EP2006097A2 - Unités de support pour un cylindre d'impression d'une machine d'impression - Google Patents

Unités de support pour un cylindre d'impression d'une machine d'impression Download PDF

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Publication number
EP2006097A2
EP2006097A2 EP08152503A EP08152503A EP2006097A2 EP 2006097 A2 EP2006097 A2 EP 2006097A2 EP 08152503 A EP08152503 A EP 08152503A EP 08152503 A EP08152503 A EP 08152503A EP 2006097 A2 EP2006097 A2 EP 2006097A2
Authority
EP
European Patent Office
Prior art keywords
bearing
bearing unit
unit according
housing
outer ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP08152503A
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German (de)
English (en)
Other versions
EP2006097B1 (fr
EP2006097A3 (fr
Inventor
Ralf Christel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Koenig and Bauer AG
Original Assignee
Koenig and Bauer AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Koenig and Bauer AG filed Critical Koenig and Bauer AG
Publication of EP2006097A2 publication Critical patent/EP2006097A2/fr
Publication of EP2006097A3 publication Critical patent/EP2006097A3/fr
Application granted granted Critical
Publication of EP2006097B1 publication Critical patent/EP2006097B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/08—Cylinders
    • B41F13/24—Cylinder-tripping devices; Cylinder-impression adjustments
    • B41F13/26—Arrangement of cylinder bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/08—Cylinders
    • B41F13/24—Cylinder-tripping devices; Cylinder-impression adjustments
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/08—Cylinders
    • B41F13/24—Cylinder-tripping devices; Cylinder-impression adjustments
    • B41F13/26—Arrangement of cylinder bearings
    • B41F13/30—Bearings mounted on sliding supports

Definitions

  • the invention relates to storage units for a printing cylinder of a printing press according to the preamble of claim 1 or 2.
  • the active vibration damping techniques described above are almost exclusively used for damping resonantly forced vibrations in machine tools where there is continuous excitation (imbalance, chatter marks, process forces). In this case, low, continuously introduced forces are sufficient for damping, which are derived from a metrological detection of the actual value and a control algorithm.
  • the channel impact vibrations of printing cylinders are caused by a single per revolution or periodic, pulse-shaped excitation.
  • the force is applied by eliminating or reducing the pressing force when the interruption of the lateral surface is overrun (eg clamping channel of the opening for receiving an elevator). Due to the very short-term impact stimulus and the requirement to almost completely suppress the first vibration, which would otherwise already be visible as a quality defect in the printed product, new concepts regarding actuator technology and control are required.
  • a bearing assembly for a printing machine wherein between a bearing inner ring and a bearing outer ring rolling elements are arranged and the bearing outer ring has a lateral mounting flange, with which it can be fixed to a housing.
  • At least one piezoelectric adjusting element is arranged between the housing and the bearing outer ring, via which an exact radial positioning of the bearing lying in the micrometer range can be achieved in the housing bore, before the bearing is then fixed in the usual manner by means of screws on the housing. In the printing operation of the printing press, the bearing is thus rigidly fixed relative to the housing.
  • the invention has for its object to provide storage units for a printing cylinder of a printing press.
  • a force can be introduced which compensates for the elimination or reduction of the compressive stress when rolling over a cylinder channel, for example a clamping channel of a plate cylinder, and thus avoids vibration excitation.
  • radial forces are introduced by means of the piezo actuators via the bearing in the printing cylinder, which substantially correspond in size and duration of action of the channel impact force. If the sum of the channel impact force and the actuator force is equal to zero at any time, movement of the center of gravity of the cylinder can be avoided.
  • the invention enables integration of a suitable actuator for moving the bearing center of the printing cylinder and a suitable measuring system for calculating the Aktorstellkurve in a pre-assembled, compact storage unit that meets the requirements for space and connecting structures of a printing cylinder in a printing press.
  • the compact and easy-to-install bearing unit which is pre-assembled, adjusted, eg B. mounted by shrink fit on the shaft seat of the printing cylinder and is mounted completely with the printing cylinder to a side frame of the printing press, resulting in no collision with adjacent modules such as page register or drive;
  • the actuators and the power electronics are mounted on the bearing housing, ie on fixed components.
  • Actuator dimensions are required in the currently typical printing unit loads, which can be rounded off in the preferred cross-sectional shape of the bearing unit, that is to say the preload side is rounded and the actuator sides are square.
  • the effective actuator length can thus be increased to approximately 50% of the cylinder radius. After the stroke is proportional to the effective length of piezo actuators Actuators relevant size can be installed, while still sufficient space for radial bearings is guaranteed.
  • an integration of actuators and sensors in a compact unit in the form of a storage unit is thus possible, with maximum utilization of the available installation space.
  • a plate cylinder for example, a web-fed rotary printing press, such as a web-fed rotary offset printing machine
  • the space constraint in the radial direction essentially results from the requirement to be able to apply several inking or dampening rollers with corresponding adjustment mechanisms around the outer surface of the plate cylinder and between plate cylinder and blanket cylinder the required center distance observed.
  • the bearing unit may comprise a side register adjustment device, which may include a thrust bearing for axially adjusting the recorded in the storage unit printing cylinder, which may be adjustable by means of a threaded device.
  • a side register adjustment device which may include a thrust bearing for axially adjusting the recorded in the storage unit printing cylinder, which may be adjustable by means of a threaded device.
  • a storage unit is particularly suitable for use in connection with plate cylinders.
  • the bearing unit 01 is used to hold a cylinder 02 not shown here (see. Fig. 4 ), in particular printing cylinder 02, for example, forme cylinder 02 or blanket cylinder 02 of a printing press, in particular a web-fed rotary printing press, for example a web-fed rotary offset printing press.
  • the printing unit cylinder 02 mounted in the bearing unit 01 can in particular be a printing cylinder 02 with a single cylinder channel on the circumference.
  • the storage unit 01 can be fastened, for example, on a side frame of the printing press, z. B. screwed, it being understood that on both sides of the cylinder 02 each have a bearing unit 01 is provided.
  • the bearing unit 01 comprises a bearing 03, for example, a roller bearing 03, with an axial bore 04 for receiving a pin 06 (see. Fig. 4 )
  • the bearing 03 includes a bearing inner ring 08, which defines the bore 04, a bearing outer ring 09 which is rotatably received in the bearing housing 07, and a recorded between bearing inner ring 08 and bearing outer ring 09 Wälzoasasatz 10.
  • the bearing housing 07 is firmly screwed through threaded holes 11 with a side frame of the printing press, not shown.
  • the bearing outer ring 09 is received in the bore 14 of the bearing housing 07 with radial play.
  • the bearing outer ring 09 has on both sides a radially outwardly extending flange 12 and a contact shoulder 12, which extends into a correspondingly shaped, adjoining the bore 14 recess 13 on the respective end outer side of the bearing housing 07.
  • the bearing outer ring 09 in the bearing housing 07 in the radial direction, d. H. in a plane perpendicular to the bearing axis movable, but received immovably in the axial direction due to the double-acting axial sliding of the abutment shoulders 12.
  • the radially outwardly extending abutment shoulders 12 additionally cause a stiffening of the bearing outer ring 09, which is advantageous in view of the bending stress of the bearing outer ring 09 by the actuators 26 described below.
  • the bearing housing 07 is formed divisible and comprises two housing halves 16; 17, which are joined together by means of dowel pins 18 and are screwed together.
  • the dividing plane of the two housing halves 16; Preferably, the bearing outer ring 09 is divided Peripheral portion 17 of the other housing half 17 is rectangular.
  • the length L1 of the long side of the rectangular housing half 17 may in particular correspond to twice the radius R of the semicircular or semicircular housing half 16 and the length L2 of the short side of the rectangular housing half may in particular correspond to the simple radius R.
  • the bearing 03 or the bearing outer ring 09 is mounted as explained above with play in the bore 14 of the bearing housing 07.
  • a rotation 19 in the form of a torsionally stiff, but flexible securing plate 19 is provided, which is annular with a ring-like portion 21 and a plurality, in particular four radially outwardly extending cranked arms 22, which preferably extend from each other at an angle of 90 °, and are preferably oriented so that two of the arms 22 extend in the direction of the two corners of the rectangular housing half 17.
  • the annular portion 21 of the locking plate 19 is secured by screws 23 on the bearing outer ring 09, while the cranked arms 22 are fixed by screws 24 on the bearing housing 07, whereby a rotation 19 of the bearing outer ring 09 is created with simultaneous possibility of movement in the radial direction.
  • each actuator 26 In the rectangular housing half 17 of the bearing housing 07 are two piezoelectric actuators 26, z. As actuators 26, for example, two piezo stack actuators 26 with integrated force plate arranged. The actuators 26 are completely received within the bearing housing 07. The actuators 26 extend The plane of each actuator 26 preferably extends perpendicular to the axis of the bearing 03 or the axis of the bearing 03 is preferably in the defined by the respective actuator 26 Level.
  • the two actuators 26 are arranged at an angle of 90 ° + f 10% to each other, preferably 90 ° +/- 3%, in particular of 90 ° to each other, so in each case each have a vertical direction of action.
  • the actuators 26 act with their radially inner end on the bearing outer ring 09 in the sense of moving the bearing outer ring 09 and thus the entire bearing 03 in a radial plane and are supported at its radially outer end on the bearing housing 07.
  • a linear guide 29, z. B. a flat cage guide 29, in particular a needle rollers or balls having needle roller flat cage 29 may be provided.
  • the two outer corner portions 27 of the rectangular housing half 17 are formed as detachable from the bearing housing 07 caps 27, in which the rear ends of the actuators 26 are encapsulated and supported by synthetic resin.
  • the caps 27 in turn are fastened by means of screws 28 to the rectangular housing half 17.
  • the actuators 26 via the actuators 26, the forces are directly over the stiffened by the flanges 12 bearing outer ring 09 in the center plane (therefore no torque input by Aktorkraft ) of the rigid bearing point initiated (the central axis of the actuator 27 is within the Wälz Scientificbachn and / or the working width of the rolling bearing 03); the actuators 26 are based on the bearing housing 07 directly from the rigid side frame of the printing press; to compensate for length or angle tolerances, the actuators 26 on the front side in each case an intermediate element 29 for transverse force coupling to the z. B. needle rollers having flat cage guide 29 is pressed and the back is set on each a spacer between the cap 27 and the bearing housing 07, an adhesive gap, which is poured with epoxy resin.
  • the two actuators 26 opposite, preferably diametrically opposite each a biasing means 31 is provided which counteracts the force of the actuators 26.
  • the biasing device 31 may in particular be formed by a spring device 31, for example by a cup spring assembly 31, which is arranged in the half-round housing half 16, radially aligned, is supported with its radially outer rear side on the housing half 16 and with its radially inner front acting on the bearing outer ring 09, wherein for decoupling of transverse forces turn a flat cage guide 29 may be provided.
  • the biasing force of each spring means 31 is adjusted so that the spring means 31 biases its associated piezoelectric actuator 26 with a force corresponding to half the maximum actuating force of the control element 26.
  • the method for reducing oscillation amplitudes of the bending modes of a printing cylinder 02 is, generally speaking, essentially that at least one bearing point of the printing cylinder 02, preferably at both or all bearing points, a dynamic capac Vietnamese pursebung occurs.
  • This dynamic capacticianverschiebung takes place in particular by means of at least one piezoelectric Actuator 26 and Aktors 26th
  • the actuators 26 by means of a suitable control or regulation, as in principle, for example, from the above-mentioned WO 2006/061432 A1 is known, energized in the required manner to initiate a force in the bearing 03, which counteracts the forces acting on the mounted cylinder 02 forces, for example when rolling over a clamping channel, or compensates for this, to avoid vibration excitations as possible.
  • the existing clearance or gap between the radially outer bearing outer race 09 and the bore 14 of the bearing housing 07 restricts the maximum deflection of the actuators 26 in the event of overload (eg, in a winder) and thus prevents destruction and / or depolarization the actuators 26 in case of overload.
  • the arrangement of the actuators 26 explained above also leads to an avoidance of transverse forces or bending moments on the actuators 26.
  • an optimal gap between the outer ring and housing is required, which is large enough to the maximum Aktorhub (here about 45 microns) - taking into account manufacturing / assembly tolerances - to realize, is small enough to limit the maximum Aktoreinfederung (permissible (F.max-F.block) * C.aktor, here about 32 microns in ideal rigid environment).
  • the gap was here dimensioned to 65 microns.
  • the game is preferably 10 - 500 microns, in particular 20 - 100 microns.
  • the second embodiment according to Fig. 4 and 5 is essentially the same as in Fig. 1 to 3 , However, additionally has a built-in storage unit 01 side register adjustment device 32, the axial displacement of the printing cylinder 02, z. B. forme cylinder 02, in particular plate cylinder 02 for Correction of the page register enabled.
  • the pin 06 of the forme cylinder 02 is non-rotatably connected to a pin extension 33, which carries a further bearing 34, namely a thrust bearing 34, for example a thrust ball bearing 34, the housing 36 at its outer periphery with a thread 37, in particular a fine thread 37,
  • a metric fine thread 37 is provided, which meshes with a corresponding thread 38 of a fixed flange 39 which is rotatably connected to the bearing outer ring 09, in particular screwed.
  • a rotation of the housing 36 of the thrust bearing 34 thus causes an axial translational movement of the housing 36 and thus ultimately of the cylinder 02.
  • the possible adjustment range here can be about +/- 1.5 mm.
  • a ring gear 41 is further mounted, which is rotatable via an additional drive gear 42, in particular spur gear 42 via a drive shaft 43 to the o. G.
  • additional drive gear 42 in particular spur gear 42 via a drive shaft 43 to the o. G.
  • p is the pitch of the thread 37
  • d m is the mean thread diameter
  • bearing unit 01 as a rubber cylinder bearing
  • the integration of a macroscopic position adjustment for pressure and rest position of the blanket cylinder 02 is possible, see. also WO 2006/061432 A1 ,

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Rolling Contact Bearings (AREA)
  • Rolls And Other Rotary Bodies (AREA)
EP20080152503 2007-05-26 2008-03-10 Unité de support pour un cylindre d'impression d'une machine d'impression Not-in-force EP2006097B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200710024767 DE102007024767B4 (de) 2007-05-26 2007-05-26 Lagereinheit für einen Druckwerkszylinder

Publications (3)

Publication Number Publication Date
EP2006097A2 true EP2006097A2 (fr) 2008-12-24
EP2006097A3 EP2006097A3 (fr) 2012-01-11
EP2006097B1 EP2006097B1 (fr) 2012-10-24

Family

ID=39877254

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20080152503 Not-in-force EP2006097B1 (fr) 2007-05-26 2008-03-10 Unité de support pour un cylindre d'impression d'une machine d'impression

Country Status (2)

Country Link
EP (1) EP2006097B1 (fr)
DE (1) DE102007024767B4 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009002899B3 (de) * 2009-05-07 2010-06-24 Koenig & Bauer Aktiengesellschaft Axialeinstellvorrichtung eines Zylinders und ein Verfahren zur Montage einer Axialeinstellvorrichtung eines Zylinders

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009046538B4 (de) 2009-11-09 2014-06-05 Koenig & Bauer Aktiengesellschaft Vorrichtungen und Verfahren zur Schwingungsreduktion
DE102010026204A1 (de) 2010-07-02 2012-01-05 Fakultät Ingenieurwissenschaften und Informatik Fachhochschule Onsabrück Verfahren sowie Vorrichtung zur Kompensation von über den Umfang eines rotierenden insbesondere zylindrischen, Bauteils, insbesondere einer Walze, periodisch wiederkehrenden Störanregungen sowie Verfahren zur Bestimmung der Oberflächenstruktur eines ringförmigen Profils zur Kompensation der Störanregungen
CN103825396B (zh) * 2014-01-03 2016-08-17 重庆大学 电主轴振动主动控制装置
CN113531041B (zh) * 2021-07-30 2022-06-28 山东大学 堆叠型压电陶瓷减振环

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11170474A (ja) 1997-12-05 1999-06-29 Toshiba Mach Co Ltd 印刷機のショックマーク防止装置
DE20011948U1 (de) 2000-07-10 2000-12-07 Skf Gmbh, 97421 Schweinfurt Lageranordnung
WO2001050035A1 (fr) 1999-12-31 2001-07-12 Koenig & Bauer Aktiengesellschaft Procede et dispositif pour la compensation de vibrations de composants rotatifs
WO2004016431A1 (fr) 2002-07-19 2004-02-26 Koenig & Bauer Aktiengesellschaft Procede et dispositif pour reduire les vibrations au niveaux d'elements rotatifs et element rotatif correspondant amorti en vibrations
WO2006061432A1 (fr) 2004-12-10 2006-06-15 Koenig & Bauer Aktiengesellschaft Procede et dispositifs pour reduire les vibrations
DE102005058787A1 (de) 2004-12-10 2006-07-13 Koenig & Bauer Ag Verfahren und Vorrichtung zur Schwingungsreduktion

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10107135A1 (de) * 2001-02-15 2002-08-29 Windmoeller & Hoelscher Rollendruckmaschine sowie Verfahren zur Schwingungsdämpfung hieran
DE10236865A1 (de) * 2002-08-12 2004-02-26 Koenig & Bauer Ag Zylinder in einer Druckeinheit mit mindestens einem Kanal mit mindestens einer Haltevorrichtung

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11170474A (ja) 1997-12-05 1999-06-29 Toshiba Mach Co Ltd 印刷機のショックマーク防止装置
WO2001050035A1 (fr) 1999-12-31 2001-07-12 Koenig & Bauer Aktiengesellschaft Procede et dispositif pour la compensation de vibrations de composants rotatifs
DE20011948U1 (de) 2000-07-10 2000-12-07 Skf Gmbh, 97421 Schweinfurt Lageranordnung
WO2004016431A1 (fr) 2002-07-19 2004-02-26 Koenig & Bauer Aktiengesellschaft Procede et dispositif pour reduire les vibrations au niveaux d'elements rotatifs et element rotatif correspondant amorti en vibrations
WO2006061432A1 (fr) 2004-12-10 2006-06-15 Koenig & Bauer Aktiengesellschaft Procede et dispositifs pour reduire les vibrations
DE102005058787A1 (de) 2004-12-10 2006-07-13 Koenig & Bauer Ag Verfahren und Vorrichtung zur Schwingungsreduktion

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009002899B3 (de) * 2009-05-07 2010-06-24 Koenig & Bauer Aktiengesellschaft Axialeinstellvorrichtung eines Zylinders und ein Verfahren zur Montage einer Axialeinstellvorrichtung eines Zylinders

Also Published As

Publication number Publication date
EP2006097B1 (fr) 2012-10-24
EP2006097A3 (fr) 2012-01-11
DE102007024767A1 (de) 2008-11-27
DE102007024767B4 (de) 2010-06-24

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