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 preamble of claim 1 or 2.
• 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.
• relatively large web widths for example web widths> 3,600 mm
• very high web take-off speeds for example
• Web take-off speeds of 15 m / s it can come when falling below a certain residual thickness to critical vibration conditions on the running roll of material due to vibration excitations in the range of intrinsic resonance speed. To avoid these critical vibration states, it is therefore often necessary that the web speed must be shut down when falling below a certain residual thickness of the material. In such applications, this means that either the roll of material can not be completely consumed in order to avoid critical vibration conditions or the web take-off speed must be reduced during the roll change. Both measures increase the printing costs in an undesirable manner.
• FR 2 076 474 shows a single receptacle for rolls of material, wherein two rows of clamping jaws are arranged one behind the other.
• DE 100 56 274 A1 discloses a mandrel with two successively arranged clamping tank rows, 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.
• EP 0 441 152 A, EP 0 708 047 A and EP 0 413 890 A disclose devices for unwinding rolls which each have supporting journals with movable clamping jaws.
• 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.
• 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 a sufficient support of the running material roll to reduce the free oscillation length is guaranteed.
• the support means at least one circumferentially mounted support belt which can be pressed against the peripheral 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 outgoing 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 and the wear appropriately assigned 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 brought into contact with the running roll of material in the position suitable for the flying reel change already before the arrangement of the outgoing material roll. During the pivoting of the roll stand for the arrangement of the running roll of material in the For flying reel change suitable position, the support device remains in engagement with the running roll of material and ensures that the running material roll is supported during the pivoting process. 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.
• a plurality of jaws adjacent to each other in each case in a jaw row in particular evenly spaced from each other, distributed over the circumference of the trunnion.
• two clamping jaw rows arranged in the axial direction, each with eight clamping jaws 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 shows a first embodiment of a roll changer with support means in a side view.
• FIG. 2 shows a second exemplary embodiment of a roll changer with supporting device in a lateral view
• 3 shows a mandrel in perspective view.
• FIG. 5 shows a cross section through a roll of material with receptacles.
• Fig. 6 is a schematic view of a scissor lift with a new roll of material
• FIG. 7 shows a schematic view of a scissor lift table with a support device on an outgoing material roll
• Fig. 8 is a schematic view of the roll changer.
• a first embodiment of a roll exchanger 01 for feeding a web of material 02, in particular a paper web, is 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.
• a supporting device 11 fastened to the foundation 09 underneath the running material roll 06 is lifted upwards until a support belt 12 mounted on rolls 13 reaches the circumference of the running material roll 06 comes 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.
• 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 running material roll 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 running roll of material 06 is unwound as the printing process progresses until a certain roll diameter, ie one 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 intrinsically critical resonance speed of the roll of material 06 is shifted to a non-critical speed range, so that the material web 02 can be removed at the same speed.
• the roll of material 06 is pivoted by pivoting the roll stand 04 in the position left of the pivot axis 03, as shown in Fig. 2. Even during the pivoting movement of the support belt 22 is on the circumference of the material roll 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, for example, is used as a tensioning dome 05 on the roll changers 01 and 16.
• 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, to the plant comes.
• a plurality of jaws 26 for non-rotatable connection of the roll of material 06; 07 with the mandrels 05 by force and form fit a plurality of jaws 26, but in particular 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 support pin 24 is shown in cross section.
• a length l24 of the trunnion 24 in the axial direction of the trunnion 24 is at least 250 mm.
• Lengths I24 of the trunnions 24 of at least 300 mm, in particular of at least 330 mm, are also advantageous.
• a length I26 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 I26 of the clamping jaws 26 is in the axial direction of the support pin 24 at least 300 mm, in particular 340 mm. In a further embodiment, the sum of the lengths I26 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 length 110 of the sleeve 10 of the roll of material 06; 07, on the Clamping jaws 26 of the trunnion 24 rests, more than 4000 mm, in particular more than 4200 mm.
• a wall thickness b10 of the sleeve 10 is more than 10 mm, in particular it is greater than 15 mm.
• a sleeve wall thickness b10 greater than 17 mm, in particular greater than 20 mm, is advantageous.
• 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 I26 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.
• a sliding carriage 31 On the sliding carriage 31 wheels 33 are mounted, through 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.
• 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 in front", the running material web 29 is separated from the material roll 07 and stopped via the axle motor of the roll stand 04. As already described above, the pushing operation of the material roll 07 is assisted by the support device 11 of the scissor lift table 31. The support belt 12 pivots from the scissor lift 31 moves to 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 shown in FIG. 8. LIST OF REFERENCE NUMBERS

Landscapes

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

Priority Applications (1)

Applications Claiming Priority (3)

Publications (3)

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• 2005
  • 2005-06-02 EP EP05752557A patent/EP1789353B2/fr not_active Not-in-force
  • 2005-06-02 DE DE502005010275T patent/DE502005010275D1/de active Active
  • 2005-06-02 WO PCT/EP2005/052543 patent/WO2006029911A1/fr active Application Filing
  • 2005-06-02 AT AT05752557T patent/ATE481340T1/de active

Non-Patent Citations (1)

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