EP1789353B2 - Procede pour effectuer un remplacement de bobine automatique - Google Patents

Procede pour effectuer un remplacement de bobine automatique Download PDF

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Publication number
EP1789353B2
EP1789353B2 EP05752557A EP05752557A EP1789353B2 EP 1789353 B2 EP1789353 B2 EP 1789353B2 EP 05752557 A EP05752557 A EP 05752557A EP 05752557 A EP05752557 A EP 05752557A EP 1789353 B2 EP1789353 B2 EP 1789353B2
Authority
EP
European Patent Office
Prior art keywords
roll
web
reel
support
running
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.)
Not-in-force
Application number
EP05752557A
Other languages
German (de)
English (en)
Other versions
EP1789353A1 (fr
EP1789353B1 (fr
Inventor
Anton Löffler
Thomas Potzkai
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Koenig and Bauer AG
Original Assignee
Koenig and Bauer AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=34969898&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1789353(B2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Priority claimed from PCT/EP2004/052176 external-priority patent/WO2005054101A2/fr
Application filed by Koenig and Bauer AG filed Critical Koenig and Bauer AG
Priority to EP05752557A priority Critical patent/EP1789353B2/fr
Publication of EP1789353A1 publication Critical patent/EP1789353A1/fr
Application granted granted Critical
Publication of EP1789353B1 publication Critical patent/EP1789353B1/fr
Publication of EP1789353B2 publication Critical patent/EP1789353B2/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H19/00—Changing the web roll
    • B65H19/10—Changing the web roll in unwinding mechanisms or in connection with unwinding operations
    • B65H19/18—Attaching, e.g. pasting, the replacement web to the expiring web
    • B65H19/1805—Flying splicing, i.e. the expiring web moving during splicing contact
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2301/00—Handling processes for sheets or webs
    • B65H2301/40—Type of handling process
    • B65H2301/41—Winding, unwinding
    • B65H2301/413—Supporting web roll
    • B65H2301/4134—Both ends type arrangement
    • B65H2301/41346—Both ends type arrangement separate elements engaging each end of the roll (e.g. chuck)
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2511/00—Dimensions; Position; Numbers; Identification; Occurrences
    • B65H2511/10—Size; Dimensions
    • B65H2511/11—Length
    • B65H2511/114—Remaining length of web roll
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2515/00—Physical entities not provided for in groups B65H2511/00 or B65H2513/00
    • B65H2515/30—Forces; Stresses
    • B65H2515/37—Elasticity modulus
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2701/00—Handled material; Storage means
    • B65H2701/10—Handled articles or webs
    • B65H2701/18—Form of handled article or web
    • B65H2701/184—Wound packages
    • B65H2701/1844—Parts concerned
    • B65H2701/18442—Core

Definitions

  • the invention relates to methods for carrying out a flying reel change according to the features of claim 1.
  • Such roll changers are used on printing machines and serve to supply the material web used as printing material.
  • paper webs are used as a rule. The material web is wound on a roll of material and runs from this roll of material.
  • the running material roll has a constantly changing intrinsic resonance speed.
  • critical vibration states at the outgoing material roll can occur when a certain residual thickness is undershot due to vibration excitations in the region of the intrinsically critical resonance speed.
  • the FR 2 076 474 shows a single recording for rolls of material, with two jaw rows are arranged one behind the other.
  • the DE 36 27 533 A1 describes a roller carrier in which a worn-out role a support device is employed.
  • the DE 100 56 274 A1 discloses a mandrel with two successively arranged rows of clamping troughs, wherein the diameter of a row of 150 to 160 mm and the diameter of the other row of 70 to 80 mm is variable.
  • the EP 0 441 152 A the EP 0 708 047 A and the EP 0 413 890 A are devices for unwinding rollers known, each having trunnions with movable jaws.
  • the US 3 516 617 A and the US 4 173 314 A describe methods for flying reel change, in which the reel change is performed at a determined for a reel diameter residual roll size.
  • the invention has for its object to provide methods for performing a flying role change:
  • the invention is based on the idea to reduce the free vibration length of the running material roll, thereby affecting the intrinsic critical resonance speed of the running material roll in the desired manner.
  • the reduction of the free oscillation length between the chucking points of the outgoing material roll on the reel changer occurs in that a support device is provided which comes into contact with the peripheral surface of the outgoing material roll.
  • This additional support of the roll of material between the clamping points the free vibration length can be significantly reduced. If the support device is brought into abutment, for example, exactly in the middle between the clamping points on the peripheral surface of the outgoing roll of material, the free oscillation length is halved in this way and the intrinsically critical Resonanzwindshot moved accordingly upward.
  • the support device is arranged such that it can come into contact with the arrangement of the outgoing roll of material in the position provided for the flying roll change position on the peripheral surface of the running roll of material. Because the critical vibration states of the running material roll occur in particular shortly before the exhaustion of the roll of material at a relatively low residual thickness, so that in particular in the phase immediately preceding the roll change, a support of the outgoing roll is necessary.
  • the support device is designed constructively, is basically arbitrary, as long as sufficient support of the running material roll to reduce the free length of vibration is guaranteed.
  • the support device has at least one circumferentially mounted support belt which can be pressed against the circumferential surface of the running material roll.
  • This support belt can for example be stored on rollers, and runs at a speed corresponding to the peripheral speed of the running material roll.
  • the free oscillation length can be greatly reduced.
  • This can be achieved in that a plurality of support means are provided, which come to rest adjacent to each other on the peripheral surface of the running roll of material to the plant.
  • the free oscillation length only corresponds to the respective distance between two adjacent support devices or the distance between the first support device and the last support device to the clamping points of the running material roll. As a result, thus the free vibration length of the running material roll can be influenced in any way.
  • the support device can be implemented particularly simply if it does not have its own drive device.
  • the support means can be driven by transmission of frictional forces from the running roll of material itself.
  • the support means should preferably be made of a wear-resistant material with a relatively high coefficient of friction in the region of the contact surface with the roll of material.
  • a drive device is provided on the support device, with which the support device is driven.
  • an electric motor may be provided for this purpose, with which one of the bearing rollers is driven for supporting the support belt.
  • the use of the support device is desired only in certain phases of the operation of the reel changer, in particular in the phase immediately before the flying reel change. For this reason, it is particularly advantageous if the support device is movably mounted between at least two functional positions.
  • the first functional position corresponds to the actual insertion position in which the support device comes to rest on the circumferential surface of the running material roll and supports the roll of material accordingly.
  • the second functional position corresponds to a rest position in which the support device is not engaged with the running material roll.
  • the support device is fastened relative to the roll changer.
  • the support means is attached to the roll stand of the roll changer. This has the advantage that the support device is moved during pivoting of the roll stand and thus no relative movement between the support means and the correspondingly associated roll of material occurs during pivoting of the roll stand.
  • the support device is brought even before the arrangement of the running roll of material in the intended position for flying role change position on the running roll of material to the plant, so that the outgoing roll of material supported even during the pivoting of the roll stand of the support means is, preferably even before the roll of material from standstill is accelerated.
  • the employment takes place simultaneously with the support belt.
  • the support means between two support arms of the roll stand can be attached, wherein the support arms also carry the corresponding associated roll of material.
  • the support device may also be fastened to a foundation below the position of the outgoing material roll intended for the flying roll change, so that the support device as a result is not an integral part of the roll changer.
  • This embodiment is particularly advantageous if the support means can be sunk in the foundation, so that the support means in its rest position, in which the support means is sunk in the foundation, no obstruction.
  • At least one sensor for measuring a supporting parameter for example the currently applied supporting force or the belt tension of the supporting belt, can be provided on the supporting device.
  • the respectively provided control device or the correspondingly used control loop can process the measurement results and control or regulate the support device to a predetermined desired value.
  • the support device After the method for operating the new reel changer, the support device is already before the arrangement of the running material roll in the position suitable for flying reel change on the running material roll brought to the plant. During pivoting of the roll stand for the arrangement of the running roll of material in the position suitable for flying roll change position, the support device remains in engagement with the running roll of material and ensures that the running roll of material is also supported during the pivoting operation. As soon as the roll stand has reached the end position in which the running material roll assumes the position suitable for flying roll change, the support device remains in engagement with the running roll of material until the flying roll change has ended and the old roll of material can be braked accordingly.
  • a support device may be provided.
  • the avoidance of intrinsically critical resonance speeds can also be improved by reducing the free oscillation length of the outgoing material web by using longer mandrels.
  • material web speeds of max. 12 m / s can be achieved.
  • clamping jaws adjacent to each other in a clamping jaw row are arranged in the circumferential direction on the clamping mandrel, which leads to a high-strength clamping of the material roll on the clamping mandrel.
  • Fig. 1 is a first embodiment of a roll exchanger 01 for feeding a web of material 02, in particular a paper web, shown schematically in a printing press, not shown.
  • a pivotable about a pivot axis 03 roll stand 04 is provided, which is formed by two in the image plane behind one another supporting arms.
  • opposite receptacles 05 for example clamping mandrels 05 are fastened, between which material rolls 06; 07 can be clamped on the roll changer 01.
  • On reel changer 01 in the process state shown, an outgoing material roll 06 and a new material roll 07 prepared for the flying reel change are clamped.
  • the roll stand 04 was previously in the in Fig. 1 shown pivoted position, so that the running material roll 06 occupies the required position for the flying role change.
  • a support belt 08 is pressed from below against the circumference of the new roll of material 07.
  • Fig. 1 Once the roll stand 04 in preparation for a flying roll change the in Fig. 1 has moved to the position shown mounted on the foundation 09 below the outgoing roll of material 06 support device 11 is extended upward until a supported on rollers 13 support belt 12 comes to rest on the circumference of the running roll of material 06 to the plant.
  • pneumatic actuating cylinder 14 are provided for extending the support means 11 .
  • the support belt 12 is synchronized by a frequency-controlled three-phase motor, not shown, to paper web speed. This web breaks are avoided when hiring.
  • the free oscillation length of the roll of material 06 is shortened between the receptacles 05, so that the intrinsic critical resonance speed of the roll of material 06 is shifted to a non-critical speed range.
  • a second embodiment of a roll changer 16 is shown.
  • the material web 02, the pivot axis 03, the roll stand 04, the receptacles 05, the expiring roll of material 06, the new roll of material 07 and a support belt 08 are provided for supporting and transmitting the driving forces of the new roll of material 07.
  • two support devices 17 and 18 are provided on the reel changer 16, which are each assigned to the left or right clamping point on the reel stand 04. As indicated by the support means 17 by dashed lines, the support means 17 and 18 can be adjusted in linear guides 19 and in this way at the changing diameters of the material rolls 06; 07 adapted and tracked.
  • each support straps 22 are provided, which at the periphery of the supported material roll 06; 07 can be brought to the plant.
  • pneumatic actuating cylinder 21 are provided by the retraction and extension of the bearing structure of the support straps 22 can be pivoted.
  • the procedure is as follows. First, the running material roll 06 is still in the so-called flow position on the right side of the pivot axis 03 (not shown). In this position, the expiring roll of material 06 is unwound as the printing process progresses until a certain roll diameter, i. H. a certain residual thickness of the roll of material 06 has fallen below. After falling below this predetermined residual thickness of the actuating cylinder 21 is extended and thereby brought the support belt 22 on the circumference of the roll of material 06 to the plant. In this way, the intrinsic resonance speed of the roll of material 06 is shifted in a non-critical speed range, so that the material web 02 can be withdrawn at an unchanged speed.
  • the roll of material 06 is pivoted by pivoting the roll stand 04 in the position to the left of the pivot axis 03, as in Fig. 2 is shown. Also during the pivoting movement of the support belt 22 abuts the periphery of the roll of material 06 and supports them in this way.
  • the support means 17; 18 can already be employed in the new, still at a standstill roll of material 07 and so rests during acceleration, it can be designed without a drive motor.
  • Fig. 3 shows a receptacle 05, which comes for example as a mandrel 05 to the roll changers 01 and 16 are used.
  • a support pin 24 is provided, whose outer circumference on the inner circumference of a roll of material 06; 07, in particular on the inner circumference of a sleeve 10, z. B. a cardboard tube 10, comes to rest.
  • a plurality of clamping jaws 26, in particular however at least four clamping jaws 26 are provided in the axial direction of the support pin 24 to the support pin 24.
  • the support pins 24 have a large insertion depth with which the free oscillation length between the clamping points can be reduced, at least two clamping jaws 26 in the direction of the longitudinal axis of the support pin 24, ie in the axial direction of the support pin 24, arranged one behind the other, which are aligned.
  • a plurality of mutually adjacent clamping jaws 26 are distributed over the circumference of the support pin 24, in particular evenly spaced.
  • the juxtaposed clamping jaws 26 form annular clamping jaw rows 27 and 28, each with eight clamping jaws 26.
  • the supporting pin 24 of the clamping mandrel 05 has an outer diameter D24 of about 150 mm.
  • a trunnion 24 is shown in cross section.
  • a length 124 of the trunnion 24 in the axial direction of the trunnion 24 is at least 250 mm.
  • lengths 124 of the trunnions 24 of at least 300 mm, in particular of at least 330 mm.
  • a length 126 of the clamping jaws 26 is in the axial direction of the support pin 24 at least 80 mm, in particular at least 95 mm.
  • a sum of the lengths 126 of the clamping jaws 26 in the axial direction of the supporting pin 24 is at least 300 mm, in particular 340 mm. In a further embodiment, the sum of the lengths 126 of the clamping jaws 26 is 380 mm.
  • a diameter D24 of the trunnion 24 is greater than 140 mm, in particular it is between 145 mm and 155 mm. Particularly advantageous is a diameter D24 between 148 mm and 152 mm.
  • Fig. 5 shows a lying in the two receptacles 05 roll of material 06; 07 with a sleeve 10, as it is preferably used in the reel changer described.
  • a wall thickness b10 of the sleeve 10 is more than 10 mm, in particular it is greater than 15 mm.
  • An inner diameter d10 of the sleeve 10 is 150.2 + 0.2 mm.
  • a determination of the web speed and / or the residual roll diameter during the flying reel change can also be carried out for carrying out the flying reel change.
  • the second, predetermined during bonding web speed or the minimum diameter of the residual role 06 is set in a further embodiment by the geometric dimension of the receptacle 10, in particular of the trunnion 24. Also, the reduced web speed depending on the length 126 of the clamping jaws 26 of the trunnion 26 can be set.
  • the reduction of the web speed and / or the determination of the minimum diameter of the residual roll 06 is controlled by a program together with the joining process.
  • the loading of the roller carrier 04 with the roll of material 06 by means of a sliding carriage 31, z. B. a scissor lift 31, as in the FIGS. 6 and 7 is shown.
  • wheels 33 are mounted, by which a horizontal movement of the sliding carriage 31 is possible.
  • a movement in height is also possible.
  • On the sliding carriage 31 is a support means 11 with a support belt 12 which is pivotally mounted on the scissor lift 31, arranged.
  • This support device 11 is essentially the same, previously described support means 11.
  • the support means 11 is motor-driven, z. B. by an AC motor, the support belt 12; 22 of the support device 11 accelerated to web speed and then applies by hydraulic to the expired roll of material 07.
  • the braking of the roll of material 07 is also supported by this engine, since the motor of the support device 11 along with the axle motor of the roller stand 04 slows down the same torque curve until the residual role 07 comes to a standstill.
  • the roll of material 06 is transported by a chain-driven trolley 32 to the paster 01. There, the trolley 32 moves with the material roll 06 mounted thereon at the ground level into the sliding carriage 31. On the trolley 32 wheels 34 are mounted, with which a movement of the trolley is made possible within the Scherenhubticians 31.
  • the scissor lift table 31 moves into a centering position and raises the roll of material 06 to about 1600 mm above the floor. Subsequently, the centered roll of material 06 is brought into the Einachsposition of the roll stand 04. Upon reaching the Einachsposition the signal "quill before" to the roll stand 04.
  • the receptacles 05 with the support pin 24 are moved into the roll of material 06. Are the receptacles 05 retracted with the trunnions 24 in the roll of material 06 and the jaws 26 spread, the scissor lift 31 is lowered and moved to the normal position with the signal "role einzeachst".
  • the support device 11 moves after the RollenarmJung to the expiring roll of material 07 (support position) and stabilizes them in the middle. With the command "knife before” the running material web 29 is separated from the roll of material 07 and stopped via the axle motor of the roll stand 04. As already described above, the stopping operation of the material roll 07 is supported by the support device 11 of the scissor lift table 31. The support belt 12 pivots off, the scissor lift table 31 moves into its loading position to load a new roll of material 07.
  • FIG. 8 A schematic view of the roll changer with different stages of roll supply is in the Fig. 8 shown.

Landscapes

  • Replacement Of Web Rolls (AREA)
  • Crushing And Grinding (AREA)
  • Air Transport Of Granular Materials (AREA)

Claims (1)

  1. Procédé pour effectuer un changement de bobine au vol, une première bande de matériau (02) d'un bobine de matériau (06) à remplacer étant reliée à une deuxième bande de matériau (29) d'une nouvelle bobine de matériau (07), la bobine de matériau (06) à remplacer défilant à une première vitesse de bande, la première bande de matériau (02) étant reliée à la deuxième bande de matériau (29) au plus tard à l'atteinte d'un diamètre minimal de la bobine résiduelle (06), ce diamètre minimal de la bobine résiduelle (06) étant déterminé avant la liaison de la première bande de matériau (02) à la deuxième bande de matériau (29), en fonction de propriété d'une douille (10) de la bobine résiduelle (06), le diamètre minimal de la bobine résiduelle (06) étant déterminé en fonction de propriétés de matériau de la douille (10) de la bobine de matériau (06 ; 07), la première vitesse de bande étant réduite à une deuxième vitesse de bande avant la liaison de la première bande de matériau (02) à la deuxième bande de matériau (29), et la première bande de matériau (02) étant reliée à la deuxième bande de matériau (29) à cette vitesse de bande réduite, la réduction de la vitesse de bande étant commandée conjointement avec le processus de liaison par l'intermédiaire d'un programme, et la détermination du diamètre minimal de la bobine résiduelle (06) étant commandée conjointement avec le processus de liaison par l'intermédiaire du programme.
EP05752557A 2004-09-15 2005-06-02 Procede pour effectuer un remplacement de bobine automatique Not-in-force EP1789353B2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP05752557A EP1789353B2 (fr) 2004-09-15 2005-06-02 Procede pour effectuer un remplacement de bobine automatique

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
PCT/EP2004/052176 WO2005054101A2 (fr) 2003-12-01 2004-09-15 Changeur de bobines et procede pour effectuer un changement de bobines automatique
EP05752557A EP1789353B2 (fr) 2004-09-15 2005-06-02 Procede pour effectuer un remplacement de bobine automatique
PCT/EP2005/052543 WO2006029911A1 (fr) 2004-09-15 2005-06-02 Procede pour effectuer un remplacement de bobine automatique

Publications (3)

Publication Number Publication Date
EP1789353A1 EP1789353A1 (fr) 2007-05-30
EP1789353B1 EP1789353B1 (fr) 2010-09-15
EP1789353B2 true EP1789353B2 (fr) 2012-09-05

Family

ID=34969898

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05752557A Not-in-force EP1789353B2 (fr) 2004-09-15 2005-06-02 Procede pour effectuer un remplacement de bobine automatique

Country Status (4)

Country Link
EP (1) EP1789353B2 (fr)
AT (1) ATE481340T1 (fr)
DE (1) DE502005010275D1 (fr)
WO (1) WO2006029911A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006042217B4 (de) * 2006-09-08 2011-07-14 KOENIG & BAUER Aktiengesellschaft, 97080 In einem Rollenwechsler für eine Rollendruckmaschine durchgeführtes Verfahren zum Verbinden einer ersten Materialbahn mit einer zweiten Materialbahn

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DE2627103A1 (de) † 1976-06-16 1977-12-22 Bhs Bayerische Berg Verfahren und vorrichtung zum automatischen erfassen des endes einer bahn oder eines abrisses und verbinden mit dem anfang einer neuen bahn, insbesondere in wellenpappenanlagen
DE2732644A1 (de) † 1977-07-19 1979-02-01 Siemens Ag Regelanordnung fuer einen rollentraeger
DE2917868A1 (de) † 1977-07-19 1980-11-13 Siemens Ag Regelanordnung fuer einen rollentraeger
EP0441152A2 (fr) † 1990-02-06 1991-08-14 MAN Roland Druckmaschinen AG Changeur de rouleaux
EP0866017A1 (fr) † 1997-03-21 1998-09-23 Schlumpf Ag Dispositif pour abloquer un tube sur un corps tubulaire entraíné rotativement
EP1046601A2 (fr) † 1999-04-23 2000-10-25 Kabushiki Kaisha Tokyo Kikai Seisakusho Mécanisme d'alimentation de bande à position ajustable pour une machine d'impression rotative
US20050184191A1 (en) † 2004-02-25 2005-08-25 Sonoco Development, Inc. Winding core and associated method

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US3516617A (en) 1968-07-24 1970-06-23 Avtron Mfg Inc Digital system for automatic splice control
US3948715A (en) * 1973-05-21 1976-04-06 Rengo Co., Ltd. Auto-detecting means for detecting drawnout termination end of old paper roll and beginning end of new paper roll in paper splicing apparatus
JPS5752301B2 (fr) * 1974-06-01 1982-11-06
DE2619236C3 (de) * 1976-04-30 1989-06-08 Siemens AG, 1000 Berlin und 8000 München Verfahren zur Steuerung des fliegenden Anschließens einer Bahn von einer zweiten Wickelrolle an eine von einer ersten Wickelrolle überlaufende Bahn
US4173314A (en) 1978-04-17 1979-11-06 Cary Metal Products, Inc. Continuous web supply apparatus
DE3927172A1 (de) * 1989-08-02 1991-02-07 Eae Ewert Ahrensburg Electroni Verfahren zur durchfuehrung eines fliegenden rollenwechsels
DE10060757A1 (de) * 2000-12-07 2002-06-13 Heidelberger Druckmasch Ag Fliegender Rollenwechsler in einer Rollenrotationsdruckmaschine
JP3451437B2 (ja) * 2001-03-15 2003-09-29 株式会社東京機械製作所 巻取紙支持装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2627103A1 (de) † 1976-06-16 1977-12-22 Bhs Bayerische Berg Verfahren und vorrichtung zum automatischen erfassen des endes einer bahn oder eines abrisses und verbinden mit dem anfang einer neuen bahn, insbesondere in wellenpappenanlagen
DE2732644A1 (de) † 1977-07-19 1979-02-01 Siemens Ag Regelanordnung fuer einen rollentraeger
DE2917868A1 (de) † 1977-07-19 1980-11-13 Siemens Ag Regelanordnung fuer einen rollentraeger
EP0441152A2 (fr) † 1990-02-06 1991-08-14 MAN Roland Druckmaschinen AG Changeur de rouleaux
EP0866017A1 (fr) † 1997-03-21 1998-09-23 Schlumpf Ag Dispositif pour abloquer un tube sur un corps tubulaire entraíné rotativement
EP1046601A2 (fr) † 1999-04-23 2000-10-25 Kabushiki Kaisha Tokyo Kikai Seisakusho Mécanisme d'alimentation de bande à position ajustable pour une machine d'impression rotative
US20050184191A1 (en) † 2004-02-25 2005-08-25 Sonoco Development, Inc. Winding core and associated method

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Title
DR.-ING. MANFRED KÖNIG, DIPL.-ING. DIRK MÜLLER: "Hartpapierhülsen in Papierrollen im Tiefdruck", INFORMATIONEN, November 1988 (1988-11-01), pages 1 - 8 †
WOLFGANG WALENSKI: "Der Rollenoffsetdruck", 1995, ISBN: 3-931436-01-2, pages: 6-11 - 117-129 †

Also Published As

Publication number Publication date
WO2006029911A1 (fr) 2006-03-23
ATE481340T1 (de) 2010-10-15
EP1789353A1 (fr) 2007-05-30
DE502005010275D1 (de) 2010-10-28
EP1789353B1 (fr) 2010-09-15

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