Patent Document

CROSS-REFERENCE TO RELATED APPLICATIONS 
   This U.S. Patent Application is the U.S. National Phase, under 35 USC 371, of PCT/DE2003/002348, filed Jul. 12, 2003; published as WO 2004/016431 A1 on Feb. 26, 2004 and claiming priority to DE 102 33 086, filed Jul. 19, 2002 and to DE 102 53 997, filed Nov. 19, 2002, the disclosures of which are expressly incorporated herein by reference. 
   FIELD OF THE INVENTION 
   The present invention is directed to a method and to a device for reducing vibrations of rotating components, as well as to a vibration-damped rotating component. The rotating components roll off against each other. At least one raised area projects from a substantially circular contour of an effective surface area of at least one of the rotating components. 
   BACKGROUND OF THE INVENTION 
   EP 0 194 618 B1 discloses a device for reducing vibrations which are caused by rolling over a groove located on the surface area. A raise in height of the circular contour for affecting the force change behavior, is provided in this device in the entry or exit area of the groove. 
   A method for compensating for vibrations of rotating components is disclosed in WO 01/50035 A1. An actuator is arranged in the area of the surface of the rotating component, which actuator counteracts the vibration by the provision of a force component in the axial direction when the actuator is activated as a function of an angle of rotation position of the rotating component. 
   SUMMARY OF THE INVENTION 
   The object of the present invention is directed to providing a method and a device for reducing vibrations of rotating components, as well as to providing a vibration damped component. 
   In accordance with the present invention, this object is attained by the provision of at least one raised area projecting from a substantially circular contour of an effective surface area of at least one of two rotating components that roll off on each other. A height of the raised area, in the radial direction, and a position of the raised area, in the circumferential direction, can be changed as a function of a value that defines a printing press status or vibration. 
   The advantages to be gained by the present invention lie, in particular, in that a possibility for effectively and variably reducing vibrations has been provided. The reduction of the vibrations can take place actively, and possibly adaptively, during a production run and can be matched to the operating requirements. 
   The method and the device in accordance with the present invention can be employed with particular advantage in connection with at least one of two components rolling off on one another, such components being, for example, cylinders or rollers in which, viewed in the circumferential direction, at least one of the components has at least one interruption, such as, for example a groove, on its surface area. 
   Because of the ability to change, and in particular because of the ability to change, by remote control, the geometry and/or the position and/or the height of the raised area or areas on the cylinder surface area, the vibration can optimally be reduced through the various operational states, such as the speed of rotation, for example, on the one hand. On the other hand, the geometry and/or the position or the height per revolution, or during a part of the revolution, can be changed or can be modulated in order to do justice to the roll-over of the interruption at each nip point, for example in connection with the contact of the rotating body with several other cylinders and/or rollers. 
   In an advantageous embodiment of the present invention, an actuator, which can be remotely controlled, is configured as an actuator which can be charged with a pressure medium, such as, for example, as a hydraulic or as a pneumatic unit. In a variation, the actuator can be piezo-electrically configured. 

   
     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 depiction of two rotating components working together, in 
       FIG. 2 , an enlarged representation of a nip point between the two rotating components depicted in  FIG. 1 , in 
       FIG. 3 , qualitative courses of an acceleration as a function of time, and showing at A: vibration without the formation of a raised area, and at B: with the formation of a raised area, in 
       FIG. 4 , a first preferred embodiment of a device for reducing vibrations in accordance with the present invention, in 
       FIG. 5 , a first preferred embodiment of the integration of a clamping or bracing device, in 
       FIG. 6 , a second preferred embodiment of the integration of a clamping or bracing device, in 
       FIG. 7 , a third preferred embodiment of the integration of a clamping or bracing device, in 
       FIG. 8 , a schematic representation of a method for controlling the device in accordance with the present invention, in 
       FIG. 9 , a qualitative representation of the interrelationship between a roll-off speed and a height of the raised area, or of the pressure, in 
       FIG. 10 , a schematic representation of a method for regulating the device, in 
       FIG. 11 , a qualitative representation of an interrelationship between a relative amplitude and the height of the raised area, or of the pressure, and in 
       FIG. 12 , a schematic representation of a method for regulating a device with four rotating components acting together respectively in pairs. 
   

   DESCRIPTION OF THE PREFERRED EMBODIMENT 
   Referring initially to  FIGS. 1 and 2  there is schematically depicted a rotating component  01 , for example a cylinder  01 , or a roller  01  of a machine, such as, for example, a treatment or a processing machine for webs and sheets, and in particular a cylinder or a roller of a rotary printing press. The cylinder  01  or roller  01  cooperates, in a contact position AN, with a second rotating component  02 , for example a cylinder  02  or a roller  02 . The two components  01 ,  02 , called cylinders  01 ,  02  in the discussion which follows, roll off on or against each other in the area of their effective surface areas  03 ,  04  and have been placed against each other in a contact position AN, and with a force which, for example, can be predetermined or set, all as seen in  FIG. 1 . In an advantageous manner, the present invention can also be applied to rollers and cylinders of similar machinery for producing web-shaped material, such as, for example paper or sheet metal, and the like, in impression cylinders or in rolling mills. 
   At least one of the cylinders  01 ,  02 , such as, for example the first cylinder  01 , configured as a transfer cylinder  01 , has, in the area of its effective surface area  03 , at least one axially extending interruption  06  of a circumferential surface contour which otherwise is circular in an unstressed state. The interruption  06  is, for example, based on a joint formed by ends of one or of several dressings  07  that are arranged on the cylinder  01 . Alternatively, interruption  06  is caused because the ends of one or of several dressings  07  are arranged in a groove  08  that is extending in an area close to the surface of the cylinder  01 . An opening from the surface area of the cylinder  01  to the groove  08  is kept as small as possible, and, in an advantageous embodiment, such a groove  08  is maximally 3 mm in circumferential width. The groove  08  can widen or open toward the cylinder interior and can have in it a device  10  for clamping and/or for bracing, as seen in  FIG. 4 . However, the interruption can also be designed solely as a slit  08 . 
   In the contact position AN, as depicted schematically in  FIG. 1 , the two cylinders  01 ,  02  are placed against each other with a force which is greater than zero, and, in the course of the passage of the interruption  06  through the nip point, the two cylinders  01 ,  02  undergo a relief as well as a subsequent renewed stress. A vibration of the cylinder  01 ,  02 , or of the cylinders  01 ,  02 , is excited or caused by this cyclical stress and relief which vibration is, inter alia, a function of the cylinder contact forces, the geometry of the interruptions  06  and the cylinders  01 ,  02 , the properties of the cylinder material, and the number of revolutions, or of a roll-off speed “v.” Such a vibration is qualitatively represented in  FIG. 3  as curve or line A, wherein the area within the dashed lines identifies the passage of the interruption  06  through the nip point. This vibration, which is excited by the passage of the interruption  06 , has been damped and should not be confused, at this point, with other vibrations that are possibly induced in the individual cylinders  01 ,  02  by balance errors, or with a bending caused by gravity and/or the line force. The vibration depicted in  FIG. 4  is excited during each revolution of the cylinder  01 ,  02  in the circumferential direction in response to alignment of the interruption  06  and the nip point. 
   To dampen the vibration, at least one of the cylinders  01 ,  02 , for example the cylinder  02  which is configured as a forme cylinder  02 , has at least one axially extending raised area  09  of a cylinder circumferential and axial surface contour, which otherwise is circular in the unstressed state, in the area of its effective surface area  04 . This raised area  09  can extend axially continuously over a length of the effective barrel of cylinder  02 , or can also extend in one or in several cylinder sections in the axial direction. As indicated in  FIG. 2 , the raised area  09  has a height h 09 , depicted as the maximum weight, in respect to the undisturbed contour or surface of cylinder  02 , and an effective distance a 09 , again depicted as the maximum distance from the interruption  06  on the cooperating cylinder  01  in relation to a roll-off path at the rotating cylinders  01 ,  02 . 
   Viewing the passage of the raised area  09 , by itself, through the nip point, a vibration is also induced in the cylinders  01 ,  02  rolling off on each other. Depending on the relative position in respect to the passage over the interruption  06 , i.e. depending on the rolled-off distance a 09  or phase relation and the height h 09 , and/or the shape of the raised area  09 , this counter-vibration causes an increase or decrease, and in the ideal case, effects a cancellation of the vibration amplitude caused by the passage of the interruption  06 . Depending on its shape and its position, the raised area  09  provides a support effect between the cylinders  01 ,  02 , which cylinders are radially moved with respect to each other by the excitation. 
   The height and the shape of the generated counter-vibration is partially a function of the shape of the raised area  09  and, in case of a raised area  09  having an asymmetrical shape with respect to the circumferential direction, is also partially a function of the direction of rotation of the cylinders  01 ,  02  rolling off on each other. A course of the resultant curve B of the vibration, caused by the superimposition of the vibration and counter-vibration is represented in  FIG. 3 , wherein the excitation was generated by the raised area  09  in the form of a ramp, as will be discussed below. An increase in an amplitude of the acceleration, which can initially be detected in the area of the passage of the interruption  06 , which initially can be detected in the area of the passage of the interruption  06 , is already followed by a clear decrease in the second period. Since the area of the interruption  06  is a non-printing area, the brief increase of the resultant vibration does not have a negative effect on the printed image, but the subsequent decrease has a positive effect. 
   The raised area  09  is now configured in such a way that its height a 09  can be changed with respect to the undisturbed cylinder surface contour, in particular during operation of the cylinder pair  01 ,  02 , i.e. during the roll-off of the cylinders  01 ,  02 . To this end, the cylinder  02  has an actuating assembly  11  for use in changing the height h 09 , for example an actuating device  11 , and in particular a remotely controllable actuator  11 . In an advantageous embodiment of the present invention, the circumferential distance a 09 , as depicted in  FIG. 4  is also configured to be changeable. 
   The provision of the raised area  09  can be technically realized in various ways. It is thus possible, for example, for fingers, which have been given a suitable shape, to be sunk, in a comb-like manner, into recesses in the surface area of the base body of the cylinders  01 ,  02 , and for such fingers to be radially movable, by linear or by rotatory movements via an actuating assembly  11 . A variation is also possible, in which an area of the surface  03 ,  04  of the respective cylinder  01 ,  02  has been structured to be elastically deformable or to be elastically resilient, within defined limits, and to be deflectable in the radial direction by an actuating assembly  11 , such as, for example, cams or an eccentric shaft, or by other actuators, which may be arranged in the interior of the cylinder. 
   The actuator  11 , or the actuators  11 , can also be structured in different ways, for example as a function of the configuration[of the raised area  09 . It can be configured as a part of a motor-driven, as a hydraulically or a pneumatically driven unit, or as a unit that operates based on magnetic or on piezo-electric forces. 
   In the following preferred embodiments, as depicted in  FIGS. 4 to 12 , the device and the method in accordance with the present invention are represented by the example of a raised area  09  structured as a tongue, alip or as a bracket  09 , which can be substantially bent out of the contour of the surface area  03 ,  04  of the respective cylinder  01 ,  02  and which can reversibly spring back into alignment with the contour of the surface area  03 ,  04 . The actuator  11  activating the tongue/lip/bracket  09  has been configured here as a part of a hydraulically operating unit. 
   In  FIG. 4 , the cylinder  02 , here provided as a[the] forme cylinder  02 , and working together with the transfer cylinder  01 , has the tongue/lip/bracket  09 , which can be raised. The tongue/lip/bracket  09 , which is in the form of a one-armed lever, is embodied by a groove  12 , which groove  12  is axially extending inside of the surface area  04  of cylinder  02 , and an interruption or cut or opening  13  of the surface area connecting the groove  12  with its surroundings. Interruption  13  may be, for example, in the form of an axial cut  13 . The tongue/lip/bracket  09  can be raised by the operation of a suitable hydraulic unit, which has an actuator  11  in the form of a reversibly deformable hollow body  11 , which body  11  can be charged with a pressure medium. The actuator  11  is situated in the groove  12  extending axially in the cylinder  02 . The hollow body  11  is arranged directly underneath the tongue/lip/bracket  09  in the interior of the cylinder  02 , as is shown in  FIG. 4 , and is supported, toward the interior of cylinder  02 , in the radial direction, at least partially on a cylindrical face  14  which is fixed in place on the cylinder. 
   Also represented in  FIG. 4  is the effective distance a 09  between the maximum raised area  09 , configured here as the edge of the cut or opening  13  and the interruption  06  on cylinder  03 , as well as an effective length l 09  of the leg of the tongue/lip/bracket  09 . The effective leg length l 09  of the one-armed lever  09  represents the length of the tongue/lip/bracket  09 , in the circumferential direction of cylinder  02  from the edge of the cut  13  to the point at which the tongue/lip/bracket  09  is “undermined” by the groove  12 , as viewed in the radial direction. In an advantageous embodiment, the tongue/lip/bracket  09  extends over the entire axial length of a barrel of the cylinder  02 . In  FIG. 4 , the tongue/lip/bracket  09  is represented in an active position, i.e. the actuator  11  is effective or is actuated. In another embodiment of the present invention, with several staggered cylinder grooves, or with several dressings, in which several interruptions  06  that are arranged side-by-side in the axial direction of the cylinder  01  are arranged offset in respect to each other in the circumferential direction, several of the raised areas  09  can be arranged staggered on cylinder  02  in the same way. 
   The actuator  11 , which may be embodied as a hollow body  11 , receives its fluid, or its other suitable operating pressure P, from the outside of cylinder  01 , for example via a rotary throughput, which is not specifically represented, in the area of a journal, also not specifically represented, of the cylinder  02 . 
   When they are placed against each other, the forme cylinder  02  acts together with the transfer cylinder  01 , on whose surface a dressing  07 , such as, for example, a rubber blanket  07 , has been secured or braced. Ends  16 ,  17  of a single dressing  07 , or of two dressings  07  that are arranged one behind the other in the circumferential direction of cylinder  01 , are retained by the provision and the use of a clamping and/or a bracing device that is located in the groove  08 . The interruption  06  in the effective surface area  03  of the cylinder  01  is formed in the area where the dressing end or ends  16 ,  17  leave the opening of the groove  08 . 
   In an advantageous embodiment of the invention, the circumferential offset distance a 09  is a length corresponding to a path of a sector of the cylinder  01 ,  02  of an opening angle of −1 to 8°, and in particular of 3° to 6°, on the surface area  03 . 
   In an advantageous embodiment of the present invention, and with cylinders  01 ,  02  of an axial length l 01 , l 02  of 1,350 to 1,550 mm, and with an effective circumference of 420 to 700 mm, and in particular of 500 to 600 mm, the tongue/lip/bracket  09  has an effective leg length l 09  of 10 to 30 mm, and in particular has a length of 16 to 21 mm. The circumferential offset distance a 09  is, for example, from 1.25 to 15 mm, and in particular is from 4 mm to 10 mm. 
   The ratio between the offset distance a 09  and the length of the cylinder circumference lies between 0.002 and 0.02, and in particular lies between 0.005 and 0.015. The ratio between the leg length l 09  and the length of the cylinder circumference lies between 0.02 and 0.04, and in particular lies between 0.03 and 0.035. 
   The raised area  09 , configured as a tongue/lip/bracket  09  in accordance with  FIG. 4 , has been made asymmetric with respect to the direction of rotation of the cylinder  01 ,  02 , or of the cylinders  01 ,  02 . In one direction of cylinder rotation, the raised area  09  acts with a ramp shape and with a correspondingly shaped impulse, while in the other direction of cylinder rotation this raised area  09  acts as an impulse that is induced at a discontinuous skip location. Both forms will exhibit the above described vibration damping or counteracting effect wherein, however, the excitation resultant with travel of the cylinder  01  over the ramp in the direction of rotation, and with a discontinuous skip location, is of greater advantage. 
   The height h 09  and/or the distance a 09  can be set differently, depending on the direction of rotation, on the number of rotations and on the force of the contact, or the linear force between the cylinders  01 ,  02 . For this purpose, it is possible to supply the direction of rotation as a value “g” defining the printing press status or the printing press to a control or regulating device explained further below. 
   A raised area  09 , corresponding to, or similar to the arrangement represented in  FIG. 4 , by way of example by the forme cylinder  02 , can be arranged on the transfer cylinder  01 , either additionally to, or in place of the forme cylinder  02 . Different variations for integrating a clamping device for the dressing  07 , or for its ends  16 ,  17 , are represented in subsequent  FIGS. 5 to 7 . These arrangements can be applied to dressings  07  which may be embodied as printing formes  07  on the forme cylinder  02 , or which may be embodied as rubber blankets  07  on the transfer cylinder  01 . In the case of rubber blankets  07 , the use of metallic printing blankets  07  including an elastically deformable layer on a metal support is advantageous, since these blankets can be configured in the area of their ends, similar to those of printing formes  07  and can be clamped in the groove  08 . 
   In  FIG. 5 , the cut, or opening or interruption  13  is embodied as an opening  13  in such a way that it has been made very narrow, less than or equal to 3 mm, wherein the ends  16 ,  17 , for example the dressing ends  16 ,  17 , are merely suspended. 
   In  FIG. 6 , the cut or opening or interruption  13  is embodied as an opening  13  in such a way that the actuator  11  simultaneously acts on one or on two dressing ends  16 ,  17 , either via a lever mechanism  20 , which is only schematically indicated, or directly, and clamps the two dressing ends  16 ,  17 . 
   In  FIG. 7 , the cut or opening or interruption  13  is embodied as an opening  13  in such a way that, for example, the leading dressing end  16  is substantially held in place by the shape of the edge. The trailing dressing end  17  is clamped by the actuator  11 . 
   As has been discussed in detail above, the height h 09  of the raised area  09  is adapted to be changeable. Preferred embodiments of a method for controlling or regulating this height h 09 , and the device required to accomplish such a method, will be explained in what follows. 
   In a first preferred embodiment, as depicted schematically in  FIG. 8 , the regulation takes place by the utilization of a control system, which control system can contain a lower order regulating circuit. 
   A value “v” defining the printing press status, and in particular defining the roll-off speed “v,” such as the number of revolutions or the angular speed, for example, is used as the command variable of the higher order control system. This value “v” can be obtained, for example, together with other values “g” defining the printing press status or the printing press, from a higher order printing press control device, or can also be measured in a suitable manner. Now, a reference variable of the manipulated variable is assigned to the value “v” in a logical unit  18  by the use of a stored interrelationship, such as, for example by the use of a table, arithmetically, or the like as the output value of the logical unit  18 . The manipulated variable can directly be a desired height h 09  of the raised area  09 , a pressure P, a distance S, a voltage U, or the like. Accordingly, a reference variable h 09   SOLL  for the height h 09  of the raised area  09 , a reference variable P SOLL  for the pressure P of a hydraulic unit, a reference variable S SOLL  for a travel or position signal S of an actuator  11 , or a reference variable U SOLL  for the voltage signal U of an actuator  11 , are determined as the output values. This reference variable h 09   SOLL , P SOLL , S SOLL , U SOLL , is again used as a command variable for a lower order regulator device  19 . A regulating device  21 , for example a regulator  21 , and in particular a controlled system  22  of the regulating device  21 , can now be embodied in different ways, and can be matched to the type of the actuator  11  and to the input values. 
   A functional, or an algebraic, and in particular a linear interrelationship between the roll-off speed “v” and the desired raised area  09  or of an appropriate travel, pressure or voltage signal has been stored in the logical unit  18  as the logic. This interrelationship, which is particularly linearized, between the roll-off speed “v” and the reference variable h 09   SOLL , P SOLL , S SOLL , U SOLL  for the height h 09  of the raised area  09 , or the pressure P, the travel S or the voltage U can be present many times for different cylinder geometries and/or for values “g” defining the printing press status or the printing press, and can be appropriately selected, as depicted in  FIG. 9 , as interrelationships C, D. 
   Such an interrelationship can also be advantageously used for starting and for running up the printing press to its operational speed, so that a suitable height for the raised area  09  is provided in connection with each roll-off speed “v.” 
   In a further development, the regulating device permits an optimization of the actual production conditions or circumstances because of its adaptive structure. 
   In case of the provision of a hydraulic unit, in accordance with the preferred embodiments in  FIGS. 4 to 7 , a linearized interrelationship between the roll-off speed “v” and the reference value P SOLL  for the pressure P is stored as the logic, for example. A known interrelationship between the pressure P in the hollow body  11  and the resulting height h 09  of the raised area  09  can be the basis for this logic. Now, the actuator  11 , which is embodied as a hollow body  11 , is charged with the appropriate pressure P, which is maintained, if required, by the use of the regulator device  19 , via the controlled system  22  which may be embodied as a valve  22 , wherein an actual value P IST  is returned to the lower order regulating circuit. This accordingly applies to the manipulated values S, U, h 09 , which differ from the pressure P. Thus, the tongue/lip/bracket  09  is raised by the corresponding height h 09  as a function of the roll-off speed “v” and in accordance with the existing pressure P IST  and is maintained there. If the roll-off speed “v,” or if another production condition, changes, the pressure P, or one of the other manipulated values is again determined and is again set. No continuous checking of the roll-off speed “v” need be performed. Instead, this can take place at discrete intervals, for example following a fixed number of cylinder revolutions. In a further development, a starting value P IST  can also be supplied to the lower order regulating circuit, which can be predetermined from a printing press control, or also manually, for example during the start-up phase or under extremely non-stationary conditions. 
   In a further preferred embodiment of the present invention, as shown in  FIG. 10 , the reduction takes place by the use of a higher order regulating device, which can again contain the previously described regulating circuit of the lower order regulator device  19 . 
   In contrast to  FIG. 8 , in the embodiment depicted in  FIG. 10 , a value e(t), which defines the cylinder on the press vibration, is fed, as the input value, to the logical unit  18 . In particular, the value e(t) contains a relative value between amplitudes a 1 , a 2 , which are measured at both cylinders  01 ,  02  and which are projected on a plane through the axes of rotation of the two cylinders  01 ,  02 . Therefore, in what follows, the value e(t) will also be called a relative amplitude e(t). If the two cylinders  01 ,  02  vibrate equiphased in this plane, at the same amplitude e(t), a resultant value of zero would result. In addition, as described in connection with  FIG. 8 , the roll-off speed “v” and/or other values “g” defining the printing press status or the printing press, can also be supplied as input values. In a further difference from  FIG. 8 , in the embodiment depicted in  FIG. 10 , the logical unit  18  has an optimization algorithm which varies the output values h 09   SOLL , P SOLL  on the basis of the values e(t) in such a way that e(t) is minimized. 
   In an advantageous embodiment of the present invention, the variation takes place in accordance with interrelationships which are stored in the logical unit  18 , for example the dependence of the relative amplitude e(t) on the height h 09  or on the pressure P, as shown in  FIG. 11 , or on the distance a 09 . It is possible to preset a group of curves or an arithmetic connection for different ranges of the roll-off speed “v,” for example the number of revolutions. With the roll-off speed “v” or the number of revolutions known, a variation now takes place along the interrelationship preset for this roll-off speed “v” or this number of revolutions. For example, in  FIG. 11  a curve identified by v 1  denotes a number of revolutions of 20,000 rph, v 2  of 40,000 rph, v 3  of 60,000 rph and v 4  of 80,000 rph. Here, too, a measurement of the vibrations and a variation possibly resulting therefrom need not take place continuously, but can be determined regularly within finite time intervals, or in accordance with a defined number of cylinder revolutions. 
   Further processing of the reference variable h 09   SOLL , P SOLL  generated in the logical unit in the described manner takes place in accordance with the process explained in connection with  FIG. 8 . 
     FIG. 12  shows a multi-roller system, and in particular a four-roller system, wherein the previously described transfer cylinder  01  works or cooperates together with its forme cylinder  02 , and also works, in the contact position AN, with a further component  23 , for example with a cylinder  23  configured as a counter-pressure cylinder  23 , which, in this case, may be a second transfer cylinder  23 . A component  24 , for example a cylinder  24 , for example a second forme cylinder  24 , is assigned to the second transfer cylinder  23  and works together with the latter in the contact position AN. Only two of the four cylinders  01 ,  02 ,  23 ,  24 , and in particular only the two transfer cylinders  01 ,  23 , each have an actuator  11  and a raised area  09 , whose height h 09  and/or whose phase relation or distance a 09  can be changed. The principal functioning can also be applied to other multi-roller systems, such as to satellite units with 3, 9 or 10 cooperating cylinder, for example. 
   Analogously to the preferred embodiment discussed in accordance with  FIG. 10 , four amplitudes, or four vibration courses a 1 , a 2 , a 3 , a 4 , and corresponding to the number of cylinders of the cylinders  01 ,  02 ,  23 ,  24  involved are determined, and from these amplitudes, a number of relative amplitudes e 1 ( t ), e 2 ( 1 ), e 3 ( 1 ), corresponding to the number of nip points, is formed, which relative amplitudes are supplied, as input values, to the logical unit  18 . Now, the optimization algorithm has an interrelationship for each nip point, for the respective passage of the raised area  09 , or the interruption  06 , through the nip point. If one of the inner cylinders  01 ,  23 , for example if the transfer cylinder  01  is considered, the passage to the forme cylinder  02  at the nip point takes place at a defined time, and the passage to the second transfer cylinder  23  takes place at another defined time. Therefore, the demands made on the optimal height h 09 , or on the desired pressure P SOLL , can be different for both passages. It is now possible to resolve this problem advantageously in two different ways. 
   In a first preferred embodiment, a height h 09   SOLL.1 , or a pressure P SOLL.1  is determined in the logical unit  18  in such a way that a compromise is found, while observing the two dependencies, taking into consideration the relative amplitudes e 1 ( t ), e 2 ( t ), which minimizes the two relative amplitudes e 1 ( t ), e 2 ( 1 ) as a whole. The same applies to the two other cylinders  23 ,  24 , taking into consideration the relative amplitudes e 3 ( t ), e 4 ( t ) for the height h 09   SOLL.2 , or the pressure P SOLL.2 . Then the respective actuator  11 . 1  or  11 . 2  is charged with the height h 09 , or with the respective pressure P 1 , P 2 , which is or which will be regulated to P SOLL.1  or to P SOLL.2 , corresponding to this compromise for the existing roll-off speed “v,” via the associated regulating device  21 . 1 ,  21 . 2 , and the controlled system  22 . 1 ,  22 . 2  which may be embodied as valves. 
   In a second preferred embodiment, a phase-dependent variation of the optimization takes place for the height h 09 , or for the pressure P SOLL . It is now possible to change the height h 09  of the raised area  09  at least twice for each revolution of the cylinder  01 ,  23  using the actuator  11 , and in this case the raised area  09  assumes different values at the times of its passage through the one or the other respective nip points. Then the height h 09  is changed for each revolution as a function of the angular position of the cylinder  01 ,  23  having the actuator  11 . If more than one interruption  06  and/or more than one raised area  09  is arranged in the circumferential direction of the cylinder(s)  01 ,  02 ,  23 ,  24 , the number of the possibly required changes, or the number of the values of the height h 09 , possibly changes accordingly. 
   In the case of the four cylinders  01 ,  02 ,  23 ,  24 , two pressures P SOLL.1 , P SOLL.2  are issued by the logical unit  18  as the reference variables P SOLL.1 , P SOLL.2 , each of which is fed into a lower order regulator device  19  of respective actuators  11  for a changeable raised area  09 . Here, the two raised areas  09  are arranged on the two transfer cylinders  01 ,  23 . 
   It is also possible to arrange more than one raised area  09 , for example to arrange two raised areas  09 , in the circumferential direction. In this case, a common regulator device  19 , as well as a common reference variable P SOLL  can be provided for each raised area  09  of the cylinder  01 ,  02 ,  23 ,  24 , and also for all of the raised areas  09  of a cylinder  01 ,  23 . Also, all cylinders  01 ,  02 ,  23 ,  24  can have raised areas  09  and/or interruptions  06 . 
   As explained above, in an advantageous embodiment of the present invention, the distance a 09 , or the phase relation, between the interruption  06  and the raised area  09  is also configured to be variable. 
   In one preferred embodiment, this can take place, for example, mechanically wherein an effective shape of the raised area  09 , or its absolute position, is changed. In the first case, an axially extending spindle, having the raised area  09 , can have an appropriate shape on its exterior surface in such a way that, when turning the spindle by the use of an actuator, which is not specifically represented, another area of the exterior of the spindle becomes effective as the raised area  09 . In the second case, fingers, which are, for example, arranged in a comb-like manner on the surface area of the base body of the cylinder  01 ,  02 , can be moved in the circumferential direction of the cylinder by an actuator, which is also not specifically represented. 
   In another embodiment of the present invention, the two cooperating cylinders  01 ,  02 ,  23 ,  24  are embodied to be variable in their angle of rotation position φ with respect to each other. In case the interruption  06  and the associated raised area  09  are arranged on different cylinders  01 ,  02 ,  23 ,  24 , the change in the relative angle of rotation position φ causes a change of the distance a 09 . For example, this can be realized in such a way that the two cylinders  01 ,  02 ,  23 ,  24  are rotatorily driven, mechanically independently of each other, by the useof separate drive motors. In this case, one of the drive motors, which, as a rule, are electronically synchronized, is impressed with an offset in its reference angular position for changing the distance a 09 . However, the change of the relative angle of rotation position can also be performed by the use of customary mechanical devices, such as are common, for example, for setting the position in the circumferential direction. 
   The control, or the regulation, of the distance a 09  can take place in a manner corresponding to the explanations of the preferred embodiments in accordance with  FIGS. 8 to 12 . As explained in connection with the height h 09 , it is then possible to store appropriate interrelationships between the roll-off speed “v” and the distance a 09 , or to store optimization algorithms for accomplishing a variation of the distance a 09  as a function of the relative amplitude e(t), and possibly of the roll-off speed “v.” 
   While preferred embodiments of a method and device for reducing vibrations on rotating parts, and vibration-damped rotating part, 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 overall sizes of the cylinders, the specific cylinder motors, 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 appended claims.

Technology Category: 7