EP0169475B1 - Cylinder for machines processing web-like material - Google Patents

Cylinder for machines processing web-like material Download PDF

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Publication number
EP0169475B1
EP0169475B1 EP85108865A EP85108865A EP0169475B1 EP 0169475 B1 EP0169475 B1 EP 0169475B1 EP 85108865 A EP85108865 A EP 85108865A EP 85108865 A EP85108865 A EP 85108865A EP 0169475 B1 EP0169475 B1 EP 0169475B1
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EP
European Patent Office
Prior art keywords
spindle
cylinder
casing
adjacent
shell
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EP85108865A
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German (de)
French (fr)
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EP0169475A2 (en
EP0169475A3 (en
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Peter Dipl.-Ing. Maier
Arnold Niedermaier
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Albert Frankenthal AG
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Albert Frankenthal AG
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    • 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
    • B41F13/22—Means for cooling or heating forme or impression cylinders

Definitions

  • the invention relates to a cylinder for web-like material processing machines, in particular a impression roller for a rotogravure printing machine, which is accommodated in the area of its ends in adjustable end shields and has a tubular jacket provided with a rubber cover, which is arranged in the direction of rotation, one with respect to the jacket inner diameter penetrated smaller outside diameter, connected to it via at least one support bearing arranged symmetrically to the jacket center and coaxially to the jacket axis and independently of the spindle passing through it is mounted on the side bearing plates by swivel bearings arranged in the region of its ends, on each of which one on the adjacent, the Sheath protruding end of the spindle engaging actuator is supported with respect to the spindle in the radial direction.
  • a cylinder of the type mentioned is known from DE-OS 30 33 230.
  • An arrangement of this type has proven itself in itself.
  • Experience has shown, however, that flexing within the rubber cover can lead to a high rubber core temperature, which is above the permissible limit in particular at high speeds and therefore has a negative effect on the service life of the rubber cover.
  • Remedy could possibly be a reduction in line pressure and thus a reduction in flexing work.
  • this is normally not possible for printing reasons, since a minimum line pressure is required even when using electrostatic printing aids or the like.
  • there is therefore a restriction of the permissible speed which is below the speed required today of 50,000 revolutions per hour.
  • the spindle in the region of each support bearing can have at least one bore opening in front of or behind the respectively assigned support bearing into the annular space between the spindle and the jacket and forming the bypass line.
  • This is a particularly simple design of the bypass line. This can be an oblique through hole or an angled hole.
  • a further, particularly expedient further development of the superordinate measures can consist in the fact that the actuating elements each have a plunger engaging in the radial bore of the respectively associated closure cap, which plunger abuts against the associated spindle end and is supported with its end facing away from the spindle on the piston rod of one on the adjacent bearing plate Cylinder-piston unit is present.
  • the only figure of the drawing shows a longitudinal section through an impression roller according to the invention for a gravure printing machine, which is included in a cooling circuit.
  • the impression roller on which the drawing is based consists of a tubular jacket 2 provided with a rubber cover 1, which is provided in the region of its ends with lateral bearing supports 3 which have a bore which is coaxial to the jacket bore and are rotatably mounted on side bearing plates 5 via pivot bearings 4.
  • Lifting cylinders 6 act on the end shields 5, by means of which the impression roller can be placed or pressed against the respectively assigned cylinder or lifted off the latter.
  • a spindle 7 extending through it and rotating in the direction of rotation, the outside diameter of which is smaller than the inside diameter of the jacket bore or the bore of the bearing connection piece 3.
  • the spindle 7 standing in the direction of rotation is connected to the jacket 2 by support bearings 8 arranged symmetrically to the jacket center and coaxially to the jacket axis.
  • the support bearings 8 are fixed on the one hand by a collar on the spindle side and on the other hand by a bushing 10 which is provided with a split clamping ring 9 and is clamped onto the spindle 7.
  • the spindle 7 is longer than the jacket 2 provided with the lateral bearing neck 3, so that the ends of the spindle 7 protrude beyond the ends of the bearing journal 3 and thus of the jacket 2.
  • To accomplish a bending compensation are provided on the spindle ends protruding from the jacket 2, which can be actuated in the radial direction with respect to the spindle or jacket axis and which are firmly connected to the adjacent bearing plate 5, as indicated in the drawing by a screw connection is.
  • the annular space 12 between the jacket 2 and the spindle 7 is included in a coolant circuit which is supplied with a cooling medium, expediently oil, via a cooling unit 13.
  • a cooling medium expediently oil
  • the ends of the spindle 7 projecting beyond the lateral bearing pins 3 are encompassed by a respectively associated closure cap 14.
  • the caps 14 are provided with connection bores 15 for the flow load 16 and the return load 17 of the coolant circuit leading over the cooling unit 13.
  • the caps 14 are screwed to the adjacent bearing plate 5.
  • the closure caps 14 can be provided with inner thrust lugs 18.
  • a movement seal in the form of a sealing ring 19 is provided between the mutually facing end faces of the closure caps 14 and the respectively adjacent journal 3.
  • a bypass line 20 is provided in the region of each support bearing 8.
  • the spindle 7 is provided with an angled bore for this purpose, which opens into the annular space 12 in front of and behind the respectively associated support bearing 8.
  • an oblique through hole could also be provided to form the bypass line 20, as indicated in the drawing by dashed lines.
  • the lines for forming the forward branch 16 and the return branch 17 can be designed as tubes or hoses.
  • the line forming the return branch 17 opens into a reservoir 21 into which the suction nozzle of a pump 22 which acts on the cooling unit 13 is immersed.
  • An operating monitoring device for example in the form of a sight glass, etc., is assigned to the pump 22. It would also be conceivable to design the operation monitoring device 23 in such a way that, if there is no pump operation, the impression roller cannot be started up or automatically brought into the pressure shutdown.
  • the temperature in the area of the forward branch 16 is kept constant at an adjustable value.
  • the oil temperature in the forward flow 16 is measured by means of a sensor 24 and a controller 26, which interacts with an adjustable setpoint generator 25, is fed in, by means of which the flow of cooling water through the cooling unit 13 designed as a heat exchanger can be regulated.
  • the cooling water line 27 of the cooling unit 13 is provided with a shut-off element 28 which can be adjusted by the controller 26.
  • the cover caps 14 are each provided with a radial bore 29 through which the adjusting element 11, which is associated with the spindle end encompassed thereby, engages in a plunger-shaped manner.
  • one or more circumferential sealing rings 30 are provided in the area of the radial bores 29.
  • the piston rod of a cylinder-piston unit forming the relevant actuator 11 could engage directly in the associated radial bore 29 of the adjacent cover cap 14. With an arrangement of this type, however, it would be necessary to disengage the piston rod from the radial bore 14 in the event of removal of the cover cap 14.
  • the actuators 11 therefore consist of plungers 32 engaging in the radial bore 29 of the two cover caps 14 and cylinder piston assemblies 34 assigned to them, the piston rod 31 of which ends radially outside the adjacent cover cap 14 and is in operative connection with the one in each case Radial bore 29 engaging plunger 32, which rests with its radially inner end on the spindle 7 and with its radially outer end on the associated piston rod 31.
  • the plungers 32 separated from the cylinder-piston assemblies 34 can accordingly remain in their engagement position in the respectively assigned radial bore 29 even in the event of / removal of the respectively assigned cover cap 14.
  • the tappets 32 are provided on the spindle side with a spherical end face which rests on a flat 33 of the respectively associated spindle end.
  • the support bearings 8 are designed as roller bearings.
  • the support bearings 8 are designed as slide bearings which, due to the hydrodynamic lubrication conditions during operation, are subject to particularly low friction and have excellent damping properties.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Nitrogen And Oxygen Or Sulfur-Condensed Heterocyclic Ring Systems (AREA)
  • Soil Working Implements (AREA)
  • Lubricants (AREA)
  • Electron Beam Exposure (AREA)
  • Processing And Handling Of Plastics And Other Materials For Molding In General (AREA)
  • Actuator (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Rotary Presses (AREA)
  • Preliminary Treatment Of Fibers (AREA)
  • Treatment Of Fiber Materials (AREA)
  • Machines For Manufacturing Corrugated Board In Mechanical Paper-Making Processes (AREA)
  • Fluid-Damping Devices (AREA)
  • Superconductors And Manufacturing Methods Therefor (AREA)
  • Extrusion Of Metal (AREA)
  • Paper (AREA)
  • Chemical And Physical Treatments For Wood And The Like (AREA)

Abstract

The cylinder has a shell (2) provided with a rubber coating (1) and a spindle (7) which penetrates said shell with clearance. The shell (2) is mounted rotatably in lateral bearing plates (5) independently of the spindle (7) and the ends of the spindle (7) project from the shell (2) and can be charged by respectively assigned actuators (11) to bring about a bending compensation. A long service life of the rubber coating (1) can be achieved even at high rotational speeds of the shell (2) in that the annular space (12) between the shell (2) and the spindle (7) is incorporated in a cooling circuit which passes over a cooling unit (13). For this purpose, the ends of the spindle (7) are enclosed in each case by a closure cap (14) which is penetrated by the actuator (11), is attached to the adjacent bearing plate (5) and is sealed off against the rotating shell (2) and which is provided with connections (15) for the forward branch (16) or return branch (17) of the coolant circuit. In order to guarantee a sufficient throughput of coolant through the annular space (12), a bypass line (20) is provided in each case in the region of the support bearings (8) arranged between the shell (2) and the spindle (7). <IMAGE>

Description

Die Erfindung betrifft einen Zylinder für bahnförmiges Material verarbeitende Maschinen, insbesondere einen Presseur für eine Tiefdruckmaschine, der im Bereich seiner Enden in verstellbaren Lagerschilden aufgenommen ist und einen rohrförmigen, mit einem Gummibezug versehenen Mantel aufweist, der von einer in Drehrichtung stehenden, einen gegenüber dem Mantelinnendurchmesser kleineren Außendurchmesser aufweisenden Spindel durchsetzt, hiermit über mindestens ein symmetrisch zur Mantelmitte und koaxial zur Mantelachse angeordnetes Stützlager verbunden und unabhängig von der ihn durchsetzenden Spindel durch im Bereich seiner Enden angeordnete Schwenklager an den seitlichen Lagerschilden gelagert ist, an denen jeweils ein am jeweils benachbarten, den Mantel überragenden Ende der Spindel angreifendes, bezüglich der Spindel in radialer Richtung betätigbares Stellorgan abgestützt ist.The invention relates to a cylinder for web-like material processing machines, in particular a impression roller for a rotogravure printing machine, which is accommodated in the area of its ends in adjustable end shields and has a tubular jacket provided with a rubber cover, which is arranged in the direction of rotation, one with respect to the jacket inner diameter penetrated smaller outside diameter, connected to it via at least one support bearing arranged symmetrically to the jacket center and coaxially to the jacket axis and independently of the spindle passing through it is mounted on the side bearing plates by swivel bearings arranged in the region of its ends, on each of which one on the adjacent, the Sheath protruding end of the spindle engaging actuator is supported with respect to the spindle in the radial direction.

Ein Zylinder eingangs erwähnter Art ist aus der DE-OS 30 33 230 bekannt. Eine Anordnung dieser Art hat sich an sich bewährt. Die Erfahrung hat jedoch gezeigt, daß die Walkarbeit innerhalb des Gummibezugs zu einer hohen Gummikerntemperatur führen kann, die insbesondere bei hohen Drehzahlen oberhalb der zulässigen Grenze liegt und daher die Lebensdauer des Gummibezugs negativ beeinflußt. Abhilfe könnte hier u.U. eine Absenkung des Liniendrucks und damit eine Verminderung der Walkarbeit bringen. Dies ist jedoch normalerweise aus drucktechnischen Gründen nicht möglich, da auch bei Verwendung elektrostatischer Druckhilfen oder dergleichen ein Mindestliniendruck benötigt wird. Bei der bekannten Anordnung ergibt sich daher eine Beschränkung der zulässigen Drehzahl, die unterhalb der heute geforderten Drehzahl von 50,000 Umdrehungen pro Stunde liegt.A cylinder of the type mentioned is known from DE-OS 30 33 230. An arrangement of this type has proven itself in itself. Experience has shown, however, that flexing within the rubber cover can lead to a high rubber core temperature, which is above the permissible limit in particular at high speeds and therefore has a negative effect on the service life of the rubber cover. Remedy could possibly be a reduction in line pressure and thus a reduction in flexing work. However, this is normally not possible for printing reasons, since a minimum line pressure is required even when using electrostatic printing aids or the like. In the known arrangement there is therefore a restriction of the permissible speed, which is below the speed required today of 50,000 revolutions per hour.

Hiervon ausgehend ist es daher die Aufgabe der vorliegenden Erfindung, unter Vermeidung der Nachteile der bekannten Anordnungen mit einfachen und kostengünstigen Mitteln eine Vorichtung eingangs erwähnter Art so zu verbessern, daß auch bei vergleichsweise hohen Drehzahlen eine hohe Lebensdauer des Gummibezugs erreicht werden kann.Proceeding from this, it is therefore the object of the present invention, while avoiding the disadvantages of the known arrangements, to improve a device of the type mentioned at the beginning with simple and inexpensive means in such a way that a long service life of the rubber cover can be achieved even at comparatively high speeds.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß die den Mantel übergreifenden Enden der Spindel durch jeweils eine Verschlußkappe umfaßt sind, die am jeweils benachbarten Lagerschild befestigt und gegenüber dem umlaufenden Mantel durch eine Bewegungsdichtung abgedichtet ist, daß die Stellorgane durch eine mit/mindestens einem Dichtring versehene Radialbohrung der jeweils zugeordneten Verschlußkappe hindurchgreifen, daß die beiden Verschlußkappen mit Anschlüssen für den Vorlaufast bzw. Rücklaufast eines über ein Kühlaggregat führenden Kühlmittelkreislauf versehen sind und daß im Bereich jedes Stützlagers eine dieses umgehende Umgehungsleitung vorgesehen ist.This object is achieved in that the ends of the spindle overlapping the casing are each encompassed by a closure cap which is fastened to the adjacent bearing plate and is sealed off from the circumferential casing by a movement seal in that the actuators are provided with / with at least one sealing ring Reach through the radial bore of the respectively assigned sealing cap, that the two sealing caps are provided with connections for the flow load or return flow of a coolant circuit leading via a cooling unit, and that a bypass line is provided in the area of each support bearing.

Diese Maßnahemn ermöglichen in vorteilhafter Weise trotz des erforderlichen Kraftangriffs an den aus dem Mantel herausgeführten Spindelenden eine Beaufschlagung des Ringraums zwischen Mantel und Spindel mit einem über ein Kühlaggregat geführten Kühlmedium, vorzugsweise Kühlöl, und ergeben somit eine Innenkühlung des mit einem Gummibezug versehenen Mantels. Die vorteilhafte Folge davon ist, daß hierbei dem durch die Walkarbeit aufgeheizten Gummibezug soviel Wärme entzogen werden kann, daß seine Temperatur auch bei hohen Drehzahlen in zulässigen Grenzen bleibt, was sich vorteilhaft auf die Lebensdauer des Gummibezugs und die erzielbare Druckqualität auswirkt. Das den Ringraum durchströmende Öl bewirkt in vorteilhafter Weise gleichzeitig eine zuverlässige Schmierung und Kühlung der Stützlager. Hierdurch ist es möglich, zur Bildung der Stützlager Gleitlager vorzusehen, die aufgrund der hierbei sich ausbildenden hydrodynamischen Schmierung während des Betriebs sehr geringe Reibwerte aufweisen und ausgezeichnete Dämpfungseigenschaften besitzen. Außerdem wird durch das Öl auch eine lokale Erwärmung des Mantels aufgrund der Lagerreibung verhindert. Die Umgehungsleitung im Bereich jedes Stützlagers stellt sicher, daß der erzielbare Kühlmitteldurchsatz durch den Ringraum zwischen Mantel und Spindel von dem in der Regel sehr geringen Durchsatz durch das Stützlager unabhängig ist.These measures advantageously enable the annular space between the jacket and the spindle to be acted upon by a cooling medium, preferably cooling oil, which is guided via a cooling unit, despite the required force application to the spindle ends led out of the jacket, and thus result in internal cooling of the jacket provided with a rubber cover. The advantageous consequence of this is that so much heat can be extracted from the rubber covering heated by the flexing work that its temperature remains within permissible limits even at high speeds, which has an advantageous effect on the service life of the rubber covering and the print quality that can be achieved. The oil flowing through the annular space advantageously simultaneously results in reliable lubrication and cooling of the support bearings. As a result, it is possible to provide plain bearings for the formation of the support bearings which, due to the hydrodynamic lubrication that is formed, have very low friction values during operation and have excellent damping properties. The oil also prevents local heating of the jacket due to bearing friction. The bypass line in the region of each support bearing ensures that the coolant throughput that can be achieved through the annular space between the casing and the spindle is independent of the generally very low throughput through the support bearing.

Es wurde auch schon vorgeschlagen (DE-PS 31 14 731), den Ringraum zwischen Mantel und Spindel mit einer Ölfüllung zu versehen. Hierbei handelt es sich jedoch um eine stehende Ölfüllung, die lediglich dazu dient, einen Wärmeausgleich herbeizuführen und eine/lokale Erwärmung des Mantels zu verhindern. Eine Kühlung des Mantels und damit des Mantelbezugs ist hiermit nicht möglich.It has also been proposed (DE-PS 31 14 731) to provide the annular space between the jacket and the spindle with an oil filling. However, this is a standing oil filling that only serves to bring about heat balance and to prevent local heating of the jacket. It is not possible to cool the jacket and thus the jacket cover.

In vorteilhafter Ausgestaltung der übergeordneten Maßnahmen kann die Spindel im Bereich jedes Stützlagers mindestens eine vor bzw. hinter dem jeweils zugeordneten Stützlager in den Ringraum zwischen Spindel und Mantel ausmündende, die Umgehungsleitung bildende Bohrung aufweisen. Hierbei handelt es sich um eine besonders einfache Ausgestaltung der Umgehungsleitung. Dabei kann es sich um eine schräge Durchgangsbohrung oder um eine abgewinkelte Bohrung handeln.In an advantageous embodiment of the superordinate measures, the spindle in the region of each support bearing can have at least one bore opening in front of or behind the respectively assigned support bearing into the annular space between the spindle and the jacket and forming the bypass line. This is a particularly simple design of the bypass line. This can be an oblique through hole or an angled hole.

Eine weitere, besonders zweckmäßige Fortbildung der übergeordneten Maßnahmen kann darin bestehen, daß die Stellorgane jeweils einen in die Radialbohrung der jeweils zugeordneten Verschlußkappe eingreifenden, am zugeordneten Spindelende anliegenden Stößel aufweisen, der mit seinem von der Spindel abgewandten Ende an der Kolbenstange eines am benachbarten Lagerschild abgestützten Zylinder-Kolbenaggregats anliegt. Diese Maßnahmen ermöglichen in vorteilhafter Weise eine einfache Demontage der Verschlußkappen, da der von der Kolbenstange getrennte Stößel dabei nicht aus derzugeordneten Radialbohrung herausgenommen werden muß. Es entfällt daher auch ein anschließendes In-Stellung-Bringen des Stößels.A further, particularly expedient further development of the superordinate measures can consist in the fact that the actuating elements each have a plunger engaging in the radial bore of the respectively associated closure cap, which plunger abuts against the associated spindle end and is supported with its end facing away from the spindle on the piston rod of one on the adjacent bearing plate Cylinder-piston unit is present. These measures advantageously enable simple removal of the caps, since the plunger, which is separate from the piston rod, does not have to be removed from the associated radial bore. There is therefore no need to subsequently bring the plunger into position.

Die vorstehend genannten Maßnahmen wirken sich demnach nicht nur günstig auf den Montageaufwand, sondern auch auf die Lebensdauer der den Stellorganen zugeordneten, verschlußkappenseitigen Abdichtung aus.The above measures work accordingly not only favorably on the assembly effort, but also on the life of the sealing cap-side seal associated with the actuators.

Weitere zweckmäßige Fortbildungen und vorteilhafte Ausgestaltungen der übergeordneten Maßnahmen ergeben sich aus der nachstehenden Beschreibung eines Ausführungsbeispiels anhand der Zeichnung in Verbindung mit den restlichen Unteransprüchen.Further expedient further developments and advantageous refinements of the superordinate measures result from the following description of an exemplary embodiment with reference to the drawing in conjunction with the remaining subclaims.

Die einzige Figur der Zeichnung zeigt einen Längsschnitt durch einen in einen Kühlkreislauf einbezogenen, erfindungsgemäßen Presseur für eine Tiefdruckmaschine.The only figure of the drawing shows a longitudinal section through an impression roller according to the invention for a gravure printing machine, which is included in a cooling circuit.

Der grundsätzliche Aufbau und die Wirkungsweise von Tiefdruckmaschinen sind an sich bekannt und bedürften daher im vorliegenden Zusammenhang keiner näheren Erläuterung mehr. Der der Zeichnung zugrundeliegende Presseur besteht aus einem mit einem Gummibezug 1 versehenen, rohrförmigen Mantel 2, der im Bereich seiner Enden mit seitlichen Lagerstutzen 3 versehen ist, die eine zur Mantelbohrung koaxiale Bohrung aufweisen und über Schwenklager 4 an seitlichen Lagerschilden 5 drehbar gelagert sind. An den Lagerschilden 5 greifen hier nicht näher dargestellte Hubzylinder 6 an, mit Hilfe derer der Presseur an den jeweils zugeordneten Zylinder angestellt bzw. angepreßt bzw. von diesem abgehoben werden kann. Innerhalb des rohrförmigen Mantels 2 ist eine ihn durchsetzende, in Drehrichtung stehende Spindel 7 vorgesehen, deren Außendurchmesser kleiner als der Innendurchmesser der Mantelbohrung bzw. der Bohrung der Lagerstutzen 3 ist. Die in Drehrichtung stehende Spindel 7 ist durch symmetrisch zur Mantelmitte und koaxial zur Mantelachse angeordnete Stützlager 8 mit dem Mantel 2 verbunden. Die Stützlager 8 sind einerseits durch einen spindelseitigen Bund und andererseits durch eine mit einem geteilten Klemmring 9 versehene, auf die Spindel 7 aufgeklemmte Büchse 10 fixiert.The basic structure and mode of operation of gravure printing machines are known per se and therefore do not require any further explanation in the present context. The impression roller on which the drawing is based consists of a tubular jacket 2 provided with a rubber cover 1, which is provided in the region of its ends with lateral bearing supports 3 which have a bore which is coaxial to the jacket bore and are rotatably mounted on side bearing plates 5 via pivot bearings 4. Lifting cylinders 6 (not shown in more detail here) act on the end shields 5, by means of which the impression roller can be placed or pressed against the respectively assigned cylinder or lifted off the latter. Provided within the tubular jacket 2 is a spindle 7 extending through it and rotating in the direction of rotation, the outside diameter of which is smaller than the inside diameter of the jacket bore or the bore of the bearing connection piece 3. The spindle 7 standing in the direction of rotation is connected to the jacket 2 by support bearings 8 arranged symmetrically to the jacket center and coaxially to the jacket axis. The support bearings 8 are fixed on the one hand by a collar on the spindle side and on the other hand by a bushing 10 which is provided with a split clamping ring 9 and is clamped onto the spindle 7.

Die Spindel 7 ist länger als der mit den seitlichen Lagerstutzen 3 versehene Mantel 2, so daß die Enden der Spindel 7 über die Enden der Lagerzapfen 3 und damit des Mantels 2 auskragen. Zur Bewerkstelligung eines Biegeausgleichs sind an den aus dem Mantel 2 herausragenden Spindelenden angreifende, bezüglich der Spindel- bzw. Mantelachse in radialer Richtung betätigbare Stellorgane 11 vorgesehen, die mit dem jeweils benachbarten Lagerschild 5 fest verbunden sind, wie in der Zeichnung durch eine Schraubverbindung scheamtisch angedeutet ist.The spindle 7 is longer than the jacket 2 provided with the lateral bearing neck 3, so that the ends of the spindle 7 protrude beyond the ends of the bearing journal 3 and thus of the jacket 2. To accomplish a bending compensation are provided on the spindle ends protruding from the jacket 2, which can be actuated in the radial direction with respect to the spindle or jacket axis and which are firmly connected to the adjacent bearing plate 5, as indicated in the drawing by a screw connection is.

Im Gummibezug 1 kommt es infolge der bei jeder Umdrehung des Presseurs sich ergebenden Walkarbeit zu einer starken Wärmeentwicklung. Um die Oberflächentemperatur und Kerntemperatur des Gummibezugs 1 dennoch in zulässigen Grenzen zu halten, wird der Ringraum 12 zwischen dem Mantel 2 und der Spindel 7 in einen über ein Kühlaggregat 13 führenden, mit einem Kühlmedium, zweckmäßig Öl, beaufschlagten Kühlmittelkreislauf einbezogen. Das durch den Ringraum 12 hindurchgeführte, diesen ausfüllendeKühlöl erfährt aufgrund der Rotation des Mantels 2 eine starke Verwirbelung, was einen zuverlässigen Wärmeübergang und einen starken Temperaturausgleich auch über der Länge des Presseurs bewirkt. Zur Einbeziehung des Ringraums 12 in den Kühlmittelkreislauf sind die über die seitlichen Lagerzapfen 3 auskragenden Enden der Spindel 7 von einer jeweils zugeordneten Verschlußkappe 14 umfaßt. Die Verschlußkappen 14 sind mit Anschlußbohrungen 15 für den Vorlaufast 16 bzw. den Rücklaufast 17 des über das Kühlaggregat 13 führenden Kühlmittelkreislaufs versehen. Die Verschlußkappen 14 sind mit dem jeweils benachbarten Lagerschild 5 verschraubt. Zur Fixierung der Spindel 7 in axialer Richtung können die Verschlußkappen 14 mit inneren Anlaufnasen 18 versehen sein. Zur Abdichtung der Schwenklager 4 gegen den Innenraum der Verschlußkappen 14 ist jeweils eine zwischen den einander zugewandten Stirnseiten der Verschlußkappen 14 und des jeweils benachbarten Lagerzapfens 3 angeordnete Bewegungsdichtung in Form eines Simmerrings 19 vorgesehen.In the rubber cover 1, a lot of heat is generated as a result of the flexing work that occurs with each revolution of the impression roller. In order to keep the surface temperature and core temperature of the rubber cover 1 within permissible limits, the annular space 12 between the jacket 2 and the spindle 7 is included in a coolant circuit which is supplied with a cooling medium, expediently oil, via a cooling unit 13. The cooling oil that passes through the annular space 12 and fills it experiences a strong swirling due to the rotation of the jacket 2, which causes a reliable heat transfer and a strong temperature compensation even over the length of the impression roller. In order to include the annular space 12 in the coolant circuit, the ends of the spindle 7 projecting beyond the lateral bearing pins 3 are encompassed by a respectively associated closure cap 14. The caps 14 are provided with connection bores 15 for the flow load 16 and the return load 17 of the coolant circuit leading over the cooling unit 13. The caps 14 are screwed to the adjacent bearing plate 5. To fix the spindle 7 in the axial direction, the closure caps 14 can be provided with inner thrust lugs 18. To seal the pivot bearing 4 against the interior of the closure caps 14, a movement seal in the form of a sealing ring 19 is provided between the mutually facing end faces of the closure caps 14 and the respectively adjacent journal 3.

Da die rotierenden Stützlager 8 den Durchsatz einer größeren Ölmenge behindern können ist im Bereich jedes Stützlagers 8 eine Umgehungsleitung 20 vorgesehen. Im dargestellten Ausführungsbeispiel ist die Spindel 7 hierzu mit einer abgewinkelten Bohrung versehen, die vor und hinter dem jeweils zugeordneten Stützlager 8 in den Ringraum 12 ausmündet. Anstelle der abgewinkelten Bohrung könnte zur Bildung der Umgehungsleitung 20 auch eine schräge Durchgangsbohrung vorgesehen sein, wie in der Zeichnung mit gestrichelten Linien angedeutet ist.Since the rotating support bearings 8 can hinder the throughput of a larger amount of oil, a bypass line 20 is provided in the region of each support bearing 8. In the exemplary embodiment shown, the spindle 7 is provided with an angled bore for this purpose, which opens into the annular space 12 in front of and behind the respectively associated support bearing 8. Instead of the angled hole, an oblique through hole could also be provided to form the bypass line 20, as indicated in the drawing by dashed lines.

Die Leitungen zur Bildung des Vorlaufasts 16 und des Rücklaufasts 17 können als Rohre oder Schläuche ausgebildet sein. Die den Rücklaufast 17 bildende Leitung mündet in ein Reservoir 21, in das der Saugstutzen einer das Kühlaggregat 13 beaufschlagenden Pumpe 22 eintaucht. Der Pumpe 22 ist eine Betriebsüberwachungseinrichtung etwa in Form eines Sichtglases etc. zugeordnet. Es wäre auch denkbar, die Betriebsüberwachungseinrichtung 23 so auszubilden, daß bei fehlendem Pumpenbetrieb der Presseur nicht in Betrieb genommen werden kann bzw. automatisch in die Druckabstellung gebracht wird. Zur Bewerkstelligung konstanter Betriebsverhältnisse wird die Temperatur im Bereich des Vorlaufasts 16 auf einem einstellbaren Wert konstant gehalten. Hierzu wird die Öltemperatur im Vorlaufast 16 mittels eines Fühlers 24 gemessen und einem mit einem einstellbaren Sollwertgeber 25 zusammenwirkenden Regler 26 aufgegeben, mittels dessen der Durchfluß von Kühlwasser durch das als Wärmetauscher ausgebildete Kühlaggregat 13 regelbar ist. Hierzu ist die Kühlwasserleitung 27 des Kühlaggregats 13 mit einem vom Regler 26 einstellbaren Absperrorgan 28 versehen.The lines for forming the forward branch 16 and the return branch 17 can be designed as tubes or hoses. The line forming the return branch 17 opens into a reservoir 21 into which the suction nozzle of a pump 22 which acts on the cooling unit 13 is immersed. An operating monitoring device, for example in the form of a sight glass, etc., is assigned to the pump 22. It would also be conceivable to design the operation monitoring device 23 in such a way that, if there is no pump operation, the impression roller cannot be started up or automatically brought into the pressure shutdown. To achieve constant operating conditions, the temperature in the area of the forward branch 16 is kept constant at an adjustable value. For this purpose, the oil temperature in the forward flow 16 is measured by means of a sensor 24 and a controller 26, which interacts with an adjustable setpoint generator 25, is fed in, by means of which the flow of cooling water through the cooling unit 13 designed as a heat exchanger can be regulated. For this purpose, the cooling water line 27 of the cooling unit 13 is provided with a shut-off element 28 which can be adjusted by the controller 26.

Die Abdeckkappen 14 sind im Bereich ihres zylindrischen Teils mit jeweils einer Radialbohrung 29 versehen, durch die das dem hiervon umfaßten Spindelende jeweils zugeordnete Stellorgan 11 stößelförmig hindurchgreift. Zur Erzielung einer zuverlässigen Abdichtung sind im Bereich der Radialbdrungen 29 einer oder mehrere umlaufende Dichtringe 30 vorgesehen. Im Prinzip könnte die Kolbenstange eines das betreffende Stellorgan 11 bildenden Zylinder-Kolbenaggregats direkt in die jeweils zugeordnete Radialbohrung 29 der benachbarten Abdeckkappe 14 eingreifen. Bei einer Anordnung dieser Art wäre es jedoch erforderlich, im Falle einer Demontage der Abdeckkappe 14 die Kolbenstange außer Eingriff mit der Radialbohrung 14 zu bringen. Bei der Wiederanbringung der Abdeckkappe 14 müßte die Kolbenstange wieder in die zugerodnete Radialbohrung eingefahren werden, wobei der Dichtring 30 beschädigt werden könnte. Im dargestellten Ausführungsbeispiel bestehen die Stellorgane 11 daher aus in die Radialbohrung 29 der beiden Abdeckkappen 14 eingreifenden Stößeln 32 und diesen jeweils zugeordneten Zylinder-Kolbenaggregaten 34, deren Kolbenstange 31 jeweils radial außerhalb der benachbarten Abdeckkappe 14 endet und sich in Wirkverbindung mit dem in eine jeweils zugeordnete Radialbohrung 29 eingreifenden Stößel 32 befindet, der mit seinem radial inneren Ende an der Spindel 7 und mit seinem radial äußeren Ende an der zugeordneten Kolbenstange 31 anliegt. Die von den Zylinder-Kolbenaggregaten 34 getrennten Stößel 32 können demnach auch im Falle einer/ Demontage der jeweils zugeordneten Abdeckkappe 14 in ihrer Eingriffsstellung in der jeweils zugeordneten Radialbohrung 29 bleiben. Die Stößel 32 sind spindelseitig mit einer balligen Stirnseite versehen, die an einer Abflachung 33 des jeweils zugeordneten Spindelendes anliegt.In the area of their cylindrical part, the cover caps 14 are each provided with a radial bore 29 through which the adjusting element 11, which is associated with the spindle end encompassed thereby, engages in a plunger-shaped manner. To educate reliable sealing, one or more circumferential sealing rings 30 are provided in the area of the radial bores 29. In principle, the piston rod of a cylinder-piston unit forming the relevant actuator 11 could engage directly in the associated radial bore 29 of the adjacent cover cap 14. With an arrangement of this type, however, it would be necessary to disengage the piston rod from the radial bore 14 in the event of removal of the cover cap 14. When the cover cap 14 is reattached, the piston rod would have to be retracted into the zoned radial bore, and the sealing ring 30 could be damaged. In the illustrated embodiment, the actuators 11 therefore consist of plungers 32 engaging in the radial bore 29 of the two cover caps 14 and cylinder piston assemblies 34 assigned to them, the piston rod 31 of which ends radially outside the adjacent cover cap 14 and is in operative connection with the one in each case Radial bore 29 engaging plunger 32, which rests with its radially inner end on the spindle 7 and with its radially outer end on the associated piston rod 31. The plungers 32 separated from the cylinder-piston assemblies 34 can accordingly remain in their engagement position in the respectively assigned radial bore 29 even in the event of / removal of the respectively assigned cover cap 14. The tappets 32 are provided on the spindle side with a spherical end face which rests on a flat 33 of the respectively associated spindle end.

Im dargestellten Ausführungsbeispiel sind die Stützlager 8 zwar als Wälzlager ausgebildet. Infolge der hier vorgesehenen Beaufschlagung des von den Stützlagern 8 überbrückten Ringraums 12 mit Kühlöl wäre es jedoch auch möglich, die Stützlager 8 als Gleitlager auszubilden, die infolge der hydrodynamischen SchmierverhäTtnisse während des 8etriebs einer besonders geringen Reibung unterliegen und ausgezeichnete Dämpfungseigenschaften besitzen.In the illustrated embodiment, the support bearings 8 are designed as roller bearings. As a result of the provision of cooling oil bridging the annular space 12 bridged by the support bearings 8, it would also be possible to design the support bearings 8 as slide bearings which, due to the hydrodynamic lubrication conditions during operation, are subject to particularly low friction and have excellent damping properties.

Claims (10)

1. A cylinder for machines processing web material, more particuiarly a form roll for a gravure printing press, which adjacent to its ends is mounted in adjustable bearing mounts (5) and has a tubular casing (2) provided with a rubber coating, through which casing there extends a spindle (7), said spindle being stationary in the direction of rotation and having an external diameter which is smaller than the internal diameter of the casing, said casing being connected with the spindle by means of at least one supporting bearing (8) arranged symmetrically with respect to the middle of the casing and centered on the casing axis and being bearinged by pivot bearings (4) arranged adjacent to its ends on the lateral bearing mounts (5), on which there bears a respective setting member (11), which engages the respectively adjacent end, extending past the casing (2), of the spindle (7) and able to be actuated in a radial direction in relation to the spindle (7), characterized in that the ends of the spindle (7) extending past the casing (2) are fitted with a closing cap (14), which is attached to the adjacent bearing mount and has a seal (19) which allows relative motion, between it and the rotating casing, in that the setting members (11) extend through a radial hole (29), having at least one sealing ring (30), in the respectively fitted cover cap (14), in that the two cover caps (14) are provided with connections (15) for the feed branch (16) and, respectively, the return branch (17) of a coolant circuit extending via a cooling unit (13), and in that adjacent to each support bearing (8) there is a bypass line (20) bypassing same.
2. The cylinder as claimed in claim 1, characterized in that adjacent to each support bearing (8) the said spindle (7) has at least one hole, placed in front or, respectively, behind the associated support bearing (8) and opening into the annular space (12) between the spindle (7) and the casing (2) so as to form the bypass duct (20).
3. The cylinder as claimed in any one of the preceding claims, characterized by a packing ring forming the respective seal (19), allowing relative motion, between the ends of the casing and the respectively associated cover cap (14).
4. The cylinder as claimed in any one of the preceding claims, characterized in that the setting members (11) each have a plunger (32) fitting into the associated radial hole (29) and engaging the associated spindle end, said plunger having its end, remote from the spindle (7), engaging the piston rod (31) of a piston and cylinder unit (34) supported on the adjacent bearing mount (5).
5. The cylinder as claimed in claim 4, characterized in that the plungers (30) have a convex end face adjacent to the spindle.
6. The cylinder as claimed in any one of the preceding claims, characterized by flats (33) adjacent to the ends of the spindle (7) and associated with the respective setting members (11).
7. The cylinder as claimed in any one of the preceding claims, characterized in that the cooling unit (13) is designed in the form of a heat exchanger, which is provided with a regulating device (24, 25, 26 and 28) to keep the temperature of the medium to be cooled constant.
8. The cylinder as claimed in any one of the preceding claims, characterized in that the cooling unit (13) is adapted to be fed from a pump (22) whose input is connected with a reservoir (21) into which the return branch (17) of the coolant circuit opens.
9. The cylinder as claimed in claim 7, characterized in that an operation monitoring device (23) is associated with the pump (22).
10. The cylinder as claimed in any one of the preceding claims, characterized in that the annular space (12) between the casing (2) and the spindle (7) is arranged to be supplied with cooled oil.
EP85108865A 1984-07-26 1985-07-16 Cylinder for machines processing web-like material Expired - Lifetime EP0169475B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85108865T ATE59338T1 (en) 1984-07-26 1985-07-16 CYLINDERS FOR WEB MATERIAL PROCESSING MACHINES.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843427624 DE3427624A1 (en) 1984-07-26 1984-07-26 CYLINDERS FOR RAILWAY MATERIAL MACHINERY
DE3427624 1984-07-26

Publications (3)

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EP0169475A2 EP0169475A2 (en) 1986-01-29
EP0169475A3 EP0169475A3 (en) 1987-09-30
EP0169475B1 true EP0169475B1 (en) 1990-12-27

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ID=6241665

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EP85108865A Expired - Lifetime EP0169475B1 (en) 1984-07-26 1985-07-16 Cylinder for machines processing web-like material

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EP (1) EP0169475B1 (en)
JP (1) JPS6137430A (en)
AT (1) ATE59338T1 (en)
DE (2) DE3427624A1 (en)
DK (1) DK155960C (en)
FI (1) FI76871C (en)
NO (1) NO162549C (en)

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US9056451B2 (en) 2008-05-29 2015-06-16 Windmoeller & Hoelscher Kg System for gripping a cylinder conducting ink in a printing press

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DE3439090A1 (en) * 1984-10-25 1986-04-30 Albert-Frankenthal Ag, 6710 Frankenthal CYLINDERS FOR RAILWAY MATERIAL MACHINERY
DE9408328U1 (en) * 1994-05-20 1994-07-21 Maschinenfabrik Goebel Gmbh, 64293 Darmstadt Forme cylinder
DE19701226B4 (en) * 1997-01-16 2004-10-07 Heidelberger Druckmaschinen Ag Printing unit of an offset rotary printing machine
DE19919877A1 (en) 1999-04-30 2000-11-02 Voith Sulzer Papiertech Patent Cooling system for a paper or board machine
DE102018119570A1 (en) * 2018-08-13 2020-02-13 TRüTZSCHLER GMBH & CO. KG Device for strengthening and / or structuring a fleece and a structural shell

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Publication number Priority date Publication date Assignee Title
US9056451B2 (en) 2008-05-29 2015-06-16 Windmoeller & Hoelscher Kg System for gripping a cylinder conducting ink in a printing press

Also Published As

Publication number Publication date
DE3427624C2 (en) 1988-06-30
NO162549C (en) 1990-01-17
NO852674L (en) 1986-01-27
JPH0420389B2 (en) 1992-04-02
DK335885D0 (en) 1985-07-24
DK155960C (en) 1989-10-30
NO162549B (en) 1989-10-09
FI852742A0 (en) 1985-07-11
DE3427624A1 (en) 1986-02-06
FI852742L (en) 1986-01-27
ATE59338T1 (en) 1991-01-15
FI76871B (en) 1988-08-31
EP0169475A2 (en) 1986-01-29
DK335885A (en) 1986-01-27
DE3581126D1 (en) 1991-02-07
FI76871C (en) 1988-12-12
EP0169475A3 (en) 1987-09-30
JPS6137430A (en) 1986-02-22
DK155960B (en) 1989-06-05

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