented by way of example in  FIGS. 11 and 17 , the four cylinders  02 ,  03 ,  07 ,  11  are each rotatingly driven in pairs by a drive motor  14  either from the forme cylinders  02 ,  11  or from the transfer cylinders  03 ,  07 , depending on the requirements. The drive wheels  30 , each constituting a gear, between the forme cylinders  02 ,  11  and the respectively assigned transfer cylinders  03 ,  07 , each constitute a driven connection together with the drive motor  14 . The two pairs of drive wheels  30  are preferably arranged in such a way, in relation to each other, that they are out of engagement, which for example takes place by an axially offset arrangement, i.e. on two driving levels. 
   Here, an embodiment of the drive wheels with spur toothing of each of the drive wheels  30 , which work together between the forme and transfer cylinders  02 ,  03 ,  07 ,  11 , can be advantageous for making possible a relative axial movement of one of the two cylinders  02 ,  03 ,  07 ,  11  without changing the relative position of the two cylinders in the circumferential direction. The latter also applies to a possibly arranged pinion between the drive motor  14  and the drive wheel of the forme cylinders  02 ,  11 , if the pair of cylinders is not driven coaxially from the forme cylinders  02 ,  11 . To this end, it is possible to embody a pair of members, which work together in the drive connection between the drive motor  14  and the forme cylinders  02 ,  11 , with spur toothing and which are axially movable with respect to each other in order to assure the axial movement of the forme cylinders  01 ,  11  without their being twisted at the same time. The drive situations respectively represented in  FIGS. 9 and 11  could be alternatingly transferred to the two represented embodiments for providing the linear movement. 
   In all of the above-mentioned cases, in an advantageous embodiment, the drive motors  14  are arranged fixed in place on the frame. However if a drive motor  14  driving the cylinders  02 ,  03 ,  07 ,  11  should be arranged fixed in place on a cylinder, in a variation, during the actuating movement and/or during the adjustment of the cylinders  02 ,  03 ,  07 ,  11  the drive motor  14  can be taken along on an appropriate, or on the same guide device or on an appropriate lever, for example on an outside of the lateral frame  20 . 
   With the embodiment with a drive motor  14  fixed in place on the frame in particular, which drive motor  14  drives the transfer cylinders  03 ,  07  of the cylinders  02 ,  03 ,  07 ,  11  driven individually or in pairs, it is advantageous to arrange the angle and offset compensating coupling  61  in the way as shown, by way of example, in  FIGS. 9 and 16 . As represented, by way of example, in  FIGS. 9 ,  11  and  16 , with coaxially driven forme cylinders  02 ,  11 , the drive mechanism has the described coupling  62  between the journal  51  and the drive motor  14 . 
   The drive motor  14  is advantageously embodied either as an electric motor, in particular as an asynchronous motor, as a synchronous motor, or as a dc motor. 
   In an advantageous further development, a gear  63  is arranged between each one of the drive motors  14  and the cylinders  02 ,  03 ,  07 ,  11  to be driven. This gear  63  can be an attached gear  63  connected with the drive motor  14 , for example a planetary gear  63 . However, it can also be a reduction gear  63  embodied in another way, for example with a pinion or belt and a drive wheel. 
   The individual encapsulation of each gear  63  is advantageous, for example as an individually encapsulated, attached gear  63 . The lubricant chambers created in this way are spatially tightly limited, prevent the soiling of adjacent press elements and also contribute to an increase of the quality of the printed product. In the case where the bell  28 , shown in  FIG. 11  is used, the gears can be arranged between the forme and transfer cylinders  02 ,  03 ,  07 ,  11  in the hollow chamber  29 , and can be encapsulated against the outside as lubricant chambers. 
   Regardless of the embodiment as individually driven or as driven in pairs cylinders  02 ,  03 ,  07 ,  11 , it is advantageous to embody each of the drive units individually encapsulated, i.e. each with its own lubricant chamber. The above mentioned individual encapsulation extends, for example, around the paired drive mechanism of two cylinders  02 ,  03 ,  07 ,  11 , or, in particular in the case of the above described bell  28 , around both pairs. A bell  28  can also be embodied for a pair of two cylinders  02 ,  03 ,  07 ,  11 . The latter is advantageous, for example, in accordance with producing modules. 
   In a further development of the preferred embodiments, it is advantageous if the inking system  21  assigned to the respective forme cylinders  02 ,  11  and, if provided, the associated dampening unit  22 , is rotationally driven by a drive motor which is independent of the drive mechanism of the printing group cylinders. The inking system  21  and the possibly provided dampening system  22  can each have their own drive motors. In the case of an anilox inking system  21 , the screen roller, and in connection with a roller inking system  21 , for example, the friction cylinder(s), can be rotationally driven individually or in groups. Also, the friction cylinder(s) of a dampening system  22  can also be rotationally driven individually or in groups. 
   In contrast to printing presses with double circumference and single width, the embodiment of the cylinders  02 ,  03 ,  07 ,  11  with double width and—at least the forme cylinders  02 ,  11 —with a “single circumference” makes a considerably greater product variability possible. Although the maximum number of possible printed pages remains the same, in the case of single-width printing groups  01 ,  12  with double circumference they are in two different “books”, or “booklets” in the assembly operation. In the present case, with double-width printing groups  01 ,  12  of single circumference, the double-width webs  08  are longitudinally cut after having been imprinted. In order to achieve a maximum booklet width, one or several partial webs are conducted one above the other in the so-called folding superstructure, or turning deck, and are folded to form a booklet on a former without assembly operations. If such booklet thicknesses are not required, some partial webs can be guided on top of each other, but others can be conducted together to a second hopper and/or folding apparatus. However, two products of identical thickness can also be conducted without being transferred to two folding apparatus. A variable thickness of two different products is thus provided. If, in case of a double folding apparatus or of two folding apparatus in which at least two product delivery devices are provided, it is possible, depending on the arrangement, to conduct the two booklets, or products, next to or above each other to one side of the printing press, or to two different sides. 
   The double-width printing press of single circumference has a great variability in particular when staggering the possible page numbers of the product, the co-called “page jump”. While the thickness per booklet, or layer in the printing press of double circumference and of single width can only be varied in steps of four printed pages during assembly operation, i.e. with maximum product thickness, the described double-width printing press of single circumference allows a “page jump” of two pages, for example when printing newspapers. The product thickness, and in particular the “distribution” of the printed pages to different books of the total product or the products, is considerably more flexible. 
   After the web  08  has been longitudinally cut, the partial web is conducted either to a former which is different in respect to the corresponding partial web, or is turned to be aligned with the last mentioned one. This means that, in the second case, the partial web is brought into the correct longitudinal, or cutting register prior to, during or after turning, but before being brought together with the “straight ahead webs”. In an advantageous embodiment, this is taken into account as a function of the circumferential direction of grooves  04 ,  06 , which are offset in respect to each other, of a cylinder  02 ,  03 ,  07 ,  11  by the appropriate design of the turning deck, for example preset distances of the bars, or of the path sections. Fine adjustment, or correction, is performed by use of the actuating paths of the cutting register control device of the affected partial web and/or partial web strand, in order to place partial webs on two different running levels on top of each other with the correct registration, when required. 
   Now, the forme cylinders  02 ,  11  can be provided, in the circumferential direction, with one vertical printed page in broadsheet format and in the longitudinal direction with at least four, as seen in  FIG. 20 . Alternatively, these forme cylinders  02 ,  11  can also be selectively provided with two pages in the circumferential direction and, in the longitudinal direction, with at least four horizontal printed pages in tabloid format, as seen in  FIG. 21 , or with two pages in the circumferential direction and, in the longitudinal direction, with at least eight vertical printed pages in book format, as seen in  FIG. 22 , or with four pages in the circumferential direction and in the longitudinal direction with at least four horizontal printed pages in book format, as seen in  FIG. 23  by the use of respectively one flexible printing plate which can be arranged in the circumferential direction of the forme cylinder  03 , and at least one flexible printing plate arranged in its longitudinal direction. 
   Thus, depending on the placement on the forme cylinders  02 ,  11  with horizontal tabloid pages, or with vertical newspaper pages, and in particular with broadsheet pages, or with horizontal or vertical book pages, it is possible by use of the double-width printing press and at least the forme cylinders  02 ,  11  of single circumference, to produce different products, depending on the width of the web  08  used. 
   With the double printing group  13 , the production, in one stage, of two vertical printed pages arranged on the forme cylinder, a “two page jump” with variable products in broadsheet format, is possible. 
   With a width of the web  08  corresponding to four, or to three, or to two vertical printed pages, or of one printed page in broadsheet format, the production of a product in broadsheet format consisting of a layer in the above sequence with eight, or six, or four, or two printed pages is possible. 
   With a web width corresponding to four vertical printed pages in broadsheet format, the double printing group can be used for producing respectively two products in broadsheet format, consisting of one layer with four printed pages in the one product and four printed pages in the other product, or with two printed pages in the one product and with six printed pages in the other product. With a web width corresponding to three vertical printed pages, it is suitable for producing respectively two products in broadsheet format consisting of one layer with four printed pages in the one product and with two printed pages in the other product. 
   Furthermore, with a web width corresponding to four vertical printed pages in broadsheet format, the double printing groups  13  can be used for the production of a product in broadsheet format consisting of two layers with four printed pages in the one layer and with four printed pages in the other layer, or with two printed pages in the one layer and with six printed pages in the other layer. With a web width corresponding to three vertical printed pages, the double printing group  13  can be used for producing a product in broadsheet format consisting of two layers with four printed papers in the one layer and two printed pages in the other layer. 
   In the case of printed pages in tabloid format, the double printing group  13  can be used for producing in one stage printed pages arranged horizontally on the forme cylinder  02 ,  11  with variable products, a “four page jump” in tabloid format. Accordingly, with a web width corresponding to four, or to three, or to two horizontal printed pages, or to one horizontal page, the double printing group  13  can be used for producing a product in tabloid form consisting of one layer in the above sequence with sixteen, or twelve, or eight, or four printed pages. 
   With a web width corresponding to four horizontal printed pages in tabloid form, the double printing group  13  can be used for producing two products in tabloid format, each consisting of one layer with eight printed pages on the one product and with eight printed pages on the other product, or with four printed pages on the one product and with twelve printed pages on the other product. With a web width corresponding to three horizontal printed pages, the double printing group  13  can be used for producing two products, each consisting of one layer with four printed pages on the one product and with eight printed pages in the other product. 
   With products in book format, the double printing group  13  can be used for producing, in one stage, eight printing pages with variable, “eight page jump” products arranged vertically on the printing cylinders  02 ,  11 . 
   With a web width corresponding to eight, or to six, or to four, or to two vertical printed pages, the production of a product in book format consisting of a layer in the above sequence with thirty-two, or twenty-four, or sixteen, or eight printed pages, is possible. 
   With a web width corresponding to eight vertical printed pages in book format, the double printing group  13  can be used for producing respectively two products in book format, each consisting of one layer, with sixteen printed pages on the one product and with sixteen printed pages on the other product, or with twenty-four printed pages on the one product and with eight printed pages on the other product. With a web width corresponding to six vertical printed pages in book format, the double printing group  13  can be used for producing respectively two products in book format, each consisting of one layer, with sixteen printed pages on the one product and with eight printed pages on the other product. 
   The double printing group  13  is furthermore usable for producing, in one stage, eight printed pages arranged vertically with variable products, “eight page jump” on the forme cylinder  03 . 
   With a web width corresponding to four, or to three, or to two horizontal printed products, or to one horizontal printed page in book format, the double printing group  13  can be used for producing a product in book format consisting of a layer in the above sequence with thirty-two, or with twenty-four, or with sixteen, or with eight printed pages. 
   With a web width corresponding to four horizontal printed pages in book format, the double printing group  13  can be used for producing respectively two products in book format, each consisting of a layer, with sixteen printed pages on the one product and with sixteen printed pages on the other product, or with twenty-four printed pages on the one product and with eight printed pages on the other product. With a web width corresponding to three horizontal printed pages in book format, the double printing group  13  can be used for producing respectively two products in book format, each consisting of a layer, with sixteen printed pages on the one product and with eight printed pages on the other product. 
   If the two partial web strands are longitudinally folded on different hoppers and thereafter conducted to a common folding apparatus, what was said above should be applied to the distribution of the products to different folded booklets, or layers, of the described variable number of pages. 
   While preferred embodiments of printing groups of a printing press in accordance with the present invention have been set forth fully and completely hereinabove, it will be apparent to one of skill in the art that various changes in for example the type of web being printed, the specific structure of the blankets or dressings secured to the cylinders, the specific cylinder clamping devices and the like could be made without departing from the true spirit and scope of the present invention which is accordingly to be limited only by the following claims.