Abstract:
An adjustable bearing arrangement is used for the remote controlled adjustment of an inking roller or a dampening roller with respect to a second, contacting roller. The journal of the roller to be adjusted is secured to an adjusting element. A pre-settable adjusting force is transferred from one roller to the other. In the adjustment position, the receiving element or elements are locked so that it is temporarily impossible for the now adjusted roller to move either in, or opposite to the direction of adjustment.

Description:
FIELD OF THE INVENTION 
     The present invention is directed to a method and to devices for adjusting a roller of a printing press. The roller is placed against another roller and a movable detent is used to hold it in place. 
     BACKGROUND OF THE INVENTION 
     A device for adjusting a roller of an inking or dampening unit of a printing press, with respect to an adjoining roller, has become known from EP 0 826 501 A1. 
     DE 199 19 733 A1 discloses a device for setting the contact pressure between two rollers of a printing press. A spring force is applied to a first roller and it is fixed in place on a frame by an arresting device. 
     DE 197 19 305 A1 discloses a bearing arrangement for a roller of an inking or dampening unit. A roller holder can be positioned by use of a spring, and can be fixed in place by being clamped. 
     DE 42 32 163 C1 describes a device for maintaining a set positioning pressure of an inking roller by use of a temperature-dependent actuator. 
     EP 0 807 520 A2 shows a switching arrangement for printing cylinders with a double-acting work cylinder. 
     EP 0 653 302 A1 and DE 42 11 379 A1 disclose devices for adjusting a roller, wherein a work cylinder presses a roller against a mechanically displaceable detent. 
     SUMMARY OF THE INVENTION 
     The object of the present invention is directed to creating a method and devices for adjusting a roller of a printing press. 
     In accordance with the present invention, this object is attained by placing the roller against at least one other roller through the use of a positioning force. A detent, which limits the positioning path of the roller, is placed against the roller or a receiver of the roller. A motor can be used for displacing the detent. The motor or other operating device can apply two different forces acting on the roller, a first for production and a second for positioning. 
     The advantages which can be gained by the present invention consist, in particular, in the compact construction of the device. In this case, the diameter of each device is equal to or preferably less than the diameter of the cylindrical shell of the roller of the inking or dampening unit. For this reason, no hindrance between these devices will be a problem when several such devices are used next to each other, for example in the situation of two adjoining inking rollers with a riding roller placed thereupon as the third roller—wherein all rollers are adjustable. 
     A preselectable positioning pressure of the inking or dampening unit roller is made dependably possible by utilization of a preselectable force that is generated, for example, by an operating device for linear movement—such as, for example, a motor for linear movements, i.e. a cylinder with a pistol; piezo-operating devices, electrochemical operating devices, etc.—gaseous or liquid media, or electrical current. This adjustment is reproducible, i.e. flattening of a rubber covering of a dampening or inking roller thus forming a roller strip. This means that the so-called “inking or dampening roller strips” can be kept at a constant width by the flattening of a rubber covering of a dampening or inking roller. 
     It is not possible to affect a so-called “channel beat” when the inking or dampening roller rolls over a gap on other rollers. The fixing pressure P F , and therefore the fixing force F F  with which the roller journal of the inking or dampening roller is held in a fixed manner, can only be set to be larger by a multiple of the positioning pressure P A , and therefore also a multiple of the positioning force F A , with which the covering of the roller is pressed against the shell of an immediately adjoining cylinder or roller. 
     A rapid pre-adjustment of the rollers, also for compensating for changes in diameter in the course of production, and/or in case of changes in the Shore hardness of the rollers, is possible. Because of this the set-up times become negligibly small. It is also possible to adjust these rollers remotely, for example centrally from a press control console. 
     The receiver of the roller or rollers can be maintained “locked in” during the entire running time. A high degree of quiet running of the rollers is assured by this, even when the printing press is running, because the “swing-up” of vibrations at the roller journals/-shafts is not possible because of the application of a clamping effect or a blocking effect. By acting on the distributing cylinder with a fixing pressure P F , or a fixing force F F , which is/are greater by a multiple than the positioning pressure P A , or the positioning force F A , a detent, which follows the performed positioning, is pressed against a counter-bearing fixed in place on the frame so strongly that, with the prevailing operational state of the roller positioning, an unintentional movement of the positioned roller in, or opposite to the roller positioning direction E is impossible. 
    
    
     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 side elevation view, in the positioning position, with the clamping opened (principal representation), on the ends of two adjoining rollers, whose first roller can be moved to position the second roller by use of the device in accordance with a first preferred embodiment of the present invention, 
     FIG. 2, a second preferred embodiment of the device in accordance with FIG. 1, and in 
     FIG. 3, a pneumatic switching diagram for controlling the device in FIGS.  1  and  2 . 
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     A first roller or cylinder  01  of an inking or print unit of a printing press is seated pivotably or fixedly in lateral frames as seen in FIGS. 1 and 2. 
     Against this first roller  01 , a second roller  02  having a shell  05  of a flexible, such as a rubber-elastic or elastomeric plastic material, for example rubber or other rubber-like material, can be placed by use of a movable, for example a shell-shaped journal receiver  03  or a shaft receiver which will be called “receiver” for short in what follows. 
     The shiftable roller  02  is rotatably seated at both ends on respective bearing shafts  06  by friction or rolling bearings. Each bearing shaft  06  is fastened, fixed against relative rotation, on a journal receiver  03 , for example by use of a screw or bolt  04 . This is accomplished by turning the screw or bolt  04  through a bore in the journal receiver  03  into a threaded bore in the journal  06 . Instead of seating or supporting the shiftable roller  02  on shafts  06 , it is of course also possible to provide the seating for roller  02  by the use of journals  06  that are attached by material-to-material contact to the roller  02 . However, it would then be necessary to arrange bearings on the receiver  03 . 
     The bearing journals  06  of the roller  02  are fastened in the shell-shaped journal receivers  03  which are assigned to each. 
     The journal receiver  03  is fastened on a set plate  09 , for example is welded to it. The set plate  09  has a plurality of guide bores  11 . In addition, a plate drive mechanism  24  or operating device is provided on set plate  09 , which drive mechanism  24  is fastened to set plate  09  by a housing  05 . 
     The plate drive mechanism  24  or operating device can be provided as a motor for rotary movements—such as an electric, pneumatic or hydraulic motor, for example—, or also as a motor for linear movements—such as a work cylinder with a piston, a linear motor, a d.c. magnet, a piezo-operating device, or as an electrochemical operating device, for example—. 
     In this connections, it is important that torque, power or output of the operating device  24  can be adjusted. 
     In the first preferred embodiment the drive mechanism  24  is designed as a motor for linear movement. A double-acting work cylinder  27  is used for this, on which a gaseous or a liquid medium, for example air or oil, can act. The housing  05  of the drive mechanism  24  or operating device, for example a work cylinder  27 , is fastened on a top surface  20  of the set plate  09  with its piston rod side  50  pointing downward. 
     A piston rod  29  of a piston  28  of the work cylinder  27  projects downward through a bore  10  of the set plate  09 . Its free end  15  is rigidly or flexibly fastened on a horizontal leg  25 , or base plate  25  of a support elbow  14 . 
     A vertical leg  16  of the support elbow  14  can be adjusted up and down in the vertical direction and can be fixed in place on the inside of a machine frame  08  of a print unit or ink unit. 
     The above described device, called “device for adjustment  26 ” as a whole, can also be arranged inside an opening or bore in the lateral frame  08  and can be supported thereon. 
     An eccentric bushing  23 , which is seated in the machine frame  08  so it can be rotated and fixed in place and has an eccentricity “e”, is used for the vertical adjustment of the adjustment device  26 . The eccentric bushing  23  has a hexagonal adjustment head  22  seated on the exterior, by use of which, a rotating movement can be introduced into the eccentric bushing  23  by utilization of a wrench. 
     A device  17  for arresting of the eccentric bushing  23  is furthermore provided. It can consist, for example, of a ratchet screw  18  with a smooth shaft  30  and a threaded part  19 . The threaded part  19  is in engagement with an interior screw thread  21  of a bore of the eccentric device  23 . The ratchet screw  18  can be tightened so securely that the set position of the vertical leg  16 , and therefore the position of the adjustment device  26  can no longer be changed. The vertical or leg  16  has been threaded on the shaft  30  by its bore which is matched to the diameter of the shaft  30 . It is possible to provide a ratchet screw  76  for additional securement, which ratchet screw  76  is screwed through a slit in the machine frame  08  into a second, lower threaded bore in the vertical or fastening leg  16  that is resting against the lateral frame  08 , as seen in FIGS. 1 and 2. It is possible to securely press the leg  16  against the inner surface of the machine frame  08 . 
     A plurality of vertically oriented guide rods  12  are fastened, for example by being welded, to a top side  42  of the horizontal leg or base plate  25 . The guide rods  12  have the job of making possible, in cooperation with tightly matched guide bores  11  on the set plate  09  movement of the set plate  09  vertically up or down along the guide rods  12  and in this way to achieve a change in a spacing distance  35  between the base plate  25  and the set plate  09 . 
     An upper end of a rod  33 , which rod  33  is oriented downwardly and at right angles to the set plate  09  and which has an exterior screw thread  44 , is welded to the underside of the set plate  09 . Lower, free end  45  of rod  33  extends freely downward, for example by 20 mm, through a bore  40  in the horizontal leg or base plate  25  of the support elbow  14 . 
     A detent  32 , for example in the shape of a disk, has been threaded on the free end  45  of the rod  33 . The distance of this detent  32  along the rod  33  can be adjusted in relation to the underside  31  of the base plate  25  along the rod  33  because rod  33  is, for example, a threaded rod. This can take place, as represented in the preferred embodiments, for example, by providing the detent  32  as a driveable adjusting nut  32 , which can be turned in a clockwise or in a counterclockwise direction on the screw thread  44  of the free end  45  of the rod  33 . 
     Instead of moving the detent  32  along the free end  45  of rod  33 , the detent  32  can also be fastened, fixed against relative rotation, on the free end  45  of the rod  33 , and the rod  33  can be arranged so that it can be moved back and forth and can be fixed in place. For example, this could take place in such a way that the rod  33  is provided with an exterior screw thread  44 , which is in engagement with a screw thread in a bore in the set plate  09 . An end of the rod  33 , which extends at the top above the set plate  09  can be connected with a drive mechanism which can be changed from running toward the right to running toward the left, for example an electric motor or a pneumatic motor, for example a step motor. The use of a servo valve would also be conceivable. 
     The detent  32  is driven by being structured as a disk-shaped detent  32 , as seen in FIG. 1, which can be moved along the length of the free end  45  of the threaded rod  33  via a threaded connection. 
     To this end, the detent  32  itself is provided, for example, with a first gear rim  36  or with a gear wheel  36 . The teeth of the gear rim, or the gear wheel  36  are in engagement with teeth of a driving gear wheel  37  which, the same as the detent  32 , is arranged underneath the horizontal leg or base plate  25 . The width of a tooth face of the driving gear wheel  37  is a multiple of the width of the tooth faces of the teeth of the gear rim  36 . 
     The detent  32 , which is embodied as a hub with the gear rim  36 , or as a part of the gear wheel  36 , can be moved along a predefined adjustment length of the threaded rod  33  without the engagement of the teeth of the gear wheel  36  and the driving gear wheel  37  being lost. 
     The driving gear wheel  37  is connected, fixed against relative rotation, with a detent drive mechanism  39  or operating device, whose direction of rotation can be reversed, for example a motor for rotary movements such as an electric, step, hydraulic, or pneumatic motor via the driveshaft  38  of the drive mechanism or operating device  39 . 
     Depending on its configuration, the drive mechanism or operating device  39  is fastened, for example, on the top  42  of the base plate  25 —i.e. in the space between the set plate  09  and the base plate  25 —, or on an underside  31  of the base plate  25 . The driveshaft  38  with the driving gear wheel  39  projects downward through a bore in the base plate  25  when the drive mechanism or operating device  39  is fastened on the top  42  of the base plate  25 . 
     In the preferred embodiment in accordance with FIG. 1, the detent  32 —in this case structured as a hub of the gear wheel  36 , can be rotated by the driving gear wheel  37 . Depending on the direction of rotation of the gear wheel  36 , and therefore of the detent  32 , detent  32  moves along the screw thread  44  of the rod  33  toward or away from the underside of the base plate  25 . Detent  32  can be stopped and fixed in place on the rod  33  at any distance from the underside  31 , but can also be stopped when it is touching the underside  31  of the horizontal leg or base plate  25 . 
     Depending on the preferred arrangement, the detent  32  can be supported either on the base plate  25 , or alternatively on the set plate  09 . 
     An essentially step-free pressing—as a function of a pressure force F A  introduced into the set plate or receiver  09 —of two immediately adjoining rollers  01  and  02  against each other is possible by utilizing the method and the devices in accordance with FIGS. 1 and 2. In this case, the movable or shiftable roller  02 , which is to be placed against the first or fixed roller  01 , and therefore also the set plate or receiver  09 —travels at least a positioning length to a final placement of the shiftable roller  02 . An indentation depth  07  in the, for example, highly elastic, or rubber-elastic or elastomeric shell  13  of one of the two rollers  01 ,  02 , or the width of the so-called roller strip defined by the deformations of the rollers  01 ,  02  placed against each other, is a measure of the pressure, which is a function of the pressure force F A . At least one of the two rollers  01 ,  02  must have a rubber-elastic or highly elastic or elastomeric cover or shell  13 . 
     To adjust the positioning pressure between the two rollers  01 ,  02 , at least one of the two rollers  01 ,  02  must be arranged so it can be placed against, or moved away from the other roller  02 ,  01 , i.e. it must be able to perform a lift or displacement distance  95  which is greater than the maximally attainable depth  07  of the indentation into the shell  13  of the opposing one of rollers  01 ,  02 . With rollers  02  and  01  pressed against each other, the shell  13  of one or both of them is compressed by the amount r b −r a  (ΓB−ΓA), which amount equals the indentation depth  07 , and results in the partially indented or compressed shell  96 . 
     The positioning of the shiftable roller  02  takes place through its two bearing shafts  06 , only one of which is represented. However, an over mounted seating would also be possible, so that there would only be one bearing shaft, or bearing journal  06 , per roller  02 . 
     For this reason one device  26  for adjusting an inking or dampening unit roller  01 ,  02  per bearing shaft  06 , each with one journal receiver  03 , and each with an available lift  95  and a presettable positioning force F A  and fixing force F F , is advantageous. 
     The limit of the lift  95  of the roller  02  to be adjusted can be set in a step-free manner. This takes place by the change of position of the detent  32  on the rod  33  in the direction of the longitudinal axis. Expressed differently, the position of the detent  32  of the set plate  09  in relation to the base plate  25 , which is fixed on the frame  08 , can be adjusted and set. 
     Before the roller  02  can be placed against the roller  01  with a preselected positioning pressure P A , or positioning force F A , the detent  32 , which may be configured as an adjusting nut, must be placed a sufficiently large distance  43  away from a stop face  31  fixed on the frame; in this case at a distance  43  from the underside  31  of the base plate  25 . In this context see the gear wheel  36  and the detent  32  shown in dashed lines in FIG.  1 . To do this, the gear wheel  36  with the detent  32  is rotatingly driven by the drive mechanism  39 ,  37  in such a way that it will have been moved along the screw thread  44  of the rod  33  from the stop face  31  to a preselectable distance  43 , which, in this case, would correspond to the maximally achievable lift  95 . 
     In the course of the above described process, or after its termination, the drive mechanism  24  now moves the set plate  09  with the journal receiver  03 , at a preset positioning force F A , away from the base plate  25 , which base plate  25  is fixed in place in the machine frame  08  and is directly or indirectly supported in the machine frame  08 . The shiftable roller  02  with its, for example, rubber-elastic shell  13  also follows this movement in the direction toward the roller  01 . The shiftable roller  02  with the shell  13  is moved, resting against the shell of the roller  01 , with a preset positioning force F A  until it is at equilibrium with the reaction force with its positioning being determined as a function of the positioning force F A . 
     Thereafter, the gear wheel  36  is driven and the detent  32  is moved in the opposite direction of rotation until, at the end, it comes into contact by means of a torque, or force, which can be preset by means of the drive mechanism  39 , and is slightly tightened. The drive mechanism  39  is immediately stopped and the positioning pressure P A , or the positioning force F A , is increased by a multiple of F A , for example four times F A  by operation of the drive mechanism  24 , and in this way a preset fixing force F F , or fixing pressure P F , is achieved. The detent  32  is pressed, or pulled, even more strongly against the stop face  31  by the increased fixing force F F , because the drive mechanism  24  acts in a manner in which the set plate  09  and the base plate  25  are moved away from each other. In this operational position, a change of the shaft distances at the rollers  01  and  02  in the direction toward the roller  01  is practically no longer possible. Thus, the ability of the receiver  03  to move is blocked. 
     In the course of a new setting of the positioning force F A , or when moving the roller  02  away from the roller  01 , the positioning pressure/force P A /F A  is set to zero. Thereafter, or simultaneously, the detent  32  is brought into a preselectable distance  45  from the stop face  31  by operation of the gear wheel  36 , which is now moved backwards by the drive mechanism  39  and is stopped; the positioning pressure/force P A /F A , or the fixing pressure/force F P /F F , are reversed in their direction. Through this step, the detent  32  achieves, in the end, a sufficient distance  43  from the stop face  31 , and the roller  02  is moved away from the roller  01 . 
     Another adjustment possibility would be a “distance-dependent” positioning. For this, the detent  32  is initially brought to a preselected distance  43  in respect to the stop face  31 . 
     Thereafter, the set plate  09  with the threaded rod  33 , the detent  32 , and the gear wheel  36  are moved by operation of the drive mechanism  24  at a preset force, for example at a fixing pressure/force F P /F F  ratio, away from the base plate  25  fixed on the frame  08  until, in the end, the detent  32  comes into contact with the stop face  31 . This fixing pressure/force F P /F F  is applied during the entire operating time. If the roller  02  is to be moved away, the direction of the fixing pressure, or of the fixing force, is reversed and the set plate  09  is pulled in the direction toward the base plate  25 . 
     However, a version is also possible, in accordance with which the detent  32  is fastened in a movable and arrestable manner on a part—for example on the guide rod  12 —of the base plate, and namely between the set plate  09  and the base plate  25 , or on a free end of the guide rod  12  passed through the guide bore  11 . 
     While the position of the detent  32  can be adjusted by the detent drive mechanism  39  or operating device, the plate drive mechanism  24  or operating device is provided for moving the set plate  09 . In the preferred embodiment, the plate drive mechanism  24  is embodied, for example, as a double-acting pneumatic or hydraulic cylinder  24  or servo cylinder  24  with a piston chamber connector  24 ( 4 ) and with a piston rod chamber connector  24 ( 2 ). 
     The piston rod chamber connector  24 ( 2 ) is connected by a pneumatic, or hydraulic line  47  with a first branch connector  51 ( 2 ) of a first pneumatic, or hydraulic distributor  51 , as seen in FIG. 3. A second branch connector  51 ( 3 ) is either connected with a piston rod chamber connector of a further servo cylinder, or it is closed. 
     A feed connector  51 ( 1 ) of the first distributor  51  is connected by a pneumatic, or hydraulic line  34  with a connector  48 ( 4 ) of a first 5/2-way directional control valve  48 , which is used as the “pressure” or “positioning” valve. A connector  48 ( 5 ) of the directional control valve  48  is connected via a pneumatic, or a hydraulic intermediate line  60  with a first exhaust line  65  via a connector  57 . 
     The piston chamber connector  24 ( 4 ) of the cylinder  27  of the plate drive mechanism  24  is connected by a pneumatic, or hydraulic line  62  with a first branch connector  49 ( 2 ) of a second pneumatic, or hydraulic distributor  49 . A second branch connector  49 ( 3 ) is either connected with a piston chamber connector of a further servo cylinder, or it is closed. 
     A feed connector  49 ( 1 ) of the second distributor  49  is connected with a connector  48 ( 2 ) of the 5/2-way directional control valve  48  by a pneumatic, or hydraulic line  46 . A connector  48 ( 1 ) of the 5/2-way directional control valve  48  is connected by a pneumatic, or hydraulic line  70  via a connector  58  of a second pneumatic, or hydraulic pressure feed line  64 , such as a pipeline or hose. 
     A first, admission connector  48 ( 3 ) is connected by a pneumatic, or hydraulic line  75 , a pipeline or hose via a connector  59  with a second exhaust line  66 , a pipeline or hose. 
     An electro-pneumatic, or electro-hydraulic pressure control valve  78 , called an “E/P pressure control valve” for short in what follows, is provided for supplying the pneumatic or hydraulic cylinders  27  with compressed air, or a pressure medium, for generating the positioning pressure P A . In accordance with an analog electrical reference variable, which can be remotely adjusted, this E/P pressure control valve  78  selects a pressure P A , which for example is proportional to the reference variable. 
     The integrated electronic device of the E/P pressure control valve  78  performs a comparison between the set positioning pressure reference variable and the actual positioning pressure P A  in the work line  73  (actual pressure value), which is detected by a piezo-resistive pressure sensor  86 . 
     A regulator  87  generates a manipulated variable, with which a 3/3-way directional control valve  90  is controlled via a clocked U/I converter  88  and a proportional magnet  89 , so that the preset “positioning pressure” P A  is available at the connector  90 (A) of the 3/3-way directional control valve. The work line  73  which is a pipeline or hose, is connected with its first end to the connector  90 (A) of the directional control valve  90 . 
     A second end of the work line  73 , which is a pipeline or hose, is connected to a connector  55 ( 4 ) of a second 5/2-way directional control valve  55 . 
     From a fluid pressure source  79 , as seen in FIG. 3, and via an input  92 ( 1 ) of a distributor  92 , a gaseous or liquid fluid such as air or hydraulic fluid charged with an operating positioning pressure P B , which can be the fixing pressure P F  at the same time, for example 6 to 12 bar, reaches a connector  90 (P 1 ) of the 3/3-way directional control valve  90  of the electro-pneumatic or hydraulic pressure control valve  78  through a first outlet  92 ( 3 ) of the distributor  92 . A second outlet  92 ( 2 ) of the distributor  92  is connected via a work line  72 , which is a pipeline or hose, with a connector  55 ( 2 ) of the second 5/2-way directional control valve  55 , having two flow-through through positions connectors, two switching positions, actuation by a proportional magnet and restoring spring and lock-in position. 
     A connector  55 ( 1 ) of the second 5/2-way directional control valve  55  is connected, via an intermediate line  84 , to the pressure feed line  64 . The connectors  55 ( 5 ) and  55 ( 1 ) of the directional control valve  55  are closed by closures  69  and  71 . 
     In the first switching position, the “fixing position”, represented in FIG. 3, of the second directional control valve  55  a higher pressure, the “fixing pressure” P F , for example the positioning operating pressure of 10 bar, is present at the connector  48 ( 1 ). In the second switching position, the “positioning position”, of the second directional control valve  55 , the “positioning pressure P a ”, is present at the connector  48 ( 1 ). As a rule, this is lower than the “fixing pressure P F ”. The “positioning pressure P a ” can be regulated and can be kept constant at, for example, 0.1 to 8.0 bar, by the pressure control valve  78 . 
     In a first position, the “fixing position” of the 5/2-way directional control valve  55 , a flow connection is made between the connectors  55 ( 2 ) and  55 ( 1 ). 
     Thus, the higher “fixing pressure P F ” now prevails in the feed line  64 . 
     In a second position, the “positioning position” of the second 5/2-way directional control valve  55 , a flow connection is provided between the connectors  55 ( 4 ) and the connector  55 ( 1 ). Thus, the lower “positioning pressure P a ” now prevails in the feed line  64 . 
     The directional control valve  48  also has two positions. A second position, the so-called “positioning position”, and the first position, the so-called “moved-away position”, as represented in FIG.  3 . 
     The connectors  48 ( 4 ) and  48 ( 1 ) of the directional control valve  48  are switched to flow-through in the “positioning position”; the connectors  48 ( 2 ) and  48 ( 3 ) are also so switched. In that case, the piston rod chamber of the servo cylinder  24  is then charged, depending on the switching position of the directional control valve  55 , either with the lower positioning pressure P A , or with the higher fixing pressure P F , over the path  24 ( 2 ),  47 ,  52 ( 2 ),  51 ( 1 ),  34 ,  48 ( 4 ),  48 ( 1 ) and the feed line  64 . 
     In this case, the piston chamber of the servo cylinder  24  is vented via  24 ( 4 ),  46 ,  49 ( 2 ),  49 ( 1 ),  62 ,  48 ( 2 ),  48 ( 3 ) and the exhaust line  66 . 
     In the “positioning position”, it is achieved that via the set plate  09 , the shiftable roller  02  is pressed against the fixed (a second roller  01  with a pressure P A —for example 2 bar—, which can be preselected and kept constant. In the course of this, a flattening, or measurable width, or indentation depth  07 , of the cover, or in the cover of the elastomeric shell  13  of the cylinder  02  is achieved. This can be changed, i.e. can be set, as a function of the selected positioning pressure P A . 
     In the “moved-away position” the roller  02  is moved away from the roller  01 . In this case, the second directional control valve  55  has been switched in such a way—flow-through between the connectors  55 ( 2 ) and  55 ( 10 —that the high operating pressure P B , which can be equal to the fixing pressure P F , is present in the feed line  64 . 
     The directional control valve  48  is in the “moved-away position”, as represented in FIG.  3 . The connectors  48 ( 2 ) and  48 ( 1 ) on the one hand, and the connectors  48 ( 4 ) and  48 ( 6 ) on the other hand, have been switched to flow-through. It follows from this, that the full pressure P F , or P B , prevails in the piston chamber of the double acting work cylinder  27 , and the set plate  09  with the cylinder  02  fastened thereon is moved away from the cylinder  01  for a predetermined distance. Venting is performed via the connectors  48 ( 4 ) and  48 ( 5 ) over the line  60  and the first exhaust line  65 . At the end of this process, the shiftable cylinder  02  is in the “rollers off position”. 
     All drive mechanisms and operating devices, such as the above described drive mechanisms  24 ,  39  and also the to be depicted drive mechanism  94 , can be controlled from a central machine control console via a central electronic control device  52 , for example, a computer  52 . as described in FIG.  3 . Moreover, the reference variables for the presettable pressures P A  and P F  can also be set. The switching of the directional control valves  48 ,  55  is performed following the input of the command “position” in the correct sequence from the “position pressure P A ” to “fixing pressure P F ”. For this purpose, the electromagnets of the directional control valves  48 ,  55  are connected via the connectors  52 ( 68 ) and  52 ( 67 ) and via electrical control lines  67 , or  68 . The actual value output  81  is connected via an electrical connecting line  53  and a connector  52 ( 81 ) with the control device  52 , and the reference variable input  82  is connected via an electrical connecting line  54  and a connector ( 52 / 82 ) with the control device. The voltage supply  56  of the control unit  52  takes place via its connector  52 ( 56 ). A sufficient number of displays of the set reference pressure and of the actual pressure are provided at the machine control console. 
     Prior to the automatic application of the fixing pressure P F , the detent drive mechanism  39  is charged in such a way that the detent  32  rests against its associated stop face  31 , or  42 , or  20 , and that it switches off when a preselected torque or motor current, for example, has been reached. The detent drive mechanism  39  can be regulated to run in the right or left direction by the control device  52  via the electrical feed line  41 . Because of this, the release of the blockage of the base plate  25  when adjusting the positioning force F A , or after the command “roller off”, can be performed. 
     It lies within the scope of the present invention that generating the positioning force F A  is not limited to pneumatic or hydraulic drive mechanisms  24 . Piezo-electrical or electro—chemical operating devices are also suitable. As represented in FIG. 2, the top  42  of the base plate  25  is used as an abutment, and the underside  83  of the set plate  09  as the force application point for the operating device  94 . For its control, the operating device  94  is connected via an electrical connecting line  61  with the control device  52 . 
     A pressure measuring arrangement  84 , with its electrical connector  85 , is arranged on the set plate  09  for the purpose of actually measuring the positioning force F A  exerted by the operating device  94 . It is used for measuring the actual value of F A . The pressure measuring arrangement  84  can consist, for example, of strain gauge strips in a Wheatstone bridge circuit. In this case, the branches of the bridge are then placed on the top  20  and on the underside  83  of the set plate  09  in the vicinity of the shaft receiver  03 . Blocking and unblocking of the set plate  09  by use of a detent  32  takes place as described above in the other preferred embodiment. 
     In the situation of an over-mounted seating, a device  26  for adjusting the pressure force F A , or fixing force F F  for each roller  02  to be positioned for each bearing journal, or bearing shaft  06 , is provided. If the positionable roller  02  is not seated over-mounted, two devices  26  are provided, which can be selectively preset and/or switched in singly or together, so that they act on one or both shaft receivers  06  per roller  02 . 
     While preferred embodiments of a method and of devices for adjusting a roller in a printing machine, 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 changes, in for example the drive for the cylinders or rollers, the specific type of printing press and the like could be made without departing from the true spirit and scope of the present invention, which is to be limited only by the following claims.