EP0179363B1 - Cylinder for web-processing machines - Google Patents

Cylinder for web-processing machines Download PDF

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Publication number
EP0179363B1
EP0179363B1 EP85112878A EP85112878A EP0179363B1 EP 0179363 B1 EP0179363 B1 EP 0179363B1 EP 85112878 A EP85112878 A EP 85112878A EP 85112878 A EP85112878 A EP 85112878A EP 0179363 B1 EP0179363 B1 EP 0179363B1
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EP
European Patent Office
Prior art keywords
spindle
cylinder
line
casing
heat exchanger
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.)
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Application number
EP85112878A
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German (de)
French (fr)
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EP0179363A2 (en
EP0179363A3 (en
Inventor
Peter Dipl.-Ing. Maier
Arnold Niedermaier
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Albert Frankenthal AG
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Albert Frankenthal AG
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Priority to AT85112878T priority Critical patent/ATE50200T1/en
Publication of EP0179363A2 publication Critical patent/EP0179363A2/en
Publication of EP0179363A3 publication Critical patent/EP0179363A3/en
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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
    • B41F13/18—Impression cylinders
    • 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 rotogravure printing presses, with a tubular jacket rotatably mounted on side bearing plates, which is penetrated by a spindle which is in the direction of rotation and has a smaller outside diameter than the inside diameter of the jacket, and thus has at least one a support bearing arranged symmetrically to the center of the cylinder and coaxially to the cylinder axis is connected, which bridges the annular space between the spindle and the casing, which is designed as a receiving space for an oil filling that at least partially occupies it.
  • a cylinder of this type is known from DE-A-3 114 731.
  • the oil filling provided here is, however, a standing oil filling, which only serves to bring about heat compensation over the cylinder length and to prevent local temperature peaks of the cylinder jacket. It is not possible to cool the cylinder jacket and thus the jacket cover.
  • the permissible cylinder speed to a value which is significantly below the speed of 50,000 revolutions per hour required in modern gravure printing machines, since at high speeds the flexing work within the rubber cover leads to a rubber core temperature which is above the permissible limit and thus negatively affects the life of the rubber cover.
  • At least one heat exchanger surrounding the spindle is arranged in the annular space between the spindle and jacket, which is received on holders attached to the spindle and by means of associated spindle recesses leading, at least partially designed as flexible hose sections, connecting lines with an external coolant supply line or drain line is connected.
  • the heat exchanger is advantageously integrated into the cylinder structure.
  • An internal heat exchanger of the type in question here advantageously offers the possibility of largely reducing temperature differences simply by means of a high coolant throughput, which has a positive effect on achieving the most uniform oil temperature possible over the entire cylinder length.
  • the cooling medium flowing through the heat exchanger can in this case simply be removed from a supply network which is under pressure on the supply side, for example a water supply network.
  • a Umisselzanla g e is therefore advantageously unnecessary here.
  • the heat exchanger or heat exchangers can be designed as a pipe coil or pipe coils surrounding the spindle. This results in a simple heat exchanger construction as well as a space-saving arrangement and a comparatively large effective surface.
  • two heat exchangers which are separated from one another by the support bearing or bearings can be provided.
  • This advantageously enables a structure that is symmetrical with respect to the cylinder center and has an advantageous effect on achieving an oil temperature that is as uniform as possible over the entire length of the cylinder.
  • the two heat exchangers can be flow-shaded one behind the other and for this purpose can be connected to one another by a connecting line which leads over a spindle recess and bridges the area of the support bearing or the support bearings.
  • a further, particularly advantageous embodiment can consist in that in a heat exchanger-free area of the annular space on the spindle, radially protruding from it and reaching into the area of the jacket, oil wipers are arranged, to which leading spindle recesses are assigned in the area of an assigned heat exchanger.
  • the oil supplied by the oil wipers to the associated spindle recesses is pumped into the area of a heat exchanger via these spindle recesses. Due to the centrifugal forces resulting from a rotation of the jacket, this automatically results in a level compensation and thus an oil return.
  • the oil circuit brought about by these measures has an advantageous effect on achieving the most uniform oil temperature possible over the entire length of the cylinder.
  • the connecting or connecting lines assigned to the heat exchangers can be designed over their entire length as flexible hose sections which extend through the assigned spindle recesses. This measure simplifies assembly and advantageously also results in the desired flexible connection of the coolant inlet and outlet lines to be installed in a stationary manner to the connecting lines to be installed on the spindle side, so that the mobility of the spindle is not impaired thereby.
  • the hose sections can expediently have an undersize in relation to the assigned spindle recess. This enables simultaneous use of these spindle recesses for oil circulation.
  • 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 mounted on side bearing plates 5 via pivot bearings 4.
  • Lifting cylinders 6 act on the end shields 5, with the aid 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 casing 2 by two support bearings 8 arranged symmetrically to the center of the press and coaxially to the press axis.
  • the support bearings 8 are fixed on the one hand by a spindle-side collar and on the other hand by a bushing which is provided with a split clamping ring and is clamped onto the spindle 7.
  • the support bearings 8 divide the annular space between the spindle 7 and the casing 2 into three separate chambers 9a, 9b, 9c.
  • 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.
  • the ends of the spindle 7 projecting over the lateral bearing pins 3 are encompassed by a respectively associated closure cap 10.
  • the caps 10 are screwed to the adjacent bearing plate 5.
  • the closure caps 10 are provided with inner thrust lugs 11.
  • a movement seal arranged between the mutually facing end faces of the caps 10 and the respective adjacent journal 3 is provided, for example in the form of a sealing ring or the like.
  • the closure caps 14 are each provided with a radial bore associated with the associated actuator 12, into which the actuator 12 associated with the spindle end encompassed thereby engages in a pestle-shaped manner.
  • the actuators 12 are associated with plungers 13 which engage in the radial bore of the respectively adjacent sealing cap 10, at the outer end of which the piston rod of the cylinder-piston unit forming the actuator 12 in question rests.
  • the annular space 9 is provided with an oil filling which partially occupies it and which in turn is continuously cooled.
  • At least one heat exchanger 14 fastened to the spindle 7 is accommodated in the annular space 9, which is arranged in such a way that its surface is immersed in an oil filling which is in contact with the inside of the jacket 2 when the jacket 2 is rotating due to the centrifugal force and which means
  • Corresponding connection lines 15 on the press side is connected to a stationary coolant supply line 16 or coolant discharge line 17 arranged outside the impression line.
  • the connecting lines 15 run in recesses provided on the spindle side.
  • two heat exchangers 14 are provided, which are accommodated in the two outer annular chambers 9a and 9c. These two heat exchangers 14 can be connected in parallel in terms of flow. In the illustrated embodiment, the two heat exchangers 14 are connected in series in terms of flow.
  • the heat The exchanger 14 is connected to one another by a connecting line 18 bridging the middle annular chamber 9b bounded by the support bearings 8.
  • the connecting line 18 runs in an associated spindle recess, so that no collisions can occur in the region of the support bearings 8.
  • blades 19 are provided which are attached to the spindle 7 and protrude radially therefrom and extend with their outer end into the area of the jacket 2.
  • the blades 19 are arranged in the region of further spindle recesses which connect the regions of the annular space 9 assigned to the blades 19 to the regions of the annular space 9 assigned to the heat exchangers 14 in terms of flow.
  • the oil stripped from the blades 9 and directed radially inward is thus pumped into the regions of the annular space 9 assigned to the heat exchangers 14. Due to the level compensation resulting from the centrifugal force, the oil automatically flows back through the support bearings 8, which are designed here as roller bearings. This oil circulation results in good temperature compensation and at the same time ensures good bearing lubrication.
  • the connecting lines 15 and the connecting line 18 can simply be designed as flexible hose sections laid in the associated spindle recess.
  • the flexibility of the hose sections makes it easier to move them into the assigned spindle recess.
  • the hose sections forming the connecting lines 15 and the connecting line 18 are opposite in the exemplary embodiment shown the clear width of the respectively assigned spindle recess undersize. This ensures that the oil circulation caused by the blades 19 can lead via the spindle recesses associated with the connecting line 18 and / or the connecting lines 15, which are provided with radial branches 20 opening out in the area of the blades 19 for this purpose.
  • the recesses in the spindle 7 are designed in the form of a centrally arranged, axial through-bore 21, from which radial bores 22 which open radially in front of and behind each heat exchanger 14 and serve to accommodate the end regions of the hose sections forming the connecting lines 15 and the connecting line 18 on the heat exchanger side and the radial bores 20 forming the branches 20 assigned to the blades go off.
  • the radial bores 22 assigned to the connecting lines 15 and the connecting line 18 are arranged inclined to the spindle axis, which facilitates the insertion of the hose sections forming the connecting lines 15 and the connecting line 18.
  • the spindle recesses could be designed as line sections, so that only connecting pieces leading away from the end cross sections of the spindle recesses would be required.
  • the use of hose sections laid in the spindle recesses simplifies the manufacture of the spindle recesses and the line assembly.
  • mounting brackets 23 which are provided with a connecting sleeve 24, on the one hand the respective adjacent end of a heat exchanger 14 and on the other hand the associated end of a connecting or connecting line 15 or 18 can be fixed by screw cap.
  • the hose sections protruding from the axial bore 21 in the area of the spindle ends and forming the connecting lines 15 are screwed to the coolant supply line 16 or coolant discharge line 17 in the area of the sealing caps 10.
  • connecting sleeves 25 inserted into the sealing caps 10 are provided. Ends 7 of the hose sections 7 projecting beyond the spindle ensure the mobility required as a result of the spindle deflection.
  • Water can be used as a coolant. Cooling water is available in many printing plants in the form of a network that is pressurized on the supply side and fed from a central cooling station. Where this is not the case, water taken from the normal water supply network can simply be used.
  • the coolant supply line 16 is accordingly designed as a branch line of such a supply network 26. The network pressure is sufficient to ensure proper coolant flow in the area of the heat exchanger 14.
  • the coolant drain line 17 opens into a drain pipe 27 which leads back to the central cooling station or, if tap water is used, opens into the normal sewage system.
  • a thermostatically controllable throttle valve 28 is provided in the area of the coolant discharge line 17, which regulates the coolant throughput as a function of the coolant temperature or, as here, suitably as a function of the oil temperature.
  • a sensor 29 that detects the oil temperature is provided.
  • an oil compensation container 30 is provided which is connected to the annular space 9 via a spur line 31.
  • the stub 31 is in the range a closure cap 10 arranged screwed ßstutzen.

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  • Mechanical Engineering (AREA)
  • Engineering & Computer Science (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Medicinal Preparation (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
  • Steroid Compounds (AREA)
  • Treatment Of Fiber Materials (AREA)
  • Superconductors And Manufacturing Methods Therefor (AREA)
  • Extrusion Of Metal (AREA)
  • Soil Working Implements (AREA)
  • Fish Paste Products (AREA)
  • Glass Compositions (AREA)
  • Replacement Of Web Rolls (AREA)
  • Fluid-Damping Devices (AREA)
  • Rotary Presses (AREA)
  • Unwinding Webs (AREA)

Abstract

A cylinder for handling continuous lengths of web material comprises a rotatably mounted tubular casing, a spindle extending from end to end of the casing and arranged to be stationary in relation to rotation of said casing and having an external diameter less than the diameter of an inner face of the tubular casing, at least one support bearing which is symmetrical in relation to the middle of the cylinder and coaxial to the cylinder, the bearing bridging over an annular space existing between the casing and the spindle, oil at least partly filling the annular space, at least one heat exchanger placed in the annular space and surrounding the spindle, mounts fixed to the spindle for locating the heat exchanger thereon, and connection ducts for coolant, at least partly in the form of lengths of flexible hose placed in recesses in the spindle, the connection ducts being adapted to join the heat exchanger with an external coolant supply and return duct.

Description

Die Erfindung betrifft einen Zylinder für bahnförmiges Material verarbeitene Maschinen, insbesondere einen Presseur für Tiefdruckmaschinen, mit einem auf seitlichen Lagerschilden drehbar gelagerten, rohrförmigen Mantel, der von einer in Drehrichtung stehenden, einen gegenüber dem Innendurchmesser des Mantels kleineren Außendurchmesser aufweisenden Spindel durchsetzt und hiermit über mindestens ein symmetrisch zur Zylindermitte und koaxial zur Zylinderachse angeordnetes Stützlager verbunden ist, das den als Aufnahmeraum für eine ihn zumindest teilweise einnehmende Ölfüllung ausgebildeten Ringraum zwischen Spindel und Mantel überbrückt.The invention relates to a cylinder for web-like material processing machines, in particular a impression roller for rotogravure printing presses, with a tubular jacket rotatably mounted on side bearing plates, which is penetrated by a spindle which is in the direction of rotation and has a smaller outside diameter than the inside diameter of the jacket, and thus has at least one a support bearing arranged symmetrically to the center of the cylinder and coaxially to the cylinder axis is connected, which bridges the annular space between the spindle and the casing, which is designed as a receiving space for an oil filling that at least partially occupies it.

Ein Zylinder dieser Art ist aus der DE-A-3 114 731 bekannt. Bei der hier vorgesehenen Ölfüllung handelt es sich jedoch um eine stehende Ölfüllung, die lediglich dazu dient, einen Wärmeausgleich über der Zylinderlänge herbeizuführen und lokale Temperaturspitzen des Zylindermantels zu verhindern. Eine Kühlung des Zylindermantels und damit des Mantelbezugs ist hierbei nicht möglich. Bei dieser bekannten Anordnung ergibt sich daher eine Beschränkung der zulässigen Zylinderdrehzahl auf einen Wert, der deutlich unterhalb der bei modernen Tiefdruckmaschinen geforderten Drehzahl von 50 000 Umdrehungen pro Stunde liegt, da bei hohen Drehzahlen die Walkarbeit innerhalb des Gummibezugs zu einer Gummikerntemperatur führt, die oberhalb der zulässigen Grenze liegt und damit die Lebensdauer des Gummibezugs negativ beeinflußt.A cylinder of this type is known from DE-A-3 114 731. The oil filling provided here is, however, a standing oil filling, which only serves to bring about heat compensation over the cylinder length and to prevent local temperature peaks of the cylinder jacket. It is not possible to cool the cylinder jacket and thus the jacket cover. In this known arrangement there is therefore a limitation of the permissible cylinder speed to a value which is significantly below the speed of 50,000 revolutions per hour required in modern gravure printing machines, since at high speeds the flexing work within the rubber cover leads to a rubber core temperature which is above the permissible limit and thus negatively affects the life of the rubber cover.

Hiervon ausgehend ist es daher die Aufgabe der vorliegenden Erfindung, einen Zylinder eingangs erwähnter Art so zu verbessern, daß auf einfache Weise eine zuverlässige Kühlung des Öls und eine vergleichsweise niedrige, über der Zylinderlänge gleichmäßige Kerntemperatur des Gummibezugs des rotierenden Mantels erreicht werden, so daß auch bei vergleichsweise hohen Zylinderdrehzahlen eine hohe Lebensdauer des Gummibezugs gewährleistet ist.Proceeding from this, it is therefore the object of the present invention to improve a cylinder of the type mentioned in such a way that reliable cooling of the oil and a comparatively low core temperature of the rubber cover of the rotating jacket, which is uniform over the cylinder length, are achieved, so that also at comparatively high cylinder speeds, a long service life of the rubber cover is guaranteed.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß im Ringraum zwischen Spindel und Mantel mindestens ein die Spindel umgebender Wärmetauscher angeordnet ist, der auf an der Spindel befestigten Haltern aufgenommen und mittels über zugeordnete Spindelausnehmungen führender, zumindest teilweise als flexible Schlauchabschnitte ausgebildeter Anschlußleitungen mit einer äußeren Kühlmittelzulaufleitung bzw. -ablaufleitung verbunden ist.This object is achieved in that at least one heat exchanger surrounding the spindle is arranged in the annular space between the spindle and jacket, which is received on holders attached to the spindle and by means of associated spindle recesses leading, at least partially designed as flexible hose sections, connecting lines with an external coolant supply line or drain line is connected.

Hierbei ist der Wärmetauscher in vorteilhafter Weise in den Zylinderaufbau integriert. Ein innenliegender Wärmetauscher hier vorliegender Art bietet in vorteilhafter Weise die Möglichkeit, Temperaturunterschiede einfach durch einen hohen Kühlmitteldurchsatz weitestgehend zu reduzieren, was sich positiv auf die Erzielung einer möglichst gleichmäßigen Öltemperatur über der gesamten Zylinderlänge auswirkt. Das den Wärmetauscher durchströmende Kühlmedium kann hierbei einfach von einem vorlaufseitig unter Druck stehenden Versorgungsnetz, beispielsweise einem Wasserleitungsnetz, abgenommen werden. Eine Umwälzanlage ist hier daher in vorteilhafter Weise entbehrlich. Dadurch, daß der Wärmetauscher auf spindelseitig befestigten Haltern aufgenommen ist und daß die über Spindelausnehmungen führenden Anschlußleitungen zumindest teilweise als flexible Schlauchabschnitte ausgebildet sind, ist sichergestellt, daß innerhalb der dem spindelseitig befestigten Wärmetauscher zugeordneten Anschlußleitungen die aufgrund einer Durchbiegung einer Spindel bzw. des gegenläufig hierzu sich durchbiegenden Mantels sich ergebenden Bewegungen aufgenommen werden können, ohne daß sich Zwangskräfte ergeben.The heat exchanger is advantageously integrated into the cylinder structure. An internal heat exchanger of the type in question here advantageously offers the possibility of largely reducing temperature differences simply by means of a high coolant throughput, which has a positive effect on achieving the most uniform oil temperature possible over the entire cylinder length. The cooling medium flowing through the heat exchanger can in this case simply be removed from a supply network which is under pressure on the supply side, for example a water supply network. A Umwälzanla g e is therefore advantageously unnecessary here. The fact that the heat exchanger is accommodated on holders fastened on the spindle side and that the connecting lines leading via spindle recesses are at least partially designed as flexible hose sections, ensures that within the connecting lines assigned to the spindle side fastened heat exchanger, the connecting lines due to a deflection of a spindle or the opposite one another bending jacket resulting movements can be absorbed without resulting in constraining forces.

In vorteilhafter Ausgestaitung der übergeordneten Maßnahmen können der bzw. die Wärmetauscher als die Spindel umgebende Rohrschlange bzw. Rohrschlangen ausgebildet sein. Hierdurch ergeben sich ein einfacher Wärmetauscheraufbau sowie eine platzsparende Anordnung und eine vergleichsweise große wirksame Oberfläche.In an advantageous embodiment of the higher-level measures, the heat exchanger or heat exchangers can be designed as a pipe coil or pipe coils surrounding the spindle. This results in a simple heat exchanger construction as well as a space-saving arrangement and a comparatively large effective surface.

In weiterer Fortbildung der übergeordneten Maßnahmen können zwei durch das bzw. die Stützlager voneinander getrennte Wärmetauscher vorgesehen sein. Dies ermöglicht in vorteilhafter Weise einen zur Zylindermitte symmetrischen Aufbau und wirkt sich vorteilhaft auf die Erzielung einer möglichst gleichmäßigen Öitemperatur über der gesamten Zylinderlänge aus. In weiterer zweckmäßiger Fortbildung dieses Gedankens können die beiden Wärmetauscher strömungsmäßig hintereinander geschattet und hierzu durch eine über eine Spindelausnehmung führende, den Bereich des Stützlagers bzw. der Stützlager überbrückende Verbindungsleitung miteinander verbunden sein. Diese Maßnahmen ergeben in vorteilhafter Weise einen sehr einfachen Aufbau. Dennoch läßt sich hierbei einfach durch einen hohen Kühlmitteldurchsatz eine nahezu gleichmäßige Oberflächentemperatur im Bereich der gesamten Wärmetauscheranordnung erreichen.In a further development of the superordinate measures, two heat exchangers which are separated from one another by the support bearing or bearings can be provided. This advantageously enables a structure that is symmetrical with respect to the cylinder center and has an advantageous effect on achieving an oil temperature that is as uniform as possible over the entire length of the cylinder. In a further expedient further development of this idea, the two heat exchangers can be flow-shaded one behind the other and for this purpose can be connected to one another by a connecting line which leads over a spindle recess and bridges the area of the support bearing or the support bearings. These measures advantageously result in a very simple structure. Nevertheless, an almost uniform surface temperature in the area of the entire heat exchanger arrangement can be achieved simply by a high coolant throughput.

Eine weitere, besonders vorteilhafte Ausgestaltung kann darin bestehen, daß in einem wärmetauscherfreien Bereich des Ringraums an der Spindel befestigte, von dieser radial wegstehende und bis in den Bereich des Mantels reichende Ölabstreifer angeordnet sind, denen in den Bereich eines zugeordneten Wärmetauschers führende Spindelausnehmungen zugeordnet sind. Das von den Ölabstreifern den zugeordneten Spindelausnehmungen zugeführte Öl wird hierbei über diese Spindelausnehmungen in den Bereich eines Wärmetauschers gepumpt. Aufgrund der bei einer Rotation des Mantels sich ergebende Fliehkräfte ergibt sich dabei automatisch ein Niveauausgleich und damit eine Ölrückführung. Der durch diese Maßnahmen bewirkte Ölkreislauf wirkt sich vorteilhaft auf die Erzielung einer möglichst gleichmäßigen Öltemperatur über der gesamten Zylinderlänge aus.A further, particularly advantageous embodiment can consist in that in a heat exchanger-free area of the annular space on the spindle, radially protruding from it and reaching into the area of the jacket, oil wipers are arranged, to which leading spindle recesses are assigned in the area of an assigned heat exchanger. The oil supplied by the oil wipers to the associated spindle recesses is pumped into the area of a heat exchanger via these spindle recesses. Due to the centrifugal forces resulting from a rotation of the jacket, this automatically results in a level compensation and thus an oil return. The oil circuit brought about by these measures has an advantageous effect on achieving the most uniform oil temperature possible over the entire length of the cylinder.

Gemäß einer weiteren, vorteilhaften Ausgestaitung der übergeordneten Maßnahmen können die den Wärmetauschern zugeordneten Anschluß- bzw. Verbindungsleitungen auf ihrer gesamten Länge als durch die zugeordneten Spindelausnehmungen hindurchgreifende, flexible Schlauchabschnitte ausgebildet sein. Diese Maßnahme vereinfacht die Montage und ergibt in vorteilhafter Weise gleichzeitig die erwünschte flexible Verbindung der stationär zu verlegenden Kühlmittelzu- bzw. -ablaufleitungen mit den spindelseitig zu verlegenden Anschlußleitungen, so daß die Bewegbarkeit der Spindel hierdurch nicht beeinträchtigt wird.According to a further advantageous embodiment of the superordinate measures, the connecting or connecting lines assigned to the heat exchangers can be designed over their entire length as flexible hose sections which extend through the assigned spindle recesses. This measure simplifies assembly and advantageously also results in the desired flexible connection of the coolant inlet and outlet lines to be installed in a stationary manner to the connecting lines to be installed on the spindle side, so that the mobility of the spindle is not impaired thereby.

Zweckmäßig können die Schlauchabschnitte gegenüber der zugeordneten Spindelausnehmung Untermaß besitzen. Dies ermöglicht eine gleichzeitige Verwendung dieser Spindelausnehmungen zur Ölumwälzung.The hose sections can expediently have an undersize in relation to the assigned spindle recess. This enables simultaneous use of these spindle recesses for oil circulation.

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

Die einzige Figur der Zeichnung zeigt einen Längsschnitt durch einen mit Wärmetauschern versehenen Presseur für eine Tiefdruckmaschine.The only figure in the drawing shows a longitudinal section through a impression roller provided with heat exchangers for a gravure printing machine.

Der grundsätzliche Aufbau und die Wirkungsweise von Tiefdruckmaschinen sind an sich bekannt und bedürfen 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 gelagert sind. An den Lagerschilden 5 greifen 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 zwei symmetrisch zur Presseurmitte und koaxial zur Presseurachse 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 versehene, auf die Spindel 7 aufgeklemmte Büchse fixiert. Die Stützlager 8 teilen den Ringraum zwischen der Spindel 7 und dem Mantel 2 in drei voneinander getrennte Kammern 9a, 9b, 9c auf.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 mounted on side bearing plates 5 via pivot bearings 4. Lifting cylinders 6 act on the end shields 5, with the aid 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 casing 2 by two support bearings 8 arranged symmetrically to the center of the press and coaxially to the press axis. The support bearings 8 are fixed on the one hand by a spindle-side collar and on the other hand by a bushing which is provided with a split clamping ring and is clamped onto the spindle 7. The support bearings 8 divide the annular space between the spindle 7 and the casing 2 into three separate chambers 9a, 9b, 9c.

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. Die über die seitlichen Lagerzapfen 3 auskragenden Enden der Spindel 7 sind von einer jeweils zugeordneten Verschlußkappe 10 umfaßt. Die Verschlußkappen 10 sind mit dem jeweils benachbarten Lagerschild 5 verschraubt. Zur Fixierung der Spindel 7 in axialer Richtung sind die Verschlukappen 10 mit inneren Anlaufnasen 11 versehen. Zur Abdichtung der Schwenklager 4 gegenüber dem Innenraum der Verschlußkappen 10 ist jeweils eine zwischen den einander zugewandten Stirnseiten der Verschlußkappen 10 und des jeweils benachbarten Lagerzapfens 3 angeordnete Bewegungsdichtung etwa in Form eines Simmerrings oder dergleichen vorgesehen.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. The ends of the spindle 7 projecting over the lateral bearing pins 3 are encompassed by a respectively associated closure cap 10. The caps 10 are screwed to the adjacent bearing plate 5. To fix the spindle 7 in the axial direction, the closure caps 10 are provided with inner thrust lugs 11. To seal the pivot bearing 4 from the interior of the caps 10, a movement seal arranged between the mutually facing end faces of the caps 10 and the respective adjacent journal 3 is provided, for example in the form of a sealing ring or the like.

Zur Bewerkstelligung eines Biegeausgleichs sind an den aus dem Mantel 2 herausragenden Spindelenden angreifende, bezüglich der Presseurachse in radialer Richtung betätigbare, als Zylinder-Kolbenaggregate ausgebildete Stellorgane 12 vorgesehen, die mit dem jeweils benachbarten Lagerschild 5 fest verbunden sind. Die Verschlußkappen 14 sind im Bereich ihres zylindrischen Teils mit jeweils einer dem zugeordneten Stellorgan 12 zugeordneten Radialbohrung versehen, in die das dem hiervon umfaßten Spindelende jeweils zugeordnete Stellorgan 12 stö- ßelförmig hindurchgreift. Im dargestellten Ausführungsbeispiel sind den Stellorganen 12 in die Radialbohrung der jeweils benachbarten Verschlußkappe 10 eingreifende Stößel 13 zugeordnet, an deren äußerem Ende die Kolbenstange des das betreffende Stellorgan 12 bildenden Zylinder-Kolbenaggregats anliegt.To accomplish a bending compensation are provided on the spindle ends protruding from the jacket 2, actuated in the radial direction with respect to the impression cylinder axis, designed as cylinder-piston units, which are firmly connected to the adjacent bearing plate 5. In the area of their cylindrical part, the closure caps 14 are each provided with a radial bore associated with the associated actuator 12, into which the actuator 12 associated with the spindle end encompassed thereby engages in a pestle-shaped manner. In the exemplary embodiment shown, the actuators 12 are associated with plungers 13 which engage in the radial bore of the respectively adjacent sealing cap 10, at the outer end of which the piston rod of the cylinder-piston unit forming the actuator 12 in question rests.

Im Gummibezug 1 kommt es infolge der bei jeder Umdrehung des Mantels 2 sich ergebenden Walkarbeit zu einer starken Wärmeentwicklung. Außerdem kann es hierbei aufgrund der Lagerreibung im Bereich der Stützlager 8 zu einer lokalen Wärmeentwicklung kommen. Um die Oberflächentemperatur und die Kerntemperatur des Gummibezugs 1 dennoch in zulässigen Grenzen zu haften und einen Temperaturausgleich über der ganzen Presseurlänge zu gewährleisten, ist der Ringraum 9 mit einer ihn teilweise einnehmenden Ölfüllung versehen, die ihrerseits laufend gekühlt wird. Hierzu ist im Ringraum 9 mindestens ein an der Spindel 7 befestigter Wärmetauscher 14 untergebracht, der so angeordnet ist, daß er mit seiner Oberfläche in die bei sich drehendem Mantel 2 aufgrund der Fliehkraft ringförmig an die Innenseite des Mantels 2 sich anlegende Ölfüllung eintaucht und der mittels entsprechender presseurseitiger Anschlußleitungen 15 mit einer außerhalb des Presseurs angeordneten, stationären Kühlmittelzulaufleitung 16 bzw. Kühlmittelablaufleitung 17 verbunden ist. Die Anschlußleitungen 15 verlaufen in spindelseitig vorgesehenen Ausnehmungen.In the rubber cover 1 there is a strong development of heat as a result of the flexing work resulting from each revolution of the jacket 2. In addition, local heat development can occur due to the bearing friction in the area of the support bearings 8. In order to adhere to the surface temperature and the core temperature of the rubber cover 1 within permissible limits and to ensure temperature compensation over the entire length of the impression roller, the annular space 9 is provided with an oil filling which partially occupies it and which in turn is continuously cooled. For this purpose, at least one heat exchanger 14 fastened to the spindle 7 is accommodated in the annular space 9, which is arranged in such a way that its surface is immersed in an oil filling which is in contact with the inside of the jacket 2 when the jacket 2 is rotating due to the centrifugal force and which means Corresponding connection lines 15 on the press side is connected to a stationary coolant supply line 16 or coolant discharge line 17 arranged outside the impression line. The connecting lines 15 run in recesses provided on the spindle side.

Im dargestellten Ausführungsbeispiel sind zwei Wärmetauscher 14 vorgesehen, die in den beiden äußeren Ringruamkammern 9a bzw. 9c untergebracht sind. Diese beiden Wärmetauscher 14 können strömungsmäßig parallel geschaltet sein. Im dargestellten Ausführungsbeispiel sind die beiden Wärmetauscher 14 strömungsmäßig hintereinander geschaltet. Hierzu sind die Wärmetauscher 14 durch eine die mittlere, durch die Stützlager 8 begrenzte Ringraumkammer 9b überbrückende Verbindungsleitung 18 miteinander verbunden. Die Verbindungsleitung 18 verläuft in einer zugeordneten Spindelausnehmung, so daß im Bereich der Stützlager 8 keine Kollisionen auftreten können. Im Bereich der mittleren Ringraumkammer 9b sind an der Spindel 7 befestigte, hiervon radial wegstehende, mit ihrem äußeren Ende bis in den Bereich des Mantels 2 reichende Schaufeln 19 vorgesehen. Diese tauchen in das bei laufendem Mantel 2 ringförmig an diesen sich anlegende Öl ein und wirken somit als Öiabstreifer. Die Schaufeln 19 sind im Bereich weiterer Spindelausnehmungen angeordnet, welche die den Schaufeln 19 zugeordneten Bereiche des Ringraums 9 mit den den Wärmetauschern 14 zugeordneten Bereichen des Ringraums 9 strömungsmäßig verbinden. Während des Betriebs wird somit das von den Schaufeln 9 abgestreifte und nach radial innen geleitete Öl in die den Wärmetauschern 14 zugeordneten Bereiche des Ringraums 9 gepumpt. Aufgrund des infolge der Fliehkraft sich ergebenden Niveauausgleichs erfolgt automatisch ein Rückfluß des Öls über die Stützlager 8, die hier als Wälzlager ausgebildet sind. Diese Ölumwälzung ergibt einen guten Temperaturausgleich und gewährleistet gleichzeitig eine gute Lagerschmierung.In the illustrated embodiment, two heat exchangers 14 are provided, which are accommodated in the two outer annular chambers 9a and 9c. These two heat exchangers 14 can be connected in parallel in terms of flow. In the illustrated embodiment, the two heat exchangers 14 are connected in series in terms of flow. For this, the heat The exchanger 14 is connected to one another by a connecting line 18 bridging the middle annular chamber 9b bounded by the support bearings 8. The connecting line 18 runs in an associated spindle recess, so that no collisions can occur in the region of the support bearings 8. In the area of the middle annular chamber 9b, blades 19 are provided which are attached to the spindle 7 and protrude radially therefrom and extend with their outer end into the area of the jacket 2. These are immersed in the oil that is applied to the ring 2 while the jacket is running and thus act as an oil wiper. The blades 19 are arranged in the region of further spindle recesses which connect the regions of the annular space 9 assigned to the blades 19 to the regions of the annular space 9 assigned to the heat exchangers 14 in terms of flow. During operation, the oil stripped from the blades 9 and directed radially inward is thus pumped into the regions of the annular space 9 assigned to the heat exchangers 14. Due to the level compensation resulting from the centrifugal force, the oil automatically flows back through the support bearings 8, which are designed here as roller bearings. This oil circulation results in good temperature compensation and at the same time ensures good bearing lubrication.

Die Anschlußleitungen 15 und die Verbindungsleitung 18 können einfach als in der zugeordneten Spindelausnehmung verlegte, flexible Schlauchabschnitte ausgebildet sein. Die Flexibilität der Schlauchabschnitte erleichtert ihren Einzug in die zugeordnete Spindelausnehmung. Gleichzeitig ergibt sich hierdurch eine flexible Verbindung der auf der mittels der Stellorgane 12 bewegbaren Spindel 7 befestigten Wärmetauscher 14 mit den stationär verlegten Kühlmittelzu- bzw. -ablaufleitungen 16 bzw. 17. Die die Anschlußleitungen 15 und die Verbindungsleitung 18 bildenden Schlauchabschnitte besitzen im dargestellten Ausführungsbeispiel gegenüber der lichten Weite der jeweils zugeordneten Spindelausnehmung Untermaß. Hierdurch ist sichergestellt, daß die mit Hilfe der Schaufeln 19 bewirkte Ölumwälzung über die der Anschlußleitung 18 und/oder den Verbindungsleitungen 15 zugeordneten Spindelausnehmungen führen kann, die hierzu mit im Bereich der Schaufeln 19 ausmündenden radialen Abzweigungen 20 versehen sind.The connecting lines 15 and the connecting line 18 can simply be designed as flexible hose sections laid in the associated spindle recess. The flexibility of the hose sections makes it easier to move them into the assigned spindle recess. At the same time, this results in a flexible connection of the heat exchanger 14 fastened on the spindle 7, which can be moved by means of the actuators 12, to the stationary coolant supply and discharge lines 16 and 17, respectively. The hose sections forming the connecting lines 15 and the connecting line 18 are opposite in the exemplary embodiment shown the clear width of the respectively assigned spindle recess undersize. This ensures that the oil circulation caused by the blades 19 can lead via the spindle recesses associated with the connecting line 18 and / or the connecting lines 15, which are provided with radial branches 20 opening out in the area of the blades 19 for this purpose.

Die Ausnehmungen der Spindel 7 sind im dargestellten Ausführungsbeispiel in Form einer zentral angeordneten, axialen Durchgangsbohrung 21 ausgebildet, von der vor und hinter jedem Wärmetauscher 14 radial ausmündende, zur Aufnahme der wärmetauscherseitigen Endbereiche der die Anschlußleitungen 15 bzw. die Verbindungsleitung 18 bildenden Schlauchabschnitte dienende Radialbohrungen 22 und die den Schaufeln 19 zugeordneten Abzweigungen 20 bildende Radialbohrungen abgehen. Die den Anschlußleitungen 15 bzw. der Verbindungsleitung 18 zugeordneten Radialbohrungen 22 sind zur Spindelachse geneigt angeordnet, was den Einzug der die Anschlußleitungen 15 bzw. die Verbindungsleitung 18 bildenden Schlauchabschnitte erleichtert. Es wäre auch denkbar, die Spindelausnehmungen als Leitungsabschnitte auszubilden, so daß lediglich von den Endquerschnitten der Spindelausnehmungen wegführende Anschlußstutzen erforderlich wären. Die Verwendung von in den Spindelausnehmungen verlegten Schlauchabschnitten erleichtert jedoch die Herstellung der Spindelausnehmungen und die Leitungsmontage.In the exemplary embodiment shown, the recesses in the spindle 7 are designed in the form of a centrally arranged, axial through-bore 21, from which radial bores 22 which open radially in front of and behind each heat exchanger 14 and serve to accommodate the end regions of the hose sections forming the connecting lines 15 and the connecting line 18 on the heat exchanger side and the radial bores 20 forming the branches 20 assigned to the blades go off. The radial bores 22 assigned to the connecting lines 15 and the connecting line 18 are arranged inclined to the spindle axis, which facilitates the insertion of the hose sections forming the connecting lines 15 and the connecting line 18. It would also be conceivable to design the spindle recesses as line sections, so that only connecting pieces leading away from the end cross sections of the spindle recesses would be required. However, the use of hose sections laid in the spindle recesses simplifies the manufacture of the spindle recesses and the line assembly.

Zur Befestigung der Wärmetauscher 14 auf der Spindel 7 sind auf dieser befestigte Haltebökke 23 vorgesehen, die mit einer Verbindungsmuffe 24 versehen sind, an der einerseits das jeweils benachbarte Ende eines Wärmetauschers 14 und andererseits das zugeordnete Ende einer Anschluß- bzw. Verbindungsleitung 15 bzw. 18 durch Schraubverschluß festlegbar sind. Die im Bereich der Spindelenden aus der Axialbohrung 21 herausragenden, die Anschlußleitungen 15 bildenden Schlauchabschnitte sind im Bereich der Verschlußkappen 10 mit der Kühlmittelzulaufleitung 16 bzw. Kühlmittelablaufleitung 17 verschraubt. Hierzu sind in die Verschlußkappen 10 eingesetzte Verbindungsmuffen 25 vorgesehen. Die Spindel 7 überragenden Enden der Schlauchabschnitte 7 gewährleisten die infolge der Spindeldurchbiegung benötigte Beweglichkeit.To fix the heat exchangers 14 on the spindle 7, there are attached mounting brackets 23, which are provided with a connecting sleeve 24, on the one hand the respective adjacent end of a heat exchanger 14 and on the other hand the associated end of a connecting or connecting line 15 or 18 can be fixed by screw cap. The hose sections protruding from the axial bore 21 in the area of the spindle ends and forming the connecting lines 15 are screwed to the coolant supply line 16 or coolant discharge line 17 in the area of the sealing caps 10. For this purpose, connecting sleeves 25 inserted into the sealing caps 10 are provided. Ends 7 of the hose sections 7 projecting beyond the spindle ensure the mobility required as a result of the spindle deflection.

Als Kühlmittel kann Wasser Verwendung finden. Kühlwasser steht in vielen Druckereien in Form eines vorlaufseitig unter Druck stehenden, von einer zentralen Kühlstation aus gespeisten Netzes zur Verfügung. Wo dies nicht der Fall ist, kann einfach aus dem normalen Wasserleitungsnetz entnommenes Wasser Verwendung finden. Die Kühlmittelzulaufleitung 16 ist dementsprechend als Stichleitung eines derartigen Versorgungsnetzes 26 ausgebildet. Der Netzdruck reicht dabei aus, um eine ordnungsgemäße Kühlmittelströmung im Bereich der Wärmetauscher 14 zu gewährleisten. Die Kühlmittelablaufleitung 17 mündet in ein Abflußrohr 27, das zur zentralen Kühlstation zurückführt oder, bei Verwendung von Leitungswasser, in die normale Abwasserkanalisation mündet. Zur Gewährleistung einer möglichst gleichbleibenden Temperatur des im Ringraum 9 vorhandenen Öls ist im Bereich der Kühlmittelablaufleitung 17 ein termostatisch steuerbares Drosselventil 28 vorgesehen, das dem Kühlmitteldurchsatz in Abhängigkeit von der Kühlmitteltemperatur oder, wie hier, zweckmäßig in Abhängigkeit von der Öltemperatur reguliert. Hierzu ist ein die Öltemperatur erfassender Meßfühler 29 vorgesehen. Um den Ölstand im Ringraum 9 auf einem gewünschten Niveau zu haften und die Entstehung eines Überdrucks im Ringraum 9 zu verhindern, ist ein au- βerhalb des Presseurs angeordneter Ölausgleichsbehäfter 30 vorgesehen, der über eine Stichleitung 31 mit dem Ringraum 9 verbunden ist. Die Stichleitung 31 ist mit einem im Bereich einer Verschlußkappe 10 angeordneten Anschlu ßstutzen verschraubt.Water can be used as a coolant. Cooling water is available in many printing plants in the form of a network that is pressurized on the supply side and fed from a central cooling station. Where this is not the case, water taken from the normal water supply network can simply be used. The coolant supply line 16 is accordingly designed as a branch line of such a supply network 26. The network pressure is sufficient to ensure proper coolant flow in the area of the heat exchanger 14. The coolant drain line 17 opens into a drain pipe 27 which leads back to the central cooling station or, if tap water is used, opens into the normal sewage system. To ensure that the temperature of the oil in the annular space 9 is as constant as possible, a thermostatically controllable throttle valve 28 is provided in the area of the coolant discharge line 17, which regulates the coolant throughput as a function of the coolant temperature or, as here, suitably as a function of the oil temperature. For this purpose, a sensor 29 that detects the oil temperature is provided. In order to adhere to the oil level in the annular space 9 at a desired level and to prevent the creation of an overpressure in the annular space 9, an oil compensation container 30 is provided which is connected to the annular space 9 via a spur line 31. The stub 31 is in the range a closure cap 10 arranged screwed ßstutzen.

Die Spindel 7 samt den hierauf anzuordnenden Teilen in Form der Stützlager 8, der Wärmetauscher 14 und der diesen zugeordneten Halteböcke 23 sowie Anschlußleitungen 15 und Ablaufleitungen 18 und der Schaufeln 19 bildet praktisch eine vormontierbare Baueinheit. Erst nach Montage dieser Teile werden der Mantel 2 aufgeschoben und die seitlichen Lagerstutzen montiert. Die Integration der Wärmetauscher 14 in den Presseur wirkt sich daher nicht nachteilig auf die Montage aus.The spindle 7 together with the parts to be arranged thereon in the form of the support bearing 8, the heat exchanger 14 and the associated support brackets 23 as well as connecting lines 15 and drain lines 18 and the blades 19 practically form a preassembled structural unit. Only after these parts have been assembled are the jacket 2 pushed on and the lateral bearing supports assembled. The integration of the heat exchanger 14 in the impression roller therefore does not have an adverse effect on the assembly.

Claims (10)

1. A cylinder for machines processing web material, more especially an impression cylinder for gravure presses, comprising a tubular casing (2) which is mounted for rotation on lateral bearing housings (5) through which there extends through a spindle (2) placed in the direction of rotation and having an external diameter smaller than internal diameter of the casing (2), and is connected therewith via at least one support bearing (8) which is arranged symmetrically in relation to the center of the cylinder and coaxially in relation to the axis of the cylinder, and the supporting bearing (8) bridges over the annular space (9), which is formed as a receiving space for a filling of oil filling it at feast in part and is placed between the spindle (7) and the casing (2), characterized in that at least one heat exchanger (14) is placed in the annular space (9) between the spindle (7) and the casing (2) and surrounds the spindle (7) and is mounted on holders (23) attached to the spindle (7) and is connected by means of connection lines (15) passing by way of associated spindle recesses (21 and 22) and at least partly in the form of flexible pipe sections, with an external coolant supply line (16) and drain line (17), respectively.
2. The cylinder as claimed in claim 1, characterized in that the heat exchanger (14) or the heat exchangers, respectively, is or are in the form of a tubular coil or, respectively, coils surrounding the spindle (7).
3. The cylinder as claimed in any one of the preceding claims, characterized in that the casing (2) is sealed off by a closure caps (10) fitting over the ends of the spindle (7) and making sealing engagement with the lateral ends of the casing, and a respective connection sleeve (25) is mounted therein, by means of which the coolant supply line (16) and, respectively, the coolant drain line (17) are connected with the respective adjacent connection line (15).
4. The cylinder as claimed in any one of the preceding claims, characterized in that the connection lines (15) each have a flexible line section at least in a region including the gap between one closure cap (10) and the adjacent end of the spindle (7).
5. The cylinder as claimed in any one of the preceding claims, characterized by at least two heat exchangers (14) and which are preferably series connected for fluid flow, and said heat exchangers are respectively connected by a connecting line (18) which passes through a recess (21 and 22) in the spindle and bridges over support bearing region.
6. The cylinder as claimed in any one of the preceding claims, characterized in that oil strippers (vanes 19) are provided in a part of the annular space (9), free of heat exchangers, and fixed on the spindle (7), said strippers extending radially from the spindle into the vicinity of the casing (2), said vanes being provided with spindle recesses (20 and 21) leading into the vicinity of an associated heat exchanger (14).
7. The cylinder as claimed in any one of the preceding claims, characterized in that the spindle (7) is provided with a centrally arranged axial through hole (21), from which radial holes (20 and 22) extend which are associated with the oil strippers (19) and, respectively, receive the adjoining lines (15) or, respectively, the connection line, and of these radial holes (20 and 22) preferably the ones (22) associated with the adjoining lines (15) and, respectively, the connection line are inclined in relation to the spindle axis.
8. The cylinder as claimed in any one of the preceding claims, characterized in that the adjoining ducts (15) and, respectively, the connection line (18) are designed overall in the form of flexible line sections running through the spindle recesses (21 and 22), and at least the flexible line section forming the adjoining line (18) and more especially all the line sections, is or, respectively, are undersize in relation to the associated spindle recess (21 and 22).
9. The cylinder as claimed in any one of the preceding claims, characterized in that the coolant supply line (16) is connected with a coolant network (26) which on the supply side is under pressure.
10. The cylinder as claimed in any one of the preceding claims, characterized by a choke valve (28) in the coolant drain line (17) and is controlled thermostatically, preferably in manner responsive to the oil temperature.
EP85112878A 1984-10-25 1985-10-11 Cylinder for web-processing machines Expired - Lifetime EP0179363B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85112878T ATE50200T1 (en) 1984-10-25 1985-10-11 CYLINDERS FOR WEB MATERIAL PROCESSING MACHINES.

Applications Claiming Priority (2)

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DE19843439090 DE3439090A1 (en) 1984-10-25 1984-10-25 CYLINDERS FOR RAILWAY MATERIAL MACHINERY
DE3439090 1984-10-25

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EP0179363A2 EP0179363A2 (en) 1986-04-30
EP0179363A3 EP0179363A3 (en) 1987-12-09
EP0179363B1 true EP0179363B1 (en) 1990-02-07

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US (1) US4617864A (en)
EP (1) EP0179363B1 (en)
JP (1) JPS61109909A (en)
AT (1) ATE50200T1 (en)
DE (2) DE3439090A1 (en)
DK (1) DK487185A (en)
FI (1) FI79058C (en)
NO (1) NO162551C (en)

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Also Published As

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DE3575887D1 (en) 1990-03-15
NO853571L (en) 1986-04-28
FI79058B (en) 1989-07-31
DE3439090C2 (en) 1987-01-08
DE3439090A1 (en) 1986-04-30
FI79058C (en) 1989-11-10
FI854113L (en) 1986-04-26
US4617864A (en) 1986-10-21
NO162551B (en) 1989-10-09
DK487185A (en) 1986-04-26
NO162551C (en) 1990-01-17
DK487185D0 (en) 1985-10-24
FI854113A0 (en) 1985-10-22
JPS61109909A (en) 1986-05-28
EP0179363A2 (en) 1986-04-30
ATE50200T1 (en) 1990-02-15
EP0179363A3 (en) 1987-12-09

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