[go: up one dir, main page]

WO2004085154A1 - Cylindre et procede permettant de reduire les vibrations du cylindre - Google Patents

Cylindre et procede permettant de reduire les vibrations du cylindre Download PDF

Info

Publication number
WO2004085154A1
WO2004085154A1 PCT/DE2003/004239 DE0304239W WO2004085154A1 WO 2004085154 A1 WO2004085154 A1 WO 2004085154A1 DE 0304239 W DE0304239 W DE 0304239W WO 2004085154 A1 WO2004085154 A1 WO 2004085154A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
shaft
jacket
rotational frequency
actuator
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.)
Ceased
Application number
PCT/DE2003/004239
Other languages
German (de)
English (en)
Inventor
Erhart Herbert GLÖCKNER
Helmut Hampl
Bernd Ulrich Herbert Keller
Dieter Peter Kilb
Uwe Johann Riedel
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
Priority to AU2003296549A priority Critical patent/AU2003296549A1/en
Publication of WO2004085154A1 publication Critical patent/WO2004085154A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • B41F13/18—Impression cylinders
    • B41F13/187—Impression cylinders for rotogravure
    • 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
    • B41F13/085—Cylinders with means for preventing or damping vibrations or shocks

Definitions

  • the invention relates to a cylinder and a method for reducing a vibration of the cylinder according to the preamble of claim 1 or 14.
  • pairs of cylinders are used which are rotatably arranged with parallel axes and define a nip through which the web of material travels, pressing along the cylinder through a nip line parallel to the axes is exposed, which has a guiding effect on the web or causes the processing.
  • This pressure must be distributed evenly along the length of the nip line, with working rolls to ensure uniform quality of work across the width of the web, and with leading rolls, to avoid unevenness in the roll-to-web slip across the width of the web which can lead to distortion of the railway. Such distortion may be the cause of register errors when printing on the web.
  • the jacket is rotatably mounted in the region of its ends by rolling bearings in adjustable bearing shields.
  • the actuator of the jacket of the impression cylinder is bent and adapted its outer shape to the shape of a hired form cylinder to him.
  • an impression cylinder which cooperates in a gravure printing machine with a forme cylinder.
  • a variable adaptation to the forme cylinder is achieved in that at the end of the counter-pressure cylinder between a fixed shaft and a rotating shell is a linear drive which acts in a vertical radial downward direction against an inner ring of a rolling bearing, while the central region the shell is rotatable but not slidably held on the shaft.
  • the US 36 38 292 A and EP 0741 253 A2 show pressure rollers, which can be acted upon in the interior with pressure medium wheels. These wheels are arranged on a common axis.
  • the US 44 55 727 A and US 33 89450 A disclose rollers which are deflectable in two offset by 90 ° planes by means of adjusting elements arranged in the interior.
  • From DE 199 63 945 C1 is a cylinder with means for generating an inner Voltage of the cylinder and a control unit / controller for driving the means and vibration sensors known to drive the detected by the vibration sensor vibration of the cylinder, the means / actuators.
  • a counter-pressure cylinder which consists of a shaft and a shaft rotatable about the shaft.
  • inflatable chambers are provided between the shaft and the jacket. As the chambers expand upon being pressurized, they cause the jacket to bow.
  • EP 03 31 870 A2 discloses a device for supporting cylinders, wherein pins of a cylinder are mounted in two bearings arranged side by side in the axial direction of the cylinder. By means of Druckzitteizylindern the bearings can be moved individually perpendicular to the axis of rotation, for example, to compensate for a deflection.
  • JP 004-236819 A describes a system for reducing bending vibrations on a shaft, wherein a rotating disk connected to the shaft is acted upon by piezo elements via electromagnets as a function of measured values with forces.
  • WO 97/03832 A1 shows in its discussion of the prior art, various ways by which a deflection or a bending vibration of counter-pressure cylinders can be statically reduced. As a dynamic solution, it proposes to measure occurring vibrations and to use these measured values for controlling and controlling actuators.
  • DE 19930 600 A1 discloses a method for reducing undesired bending vibrations on a rotating component of a coating device with an actuator, wherein the actuator acts on a bearing journal.
  • DE 42 34 928 A1 describes a device for damping vibrations in printing machines, wherein an actuator is associated with rotating parts, which is controlled by a sensor.
  • Registration errors between the center and one edge of the web could be compensated for by means of an inlet roller entangled between two printing gaps. Disadvantage is, however, that thereby on the other side of the paper web, the registration errors are the greater, and that there is a risk of lateral drifting of the paper web.
  • the invention has for its object to reduce vibrations on a rotating cylinder.
  • the object is achieved by the features of claim 1 or 14. While in known methods and devices oscillating balancing forces exerted on the cylinder and mechanical work is done to counteract oscillatory movements of the cylinder, the solution according to the invention prevents from the outset the emergence of unwanted vibration.
  • the resonance frequency of a cylinder depends, among other things, on its internal stress.
  • the internal voltage is changed when the vibration sensor registers an exceeding of an allowed magnitude of the vibrations of the cylinder, which occurs in particular when the rotational frequency of the cylinder or an integer multiple of the rotational frequency corresponds to its resonance frequency, the resonance frequency of the Cylinder moved and in this way suppresses the resonance.
  • the change in the internal tension of the cylinder may be accompanied by a deformation of the cylinder, so that possibly also the means for generating the internal stress perform mechanical work on the cylinder, but the execution of a work is not a prerequisite for the effectiveness of the vibration suppression.
  • the energy required for vibration suppression is therefore negligible compared to conventional, the oscillatory movements actively counteracting systems.
  • the force exerted by the means for generating the internal stress on the cylinder is variable over time, the change in that force is generally not periodic and takes place in periods substantially longer than that Rotation period of the cylinder are.
  • control movements performed by the means for generating the internal stress are much slower than those of conventional, active oscillatory movements counteracting actuators, these means can be simple be constructed and because their control movements are very rare compared to those of the active actuators, they can achieve much higher trouble-free operating times than these.
  • the cylinder comprises a shaft and a shell rotatable about the shaft, which is supported on the shaft in at least three places, wherein the means for generating an internal stress comprise at least one actuator which engages the shell and shaft and which is designed to exert a force acting in the radial direction of the shell force between the jacket and shaft.
  • the means for generating an internal stress comprise at least one actuator which engages the shell and shaft and which is designed to exert a force acting in the radial direction of the shell force between the jacket and shaft.
  • Such a cylinder has the further advantage that it can be adapted to an outer shape of a second cylinder attached to it. This is necessary above all in web-processing devices in which the cylinder and the second cylinder form a clamping gap through which a moving material web is guided. For the processing of the material web over the length of the nip uniform pressure is necessary, which is ensured by the adaptation of the cylinder.
  • At least one of the actuators has a return spring.
  • a force exerted by such a spring on an actuator spring bias causes a retraction of the actuator from the jacket, as soon as the actuator is not acted upon by a straightening force.
  • At least one of the actuators can act on the jacket via a wheel.
  • the wheel ensures a low-friction contact between the stationary actuator and the rotating shell by the wheel is taken from the jacket.
  • an actuator may also comprise a plurality of wheels which may be arranged on a common axis or on staggered axes in the circumferential direction of the shell. These wheels and rollers serve as rolling bearings for the jacket.
  • At least one actuator engages one on the inside of the shell existing race on.
  • the wear between the shell and actuator can be reduced and overall improve the rolling of the shell on the actuators.
  • At least one of the actuators is hydraulically operated.
  • the cylinder may have a hollow shaft and a circuit for a coolant and / or lubricant in which the coolant and / or lubricant flows between shaft and jacket.
  • a coolant and / or lubricant is, for example, cooled thermal oil, with the example, a lubrication of the wheels and rollers of the actuators takes place. At the same time it serves to dissipate heat generated by flexing work and friction on the jacket of the cylinder. Sealing elements on the actuators prevent passage of the coolant and / or lubricant into the interior of the hollow shaft.
  • the shell length is between 1, 5 m to 4 m, so that the cylinder can be used for the processing of material webs with large widths.
  • the cylinder is particularly preferably used in web-processing machines.
  • the cylinder forms a gap with a second cylinder attached thereto, through which a moving material web is guided.
  • the cylinder may be an impression cylinder and the second cylinder may be a forme cylinder, in particular a gravure printing press.
  • Fig. 2 is a schematic front view of the cylinders of the printing unit with exaggerated deflection
  • Fig. 3 is a side view of the printing unit
  • FIG. 4 shows a longitudinal section through an impression cylinder.
  • FIG. 5 shows a first spatial representation of a bearing for the impression cylinder
  • FIG. 6 shows a second spatial representation of a bearing for the impression cylinder
  • Fig. 8 is a side view of the printing unit of Fig. 3;
  • FIG. 11 shows a further longitudinal section through an alternative impression cylinder
  • Fig. 12 is a schematic longitudinal section through the alternative impression cylinder in plan view
  • Fig. 13 is an actuator in a spatial representation; 14 shows an enlarged detail of the longitudinal sections shown in FIGS. 10 and 11;
  • Fig. 16 effects of various deflections of the roller on a picture elements having web
  • Fig. 17 is a schematic representation of a curvature in the direction of a material web having roller.
  • Fig. 1 is a per se known printing unit of a gravure printing machine is shown schematically in cross section. It consists of a first cylinder 06 and a second cylinder 02, which delimit a gap 07 through which a web of paper 04 to be printed is guided as material web 04 and clamped along a clamping line 08 that is perpendicular to the plane of FIG.
  • the second cylinder 02 is provided with an engraved copper surface. It is in the second cylinder 02 to a dipping into a paint box 01 form cylinder 02, which is mounted on here not shown and known per se easily removable in a frame not shown in FIG. 1 and coupled to a drive.
  • a squeegee 03 for doctoring excess, taken from the forme cylinder 02 from the ink fountain 01 color is employed on the forme cylinder 02.
  • the first cylinder 06 is a counter-pressure cylinder 06. It is pressed against the forme cylinder 02 and is carried along by it by friction. Under the effect of the indicated by an arrow contact force and its own weight, the forme cylinder bends in the middle, as shown in Fig. 2 and in the side view of FIG. 3 exaggerated. In order to achieve a uniform pressure over the entire length of the nip line 08, from one end of the cylinder to the other, the impression cylinder 06 of the Bending of the forme cylinder 02 follow, as Fig. 2 further reveals.
  • the impression cylinder 06 is shown in longitudinal section. It is rotatable about a shaft 09 and has a hollow cylindrical shell 11.
  • the jacket 11 has a rubber-coated surface.
  • the shaft 09 comprises two opposite end portions 15 and a central portion 13.
  • Two hollow pins 12 are each rotatably connected to the shell 11 and via bearings, for. B. bearings rotatably supported in a frame of the gravure printing machine.
  • the middle section 13 is over its end sections
  • a bearing bushing 16 which is mounted on the frame on both sides of the impression cylinder 06 to receive the pins 12, is shown in a spatial view in FIGS. 5 and 6 and in a section along the line A - A in FIG. 5 shown.
  • the bearing bushing 16 is shown in a spatial view in FIGS. 5 and 6 and in a section along the line A - A in FIG. 5 shown.
  • FIG. 16 has a recess 17 which accommodates a rolling bearing supporting a pin 12 in a region of large diameter facing the counter-pressure cylinder 06 and serving in a narrower region remote from the impression cylinder 06 for receiving an end portion 15 of the central portion 13 of the shaft 09, as in FIG Fig. 6 can be seen.
  • Two ports 18 serve as inlet and outlet for a coolant or lubricant, which flows through the impression cylinder 06 in a circuit along a gap between the central portion 13 of the shaft 09 on the one hand and the jacket 11 and the pin 12 on the other.
  • the coolant or lubricant is a thermal oil which on the one hand serves to lubricate the impression cylinder 06 and on the other hand dissipates heat generated during the operation of the impression cylinder 06 as a result of flexing work and contributes to the cooling of the impression cylinder 06.
  • plunger 19 in the form of a Brass bolt 19 is provided, which is hydraulically adjustable against the recorded in the bearing bush 16 end pin of the central portion 13 is pressed.
  • two diametrically arranged to the central axis of the shaft 09 screws 21 are provided in the bearing bush 16, which also represent actuators 21. These are each a horizontal force exerted on the end pin.
  • Both the plunger 19 and the screws 21 are provided with sealing elements 22 in the amount of a bore in the wall of the bearing bush 16, in which they are inserted, in order to prevent leakage of the thermal oil from the bearing bush 16.
  • the plunger 19 presses with a force on the end pin and thereby exerts a vertically directed force on the central portion 13 from.
  • This force is transmitted via the rolling bearing 14 on the shell 11, which is thereby brought to the bending form cylinder 02 in abutment.
  • the rolling bearings 14 ensure that, despite the considerable pressure and deformation forces, the casing 11 remains easily rotatable. They are preferably formed as a cylindrical roller bearing 14 to prevent tilting of the shell 11 at the central portion 13, which could affect the rotatability.
  • the width of the oil-flowed space it is seen so dimensioned that it comes at a force under the action of the force applied by the plunger 19, possibly bending of the central portion 13 at no point to a sliding contact between this and the shell 11. In practice, this distance is a few millimeters.
  • the central portion 13 Since the central portion 13 has to transmit only the force applied by the plunger 19 force on the jacket 11, is sufficient in itself a arranged in the middle of the shell 11 bearings 14.
  • two symmetrically arranged to the shell center bearings 14 are provided, the mutual distance about one third of the effective length of the shell 11 corresponds. This allows it Mantle 11, in its lying between the rolling bearings 14 central region optionally a pressure of the forme cylinder 02 yield a little way.
  • a plurality of picture elements are printed on a material web, as shown in Fig. 16, a plurality of picture elements are printed.
  • a plurality of first picture elements are printed side by side in a first printing unit and corresponding second picture elements are printed in a second printing unit in the axial direction.
  • the illustrated roller in particular impression cylinder, belongs to the second printing unit.
  • the position of the middle picture elements is changed relative to the position of the two outer picture elements.
  • the web has at least four groups of pixels, each printed by a printing unit.
  • Fig. 8 shows the effect of the superposition of the force exerted by the plunger 19 vertical force and the force exerted by the adjusting screws 21 horizontal force, shown in Fig. 8 respectively by 19 and 21 designated arrows on the end portion 15 of the shaft 09th Due to the bending of the shell 11 in the direction of the paper web 04, a curvature of the nip line 08 also takes place in the running direction of the paper web 04. Effective there is a displacement of the central region of the shell 11 relative to the end regions in a direction which forms an angle with a plane passing through the axes of the forme cylinder 02 and the shaft 09 or the shell 11. This results in a corresponding curvature of the nip 08.
  • Fig. 10 is a longitudinal section through an alternative cylinder 23, namely an impression cylinder 23, shown in front view
  • Fig. 11 is a longitudinal section through the impression cylinder 23 in plan view.
  • the impression cylinder 23 essentially comprises a hollow shaft 24, a jacket 26, which at its ends via bearings, for. B.
  • Rolling bearing is rotatably supported on the shaft 24, as well as in the shaft 24 and inserted over an annular gap between the shaft 24 and shell 26 away on the shell 26 attacking, as actuators 27; 28; 29 trained means 27; 28; 29 for generating an internal stress of the impression cylinder 23.
  • the jacket 26 is provided with an outer rubber layer.
  • Pins of the shaft 24, which extend beyond the jacket 26 in the axial direction, are in a frame, not shown, of a gravure printing machine in bearings 43; 44, z.
  • first actuators 27; 28; 29 is distinguished between first actuators 27 and second actuators 28 and 29.
  • the upper longitudinal section of FIG. 10 runs in this way by the impression cylinder 23, that it cuts the first actuators 27, while the longitudinal section shown in Fig. 11 below runs through the impression cylinder 23 in such a way that it intersects the second actuators 28 and 29.
  • the actuators 27; 28; 29 are structurally the same; they only differ in their orientation.
  • Fig. 12 is a longitudinal section through the impression cylinder 23 simplified as a schematic schematic diagram shown.
  • the impression cylinder 23 further comprises a vibration sensor 46 and a control unit 47, which communicates with the vibration sensor 46 and which controls the actuators 27 shown by way of example via a hydraulic connection.
  • FIG. 13 is a perspective view of one of the actuators 27; 28; 29, while in Fig. 14, the arrangement of such an actuator 27; 28 or 29 in the impression cylinder 23 as an enlarged partial section of a longitudinal section through the impression cylinder 23 can be seen.
  • FIG. 15 shows a section of the actuator 27 arranged in the impression cylinder 23; 28; 29 along the line C - C shown in FIG. 14.
  • the actuators 27; 28; 29 have an angular shank 31 with integrally formed flange 32 which is inserted with little clearance and with the interposition of a seal 33 between flange 32 and shaft 24 in a window of the shaft 24.
  • the angular shape of the shaft 31 acts as a rotation for the actuator 27; 28; 29.
  • a pressure cylinder 34 is inserted, in the chamber of which a piston 36 is displaceable under the influence of hydraulic fluid supplied via a hydraulic connection 37.
  • the hydraulic port 37 is in one of two on the chamber opening bores 48 of the printing cylinder 34 mounted.
  • the second bore 48 shown as being unloaded in FIG. 15, is in practice provided with a blind plug or with a second hydraulic port 37, from which a pipeline leads to an adjacent actuator.
  • the actuators 27, 28, 29 can be combined into several groups of interconnected, with a same, but acted upon from group to group independently controllable pressure actuators.
  • Each of the actuators 27, 28, 29 is combined with wheels 38 to form a module which can be disassembled as a whole.
  • the piston 36 carries in the illustrated embodiment, two rotatable about a common axis 35 wheels 38, which together form a roller bearing acting as a double role, which roll when extended piston 36 on a retracted between the shell 26 and the shaft 24 raceway 39.
  • the axis 35 is connected to the actuator 27, 28, 29 via a z. B. connected as adjusting bearing 40 formed joint 40.
  • Each actuator 27, 28, 29 carries its own, independently movable axis 35. These axes 35 are not connected to each other.
  • the axle 35 carries two roller bearings 38 mounted on wheels. The circumference of the wheels 38 is completely outside the axis of rotation of the casing 26 in all embodiments.
  • the actuators 27 When the actuators 27 are pressurized, they cause deflection of the central region downward in FIG. 10 and transverse to the plane of FIG. 11. By pressurizing the actuators 28 or 29, a deflection can be made either upward or downward in FIG 11 or, with simultaneous application of the actuators 27, in an oblique to the sectional planes of Fig. 10 and 11 oriented direction can be achieved. It is also possible, the oppositely oriented actuators 27; 28 to act simultaneously, which does not necessarily lead to a deflection of the shell 26, but to a distortion of its cross-section to an ellipse. As can be seen in FIGS.
  • the shaft 24 has on both sides inflows and outflows 41 for a thermal oil, which serves as coolant or lubricant for the impression cylinder 23.
  • the thermal oil flows through lines 42 in the annular gap between the shell 26 and the shaft 24. It flows through the impression cylinder 23 in this gap over its entire length and leaves it via corresponding lines 42 and inflows and outflow 41 on the opposite side , In this way, the wheels 38 of the actuators 27; 28; 29 on the one hand lubricated, on the other hand, the thermal oil performs frictional heat, which arises as a result of performed on an outer rubber layer of the shell 26 flexing work of the shell 26 and due to friction.
  • the jacket 26 of the impression cylinder 23 rotates about the shaft 24.
  • the impression cylinder 23 must be adapted to an outer shape of the forme cylinder 02. This happens with the actuators 27; 28; 29.
  • the pistons 36 are extended, and the wheels 38 press against the shell 26, which leads to a displacement of the shell 26 relative to the shaft 24.
  • the outer shape of the shell 26 can be adapted to a deflection or other irregularity of the shape of the forme cylinder 02 and a desired pressure distribution in the nip line 08 can be realized.
  • the right-angle arrangement of the first actuators 27 and the second actuators 28 and 29 allows a bending of the shell 26 at arbitrary angles with respect to a plane passing through the axes of the impression cylinder 24 and the form cylinder 02 set against him level and thus the setting of a width direction of the Paper web 04 variable path length of the web between two fixed points such as guide rollers on both sides of the gap 07th
  • the jacket 26 rotates in the operation of the impression cylinder 23 about the shaft 24.
  • vibrations of the impression cylinder 23 occur, which are too great strengths can rock when the rotational frequency of the shell 26 or an integral multiple of it corresponds to a resonant frequency of the impression cylinder 23.
  • the strength of these vibrations is measured by the vibration sensor 46 and the result of the measurement is transferred to the control unit 47.
  • the control unit 47 detects an increase in the magnitude of the vibrations above a predetermined threshold indicating the presence of resonance, it controls the actuators 27; 28; 29 hydraulically. When they press against the jacket 26, they cause a deflection of the shell 26 and to a lesser extent, the shaft 24.
  • roller bearings roller bearings, spherical roller bearings

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rotary Presses (AREA)
  • Paper (AREA)

Abstract

L'invention concerne un cylindre comprenant au moins un moyen (27) permettant de produire une tension interne du cylindre, une unité de commande (47) permettant de commander le moyen et un détecteur de vibrations (46). L'unité de commande commande le ou les moyens cités en fonction d'une vibration du cylindre, laquelle vibration est détectée le détecteur.
PCT/DE2003/004239 2003-03-26 2003-12-22 Cylindre et procede permettant de reduire les vibrations du cylindre Ceased WO2004085154A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003296549A AU2003296549A1 (en) 2003-03-26 2003-12-22 Cylinder and method for reducing the vibrations of said cylinder

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2003113442 DE10313442B3 (de) 2003-03-26 2003-03-26 Zylinder
DE10313442.5 2003-03-26

Publications (1)

Publication Number Publication Date
WO2004085154A1 true WO2004085154A1 (fr) 2004-10-07

Family

ID=32319152

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2003/004239 Ceased WO2004085154A1 (fr) 2003-03-26 2003-12-22 Cylindre et procede permettant de reduire les vibrations du cylindre

Country Status (3)

Country Link
AU (1) AU2003296549A1 (fr)
DE (1) DE10313442B3 (fr)
WO (1) WO2004085154A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1820643A2 (fr) 2006-02-16 2007-08-22 Koenig & Bauer Aktiengesellschaft Procédé destiné à la réduction de vibrations

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3389450A (en) 1966-05-20 1968-06-25 Mount Hope Machine Company Inc Non-deflecting roll
US3638292A (en) 1969-10-29 1972-02-01 Vlaanderen Machine Co Van Roll for applying uniform pressure
DE3033230C2 (de) 1980-09-04 1983-08-04 Albert-Frankenthal Ag, 6710 Frankenthal Zylinder für bahnförmiges Material verarbeitende Maschinen
US4455727A (en) 1981-02-13 1984-06-26 Kleinewefers, Jaeggli Textilmaschinen Ag Friction-driven roll for treating web-like intermediate products by compression
DE8808352U1 (de) 1987-08-31 1988-08-11 Sulzer-Escher Wyss GmbH, 7980 Ravensburg Druckwalze
EP0741253A2 (fr) 1995-05-05 1996-11-06 De Pretto-Escher Wyss s.r.l. Cylindre de pression et machine équipée d'un tel cylindre
DE19907079A1 (de) * 1999-02-19 2000-08-24 Voith Sulzer Papiertech Patent Verfahren und Vorrichtung zum Vermeiden von Kontaktschwingungen rotierender Walzen in einer Maschine zur Herstellung oder/und Behandlung einer Materialbahn
DE19963945C1 (de) 1999-12-31 2001-07-19 Koenig & Bauer Ag Verfahren und Anordnung zur Kompensation von Schwingungen rotierender Bauteile
DE10023205A1 (de) 2000-05-12 2001-11-22 Koenig & Bauer Ag Zylinder einer Rotationsdruckmaschine
DE10039761A1 (de) * 2000-08-16 2002-02-28 Volkswagen Ag Verfahren zur Reduzierung von Schwingungen
US6500304B1 (en) * 1998-08-14 2002-12-31 Metso Paper, Inc. Method and device for changing the natural frequency of a nip roll construction in a paper or board machine

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3389450A (en) 1966-05-20 1968-06-25 Mount Hope Machine Company Inc Non-deflecting roll
US3638292A (en) 1969-10-29 1972-02-01 Vlaanderen Machine Co Van Roll for applying uniform pressure
DE3033230C2 (de) 1980-09-04 1983-08-04 Albert-Frankenthal Ag, 6710 Frankenthal Zylinder für bahnförmiges Material verarbeitende Maschinen
US4455727A (en) 1981-02-13 1984-06-26 Kleinewefers, Jaeggli Textilmaschinen Ag Friction-driven roll for treating web-like intermediate products by compression
DE8808352U1 (de) 1987-08-31 1988-08-11 Sulzer-Escher Wyss GmbH, 7980 Ravensburg Druckwalze
EP0741253A2 (fr) 1995-05-05 1996-11-06 De Pretto-Escher Wyss s.r.l. Cylindre de pression et machine équipée d'un tel cylindre
US6500304B1 (en) * 1998-08-14 2002-12-31 Metso Paper, Inc. Method and device for changing the natural frequency of a nip roll construction in a paper or board machine
DE19907079A1 (de) * 1999-02-19 2000-08-24 Voith Sulzer Papiertech Patent Verfahren und Vorrichtung zum Vermeiden von Kontaktschwingungen rotierender Walzen in einer Maschine zur Herstellung oder/und Behandlung einer Materialbahn
DE19963945C1 (de) 1999-12-31 2001-07-19 Koenig & Bauer Ag Verfahren und Anordnung zur Kompensation von Schwingungen rotierender Bauteile
DE10023205A1 (de) 2000-05-12 2001-11-22 Koenig & Bauer Ag Zylinder einer Rotationsdruckmaschine
DE10039761A1 (de) * 2000-08-16 2002-02-28 Volkswagen Ag Verfahren zur Reduzierung von Schwingungen

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1820643A2 (fr) 2006-02-16 2007-08-22 Koenig & Bauer Aktiengesellschaft Procédé destiné à la réduction de vibrations
DE102006007179A1 (de) * 2006-02-16 2007-08-30 Koenig & Bauer Aktiengesellschaft Verfahren zur Schwingungsreduktion
EP1820643A3 (fr) * 2006-02-16 2010-09-29 Koenig & Bauer Aktiengesellschaft Procédé destiné à la réduction de vibrations

Also Published As

Publication number Publication date
DE10313442B3 (de) 2004-06-17
AU2003296549A1 (en) 2004-10-18

Similar Documents

Publication Publication Date Title
DE69818926T2 (de) Druckmaschine mit selbstangetriebenen, fliegend gelagerten Zylindern
DE102007052761B4 (de) Anilox-Druckwerk
EP0047435B1 (fr) Cylindre pour machines à travailler des matériaux en forme d'une bande
DE3033230C2 (de) Zylinder für bahnförmiges Material verarbeitende Maschinen
DE3025799C2 (de) Preßwalze, deren Durchbiegung einstellbar ist
DE68920395T2 (de) Druckmaschinenwalzen.
EP0258478A1 (fr) Rouleau à compensation de déflexion
DE3529680C2 (fr)
DE10313444B4 (de) Druckwerk einer Tiefdruckmaschine
DE2333731C3 (de) Walze zur Ausübung eines gleichmäßigen Drucks
DE102006042959B4 (de) Verfahren und Vorrichtung zum Reduzieren von Schwingungen eines rotierenden Zylinders einer Druckmaschine
EP0534160B1 (fr) Machine à imprimer rotative
EP1280666B1 (fr) Mecanisme permettant d'ajuster l'ecart entre les axes de rotation de cylindres
AT392661B (de) Presswalze, deren durchbiegung einstellbar ist
EP0267504B1 (fr) Palier pour rouleaux applicateurs à mouvement de va-et-vient dans les machines d'impression
CH684070A5 (de) Formzylinder einer Rotationsdruckmaschine.
DE102005014255A1 (de) Lagerung von Walzen und/oder Zylindern in Druckwerken von Rotationsdruckmaschinen
DE10313443B4 (de) Zylinder mit Welle und drehbarem Mantel
WO2004085154A1 (fr) Cylindre et procede permettant de reduire les vibrations du cylindre
DE19882190B4 (de) Verfahren und Vorrichtung zum Verhindern von Walzenvibrationen in einem Filmtransferbeschichter
EP0791105B1 (fr) Appareillage de couchage
WO1991005913A1 (fr) Calandre
EP1707361B1 (fr) Rouleau applicateur pour un groupe d'impression offset
EP1518674B1 (fr) Rouleau d'encrage ou mouillage d'une machine d'impression
DE9105073U1 (de) Durchbiegungseinstellwalze

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BW BY BZ CA CH CN CO CR CU CZ DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): BW GH GM KE LS MW MZ SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LU MC NL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
122 Ep: pct application non-entry in european phase
NENP Non-entry into the national phase

Ref country code: JP

WWW Wipo information: withdrawn in national office

Country of ref document: JP