EP0179363B1 - Cylindre pour machines de transformation de matériau en bande - Google Patents

Cylindre pour machines de transformation de matériau en bande 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
Authority
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.)
Expired - Lifetime
Application number
EP85112878A
Other languages
German (de)
English (en)
Other versions
EP0179363A2 (fr
EP0179363A3 (en
Inventor
Peter Dipl.-Ing. Maier
Arnold Niedermaier
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Albert Frankenthal AG
Original Assignee
Albert Frankenthal AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Albert Frankenthal AG filed Critical Albert Frankenthal AG
Priority to AT85112878T priority Critical patent/ATE50200T1/de
Publication of EP0179363A2 publication Critical patent/EP0179363A2/fr
Publication of EP0179363A3 publication Critical patent/EP0179363A3/de
Application granted granted Critical
Publication of EP0179363B1 publication Critical patent/EP0179363B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/08—Cylinders
    • B41F13/18—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.

Landscapes

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

Claims (10)

1. Cylindre destiné à des machines de traitement de matières en forme de feuille, en particulier un cylindre presseur pour des machines d'impression en héliogravure, ce cylindre étant muni d'une enveloppe tubulaire (2) montée en pivotement sur des flasques latérales (5), cette enveloppe étant traversée par un arbre (7) immobile dans le sens de rotation et présentant un diamètre externe inférieur au diamètre interne de l'enveloppe (2), celle-ci lui étant reliée via au moins un palier d'appui (8) disposé symétriquement au milieu du cylindre et coaxialement à l'axe de ce dernier, ce palier d'appui franchissant l'espace annulaire (9) ménagé entre l'arbre (7) et l'enveloppe (2), et conçu pour que vienne s'y loger un bain d'huile qui l'occupe au moins en partie, caractérisé en ce que dans l'espace annulaire (9) ménagé entre l'arbre (7) et l'enveloppe (2), est disposé au moins un échangeur de chaleur (14) entourant l'arbre (7), cet échangeur de chaleur étant logé sur des supports (23) fixés à l'arbre (7), tandis qu'il est relié à une canalisation externe d'admission (16) ou d'évacuation (17) d'agent réfrigérant, au moyen de canaux de jonction (15) réalisés au moins partiellement en forme de sections flexibles de tuyau souple, ces canaux de jonction passant par des évidements (21, 22) qui lui sont attribués et qui ont été pratiqués dans l'arbre. 2. Cylindre selon la revendication 1, caractérisé en ce que le ou les échangeur(s) de chaleur (14) peut (peuvent) être réalisés en forme de serpentin(s) entourant l'arbre (7).
3. Cylindre selon l'une quelconque des revendications précédentes caractérisé en ce que l'enveloppe (2) est étanchée par des clapets (10) recouvrant les extrémités de l'arbre (7) et venant s'appliquer en étanchement contre ses extrémités latérales, clapets dans lesquels est chaque fois logée une douille d'accouplement (25) au moyen de laquelle le conduit d'admission (16) de l'agent réfrigérant ou le conduit d'évacuation (17) de l'agent réfrigérant est relié à chaque conduit de jonction (15) adjacent.
4. Cylindre selon l'une quelconque des revendications précédentes caractérisé en ce que les conduits de jonctions (15) présentent chacun une section flexible de tuyau souple au moins dans la zone franchissant la distance comprise entre un clapet (10) et l'extrémité adjacente de l'arbre (7).
5. Cylindre selon l'une quelconque des revendications précédentes caractérisé en ce que l'on prévoit le fait qu'au moins deux échangeurs de chaleur (14) montés, de préférence, en série conformément à l'écoulement, soient reliés l'un à l'autre via un conduit de raccordement (18) franchissant la zone des paliers d'appui, et qui traverse un évidement (21, 22) pratiqué dans l'arbre.
6. Cylindre selon l'une quelconque des revendications précédentes caractérisé en ce que l'on prévoit, dans une zone de l'espace annulaire (9) exempte d'échangeur de chaleur, des racleurs d'huile (ailettes 19) s'étendant jusque dans la zone de l'enveloppe (2), ces racleurs d'huile étant fixés à l'arbre (7), tout en s'en écartant radialement, des évidements (20, 21) pratiqués dans l'arbre et conduisant à la zone occupée par un échangeur de chaleur (14) leur étant attribué.
7. Cylindre selon l'une quelconque des revendications précédentes caractérisé en ce que l'arbre (7) est muni d'un alésage axial (21) de passage disposé en position centrale, alésage d'où partent les évidements radiaux (20, 22) dans lesquels viennent se loger les conduits de jonction (15) ou les conduits de raccordement (18), ou encore les évidements radiaux attribués aux racleurs d'huile (19), les évidements radiaux (22) attribués aux conduits de jonction (15) ou au conduit de raccordement (18) étant disposés, de préférence, en position inclinée par rapport à l'axe de l'arbre.
8. Cylindre selon l'une quelconque des revendications précédentes caractérisé en ce que les conduits de jonction (15) ou le conduit de raccordement (18) sont réalisés dans leur ensemble en forme de sections flexibles de tuyau souple, traversant les évidements (21, 22) qui leur sont attribués et qui sont pratiqués dans l'arbre, tandis qu'au moins la section de tuyau souple constiu- ant le conduit de raccordement (18) et, de préférence, toutes les sections de tuyau souple est ou sont sous-dimensionnées par rapport à l'évidement (21, 22) qui lui ou leur est attribué et qui est pratiqué dans l'arbre.
9. Cylindre selon l'une quelconque des revendications précédentes caractérisé en ce que le conduit d'admission (16) de l'agent réfrigérant est relié à un réseau (26) d'agent réfrigérant se trouvant sous pression, dans le sens aller.
10. Cylindre selon l'une quelconque des revendications précédentes caractérisé en ce que l'on prévoit, dans le conduit d'évacuation (17) de l'agent réfrigérant, une soupape thermostatique d'étranglement (28) commandée, de préférence, en fonction de la température de l'huile.
EP85112878A 1984-10-25 1985-10-11 Cylindre pour machines de transformation de matériau en bande Expired - Lifetime EP0179363B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85112878T ATE50200T1 (de) 1984-10-25 1985-10-11 Zylinder fuer bahnfoermiges material verarbeitende maschinen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3439090 1984-10-25
DE19843439090 DE3439090A1 (de) 1984-10-25 1984-10-25 Zylinder fuer bahnfoermiges material verarbeitende maschinen

Publications (3)

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

Family

ID=6248748

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85112878A Expired - Lifetime EP0179363B1 (fr) 1984-10-25 1985-10-11 Cylindre pour machines de transformation de matériau en bande

Country Status (8)

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

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WO2006000516A1 (fr) 2004-06-25 2006-01-05 Koenig & Bauer Aktiengesellschaft Cylindres pour machines traitant des materiaux sous forme de bande

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006000516A1 (fr) 2004-06-25 2006-01-05 Koenig & Bauer Aktiengesellschaft Cylindres pour machines traitant des materiaux sous forme de bande
DE102004030702B3 (de) * 2004-06-25 2006-02-09 Koenig & Bauer Ag Zylinder für bahnförmiges Material verarbeitende Maschinen

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NO162551B (no) 1989-10-09
NO162551C (no) 1990-01-17
FI79058C (fi) 1989-11-10
DE3439090A1 (de) 1986-04-30
JPS61109909A (ja) 1986-05-28
US4617864A (en) 1986-10-21
DK487185A (da) 1986-04-26
FI854113L (fi) 1986-04-26
EP0179363A2 (fr) 1986-04-30
DE3575887D1 (de) 1990-03-15
DE3439090C2 (fr) 1987-01-08
DK487185D0 (da) 1985-10-24
FI854113A0 (fi) 1985-10-22
NO853571L (no) 1986-04-28
ATE50200T1 (de) 1990-02-15
FI79058B (fi) 1989-07-31
EP0179363A3 (en) 1987-12-09

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