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WO2025110987A1 - Fermoir pour produire des produits en rouleau sans noyau - Google Patents

Fermoir pour produire des produits en rouleau sans noyau Download PDF

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Publication number
WO2025110987A1
WO2025110987A1 PCT/US2023/080453 US2023080453W WO2025110987A1 WO 2025110987 A1 WO2025110987 A1 WO 2025110987A1 US 2023080453 W US2023080453 W US 2023080453W WO 2025110987 A1 WO2025110987 A1 WO 2025110987A1
Authority
WO
WIPO (PCT)
Prior art keywords
log
mandrel
logs
conveyor
mandrels
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.)
Pending
Application number
PCT/US2023/080453
Other languages
English (en)
Inventor
Michael E. Techlin
Cory Schubring
Benjamin MANDERS
Emanuele MORICONI
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.)
BW Converting Inc
Original Assignee
BW Converting Inc
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 BW Converting Inc filed Critical BW Converting Inc
Priority to PCT/US2023/080453 priority Critical patent/WO2025110987A1/fr
Publication of WO2025110987A1 publication Critical patent/WO2025110987A1/fr
Pending 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
    • B65H19/22—Changing the web roll in winding mechanisms or in connection with winding operations
    • B65H19/2292—Removing cores or mandrels from web roll after winding
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H75/00—Storing webs, tapes, or filamentary material, e.g. on reels
    • B65H75/02—Cores, formers, supports, or holders for coiled, wound, or folded material, e.g. reels, spindles, bobbins, cop tubes, cans, mandrels or chucks
    • B65H75/18—Constructional details
    • B65H75/24—Constructional details adjustable in configuration, e.g. expansible
    • B65H75/242—Expansible spindles, mandrels or chucks, e.g. for securing or releasing cores, holders or packages
    • B65H75/248—Expansible spindles, mandrels or chucks, e.g. for securing or releasing cores, holders or packages expansion caused by actuator movable in axial direction
    • B65H75/2484—Expansible spindles, mandrels or chucks, e.g. for securing or releasing cores, holders or packages expansion caused by actuator movable in axial direction movable actuator including wedge-like or lobed member
    • 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
    • B65H2301/414—Winding
    • B65H2301/41419—Starting winding process
    • B65H2301/41429—Starting winding process in coreless applications
    • 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
    • B65H2301/417—Handling or changing web rolls
    • B65H2301/418—Changing web roll
    • B65H2301/4181—Core or mandrel supply
    • B65H2301/41818—Core or mandrel supply mandrels circulating (cycling) in machine or system
    • 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
    • B65H2701/19—Specific article or web
    • B65H2701/1924—Napkins or tissues, e.g. dressings, toweling, serviettes, kitchen paper and compresses

Definitions

  • This disclosure is directed to methods and apparatus for producing coreless roll products, and more particularly to the production of coreless bathroom tissue and kitchen towel (also called household towel).
  • the disclosure is also applicable to the production of other coreless rolled products, such as nonwovens for canister wipes.
  • Some of the methods and apparatus are also applicable to the production of roll products with cores, which are typically, though not exclusively, tubes made of cardboard or other relatively thick paper.
  • a rewinder is used to convert large parent rolls of paper into smaller sized rolls of bathroom tissue, kitchen towel, hardwound towel, industrial products, and the like.
  • a rewinder line usually comprises one or more unwinds, modules for paper finishing (e.g., embossing, printing, perforating), a rewinder for winding the paper into an elongated roll, commonly referred to as a log, and a tail sealing unit.
  • the rewinder line may also include a mandrel extractor for withdrawing winding mandrels to make coreless logs.
  • the rewinder produces logs which are about 90 to 203 mm in diameter for bathroom tissue and kitchen towel and about 100 to 350 mm in diameter for hardwound towel and industrial products.
  • Log length is usually about 1.5 to 5.4 m, depending on the width of the parent roll.
  • the logs are subsequently cut transversely to obtain small rolls about 90 to 115 mm long for bathroom tissue and about 200 to 300 mm long for kitchen towel and hardwound towel.
  • the web from which a through air dried (TAD) household towel product is made may be of such a high caliper (thickness) that a coreless roll made with it can be of sufficient density and column strength to withstand the demands of packaging and shipping with a relatively short length of paper in the roll, which means a higher cycle rate is required to run at a given web speed.
  • TAD through air dried
  • Increasing consumer demand for coreless products also tends to drive the cycle rates required of the coreless converting equipment higher, as producers require higher throughput to keep up with production needs.
  • the method and apparatus described herein provides for sustained, reliable, high throughput production of coreless rolls of high quality.
  • Figure 1 is a schematic side elevation of a coreless winding mandrel extraction and mandrel return system.
  • Figure 2 is a plan view of the system of Figure 1.
  • Figures 3A and 3B are isometric views of the system of Figure 1.
  • Figure 4 is a detail view of Figure 1 showing the side elevation of a 3-puller mandrel extractor and a portion of a mandrel return system.
  • Figure 5 is a detail view of Figure 1 showing the side elevation of a 3-puller mandrel extractor.
  • Figure 6 is a schematic side elevation of a 4-puller mandrel extractor.
  • Figure 7 is an alternate embodiment of a vertically oriented 2-puller mandrel extractor.
  • Figure 8 is a perspective view of an infeed roller assembly.
  • Figure 9 is a front view of a log alignment conveyor.
  • Figure 10 is a perspective view of a log lift conveyor.
  • Figure 11 is a perspective view of a lower infeed belt assembly.
  • Figure 12 is a front and side view of an upper infeed belt assembly.
  • Figure 13 is a perspective view of a main log conveyor assembly.
  • Figure 14 is a front view of an exemplary 3-puller mandrel extractor.
  • Figure 15 is a perspective view of the mandrel extractor of Figure 14.
  • Figure 16 is another perspective view of the mandrel extractor of Figure 14.
  • Figure 17A is a cross sectional view of a clasp of the mandrel extractor of Figure 14.
  • Figure 17B show isometric views of a clamping wedge of the clasp of Figure 17A.
  • Figure 17C is an isometric view of an actuator wedge of the clasp of Figure 17A.
  • Figure 18 is a plan view of a mandrel puller assembly with the mandrel extractor of Figure 14.
  • Figure 19 is perspective view of the mandrel puller assembly of Figure 18.
  • Figure 20 is a perspective view of a mandrel return alignment conveyor.
  • Figure 21 is a top view of a mandrel return conveyor.
  • Figure 22 is a perspective view of the mandrel return conveyor of Figure 21.
  • Figure 23 is a side elevation view of a mandrel return elevator.
  • Figure 24 is a perspective view of a mandrel return infeed table.
  • Figures 25-27 are graphs showing exemplary mandrel puller motion profiles.
  • Figures 28-29 are isometric views of a mandrel justifier.
  • Figure 30 is an isometric view of a mandrel assist wheel in a rewinder.
  • Figure 31 is an isometric view of a mandrel braking shoe and mandrel stop in a rewinder.
  • the rewinder may be in accordance with one of the several examples in the figures in US patent 11,247,863; the log formation and winding process may be assessed, and the converting line controlled based on the assessments, in accordance with the principles described in US patent 11,261,045; the winding mandrel may be introduced and inserted into the rewinder in accordance with US patent 6,422,501; a line of glue for web transfer may be applied to the winding mandrel in accordance with patent US 6,422,501; and transfer of the web onto the mandrel in the rewinder may be in accordance with US patent 6,056,229, the disclosures all of which are incorporated by reference herein.
  • a reinforcing agent and/or coating, and its application, may be in accordance with US patents 4,487,378, 5,730,387, 6,838,187, 10,213,066, and 11,046,540, Italian patent IT 102016000073544, Great Britain patent GB 1,554,619, and European patents EP 3,688,224 and EP 3,688,226, the disclosures all of which are incorporated by reference herein.
  • the roll product, the coreless production method and apparatus, and the mandrel extractor may be in accordance with US patents 9,284,147, 9,919,888, 9,975,720, 10,676,304, and 11,383,947, and with pending US 2021/0403266 (application ser. no. 17/350,213), the disclosures all of which are incorporated by reference herein.
  • the infeed table may be in accordance with pending US application ser. no. 17/944,688, the disclosure of which is incorporated by reference herein.
  • the roll product may be compressed and packaged in accordance with any known method and apparatus, for example US patents 5,027,582 and 5,186,099, and US 2016/0137398 (application ser. no. US 14/942,866), the disclosures all of which are incorporated by reference herein.
  • FIG. 1 shows a schematic drawing of a side elevation of a coreless winding mandrel extraction system and mandrel return system.
  • the process flow for the logs (L) is from left to right, while the process flow for the mandrels (M) returning on the system is from right to left.
  • the logs wound with the mandrels exit a rewinder 30, pass through a tail sealer 32, and then move to an infeed roller assembly 34, an alignment conveyor 36, a lift conveyor 38, an infeed conveyor assembly 40, and a main log conveyor 42 where extraction of the mandrels occurs in a mandrel extractor 44.
  • Fig. 2 shows a plan view of the system of Fig. 1. In Fig.
  • Figures 3A and 3B are isometric composites of Figs. 1 and 2.
  • the mandrels which have been extracted from logs are recirculated for reuse in winding new logs.
  • a mandrel is introduced by an infeed conveyor into a conventional rewinder 30 for winding a log (L) around the mandrel (M).
  • Figs. 4 and 5 are enlarged views of detail area 4-4 of Fig. 1 showing the side elevation of a 3-puller mandrel extractor 44 and a portion of a mandrel return system. Extracted mandrels are delivered to a return conveyor 50 for conveying the mandrels to an alignment conveyor 52 which shifts the mandrels over so that they can be picked up by a return elevator 56 and conveyed back to the storage magazine or hopper 58 for reuse in the rewinder 30.
  • Figs. 4 and 5 show the side elevation of a 3-puller mandrel extractor 44, where Fig. 5 omits the portion of the mandrel return conveyor system 50 shown in Fig. 4.
  • mandrels (M) are preferably extracted from logs (L) in groups of three. However, mandrels may be extracted from logs in groups of two, or even just one, using this machine.
  • a log (L) rolls down the infeed table 80 from the tail seal unit 32. The log's arrival at the end of the table may be predicted by sensors positioned along the table. The log rolling velocity may be attenuated by the infeed roller 82 shown in Fig. 8.
  • the infeed roller 82 may assist in providing timed delivery of the logs to the extractor by reducing or eliminating variation in the arrival times of the logs from the tail sealer.
  • the log next arrives at log alignment conveyor 36, for instance, as shown in Fig. 9.
  • the log alignment conveyor is adapted and configured to shift the log in the cross-machine direction toward the side of the machine with pullers to extract the mandrels (out of the page in Figs. 4 and 5).
  • the log alignment conveyor 36 ensures the axial ends, or faces, of the logs are aligned in a common plane, for instance, against a reference plate, which may be an axial end restraint associated with the mandrel extractor 44.
  • the logs are then directed to a log lift conveyor 38, for instance, as shown in Fig. 10.
  • the log lift conveyor 38 is adapted and configured to queue three successive logs.
  • the log lift conveyor 38 comprises a flighted belt conveyor.
  • the log lift conveyor 38 Upon the arrival of a log to the log lift conveyor 38 and alignment by the log alignment conveyor 36, the log lift conveyor receives the log and then indexes one flight (up in the drawings) to allow for the arrival and alignment of a second log. After the second log has arrived and been aligned, the log lift conveyor 38 indexes one flight up to allow for the arrival and alignment of a third log. After the third log has arrived and been aligned, the log lift conveyor 38 triple-indexes to feed the three logs through an infeed conveyor assembly 40 of the mandrel extractor and onto a main log conveyor 42, where the mandrels are extracted.
  • the first log in the three log succession, which was residing between the upper and lower infeed belts, is delivered to a first (rightmost position in the drawings) extraction station by the main log conveyor
  • the second log which was residing on the upper pulley of the log lift conveyor is delivered to a second (the center position in the drawings) extraction station by the main log conveyor
  • the log which was residing on the infeed table, at the pickup position of the log lift conveyor is delivered to a third (the leftmost position in the drawings) extraction station by the main log conveyor.
  • the main log conveyor 42 comes to a stop
  • the main log conveyor has aligned the longitudinal center axis of each mandrel with a clasp 60 (Figs. 14-17A,B,C) in a mandrel puller 62 (Figs. 18-19) of the mandrel extractor 44, for removal of the mandrels from the logs as described below.
  • the log lift conveyor 38 and infeed conveyor assembly 40 are free to execute single index motions, as described above, to accumulate arriving logs and stage them in preparation for the next tripleindex.
  • the time duration for removing the mandrels in the mandrel extractor 44 can be greater than the time interval between the arrival of logs at the log lift conveyor 38.
  • the next triple-index motion may be executed, which delivers the next group of three logs, staged at the infeed conveyor assembly 40 and log lift conveyor 38, to the extraction stations, and simultaneously delivers the current group of logs, which are now coreless logs, onto the outfeed table 46.
  • the discharged logs roll on the outfeed table 46 into a space beneath outfeed belts 47 which control the translational velocity of the rolling logs and meter them into the next machine in the process, typically a log accumulator 48.
  • each log on the main log conveyor 42 When each log on the main log conveyor 42 is in a position in which each mandrel's axis coincides substantially with the central axis of a clasp 60, restraints, for example as shown in US patent publication US20210403266A1, engage the periphery of each log to restrain the log from moving axially. Restraint of the log periphery may also prevent the log from rotating and also prevent the log from changing length.
  • the clasps 60 are moved toward the mandrel ends of the next group of logs by translating the puller carriage 92 toward the mandrel ends of the next group of logs, stopping when the clasps are in a mandrel engagement position to engage the ends of the mandrels. The clasps 60 then engage the mandrel ends.
  • the clasps 60 are capable of engaging the mandrel ends securely to apply an axial force to pull the mandrels out of the logs and also optionally to apply a rotational torque to rotate the mandrels inside the logs.
  • the mandrels are preferably rotated as they are withdrawn.
  • the mandrel puller carriage 92 may begin to travel slowly, moving the clasps 60 away from the logs slowly to facilitate stretching the mandrels and generate localized breakaway of the mandrels progressively within the logs. Without stopping following this relatively slow pulling, the mandrel puller carriage 92 may accelerate to a relatively higher velocity to withdraw the mandrels rapidly, to minimize the cycle period, which is favorable for operation at higher cycle rates.
  • the clasps 60 unclamp the mandrel ends. Due to inertia the mandrel ends tend to stay in the clasps 60 and remain in contact with the clasps. Drag guides 66 may engage the mandrels in a pinching fashion to restrain them axially, causing the mandrel ends to emerge from the clasps as the clasps continue traversing to their stop position.
  • the mandrel ends that are closer to the logs may be supported after the mandrels are withdrawn from the logs by mandrel end supports 65 that are raised into contact with the undersides of the mandrels for this purpose as the mandrels are withdrawn from the logs.
  • the mandrel puller carriage 92 comes to a stop.
  • the drag guides 66 disengage the mandrels.
  • the lower drag guides and the mandrel end supports move downward and deliver the mandrels onto the return conveyor 50 (Figs. 18-19, 21-22), which delivers them to the mandrel alignment conveyor 52 (Fig. 20), which shifts them in the cross-direction onto the elevator infeed table 54 (Fig. 24), which, when gate 55 opens, feeds them to the return elevator 56 (Figs. 1-3, 23) for delivery to the storage magazine or hopper 58.
  • the following process may be used.
  • the logs are directed to the log lift conveyor 38, as before, which is adapted and configured to queue two successive logs. All three paddles 88 on the log lift conveyor may be mounted, if the product logs will fit between them.
  • the center paddle can be removed to make more space between the first and last paddles, which may allow for larger diameter logs to be processed by the extractor.
  • the log lift conveyor 38 Upon the arrival of a log to the log lift conveyor 38 and alignment by the log alignment conveyor 36, the log lift conveyor receives the log and then executes a double-index, advancing the log from the pickup position to a dwell position in the infeed belts 40 without stopping the log on the uppermost pulley of the log lift conveyor. After the second log has arrived and been aligned, the log lift conveyor 38 triple-indexes to feed the two logs through the infeed conveyor assembly 40 of the mandrel extractor and onto the main log conveyor 42, where the mandrels are extracted.
  • the left and right extraction stations on the main log conveyor contain logs and are utilized, the center extraction station does not have a log and is not utilized.
  • the mandrel extraction process is similar to that described above for processing logs in groups of three, except two mandrels are withdrawn instead of three.
  • the logs are then discharged from the extractor during the next triple index motion.
  • the maximum log rate is less when logs are processed in groups of two than when logs are processed in groups of three, but the maximum log diameter that may be processed by the extractor is larger, which is a benefit.
  • a reinforcing agent and/or a coating with some coreless roll products.
  • a reinforcing agent may be applied on the first wrap or first several wraps of paper near the central hole, or to the surface of the mandrel itself, while a coating may be applied over a larger proportion of the wraps of paper.
  • Additives and/or coatings may be used to facilitate removal of a winding mandrel from the central hole of a roll of wound web material during manufacture. Additives and/or coatings may be used to improve the appearance of the central hole. Additives and/or coatings may be used to help the central hole retain its shape during the rest of the manufacturing process, shipping, or use by a consumer.
  • Additives and/or coatings may be used to facilitate the central hole returning to a round shape by a consumer if the roll is a compressed roll format or if the hole has become misshapen.
  • a reinforcing agent or a coating, or both may be applied, and may be the same composition or different compositions. If applied directly to the mandrel it may be a liquid, a solid, or a film.
  • the additive and/or coating may be water, or water-based.
  • Conventional spray nozzles may be provided to direct a reinforcing agent or a coating to a web or onto the mandrel surface.
  • Electrostatic spray guns may be provided to direct a reinforcing agent or a coating to a web.
  • a rewinder intended for webs around 2.8m (110 inches) wide may be provided with an array of around 10 spray nozzles or guns spaced across the width of the web. More or fewer spray guns may be provided depending on the width of their spray pattern and desired amount of overlap of the spray patterns. More spray guns may be provided for wider webs, and fewer for narrower webs.
  • the reinforcing agent or coating may be provided with a positive electrostatic charge. The reinforcing agent or coating may be provided with a positive electrostatic charge in a storage system located remotely to the electrostatic spray gun, reducing the risk of high voltage on the spray guns that could produce an arc.
  • the Trilogy model of spray gun offered by Nordson Corporation, 28601 Clemens Road, Westlake, OH 44145, may be a suitable spray gun.
  • the spray guns may be located opposite a fixed plate, with web passing between the spray guns and the plate.
  • the fixed plate may be a "pinch" plate disposed within a type of rewinder wherein it cooperates with pinching pads to sever the web, and thus is in a favorable position for the application of a reinforcing agent or coating to the portion of web following the web transfer, which will constitute the first wraps of web within the log.
  • the pinch plate may be grounded.
  • the pinch plate may be provided with a negative electrostatic charge.
  • the reinforcing agent and/or coating may be provided with a negative charge and the pinch plate may be provided with a positive charge.
  • An intent of having the reinforcing agent and/or coating oppositely charged from the pinch plate is to maximize the amount of sprayed material that deposits on the web and minimize the amount that drifts and lands elsewhere by having the airborne material drawn to the web by the opposite electrostatic charges in addition to having the material spray aimed at the web. Sprayed material that lands elsewhere is wasted, and it can contaminate the machine, requiring downtime to clean, and other inefficiencies.
  • the web may be provided with an electrostatic charge by suitable noncontact induction means, or by a contact method, such as by a rotating roll with a rubber, or other elastomer, cover suited to generating an electrostatic charge.
  • the spray guns may be timed to apply additive or coating to a length of web that will be wound near the central hole of the roll. If the web is severed at a perforation for transfer, the spray guns may be timed to begin applying reinforcing agent or coating to the web after the perforation which will be severed for transfer has moved past the spray zone.
  • the spray guns may be timed to stop applying reinforcing agent or coating after a suitable length of web has had reinforcing agent or coating applied to it given the purpose of the reinforcing agent or coating.
  • the flow rate of reinforcing agent or coating applied may be scaled according to the web speed, which may be done to minimize variation in the amount of reinforcing agent or coating applied per unit area of web or unit length of web as the web speed is changed. Applying the reinforcing agent or coating in the machine immediately prior to the web transfer area may help with machine hygiene, as no machine elements such as rollers touch the side of the web with the reinforcing agent or coating applied thereon. It may be advantageous to spray the reinforcing agent or coating with a component of velocity which is in generally the same direction as the web travel.
  • an array of piezoactuated flow channel dispensers may be provided to direct a reinforcing agent or a coating to the web. Piezoactuated flow channel dispensers available from Alchemie Technology Ltd, Future Business Centre, Kings Hedges Road, Cambridge, CB4 2Q.T, UK may be suitable.
  • the reinforcing agent and/or coating may be applied with a rotary disk fluid casting system, such as the Rotor Spray system available from Ahlbrandt, AltebergstraRe 23-25, 36341 Lauterbach (Hessen) Germany. Application with a rotary disk system could be turned on and off rapidly with a servo-actuated shutter.
  • the reinforcing agent and/or coating may be applied by a contact means to the mandrel or the web, such as with an applicator roll or a brush.
  • the rewinder core introduction and insertion apparatus and methods disclosed in US patent 6,422,501 may be used for both traditional cardboard cores and for coreless winding mandrels.
  • coreless winding mandrels because they are recirculated and reused numerous times, because they have a lower friction surface than cores, and because of their material properties, by their nature may have a narrower operating window for reliable operation than cardboard cores.
  • most or all of the transfer glue may be wiped clean in the mandrel extraction process for many grades of glue and types of substrate, in other cases, glue may remain on the mandrels due to the type of glue used and/or a relatively lower absorbency of the wound web.
  • the assist wheel 30-1 is driven in rotation at constant speed as the mandrel enters. Its rotation speed may be varied. Its rotation may be stopped between mandrels, which may reduce wear of the wheel and/or wear of the mandrels.
  • a mandrel braking shoe 30-3 is provided above the assist wheel 30-1 to press the mandrel against the assist wheel. As mandrels are reused, they may become less than perfectly circular, especially at and near their ends, which is where the mandrel assist wheel 30-1 that seats the mandrels against a mandrel stop 30-2 (Fig. 31), and the mandrel braking shoe 30-3 operate on the mandrel.
  • An oval-shaped mandrel may arrive at the mandrel assist wheel 30-1 in an unfavorable orientation, for instance with its minor diameter aligned to the mandrel assist wheel 30-1 and braking shoe 30-3 (Fig. 31), so the contact force is reduced, or non-existent, and the mandrel is not controlled correctly, or for instance with its major diameter aligned to the mandrel assist wheel 30-1 and braking shoe 30-3, so the contact force is excessive and the mandrel is not controlled correctly.
  • a mandrel assist wheel 30-1 contaminated with glue build-up or dust may result in the mandrel M being incorrectly positioned in the cross-direction in the rewinder because of insufficient interface friction for the assist wheel to decelerate the mandrel and/or to drive the mandrel end to the mandrel stop 30-2 properly.
  • Plastic mandrels may tend more than cardboard cores to rebound in the cross-direction when they hit the mandrel stop 30-2, due in part to them having a lower coefficient of friction, and due in part to the mandrels typically having greater mass than an equivalent size cardboard core, so they arrive at the mandrel stop with greater momentum if at the same velocity, which may result in the mandrels being incorrectly positioned in the cross-direction in the rewinder.
  • a mandrel justifier 70 as shown in Figs. 28 and 29 may be used to ensure that mandrels are correctly positioned in the rewinder 30 for mandrel insertion and transfer.
  • This device may be mounted near the inside of the frame of the rewinder 30 on the side of the machine from which mandrels are introduced in the cross-direction.
  • a swivel clamp 72 with a pusher 74 for example, a Festo model CLR, may be used to provide the combination of linear and rotational movement needed for this device.
  • the pusher 74 rotates out of the way, allowing a mandrel (M) to be introduced into the rewinder in the crossdirection.
  • the swivel clamp 72 may be retracted so that the face of the pusher 74 pushes against the end face of the mandrel to locate the mandrel to be introduced in the rewinder in the correct position. Bumpers may be provided at each end of the stroke of the swivel clamp for cushioning.
  • a toggle stop comprising a spring (mounted to a spacer or other suitable member, not shown) may be provided to help prevent mandrel rebound and help position the next mandrel with the mandrel justifier.
  • the toggle stop may comprise a lightweight spring-loaded device, or even simply a formed piece of plastic or thin metal with inherent springiness.
  • the toggle stop device is mounted adjacent the path of the incoming mandrels, at the side of the rewinder from which the mandrels enter. When the mandrel enters, its leading end displaces the toggle stop out of its path. As the mandrel passes by, it holds the toggle stop at the displaced position.
  • the shape of the toggle stop profile may be roughly that of a right triangle.
  • the long leg is substantially parallel to the mandrel feeding path
  • the short leg is substantially perpendicular to the mandrel feeding path
  • the hypotenuse is in the mandrel feeding path, facing the leading ends of the incoming mandrels. The incline of the hypotenuse allows the leading end of the mandrel to smoothly displace the toggle stop out of the way for mandrel entry.
  • the braking shoe 30-3 which presses the mandrel against the mandrel assist wheel 30-1 may be mounted with a spring, or other elastically yielding member. Or it may comprise a formed piece of plastic or thin metal with inherent springiness which contacts the mandrel directly. Thus, the braking shoe 30-3 may be set to have greater interference on the mandrel to reduce or minimize the negative effects of non-circular mandrel ends.
  • the spring-loaded shoe may nonetheless contact the mandrel and press it against the assist wheel with enough force for the mandrel to be controlled, or if an oval-shaped mandrel arrives at the assist wheel with its major diameter aligned to the wheel and braking shoe, the spring-loaded shoe may deflect away from the mandrel readily and thereby apply a force which is not excessive so that the mandrel is controlled.
  • the spring-loaded braking shoe may also be used with cores if desired.
  • the mandrel extraction system is typically provided with an infeed table 80 down which the logs roll as they exit the previous machine in the process, which is often a tail sealer 32.
  • the infeed may be in accordance with pending US 2023/010524 (application ser. no. 17/944,688), the disclosure of which is incorporated by reference.
  • Detectors preferably photo-eyes, positioned along the table 80 may detect the log's approach and be used to predict the log's arrival time. Logs may exit the tail sealer 32 at uneven intervals because there is variation in how long each log takes to undergo the tail sealing process.
  • logs may arrive at the tail sealer 32 with the tail end of the web in varying orientations around the log (e.g., with the tail end of the web at the 3 o'clock position, then at the 8 o'clock position, etc., randomly), which may result in variations in the time required for the tail sealer 32 to complete the tail sealing process.
  • Logs may arrive in the tail sealer 32 with the unsealed tail more or less wrinkled or sometimes folded over, and thus require more or less time for the tail to be laid flat as part of the tail sealing process.
  • Logs may bounce when they are abruptly stopped at the end of the infeed table 80, which requires providing a waiting time in the extractor log loading process to allow the log to settle, which increases the process cycle time and reduces the cycle rate.
  • an infeed roller assembly 34 such as that shown in Fig. 8 may be positioned above the infeed table 80, with a gap between a roller 82 of the assembly and the table 80 that is slightly smaller than the log diameter.
  • the roller 82 may be covered with a high or moderately-high traction surface, such as sprayed tungsten carbide or sprayed plasma coating, or a resilient material with high or moderately high grip such as foam, rubber, nitrile, urethane, or the like, for example, 25 Shore A Valrite or 40 Shore A Valthane, available from Valley Roller, N257 Stoney Brook Rd, Appleton, Wl 54915.
  • the roller 82 may be covered with a resilient material, or by providing the roller as a "no crush” roller or series of roller segments, for example from Wagner Industries Inc. of Frackville, PA 17931.
  • the roller 82 preferably rotates in the opposite direction of the logs' rolling rotation to receive the log gently and then to expel the log.
  • the roller 82 is driven in rotation by a motor 84.
  • the infeed roller 82 decelerates the log, reducing its translational velocity, so that the log has less energy and may bounce less when it is stopped at the end of the infeed table 80.
  • the log alignment conveyor 36 (see next section) is at the end of the infeed table 80.
  • the rotational velocity of the infeed roller may be constant from log to log, at a velocity slow enough to reduce or minimize bounce-back of the logs, and yet fast enough to load them expeditiously to the log lift conveyor for the required cycle rate.
  • the compression of the infeed roller 82 on the logs may be varied according to at least the log firmness, log diameter, log mass, or substrate friction characteristics.
  • the rotational speed of the infeed roller 82 may be varied according to at least the log firmness, log diameter, log mass, substrate friction characteristics, line speed, or required cycle rate.
  • the rotational speed of the infeed roller 82 may be varied from log to log, or log set to log set. Variation of the roller rotational speed may be used to counteract the variation in log arrival time and thus deliver the logs to the downstream process with a uniform or more nearly uniform periodicity.
  • Such periodicity restoration functionality has a high value, because if a log arrives later than the average periodicity, the lost time can only be recovered by having, and utilizing, available excess cycle rate capacity in the system.
  • Variation of the infeed roller rotational speed may be based on a signal from the tail sealer 32 regarding how long it took to complete the tail sealing function of a log. It may be based on the predicted time of arrival of the logs at the infeed roller, which may be determined with calculations using signals from the aforementioned detectors positioned along the infeed table.
  • Using the arrival time predicted by the detectors may be preferable because it takes into account more potential sources of variation among products, for instance the rolling time of the logs on the table 80.
  • Rotation of the infeed roller 82 may be stopped between the arrival of logs, but preferably it rotates continuously, which is preferable for accommodating higher cycle rates which have shorter intervals between logs.
  • the infeed roller 82 may rotate at a baseline speed, as described above, and then be modulated faster or slower, as described below. When a log is predicted to arrive at the infeed roller earlier than the average periodic interval, then the speed of the infeed roller may be decreased, to slow the log a greater amount.
  • the average periodic interval may be calculated based on a signal from the rewinder, or an average of the logs processed by the tail sealer 32, or a virtual signal such as may be generated by the PLC.
  • a detector preferably a photo-eye, is preferably located downstream from the infeed roller 82, preferably near the end of the infeed table 80, to detect the time of arrival of logs expelled from the infeed roller.
  • the signal from this detector may be used as feedback to adjust and alter and optimize the modulation of the infeed roller, with the objective of delivering logs to the extractor at a more nearly uniform interval than the logs arrive at the infeed roller, and more preferably at a uniform interval substantially corresponding to the period of the rewinder cycle rate for log production.
  • the adjustments to the modulation based on the feedback from the detector are executed automatically by the PLC as a type of self-learning system.
  • the height of the roller 82 above the table 80 may be adjustable to allow for logs of different diameters, in either a manual or an automatic fashion.
  • modulation of the infeed roller to improve the periodicity of logs is explained here in the context of a mandrel extractor infeed, its utility is not limited to this application. It may be used ahead of other modules that may benefit from a more uniform time span between arrival of logs. Non-limiting examples, for instance, include tail sealers and log accumulators.
  • an actuator such as a pneumatic cylinder
  • a pneumatic cylinder may be used to push the log end face against restraint plates in order to align the log in a direction along its axis (the cross-direction) for mandrel removal after the log is in a position in which the mandrel's axis coincides with the axis of a clasp.
  • a drawback of this approach is that it takes time during a part of the process that is critical to maximum cycle rate.
  • Another drawback is that with multiple puller extractors an actuator is required at each station to shift the logs.
  • An improved method includes aligning the logs prior to moving the logs into positions in which each mandrel's axis coincides with the axis of a clasp.
  • a way to accomplish this cross-direction pre-alignment is to provide a log alignment conveyor 36 as shown in Fig. 9.
  • the log alignment conveyor comprises a flat belt conveyor at the end of the infeed table 80.
  • the log alignment conveyor 36 moves the logs in the cross-direction as they arrive at the end of the infeed table.
  • the log alignment conveyor 36 may be positioned where the log lift conveyor 38 picks up the logs, to afford a more compact design.
  • the conveyor 36 may be segmented, so as to allow the paddles of the log lift conveyor 38 to pass through the gaps between the segments.
  • the log alignment conveyor belt material may have moderate or moderately low traction to prevent scuffing or tearing the logs so that the belt may run continuously, even after a log on it has been aligned. Movement of the log alignment conveyor may be stopped between logs, but preferably it moves continuously, which is preferable for accommodating higher cycle rates which have shorter intervals between logs.
  • the conveyor may be driven by an electric motor.
  • the speed of the log alignment conveyor 36 may be varied according to at least the log firmness, log diameter, log mass, substrate friction characteristics, line speed, or required cycle rate.
  • the log alignment conveyor is canted at an angle so that logs tend to roll across it expeditiously.
  • logs may be aligned in the cross-direction as they complete their translation from the infeed roller assembly 34 to the log lift conveyor 38 pickup position. Shifting the logs with the log alignment conveyor 36 as the logs roll to the mandrel extractor 44, instead of when they are stationary in the mandrel extractor, may reduce the cycle time and increase the attainable cycle rate.
  • the conveyor belt is inherently a faster alignment system than the pneumatic cylinders which operate at low pressure and force to avoid axially compressing relatively low firmness logs.
  • the log alignment conveyor can operate with only one actuator, in the above example an electric motor.
  • a stop reference plate 86 Disposed near the end of the log alignment conveyor 36, at the same side of the machine from which the mandrels are withdrawn, is a stop reference plate 86 against which the face of the side-shifting log is moved by the conveyor.
  • the stop plate 86 has a profile which allows the end of the mandrel, which protrudes beyond the face of the log, to extend beyond the face of the plate.
  • the position of the stop plate 86 may be adjusted in the cross-direction to accommodate various log lengths and preferred stop positions and may be adjusted relative to the height of the infeed table and conveyor belt to accommodate logs of various diameters.
  • the mandrel loading and log winding processes may be set up such that the end of the mandrel, which will be grasped by the clasp for removal from the log later in the process, protrudes a consistent distance from the end of the log.
  • the end of the mandrel By then moving the log in the cross-direction until its end face contacts the stop plate 86, the end of the mandrel may be placed in a suitable cross-direction location for mandrel removal from the log.
  • the log lift conveyor 38 is shown in Fig. 10, and satisfies multiple functions in the mandrel extraction system.
  • a converting line for coreless rolls it is desirable for a converting line for coreless rolls to be as similar as possible to a converting line that makes rolls with cores, so that the need for specialized equipment is minimized.
  • the log exit point from the tail sealer 32, and the log entry point into the log accumulator 48 be at approximately the same height in a coreless line as in a converting line that makes only rolls with cores, where the extractor is omitted, so that the same tail sealer and accumulator modules may be used in both types of converting lines.
  • the log lift conveyor 38 provides a mechanism to queue several logs for introduction to the mandrel extractor 44.
  • Figures 5 and 6 show mandrel extractors with three and four mandrel pullers, respectively. Fewer mandrel pullers or more mandrel pullers may be provided. Adding mandrel pullers increases the maximum theoretical cycle rate, but with diminishing returns. Adding mandrel pullers decreases the ease with which the inner mandrel pullers may be accessed by machine operators, and increases the cost of the mandrel extractor.
  • the log lift conveyor 38 may include flights 88 on a belt.
  • the log lift conveyor 38 may index one flight length to raise the log, making room for the next log to arrive. After the next log arrives the log lift conveyor may index one flight length again to make room for the third log to arrive.
  • a 3-puller extractor (Fig. 5) after the third log arrives and has been aligned in the cross-direction with the log alignment conveyor 36, the log lift conveyor 38 and infeed conveyor assembly 40 may triple-index to deliver the three logs to the carriers 90 on the main log conveyor 42.
  • a 4-puller extractor (Fig. 6) after the fourth log arrives, the log lift conveyor 38 and infeed conveyor assembly 40 may quadruple-index to deliver the four logs to the carriers on the main log conveyor 42.
  • log accumulation function allows the mandrel extractor to receive logs at the average interval between their production and yet take longer than this duration to execute the steps required for mandrel extraction.
  • staging function sets the correct phasing of the three logs to the carriers 90 on the main log conveyor 42 into which they will be loaded, so the triple index can be executed in a short time, which facilitates operating at high overall cycle rates.
  • each log lift conveyor belt in a 3-puller extractor has at least three paddles or flights 88 mounted on it, one for each log in the set. To accommodate larger diameter logs that may not fit between the paddles 88, the center paddle on each belt may be removed.
  • the system may execute a double-index when the first log in the set arrives, so it is advanced from the log pickup position to a dwell position in the infeed belts assembly 40.
  • the system may execute a triple-index after the second log in the set arrives, to advance the two logs and load them to the main log conveyor 42. Two logs are loaded, one to the rightmost extraction station, one to the leftmost extraction station, and the center extraction station is empty.
  • the inclination angle of the log lift conveyor 38 may be selected to minimize negative effects on the phasing of the logs to the carriers 90 on the main log conveyor 42.
  • the first log may settle and align in the generally V-shaped region between the paddle 88 and the surface of the belt on the uppermost pulley of the log lift conveyor when the conveyor motion stops.
  • the second log may likewise settle and align in the generally V-shaped region between its paddle 88 and the surface of the belt on the uppermost pulley of the log lift conveyor after the log lift conveyor 38 finishes indexing a flight length to advance the first and second logs.
  • the third log travels from the pickup position to a carrier 90 on the main log conveyor 42 without stopping. Because the third log travels over the uppermost pulley of the log lift conveyor without the conveyor stopping, typically without the conveyor slowing down, its trajectory, or approach angle, is relevant to whether or not the log remains in contact with the conveyor belt on the pulley. If the conveyor inclination is less steep, then the centripetal acceleration vector required to make the log deviate from its straight path and start to orbit around the conveyor pulley is more closely aligned with the gravitational acceleration vector, so the conveyor can run faster without the log losing contact with the belt surface.
  • the conveyor inclination is steeper, then the centripetal acceleration vector required to make the log deviate from its straight path and start to orbit around the conveyor pulley is less closely aligned with the gravitational acceleration vector, so the conveyor may have to run slower to keep the log from losing contact with the belt surface.
  • the logs to be correctly phased to their carriers on the main log conveyor they should preferably remain in contact with the log lift conveyor belt surface and paddle surface until they have reached the entrance of the infeed belts 40. As explained above, whether or not this preferred behavior is attained, especially at high speeds, is influenced by selection of the log lift conveyor inclination angle.
  • log guides may be provided in proximity to the log lift conveyor at the log pickup position that prevent logs from contacting the log lift conveyor belts until after the logs have been lifted off of the log alignment conveyor 36. This may be done so that the logs do not rub against the log lift conveyor belts or do not contact the edges of the log lift conveyor belts as the logs are being shifted in the cross-direction by the log alignment conveyor. If such log guides are provided, each log may initially ride upward along these guides when picked up by the log lift conveyor before starting to migrate downward into contact with the log lift conveyor belt, which may occur after the logs have passed beyond the tops of the guides.
  • the conveyor inclination is less steep, then the acceleration vector required to make the log move downward into contact with the log lift conveyor belt is more closely aligned with the gravitational acceleration vector, so the conveyor may run faster and still allow time for the log to move downward into contact with the log lift conveyor belt before the log has to start orbiting around the log lift conveyor uppermost pulley. If the conveyor inclination is steeper, then the acceleration vector required to make the log move downward into contact with the log lift conveyor belt is less closely aligned with the gravitational acceleration vector, so the conveyor may have to run slower to allow time for the log to move downward into contact with the log lift conveyor belt before the log has to start orbiting around the log lift conveyor uppermost pulley.
  • the logs should preferably remain in contact with the log lift conveyor belt surface and paddle surface until they have reached the entrance of the infeed belts 40.
  • This preferred behavior may be facilitated by having the log move into contact, or closer to contact, with the belt surface before the log has to start orbiting around the log lift conveyor uppermost pulley.
  • whether or not this preferred behavior is attained, especially at high speeds, is influenced by selection of the log lift conveyor inclination angle.
  • the inclination angle of the log lift conveyor 38 may be selected to minimize negative effects of log bounce-back at its log pickup position.
  • the infeed roller may be used to reduce or minimize bounce-back of logs at the log lift conveyor pickup position.
  • log bounce-back is not eliminated, especially at high cycle rates where the logs must enter between the log lift conveyor paddles 88 in a short amount of time. This may be encountered when running coreless products. It may be more acute when the extractor operates in bypass mode. In bypass mode the logs are produced with cores that are not extracted.
  • the logs can theoretically be bypassed through the unit at higher cycle rates than when extracting mandrels.
  • the extractor may operate in bypass mode at rates of 50 logs per minute (LPM) or even 60 LPM.
  • LPM logs per minute
  • high cycle rates it may be preferable to index the log lift conveyor before logs at the pickup position settle, when they are still bounced back away from the intended pickup position.
  • the fast-moving conveyor paddle may carry the log up the conveyor without the log touching the guides, in which case the log has farther to move downward to come into contact with the log lift conveyor belt surface. This may cause a problem for the phasing of the last log in a set if the conveyors are performing a triple-index, as explained above, or for the first log in a set if performing a double-index.
  • the conveyors are performing a single-index it may not be a problem, as explained above, because the log may settle and align in the generally V-shaped region between its paddle 88 and the surface of the belt on the uppermost pulley of the log lift conveyor when the conveyor motion stops. But, it may be a problem for log phasing at higher cycle rates also when the conveyors are performing a single-index if the log has not properly settled or is still rocking when the log lift conveyor indexes again. In that case the log may be out of contact with the belt or the paddle when the log lift conveyor resumes motion.
  • the conveyor inclination is steeper, then the acceleration vector required to make the log move downward into contact with the log lift conveyor belt, or the proximate log guide, is less closely aligned with the gravitational acceleration vector, so the conveyor may have to run slower to allow time for the log to move downward into contact with the log lift conveyor belt, or the proximate log guide, or at least closer to contact, before the log has to start orbiting around the log lift conveyor uppermost pulley. Having the log in contact, or closer to contact, with the log lift conveyor belt surface when the log starts to orbit around the log lift conveyor uppermost pulley may help to reduce or minimize rocking of the log at its single-index dwell position on the pulley.
  • rocking of the log at this dwell position may be tolerated, of course, but the point here is that the for the logs to be correctly phased to their carriers on the main log conveyor, especially at high cycle rates, the amount of rocking should preferably be minimized, or at least not excessive, and whether or not this preferred behavior is attained, especially at high speeds, is influenced by selection of the log lift conveyor inclination angle.
  • a less steep inclination of the conveyor may allow for higher conveyor speeds and thus higher cycle rates, but it would tend also to increase the length of the machine, making it less compact.
  • the infeed conveyor 40 may have lower and upper infeed belts 40a, 40b, as shown in Figs. 11, 12 respectively, that receive logs from the log lift conveyor 38 and deliver the logs to the main log conveyor 42.
  • the infeed belts 40a, 40b may be provided with a slight downward inclination for a smooth hand-off of logs to the carriers 90 on the main log conveyor 42.
  • the upper and lower belts 40a, 40b are moved at the same surface speed, so the logs are advanced solely by translation, without rotation. That said, the belts may be operated at differing speeds to rotate the logs relatively forward or backward.
  • the speed of the belts at the moment of log handoff to the main log conveyor is controlled so that the component of the log velocity parallel to the direction of travel of the main log conveyor is substantially equal to the velocity of the main log conveyor.
  • the speed of the belts 40a, 40b may be modulated faster or slower to adjust the phasing of the logs to the phasing of the carriers 90 on the main log conveyor 42.
  • a detector preferably a photo-eye, may be located such that it can detect the time of arrival of logs to a predefined point in the infeed belts 40a, 40b.
  • the signal from this detector may be compared to the planned or preferred time of arrival for the log at this point in the infeed belts and used to adjust and alter and/or optimize the modulation of the infeed belts, with the objective of delivering logs to the carriers 90 on the main log conveyor 42 with greater precision of the phasing.
  • adjustments to the infeed belts modulation based on the sensor feedback are executed automatically by the PLC as a type of self-learning system.
  • the phase relationship between logs delivered by the infeed belts and the carriers on the main log conveyor may be good, or at least sufficient, without automatic modulation of the infeed belts' speed by the PLC, it is possible this method for automatic modulation may make it better, or may serve to make it more consistent over an extended time of operation.
  • a log guide 41 (Figs. 4-5, 12) may be provided.
  • the log guide may comprise an elongate member.
  • the log guide may be positionable relative to a surface of the main conveyor 42 of a mandrel extractor 44 at a distance sufficient to allow a log L from an infeed conveyor system 40 to pass between the surface of the main conveyor and the log guide while maintaining the log in register with the mandrel extractor.
  • One or more log guides may extend over at least a portion of the main log conveyor 42. Multiple log guides may also be used, preferably with a guide located above each belt of the main log conveyor.
  • the log guide or guides may preferably extend at least over the region of the main log conveyor where the logs are transferred from the infeed belts 40 to the carriers 90 on the main log conveyor 42.
  • the log guide or guides may extend over the first (nearest) mandrel extraction station.
  • the log guide or guides may extend over the first mandrel extraction station, over the first and second (center) mandrel extraction stations, or over all the mandrel extraction stations.
  • the log guide or guides may be used to ensure the logs delivered by the infeed belts to the main log conveyor seat in the carriers on the main log conveyor. If the logs arrive at the main log conveyor slightly out of phase with the carriers on the main log conveyor, they may rock in the carriers, especially as the main log conveyor accelerates or decelerates.
  • the log guide or guides arranged above the main log conveyor 42 may serve to guide or press or displace the logs into the carriers, reducing their phase mismatch, so the logs do not rock, or they rock less.
  • the log guide or guides may have a profile shape conducive to guiding, pressing, and/or displacing the logs downward into the carriers 90 at or following the region where the logs are transferred from the infeed belts 40 to the carriers 90 on the main log conveyor 42.
  • the log guide or guides may be arranged to not press the logs into the carriers, but nonetheless keep the logs from rocking excessively by being in close proximity to the logs so that if a log starts to rock in the carrier it will contact a guide and have its rocking motion limited.
  • the log guide 41 may be removably connected to the frame structure of the upper infeed belts 40b. Having the log guide or guides removably attached to the upper infeed belts structure, which is adjusted in height when changing the log diameter, causes the height of the guide or guides to also be adjusted when changing the log diameter, so the guide or guides may be correct for the new log diameter, or require only a relatively smaller separate adjustment.
  • the guides may have an independent mounting, for example, brackets on the machine framework comprising the main log conveyor 42 or the mandrel extractor 44.
  • the guides may be stationary during operation of the extractor.
  • the guides may be mounted with springs or pneumatic devices, or equivalent, so they displace and their pressure on the logs may be consistent during operation of the extractor.
  • the log guides may be operatively removably attachable to the mandrel extractor, main conveyor or infeed conveyor system to allow replacement when worn.
  • the main log conveyor 42 is shown in Fig. 13.
  • the main log conveyor 42 may be configured as log carriers 90 attached to timing belts.
  • the log carriers 90 may be provided with a shape, such as a V-shape, that tends to keep the logs in a constant position relative to the log carriers when subjected to high accelerations necessitated by high-speed movements.
  • the main log conveyor 42 of the 3-puller extractor may be provided with a slight upward slant to elevate the logs to a suitable height for delivery to the outfeed table 46 that carries logs to the downstream module, typically a log accumulator 48.
  • This upward slant may not be necessary in a 4-puller extractor, because the log lift conveyor, having a capacity for four logs, may be taller than the log lift conveyor of the 3-puller extractor.
  • the timing belts of the main log conveyor preferably operate on timing pulleys, except in the region of log discharge, where they may operate on a profiled turning block 43. In this place a profiled turning block may be used to better set and control the accelerations imposed on the logs as the conveyor discharges them. If a timing pulley was used in this place the logs would tend to undergo a large step change in acceleration.
  • Using a profiled turning block 43 allows the step change in acceleration to be reduced, so the main log conveyor can be operated at higher speeds and the logs still be controlled well enough at discharge.
  • a straight section, or longer straight section, of main log conveyor 42 after the last mandrel puller (which is nearest the outfeed table 46), before the turning block, may be beneficial so the conveyor can be accelerated to constant velocity, or closer to constant velocity, before the first carrier with a log starts to rotate around the turning block. If the conveyor is traveling at constant velocity the motion profile acceleration is zero, so it does not add to the peak acceleration seen by the log as it passes over the turning block. If the conveyor is still accelerating as the log passes over the turning block, a component of this motion profile acceleration is seen by the log, increasing its total acceleration.
  • the next triple-index motion may be executed, which delivers the next group of logs, staged at the infeed conveyor assembly 40 and log lift conveyor 38, to the extraction stations, and simultaneously delivers the current group of logs, which are now coreless logs, onto the outfeed table 46.
  • the logs roll on the outfeed table 46 into a space beneath the outfeed belts 47 which control the translational velocity of the rolling logs and meter them into the next machine in the process, typically a log accumulator 48.
  • the triple index is preferably executed in a short duration of time, which means the logs may be discharged from the main log conveyor at a relatively high translational velocity and instantaneous log rate.
  • the logs may be discharged from the main log conveyor at instantaneous rates in excess of 100 LPM, in excess of 120 LPM, potentially even in excess of 135 LPM.
  • the outfeed belts decelerate the logs to an instantaneous rate the downstream equipment can accommodate, typically in the range of 20 - 60 LPM for a log accumulator, though slower or faster log delivery rates may be provided.
  • the outfeed belts may be pivoted to a raised position 47b (Fig. 5) when not in use, such as when operating the extractor in bypass mode, when only single indexing is utilized, or for personnel access to the extractor module when the machine is not running.
  • the outfeed table 46 may also be pivoted up (not shown) for access to the extractor module.
  • a log cull system 45,49 may be provided between the mandrel extractor and the next module downstream, most often a log accumulator.
  • the cull system may be located close to the extractor, but a disadvantage to this arrangement is that logs may emerge at too great of a velocity or instantaneous log rate for the gate to cull only one log in the set, or possibly even to cull multiple logs correctly.
  • Fig. 5 shows a preferred location for a log cull system, nearer the next downstream module, in this case a log accumulator.
  • the log cull gate 45 is mounted on a pivotable shaft. The gate is shown in its closed position, where it forms part of the table which delivers logs to the accumulator.
  • the gate When a log is to be culled, or logs are to be culled, the gate is pivoted downward, so that the log or logs are diverted from the normal processing path to a log conveyor 49 located beneath the table, which carries logs in the machine cross-direction, out of the rewinder line, where they can be retrieved by the operator or otherwise disposed of.
  • An advantage of locating the log cull system 45,49 nearer the downstream module, near the end of the outfeed belts 47, is that the logs may be decelerated to a lower instantaneous log rate when, or before, they arrive at the cull gate. Because the logs pass over the log cull gate with a lower instantaneous log rate, the gate may be used to cull any one of the logs in the set or any combination of logs in the set: only the first log, only the second log, only the third log, the first and second logs, the second and third logs, the first and third logs, or all three logs.
  • this functionality requires that the conveyor 49 can take the logs away at least as fast as the logs fall from the cull gate. This may be achieved by using a fast enough belt velocity and high enough traction surface on the belt.
  • the log cull system may comprise a gate with pivot to its upstream side, which pivots downward to cull logs.
  • the log cull system may comprise a gate with pivot to its downstream side, which pivots upward to cull logs.
  • the log cull system may comprise both types of gates, which advantageously may cooperate to cull logs of larger diameter than either gate alone may accommodate.
  • FIG. 14-19 A portion of the mandrel extractor 44 is shown in Figs. 14-19 and includes a mandrel puller module 62 with a traveling carriage 92 and the clasps 60 mounted to the carriage 92.
  • the system shown in Figs. 14-19 improves upon the mandrel extractor system of US Pat. No. 9,284,147.
  • the mandrel extractor may also be configured to work with systems as shown in US Pat. No. 9,290,347 and PCT patent application WO2020245319A1, which show examples of mandrels that are provided with mechanical features such as sockets and coupling elements to provide mechanical means for connecting to a mandrel clasp with corresponding mechanical features.
  • the clasp is in a position to engage an end of the mandrel when no relative movement between the mandrel and the clasp in a direction along the axis of the mandrel is required in order for the clasp to engage the mandrel.
  • the clasp illustrated in Figs. 12 - 15 of US 9,284,147 may be modified to accommodate variations in the radial travel of the clamping blocks during clamping.
  • Winding mandrels may be tubular.
  • the mandrels may be made of a homogenous material.
  • the mandrels (M) may be substantially axially elastic and comprised of a material having a tensile yield strength divided by elastic modulus greater than 2.0%, for example High Density Polyethylene (HDPE).
  • Fig. 14 of US 9,284,147 shows a clasp in a position to engage an end of a tubular mandrel, in which the end of the mandrel is inserted over the prong of the clasp, and the clamping blocks of the clasp can be forced radially inwardly to clamp the mandrel between the clamping blocks and the prong.
  • the retaining plate 95 may be mounted with integral screw threads on the outer diameter of the clasp housing 94 so the retaining plate is configured as a "screw-on" cover rather than with multiple individual fasteners as shown in US 9,284,147.
  • This design makes it easier and faster to access the inside of the clasp.
  • the prong 96 (indicated with reference character 90 in US 9,284,147) may be made as a separate, removable piece, instead of integral with the housing as shown in US 9,284,147. This design results in a quicker change between clasp configurations among different mandrel diameters because the prong size can be changed without removing the clasp housing.
  • the clasp 69 is provided with radially oriented screws 100 with radially oriented compression springs 99 to retract the clamping wedges 92 radially when the cylinder 70 extends to retract the actuator wedges 101 and disengage the mandrel.
  • the actuator wedges 98 and clamping wedges 100 of the clasp 60 may be provided with corresponding elongated T-shaped protrusions and elongated T- shaped slots which are arranged in an interlocking fashion.
  • the actuator wedges 98 to positively move the clamping wedges 100 radially away from the mandrel when the actuator wedges are retracted axially by extending the cylinder actuator 102 to disengage the mandrel.
  • the actuator wedges 98 and clamping wedges 100 of the clasp 60 may be provided with corresponding elongated dovetail shaped protrusions and elongated dovetail shaped slots which are arranged in an interlocking fashion.
  • the actuator wedges may be made of steel, aluminum, brass, or an engineering plastic.
  • the clamping wedges may be made of steel, aluminum, brass, or an engineering plastic.
  • the actuator wedge may be made of brass and the clamping wedge may be made of steel.
  • the surface of the clamping wedge which clamps the mandrel between the clamping wedge and the prong may be knurled or provided with other textured surface features or a coating for grip traction.
  • the knurled surface or other textured surface features and the side surfaces of the clamping wedge may be hardened.
  • Figs. 17A-17C illustrates a clasp 60 with a specific method of providing compliance between the shared cylinder actuator 102 and the individual actuator wedges 98.
  • a compression die spring 104 is disposed on each actuator wedge's screw 106, and secured with a nut and washer to provide a minor preload to the spring.
  • clamping wedges 100 If one or several of the clamping wedges 100 is stopped by clamping the mandrel wall before other clamping wedges, their compression die springs 104 will compress in length, allowing the other actuator wedges 98 to continue moving axially, causing their associated clamping wedges 100 to continue moving radially.
  • This design allows the clamping wedges 100 in the clasp 60 to press and clamp the tubular mandrel wall more evenly and uniformly, to better accommodate and possibly even compensate for mandrels that have varying wall thickness, lack of concentricity between the internal and external diameters, or have worn unevenly or somehow been deformed, or for uneven wear of the wedges and other components in the clasp. This design may make the clasp easier to set up when new, requiring fewer measurements and adjustments.
  • a clasp may be configured for engaging an end of a tube.
  • the clasp may include: (i) a prong having a generally cylindrical outer surface, the outer surface being adapted to be inserted into a bore of a tube, for instance, a mandrel; (ii) a housing being adapted to house a plurality of clamping wedges, the clamping wedges being spaced circumferentially around the prong within the housing, the plurality of clamping wedges being moveable between a disengaged position and an engaged position, wherein in the disengaged position, the plurality of clamping wedges are spaced radially outwardly from the outer surface of the prong at a distance sufficient such that a tube is insertable between the prong and the clamping wedges, and wherein in the engaged position, the plurality of clamping wedges are positioned radially inward of the disengaged position toward the prong, and wherein in the engaged position and when a tube is disposed between the clamping wedges and the prong, the plurality of clamping wedges presses the tube against the prong; (ill)
  • Such a clasp may further comprise a retaining plate, wherein the retaining plate is threadably connected to the housing.
  • the corresponding elongated protrusions and elongated slots are T-shaped.
  • the corresponding elongated protrusions and elongated slots are dovetail shaped.
  • the prong may be threadably connected to the housing.
  • three clasps 60 may be provided on the carriage 92 to remove mandrels from a group of three logs simultaneously.
  • the clasps 60 may be mounted to a common moveable framework, or carriage 92 of the mandrel puller 62, that traverses along a path parallel to the direction of the axes of the logs and mandrels to remove the mandrels from the logs.
  • the clasps 60 may be mounted to the carriage 92 with bushings or bearings, preferably tapered roller bearings suitable for withstanding the axial pulling force applied to the mandrel by the mandrel puller 62, in addition to providing a rotational degree of freedom of the clasps about their central axes.
  • the mandrel may be rotated relative to the log as the log is held stationary by restraints 64 at its periphery, by rotating the clasp 60 about its central axis.
  • the mandrel may be rotated relative to the log to disperse or smear the transfer adhesive as disclosed in patent US 9,975,720.
  • the mandrel may be rotated in the direction of the wind of the log.
  • the mandrel may be rotated in the direction opposite to the wind of the log. It was observed with a tissue product that rotating the mandrel in the same direction as the wind may more effectively attach the internal tail to the side of the hole in the coreless log, making it less likely to be rendered loose when cut by the log saw and subsequently unravel.
  • the mandrel may be rotated relative to the log before pulling of the mandrel is commenced, as pulling of the mandrel is commenced, and/or after pulling of the mandrel is commenced. Rotating the mandrel before pulling of the mandrel for extraction is commenced may be more effective at comprehensively smearing the transfer adhesive. But, rotating the mandrel during extraction of the mandrel has the benefit of taking less of the cycle time, which facilitates operation at higher cycle rates. Also, for some products it is helpful to pull and elongate the mandrel to reduce the torque required for the relative rotation before starting the relative rotation.
  • the mandrel clasps may be rotated by their own individual rotation actuators, in which case the actuators may be coaxial with the central axes of the clasps. Or they may share a common actuator 110 through a drive train 108, as shown in Fig. 14.
  • the actuator may be a pneumatic rotary actuator, an electric motor, or similar.
  • all the clasps are driven through a drive from a single electric servo motor 110, preferably through a serpentine timing belt drive train 108.
  • Using a single shared actuator is economical.
  • Using a servo motor allows for mandrel rotation of virtually any magnitude, from a partial revolution to multiple revolutions, allows for reversing the rotation, allows for executing precision accelerations to afford smooth movement, and provides for fault detection from its feedback signals.
  • Another advantage of the preferred embodiment is that the clasps 60 can be mounted with hollow bore shafts through which the pneumatic lines for actuating the clasps are routed, which provides some containment and protection to prevent damage to the pneumatic lines during the pull
  • a sensor for example a photo-eye array or a camera, may be provided to measure the actual protrusion of the mandrel ends beyond the faces of the logs.
  • the PLC may adjust the stop position of the clasps for mandrel engagement to be farther from the logs and continue without stoppage or a fault. If the protrusion of the mandrels is less than can be accommodated by the clasps at their planned engagement positions, but is close enough to uniform among the three logs, the PLC may adjust the stop position of the clasps for mandrel engagement to be closer to the logs and continue without stoppage or a fault.
  • the PLC may generate a fault and stop the machine without damage to the mandrel ends.
  • the extractor may actuate the clasp or clasps for the mandrel or mandrels that may be extracted but not the clasp or clasps for the mandrel or mandrels that cannot be extracted.
  • Figs. 25-27 show a motion profile which may be used for a mandrel puller that traverses back and forth and is used to extract mandrels from logs of wound web material.
  • the mandrel puller is configured with the clasp positioned at a mandrel engagement position to engage the end of a mandrel.
  • the puller is stationary, dwelling in this position briefly to allow the clasp to actuate and engage the end of the mandrel.
  • the duration of segment 1 is preferably at least as long as the time for the clasp cylinder to actuate the clamping wedges against the mandrel.
  • Segment 2 is slow pulling by the clasp on the mandrel.
  • the puller begins to travel slowly from the mandrel engagement position, moving the clasp away from the log slowly to facilitate stretching the mandrel and generate localized breakaway of the mandrel progressively within the log.
  • the duration of segment 2 may be around 0.9 seconds, which is adequate for many products.
  • the duration of segment 2 may be longer or shorter depending upon the nature of the products.
  • the slow pull magnitude may be denominated in duration of time, as aforementioned, or in distance of travel. Using time is convenient for ensuring the desired cycle rates can be attained. Using distance is helpful for setting the pull magnitude relative to its objectives.
  • the puller translation velocity may be constant for a portion of the slow pull duration. Alternatively, the puller translation velocity may be slowly increased throughout the slow pull duration.
  • An objective of the slow pull is to reduce, minimize, or optimize the peak force between the log and mandrel to extract the mandrel from the log. This is favorable for keeping the stresses in the mandrel low and for minimizing the likelihood of damage to the log. If the mandrel breaks free of the log progressively for a short portion of its length of engagement with the log, the peak force may be higher as the remaining length of its engagement breaks free suddenly. If the mandrel breaks free of the log progressively for a larger portion of its length of engagement with the log, the peak force may be lowered. If the mandrel breaks free of the log progressively for the entirety of its length of engagement with the log, the peak force may be lowered to a greater degree, even minimized.
  • Logs which have lower firmness, and/or lower interlayer pressure, and/or lower interlayer friction, and/or lower column stiffness, and/or higher tack or gummier transfer glue, which generally are less resistant to axial collapse and/or internal shifting of the wraps of web in the log, may benefit from a longer duration of slow pull.
  • optimization of the slow pull may be done according to force feedback from the mandrel puller system. This feedback may be obtained by mounted force sensors or by observing the servo motor torque signal, which may be converted to pull force by known methods.
  • the pull force feedback may be charted versus time, or distance traveled of the puller, and monitored for a change in slope of the graph which indicates the mandrel has broken free of the log and has relative axial sliding motion for the entirety of its length of engagement with the log.
  • the puller may accelerate to a relatively faster pulling speed because continued slow pulling would typically afford little if any further benefit.
  • the puller may start to accelerate to a relatively faster pulling speed earlier, in anticipation of this point, since acceleration takes time, and therefore its velocity would be only a little greater at this point.
  • the puller may start to accelerate to a relatively faster pulling speed earlier than this point if it is expected the product and mandrel will be okay and reducing the duration of the slow pull to attain a higher cycle rate is desired.
  • the puller force feedback may be used by an operator to adjust, alter, and/or optimize the slow pull duration and/or distance, but more preferably it may be done automatically by the PLC
  • the pullers may be accelerated to a relatively higher velocity in segment 3 to withdraw the mandrels rapidly, to minimize the cycle period, which is favorable for operation at higher cycle rates.
  • Mandrel rotation may occur during segment 2 or segment 3 or segments 2 and 3.
  • the puller starts to slow down to the speed in segment 4.
  • the clasp may unclamp and release the mandrel during the deceleration in segment 3.
  • the mandrel end may be removed from the clasp.
  • the velocity during segment 4 may be constant, to promote consistent positioning of the mandrels when released by the clasp, but continuing the deceleration from segment 3 into segment 4 is not ruled out.
  • the mandrel may be separated from the clasp in segment 4 such that the clasp is no longer in a position to engage the mandrel end.
  • drag guides may move to engage the outside of the mandrel, and may press or pinch the outside of the mandrel, to restrain it from moving axially as the clasp continues its movement, so that the mandrel end emerges from the clasp.
  • the puller slows down further and comes to a stop at a puller stop position at the end of segment 4. From the start of the mandrel pulling (beginning of segment 2), to the time the puller stops without a mandrel (end of segment 4), the puller moves continuously, without stopping. This continuous motion affords an efficiency of time which facilitates operation at higher cycle rates.
  • the puller dwells at the puller stop position and remains stationary to allow time for the mandrel to be removed from the return path of the puller clasp carriage.
  • the mandrel may be lowered or dropped onto guides or a conveyor and returned to the rewinder to be reused.
  • the mandrel may be lowered or dropped by utilizing gravity.
  • the drag guides 66 and mandrel end supports 65 may lower the mandrel onto a mandrel return conveyor 50. Disengaging the mandrels from the clasps and quickly and reliably moving them out of the return path of the puller carriage is a critical phase of the extractor process. Therefore, this position is advantageously the position of the puller during its variable duration dwell.
  • this dwell is increased rather than the time being wasted.
  • the mandrels may be lowered to the return conveyor.
  • the mandrels may bounce and then settle on the conveyor.
  • Sensors at the conveyor may detect the mandrels are correctly in position and out of the return path of the puller carriage, so they are not damaged, and the motion planner may reset the virtual axis for the mandrel puller to follow. Having these functions and actions occur during this mandrel puller dwell of maximized duration affords greater process reliability and timeline efficiencies which facilitate operation at higher cycle rates.
  • the time for the end of segment 5, when the puller initiates its return motion in order to engage the mandrels in the next group of logs depends on the duration required for its return travel and the time that the next group of logs will be in position and ready for the mandrel extraction.
  • the log lift conveyor, infeed belts, main log conveyor, and outfeed belts can initiate a triple-indexing motion sequence to simultaneously unload the current group of coreless logs and load the next group of logs for mandrel extraction.
  • the puller may execute its return travel motion.
  • the start of the return travel motion may be timed in accordance with the return travel duration so that the puller clasps move onto the mandrel ends at the moment the group of logs arrive at the extraction positions or slightly thereafter. It is preferable, if time in the cycle permits, to move the clasps onto the mandrel ends after the logs have been restrained at their periphery, so that incidental contact between the clasps and the mandrel ends does not cause the logs to shift axially in the extractor.
  • the puller may execute its return travel as depicted in segments 6 and 7, wherein it moves at a relatively lower constant velocity in segment 7 as the clasps move onto the mandrel ends.
  • the puller may move the clasps onto the mandrel ends as it is decelerating from the relatively higher velocity of its return travel.
  • the puller comes to a stop at the end of segment 7 it is in a position where the clasps can engage the ends of the mandrels in the next group of logs. From the start of the puller return motion (beginning of segment 6), to the time the puller stops with the clasps on the mandrel ends (end of segment 7), the puller moves continuously, without stopping. This continuous motion affords an efficiency of time which facilitates operation at higher cycle rates.
  • a practice in previous extractors was to stop the mandrel puller on its return path from its mandrel extracted and released position to its mandrel engagement position.
  • the mandrel puller was stopped with the puller clasps in relatively close proximity to where the ends of the mandrels to be withdrawn from the next group of logs would be when those logs were ready for mandrel extraction.
  • the mandrel puller would wait (dwell) in that position until the next group of logs was ready for mandrel extraction. If the actual rate of logs received by the extractor was less than the tuned rate capacity of the extractor, then the puller would dwell there longer because this was its position of variable dwell.
  • eliminating the intermediate dwell may be facilitated by coordinating the extractor sequence of operations with a virtual time signal (see section Motion Optimization) which allows for coordinating the arrival of the puller clasps at the ends of the mandrels to be withdrawn when, or immediately after, the logs are ready for mandrel extraction, even with the compressed timelines that are required at high cycle rates.
  • a virtual time signal see section Motion Optimization
  • a benefit to this change in puller operation is that time the mandrel puller spent in dwell near the mandrel ends may be reallocated to other places in the timeline rather than wasted. For instance, the duration of the puller dwell at its mandrel extracted and released position may be increased.
  • Another benefit is that because the puller does not stop and restart on its return path, it makes more efficient use of time. It may travel at a reduced maximum velocity and move from its mandrel extracted and released position to its mandrel engagement position in the same amount of time. Or, it may move at the same maximum velocity and return in less time, allowing higher cycle rates to be attained.
  • the freed-up time may be allocated to the mandrel extraction step, allowing for longer duration of slow pulling, reduced maximum velocity during extraction, or reduced velocity during engagement of the drag guides, without a reduction in the attainable cycle rate.
  • This more efficient use of time allows for increasing the attainable cycle rate of the extractor and/or making the extractor process more robust by allowing more time for other steps in the process.
  • the actual log arrival rate may also be lower due to something as simple as running the rewinder line slower for a process reason without adjusting the extractor timing and motions. Regardless of the cause, it is typical that the mandrel extractor will have a variable duration dwell where it waits for the last log in a set to arrive. In previous practice, this time was wasted because it increased the duration of the mandrel puller dwell at its intermediate stop position on the return path. By contrast, in the present disclosure, the duration of the mandrel puller dwell at its mandrel extracted and released position is increased, which is more helpful, as explained above.
  • Figs. 14 - 19 show a portion of the mandrel extractor 44 that withdraws the mandrels from the logs.
  • Figs. 18 - 19 show the mandrel puller module 62.
  • the mandrel puller module 62 is typically mounted on vertical guides and supported by a lifting system (not shown), so that its height may be adjusted to bring the heights of the puller clasps into vertical alignment with the mandrel centers in the logs. Thus the height of the puller module 62 may be adjusted with the lifting system for log diameter changes— to a higher elevation for larger diameter logs and to a lower elevation for smaller diameter logs.
  • the lifting system may be linear screw actuators, a slider-crank device, rack and pinion system, or any other suitable device.
  • the motion direction of the puller carriage 92 is from left to right when moving away from the logs.
  • its motion direction is from left to right when extracting mandrels from the logs, moving from a mandrel engagement position nearer the logs to a position farther from the logs where it stops after the mandrels are extracted.
  • its motion direction is from right to left when moving from a stopped position following mandrel extraction back to the mandrel engagement position, nearer the logs.
  • Figs. 18 - 19 show the mandrel puller carriage 92 at a stopped position following mandrel extraction, spaced apart from the mandrels Ml, M2, M3 which are released from the clasps 60.
  • the mandrel Ml is shown extracted from the log at the first extraction station, the mandrel M2 is shown extracted from the log at the second (center) extraction station, and the mandrel M3 is shown extracted from the log at the third extraction station.
  • the puller module 62 may be comprised of plate frames 61 which are spaced apart and connected by elongated beams 63.
  • the puller carriage 92 may be supported and guided by linear rails or tracks which are oriented parallel to the axis of the logs. These linear rails or tracks may be mounted to the underside of the upper elongated beams 63.
  • the puller carriage may be movably secured with one degree of freedom to the linear rails by bushings or bearings affixed to the puller carriage framework.
  • the bushings or bearings may be provided with lubrication, such as grease or oil. Additionally, they may be provided with an on-board automatic relubrication system so they are relubricated frequently to prolong their life.
  • the puller carriage 92 must travel at high velocities and be located with precision, so it is preferable that the drive system used to move it along its path is lightweight and stiff.
  • the puller carriage 92 is preferably driven along its path by one or more timing belts 67. Other flexible transmission devices, such as roller chain or cables are not ruled out.
  • the timing belts may wrap around and be supported by idler pulleys 71 which may be located at the end of the mandrel puller module that is closer to the logs.
  • the timing belts may wrap around drive pulleys 68 which may be located at the end of the mandrel puller module that is farther from the logs.
  • the drive pulleys 68 may be mounted on a common drive shaft 79 and share a common drive motor and gearbox 69 that may be mounted to the puller module frame 61. This does rule out using a single timing belt, if sufficient for the needs, or more than two timing belts, if preferred or necessary.
  • the lower spans 67a of the timing belts 67 are attached to the puller carriage 92.
  • the upper spans 67b of the timing belts complete the loop of the belts so that the puller carriage 92 can be driven left or right by the drive train actuator 69.
  • the drive train actuator 69 may include a gearbox and preferably an electric servo motor.
  • the drive train for the puller carriage may be a rack and pinion system (not shown) wherein a gear-tooth rack is provided along a support beam 63 and a gear-tooth pinion with motor is provided on the puller carriage.
  • Plates 75a, 75b for restraining the log end faces may be provided with mounting from the frame 61 of the mandrel puller module.
  • the plates may be mounted from a different frame, but preferably they are mounted from the frame of the puller module so that they are raised and lowered with the puller module for log diameter changes and thus do not require a separate height adjustment for log diameter changes.
  • Plate 75a is arranged below the path of the mandrels.
  • Plate 75b is arranged above the path of the mandrels. The height of each may be adjusted independently to accommodate various diameter mandrels.
  • the lower plate 75a may be moved downward and the upper plate 75b moved upward to increase the gap between them to accommodate larger diameter mandrels.
  • the lower plate 75a may be moved upward and the upper plate 75b moved downward to decrease the gap between them to accommodate smaller diameter mandrels.
  • the gap between them may be made very large to accommodate the passage of logs between them when running in bypass mode.
  • the gap between them may extend from the log infeed end to the log outfeed end so that the logs with protruding mandrels to be extracted may pass in to the mandrel extraction stations, and any protruding mandrels that are not withdrawn can pass out from the mandrel extraction stations to the downstream region where they may be culled by the log cull system 45,49.
  • the cross-direction position of the log face restraint plates 75 may be adjusted, for instance to set them at the correct position for a given log length, or move them to a different position for a different log length. They may be supported by, and slide on, linear guides such as rails or shafts.
  • logs may be shifted in the cross-direction by a log alignment conveyor before they are carried to their mandrel extraction positions by the main log conveyor. Thus, they need not be shifted in the cross-direction to the log face restraint plates 75 after arriving at their mandrel extraction positions.
  • the upstream ends of the plates may be provided with chamfers and/or radii to reduce the chance of the log ends catching on the upstream edges of the plates as the logs are conveyed into the extraction stations. More preferably, however, the face restraints are reciprocated linearly in the cross-direction, so there is clearance between the plates and the log ends as the logs are conveyed into the extraction stations. Actuators 77, preferably pneumatic cylinders, may be provided to effect this reciprocation. In the exemplary embodiment the actuators in hold the face restraint plates away from the log ends as the logs are conveyed toward their mandrel extraction positions.
  • the actuators may move the restraint plates toward the log ends.
  • the reciprocating log face restraint plates have the further advantage of optionally applying axial compression to the logs. This may be accomplished by adjusting the position of the face restraint plates 75 or by adjusting the relative position of the log stop plate 86 at the CD alignment conveyor. A small amount of axial compression or preload on the logs may be beneficial to ensure the logs are stable and stationary during the mandrel extraction.
  • Figs. 18 - 19 also show possible embodiments for the mandrel end supports 65 and the mandrel drag guides 66.
  • the mandrel end supports are disposed at the end of arms arrayed on a pivoting shaft.
  • the pivoting shaft is below the space where the mandrels are withdrawn from the logs.
  • Rotation of the shaft is effected by an actuator, which may be an electric servo motor, but is more preferably a pneumatic cylinder for cost reasons.
  • the mandrel end supports may be pivoted upward and downward, in oscillating fashion, by rotating the shaft back and forth.
  • the mandrel end supports may be pivoted upward so they support the ends of the mandrels that are closer to the logs when the ends of the mandrels emerge from the logs.
  • the mandrel drag guides are also disposed at the end of arms arrayed on pivoting shafts.
  • the pivoting shaft for the lower drag guides is below the space where the mandrels are withdrawn from the logs.
  • the pivoting shaft for the upper drag guides is above the space where the mandrels are withdrawn from the logs. Rotation of each shaft is effected by an actuator, which is preferably an electric servo motor, for reasons of speed and precision.
  • the mandrel drag guides may be pivoted upward and downward, in oscillating fashion, by rotating the shafts back and forth. After the mandrels are withdrawn from the logs, the upper drag guides may be pivoted downward and the lower drag guides may be pivoted upward to pinch and press the mandrels between them, causing the mandrels to cease translating in the cross-direction after the mandrels have been unclamped by the clasps.
  • the mandrel puller carriage may move the clasps a little farther from the restrained mandrels so that the ends of the mandrels emerge from the clasps. Then the mandrel end supports 65 and the lower drag guides may be pivoted downward to lower the mandrels onto the mandrel return conveyor 50. As the mandrels are lowered, the upper drag guides may be pivoted upward to move them out of the way so the mandrel puller carriage can execute is return motion when it is time to extract mandrels from the next set of logs.
  • a machine such as a mandrel extractor may be programmed to execute its sequence of operations step-wise according to positive signals from mandrel and log detectors. That is, it may wait to perform the next action until a signal is received from a detector indicating the previous action was completed. It is fairly simple. However, it is not efficient for processes with numerous actions and elements, because the time interrogating and responding to the sensors for the numerous steps adds up to significant wasted time. Thus, the maximum rate in practice may be significantly less than the theoretical rate of the process.
  • An alternative, which may be used with this mandrel extractor, is to coordinate the sequence of operations according to a virtual time signal. That is, the actions are performed in accordance with a pre-planned timeline which does not wait for signals from sensors or detectors.
  • This method is more efficient for operation at high cycle rates because time is not wasted interrogating and responding to sensors for the numerous steps. Instead, the sensors are interrogated concurrent with execution of the timeline to verify things are performing according to the timeline. If a step in the process lags too far behind, or a log or a mandrel is out of position, a fault is returned and the machine may be stopped automatically by the PLC if a corrective action by the PLC while running is not feasible. Because the extractor actions are executed without incurring cumulative wasted time for detector interrogation and responses by the PLC, the maximum rate in practice is closer to the theoretical rate of the process, preferably even matching the theoretical rate of the process.
  • the rate limit is the maximum log rate the extractor can process. At higher rate limits the sequence of operations must occur in less time. At lower rate limits the sequence of operations may take place over greater time. If the extractor rate limit is high, for instance 30 LPM, even when the rewinder line is producing logs at a relatively low rate, for instance 18 LPM, perhaps due to winding speed or laminating speed limitations, the extractor will execute its motions more rapidly than necessary and then be idle as it waits for the next set of logs to arrive.
  • the extractor should preferably be tuned to operate at, for instance, a value such as 20 LPM.
  • a value such as 20 LPM.
  • the log conveyors, mandrel conveyors, and mandrel puller may operate with lower velocity and acceleration values, experience less rapid wear and tear as a result, and the extractor may tend to have fewer problems from logs and mandrels being mishandled at the lower speeds and relaxed timeline.
  • the extractor may preferably be tuned to operate at, for instance, 30 LPM.
  • the log conveyors, mandrel conveyors, and mandrel puller will operate with higher velocity and acceleration values because it is necessary, which is appropriate. Due to the quantity of conveyors and actuators and complexity of the timeline, as well as a preference to reduce the training and knowledge burden required, it is preferred to have the PLC perform the rate scaling rather than have operators or technicians attempt to do it. Thus the operator may simply enter a requested rate limit value on the HMI, or the rate limit from the rewinder may be used, and based on this value the PLC may automatically adjust the timeline sequence and conveyor motions so the extractor is tuned to operate at that rate.
  • Figs. 18-24 show a mandrel return system associated with the mandrel extractor 44.
  • Figs. 21-22 show a mandrel return conveyor 50 onto which the mandrels are dropped or lowered after they are extracted from the logs.
  • the mandrel return conveyor 50 may comprise two or more flighted belts, with the flight spacing approximately matching the spacing between the clasps of the mandrel puller so that the mandrels can be lowered directly into the flights.
  • Fixed guides and supports 28 may be provided as well to add support for the mandrels and guide the mandrels as they travel on the conveyor.
  • the conveyor may triple-index to deliver the mandrels onto a mandrel alignment conveyor 52 (Fig. 20) for alignment with the return elevator 56 (Fig. 23).
  • a mandrel alignment conveyor 52 may be provided when the mandrel storage hopper/magazine 58 is located in a different cross-direction location than the mandrel return conveyor 50 of the extractor.
  • the mandrel alignment conveyor 52 may comprise an endless flat belt with two flights.
  • the mandrel alignment conveyor may transport the mandrels in the cross-direction until they are aligned with the mandrel return elevator 56.
  • the mandrel alignment conveyor 52 may be canted at an angle so that the mandrels roll onto it from the return conveyor 50, and then off of it down the elevator infeed table 54 (Fig. 24) toward the return elevator 56, expeditiously.
  • the mandrel alignment conveyor 52 and elevator infeed table 54 may be provided with a gate 55 (Fig. 24) that keeps the mandrels from rolling off the conveyor or down the inclined table toward the return elevator, until their cross-direction alignment is completed and the mandrel return elevator 56 is ready to receive them.
  • the gate 55 may open to allow the mandrels to roll down an inclined infeed table 54 to the mandrel return elevator.
  • the gate may provide time for a prior set of mandrels to be lifted off the table by the return elevator 56 as the next set of mandrels is shifted over by the alignment conveyor 52, thus allowing for a higher maximum cycle rate.
  • the infeed table 54 may be provided with openings for mandrel carriers on the mandrel return elevator 56 to pass through.
  • the mandrel return elevator 56 may be provided with major and minor flight distances between the carriers 112, with carriers in the minor flights (groups of three in this example) spaced a short distance apart, and these groups (of three in this example) spaced farther apart at the major flight distance. Configuring the mandrel return elevator 56 this way, as opposed to well-known core elevators with uniform flights spaced by the minor flight distance all along the conveyor, has the benefits of reducing the number of mandrels required for operation and of limiting the time the mandrels spend with partial support on the elevator, thereby tending to reduce development of mandrel sag.
  • Mandrels may stretch during mandrel extraction. If mandrel extraction forces are high relative to the elastic modulus of the mandrel, either because the logs are tightly wound, or because the mandrels are very slender, or both, mandrels may stretch a relatively large amount. Mandrels may elongate within the log as the log is wound. If the interlayer pressure between the web wraps is high due to tight winding, or the mandrels are slender, or both, the mandrels may be elongated a relatively large amount. A mandrel that remains elongated following extraction tends to contract toward its original length if given time to rest.
  • the mandrel may elongate permanently if it is reused before it has returned close enough to its original length.
  • a mandrel circulation conveyor may be provided.
  • the mandrel circulation conveyor may be positioned between the mandrel return elevator 56 and the mandrel storage hopper/magazine 58.
  • a mandrel circulation conveyor provides additional time for the mandrels to rest and contract in length before being reused in the rewinder.
  • the size of the mandrel circulation conveyor and recommended quantity of mandrels in circulation can be determined from the cycle rate at which the logs are produced and the time required for a mandrel to return to its original length or close enough to its original length.
  • a mandrel circulation conveyor may be advantageous in, as a non-limiting example, a rewinder line producing industrial type bath tissue rolls wound to a relatively high degree of tightness on a relatively small diameter mandrel (for example, less than 25 mm diameter).
  • the length of each mandrel may be measured to confirm it has returned close enough to its original length before being reused in the rewinder and ejected from recirculation if it is too long.
  • this measurement is performed by the machine automatically.
  • the measurement may be performed by a camera vision system or other optical sensor.
  • the mandrels may not return fully to their original length in the circulation conveyor, but instead increase in length by a small amount with each cycle. This may be economical if the increase in length with each use is small enough so an adequate cycle life of the mandrel is obtained relative to its replacement cost. In this case also the additional rest time afforded by the circulation conveyor may be used to extend the usable cycle life of the mandrels.
  • An alternative embodiment of the concept is to add more flights, along with more mandrel supports in the cross-direction, to a mandrel return elevator, and increase its length to increase its capacity of mandrels, thereby increasing the rest time of the mandrels during their return circulation.
  • Fig. 7 shows an alternate embodiment for a 2-station mandrel extractor 200 (with two puller clasps) that has a vertical path for the main log conveyor 202. It would have a lower maximum cycle rate than the 3-station and 4-station extractors discussed above, but should cost far less to construct.
  • the logs are split into two paths prior to the pickup point at the infeed, by a simple and inexpensive pivoting gate 204, which obviates the need for the log lift conveyor, lower infeed belts, upper infeed belts, and a positioning mechanism to adjust the height of the upper infeed belts structure in the embodiments described above. It may use a brush 206 to decelerate the logs, instead of the infeed roller and accompanying positioning mechanism to adjust the height of the infeed roller structure.
  • the embodiment shown in Fig. 7 allows the elimination of 3 conveying systems and corresponding servo motors, and a roller.
  • the main log conveyor 202 includes a flighted belt with log carriers 208.
  • the main log conveyor 202 may include four timing belts which may have a 14 mm pitch and 85 mm width.
  • the log carriers 208 may be attached directly to the timing belts such that the belts may operate with only a guide 210 behind the belt 202 for stability of the belt and carriers.
  • the distance from the lower timing pulley to the upper timing pulley may be set to control the length of the span (for instance, 1 m (39.4")), which is favorable for controlling the belt deflection.
  • the relatively large pitch and width timing belts may be set to substantially high tension in this span also to control deflection of the belt due to a tendency of the carriers to tip under the weight of the logs.
  • the belts may be configured to support the weight of three logs in the middle portion of this span. If found to be necessary, the carriers may be supported additionally with guides in tracks parallel to the belt path.
  • the pitch distance of the carriers may depend upon the product format. For typical consumer bathroom tissue and kitchen towel products, the pitch distance may be 252 mm (9.92"). Extraction takes place on sets of two logs.
  • the main log conveyor 202 remains stationary for loading two logs, and then executes a double index to bring the two logs from the infeed positions 203 to the extraction positions 205. During the double index the main log conveyor also discharges two logs (with mandrels removed) at an outfeed 212, and makes space for two logs to load at the infeed.
  • the infeed gate 204 opens (pivots down), for instance, by a pneumatic cylinder, and the second log loaded rolls to the lower position.
  • the log carrier at the lower position may be recessed slightly below log supports, so the bouncing log does not hit the carrier causing stress to the carrier mounting and possibly disturbing other logs on the conveyor. This precaution may be taken because the second log, moving to the lower position, falls farther and thus may have greater kinetic energy when it loads. So that the lower log can pass upward during the double index, the upper log load position may not have log supports, but rather the log may roll directly onto the log carriers 208.
  • the brush 206 may be configured to decelerate the logs as they roll to the upper load position and thereby reduce their kinetic energy when they contact the carrier and belt of the main log conveyor 202.
  • a vertical guide 210 behind the belt of the main log conveyor 202 may be provided to keep the log carrier 208 from moving excessively when a log is loaded onto the carrier and bumps into the belt 202.
  • log supports (not shown) may be provided at the upper log load position to temporarily take the log weight, so the carrier is not disturbed excessively during log loading, and which are then pivoted out of the way, for instance by a pneumatic cylinder, at the same time the gate 204 is pivoted downward for arrival of the second log.
  • the tip of the infeed gate 204 may extend into the path of the logs. Therefore, after the infeed gate 204 has pivoted down for the log to load at the lower position, the infeed gate may stay in the lowered position (pivoted down) until the main log conveyor has executed approximately one-half of its double index motion. Then, the infeed gate may be pivoted back up for the next log to arrive as the lower log clears the load position for the upper log.
  • the brush 206 may be configured to allow for deceleration of the log rolling to the upper log load position.
  • the brush 206 may be located so it also operates on the log going to the lower load position. It may be configured to allow for deceleration of the logs rolling to both the upper and lower load positions if it is located farther upstream, nearer and for instance generally above the pivot of the infeed gate 204. Or, if it is located farther downstream, generally above the gate opening, it may serve as a deflector to direct the log downward toward the lower log load position.
  • more than one brush may be used, with a brush at each location.
  • the brush may be mounted to the same carriage framework as the upstream (anterior) peripheral restraints 220, which is moveable on substantially vertical linear slides to be adjusted for log diameter changes.
  • the main log conveyor 202 executes the double index movement
  • the main log conveyor moves the two logs from the log load positions 203 to the mandrel extraction positions, or stations, 205 just above.
  • the logs may be aligned in the cross-direction by actuators, such as pneumatic cylinders, that are configured to push the logs from the far side against axial face restraint plates 214 at the near side of the machine. Alignment of the logs in the cross-direction may be performed during indexing of the main log conveyor if, for instance, higher cycle rate log handling is desired.
  • the axial face restraint plates 214 do not have to be reset or moved for log diameter changes, but only for mandrel diameter changes.
  • the axial face restraint plates do not have to be adjusted in the vertical direction.
  • the axial face restraint plates require only two adjustments: horizontal in the machine direction for mandrel diameter changes and horizontal in the cross-direction for web width (log length) changes. These adjustments may be done with actuators, but for cost considerations may be done as manual adjustments.
  • peripheral restraints 216,220 may be moved to engage the logs.
  • the peripheral restraints may comprise three anterior troughs 220 and three posterior troughs 216 per log.
  • the three anterior troughs 216 and three posterior troughs 220 may be nested between the four main log conveyor timing belts.
  • the troughs 216,220 may be configured for a pivoting motion between engagement and disengagement positions with the log.
  • the troughs 216,220 may be configured with low moments of inertia, so the pivoting motion can be effected with small servo motors and gearboxes.
  • Servo motors may be used to provide quick and precise pivoting motion between engagement and disengagement positions with the log.
  • the peripheral restraint system may be configured such that the anterior restraints 220 share a common servo motor and the posterior restraints 216 share a common servo motor.
  • a drive train for instance a 4-bar linkage, or possibly a timing belt or similar, may be used to couple the pivot shafts of the respective restraints so they move in unison, with one actuator.
  • the posterior restraints 216 do not require linear slides for adjustment.
  • the pivoting motion of the posterior restraints 216 for instance, by choosing the shaft location for the posterior restraints judiciously, may be sufficient to accommodate log diameter changes in addition to performing the engagement and disengagement motion.
  • the anterior restraints 220 may include substantially vertical linear slides for adjustment of the height of their pivots when changing log diameter.
  • the anterior restraints 220 may be provided with an adjustable carriage at the infeed side to support the anterior peripheral restraints system. Motion of the carriage along the linear slides may be effected with the use of linear actuators by motor, or manually.
  • the brush 206 may be mounted to this same carriage as the anterior restraints 220. A gross position height adjustment of the brush may be effected by movement of the carriage: lower for smaller diameter logs, higher for larger diameter logs.
  • the brush 206 may include a fine adjustment relative to the carriage.
  • the belts of the main log conveyor 202 may include log carriers 208 that are configured with a general bow tie shape, instead of the carriers with a general chevron shape as shown in Fig. 7.
  • the bow tie shape configuration may allow the logs to transition from riding on the tops of the carriers when going up the main log conveyor, at the infeed side, to riding on the bottoms of the carriers when going down the main log conveyor, at the outfeed side.
  • the belts of the main log conveyor 202 may include log carriers 208 that are configured with a general C shape, instead of the carriers with a general chevron shape as shown in Fig. 7.
  • the opening of the C shape carriers may face leftward when at the infeed side, to receive logs, and face rightward when at the outfeed side, to discharge logs.
  • the C shape configuration may allow the logs to transition from riding in the trailing portion of the carriers when going up the main log conveyor, at the infeed side, to riding in the leading portion of the carriers when going down the main log conveyor, at the outfeed side.
  • An outfeed table 212 may be provided to unload and receive logs from the main log conveyor.
  • a roll down table may be used to deliver the logs from this point to the next processing module in the converting line, typically a log accumulator.
  • the log accumulator may be configured to receive the logs at this higher elevation so the logs do not have to be lowered to the typical log accumulator infeed height.
  • the logs may be lowered from this discharge height to a relatively lower height, for instance, by a conveying system (not shown).
  • the main log conveyor may be used to convey the logs to a relatively lower height for delivery to a log accumulator or a log cull system.
  • the outfeed table 212 near the top of the main log conveyor would be omitted.
  • the logs may transfer from the top sides of the bow tie shape carriers to the undersides of the bow tie shape carriers ahead of them as they pass over the upper timing pulley, and then ride down the right side of the main log conveyor on the bow tie shape carriers to a height nearer the floor before being unloaded.
  • the logs may migrate from the trailing portion of the C shape carriers to the leading portion of the C shape carriers as they pass over the upper timing pulley, and then ride down the right side of the main log conveyor in the C shape carriers to a height nearer the floor before being unloaded. Additional timing pulleys may be provided within the main log conveyor belts to extend their loop length and allow the logs to be unloaded at a preferred height. Because the main log conveyor executes a double index, it would discharge two logs in rapid succession, except for the following method which may be used to cause the logs to discharge from the main log conveyor at a substantially uniform interval.
  • a log unloading portion of roll down table may be arranged at a good height for logs to roll to the next module, for instance a log cull system and/or accumulator infeed. It may be actuated up and down by a pneumatic cylinder or other suitable actuator.
  • the system may be arranged so that when the main log conveyor is at its dwell position, the carrier with the first log to be unloaded is just above this portion of table, with the table in its down position. While the main log conveyor is stationary, this portion of table may be actuated upward to lift and unload the log from the carrier. The unloaded log may then roll down a fixed portion of inclined table to the next module.
  • this system may be configured to unload logs at a substantially uniform interval, at the cycle rate of the rewinder, because it can unload every other log (odd logs) when the main log conveyor is stationary, and the other logs (even logs) during the main log conveyor double index movement.
  • any single log may be culled following the extractor, without having to slow down the converting line, because the instantaneous log delivery rate would substantially match the average log rate.
  • This method obviates the need for the outfeed belts and a positioning mechanism to adjust the height of the outfeed belts structure in the embodiments described above.
  • the logs After the logs are unloaded they may roll down an inclined table and can be culled by a gate integrated in the table at the infeed to the accumulator 48, or pass into the accumulator, as with the embodiments described above.
  • the cull system may or may not be integrated with the accumulator infeed so it can be more generic.
  • the height of the mandrel puller clasps in the mandrel extractor has to be adjusted to compensate for changes in log diameter (as it was for the embodiments described above). This may be done by mounting the puller in a framework moveable along vertical linear slides and adjusting its height with linear actuators, or other mechanisms, by a motor, or manually with a hand wheel.
  • the clasps of the mandrel extractor may be configured as shown in Fig. 17A-17C.
  • the drag guides and mandrel end supports described previously may be supported in a way that does not prevent using a single carriage and motor for moving the carriage and the two clasps.
  • the drag guides and mandrel end supports may be configured to reliably restrain the mandrels, facilitate clearing the mandrels from the path of the returning pullers, and facilitate clearing themselves from the path of the returning pullers.
  • the mandrel return may include mandrel return guides utilizing gravity, which obviates the need for the mandrel return conveyor described previously.
  • a mandrel alignment system may be configured to shift the mandrels over in the crossdirection for the return trip to the storage magazine or mandrel hopper. This may be done with a rod-less pneumatic cylinder pushing the mandrels on a stationary table surface. The pusher would extend rapidly to move the mandrels and then can retract while mandrels are still on the table, before the mandrel return elevator has finished picking up the mandrels.
  • the mandrel return elevator may be configured to pick the mandrels up directly from the table of the mandrel alignment system.
  • a technique to reduce the incidence of log instability is to automatically adjust the line speed based on a measured magnitude of the log instability or vibration. This method may also be used to control the severity of the instability. The magnitude of the instability or vibration may be reduced, minimized, or eliminated; or it may be optimized, according to the preference of the converter. There may be times minor instability causes no defects. There may be times operating at higher winding speed is deemed worth some level of imperfection in the product and this method of active monitoring can be used to maintain the desired result as material properties or other conditions change. It is known that the log makes noise and vibrates when it is unstable.
  • capturing audio from the area or leveraging feedback signals in the motion control system from the servo axes which control winding of the log.
  • suitable signals include torque or current feedback, or simply velocity error.
  • One way to filter the signals would be to apply a time to frequency domain transform based on the average log diameter during the winding process relative to an optimized window of time series data stored in a FIFO updating each new sample. The fundamental frequency would also update each sample to the new average log diameter for the window of time series data.
  • One possible methodology would be to use a Goertzel style algorithm, or conventional Discreet Fourier Transform (DFT), to calculate the continuous evolution of the power magnitude of the desired fundamental frequency and associated harmonics of the log rotation as it builds diameter. This signal can then be analyzed for characteristics, such as, but not limited to, absolute magnitude or rate of change. Given target characteristics, the line speed can be modulated to maintain the log stability within ideal bounds which would help maximize efficiency.
  • DFT Discreet Fourier Transform

Landscapes

  • Replacement Of Web Rolls (AREA)

Abstract

L'invention concerne un fermoir qui peut venir en prise avec une extrémité d'un tube. Le fermoir a une broche qui peut être insérée dans un alésage du tube. Le fermoir a un boîtier avec une pluralité de coins de serrage. Les coins de serrage sont espacés de manière circonférentielle autour de la broche et mobiles entre une position séparée et une position en prise. Dans la position en prise avec un tube disposé entre les coins de serrage et la broche, les coins de serrage pressent le tube contre la broche. Un coin actionneur peut venir en prise de manière coulissante avec le coin de serrage correspondant le long de surfaces en forme de coin complémentaires et coopérantes de telle sorte qu'un mouvement axial du coin actionneur provoque un mouvement radial du coin de serrage correspondant entre la position séparée et la position en prise. Un ressort est relié de manière fonctionnelle à un coin actionneur correspondant pour solliciter le coin d'actionneur vers la position en prise.
PCT/US2023/080453 2023-11-20 2023-11-20 Fermoir pour produire des produits en rouleau sans noyau Pending WO2025110987A1 (fr)

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Citations (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1554619A (en) 1976-05-19 1979-10-24 Moelnlycke Ab Roll of web material
US4487378A (en) 1982-05-19 1984-12-11 Masashi Kobayashi Coreless toilet paper roll and method for manufacture thereof
US5027582A (en) 1989-04-14 1991-07-02 The Procter & Gamble Company Compact, core-wound paper product and method of making
US5186099A (en) 1988-12-23 1993-02-16 China Henan Light Industrial Products Import And Export Corporation Method of saving space occupied by toilet rolls in transportation and storage processes and related special devices
US5730387A (en) 1992-09-25 1998-03-24 Yamazaki; Tokushichi Apparatus for making coreless roll of web material
US6056229A (en) 1998-12-03 2000-05-02 Paper Converting Machine Co. Surface winder with pinch cutoff
US6422501B1 (en) 2000-11-27 2002-07-23 Paper Converting Machine Company Core infeed apparatus for winder
US6838187B2 (en) 2002-05-10 2005-01-04 National Starch And Chemical Investment Holding Corporation Water based adhesive composition with release properties
JP3777150B2 (ja) * 2002-11-15 2006-05-24 株式会社不二鉄工所 巻芯成形機能を備えた巻取機の巻芯軸
US9284147B2 (en) 2012-09-21 2016-03-15 Paper Converting Machine Company Method and apparatus for producing coreless rolls of paper
US9290347B2 (en) 2011-02-23 2016-03-22 Fabio Perini S.P.A. Device and a method for extracting winding spindles from a log of web material
US20160137398A1 (en) 2014-11-17 2016-05-19 Georgia-Pacific Consumer Products Lp Compressed Hollow Coreless Re-Formable Roll Products
IT201600073544A1 (it) 2016-07-14 2018-01-14 Paper Converting Machine Company Italia S P A Metodo per mantenere la forma circolare del foro centrale di rotoli coreless di carta tissue e relativo rotolo
US10213066B2 (en) 2016-04-01 2019-02-26 Essity Operations France Coreless roll of absorbent sheet and method for manufacturing the same
EP3688224A1 (fr) 2017-09-29 2020-08-05 Essity Hygiene and Health Aktiebolag Rouleau sans mandrin de feuille absorbante et son procédé de fabrication
EP3688226A1 (fr) 2017-09-29 2020-08-05 Essity Hygiene and Health Aktiebolag Rouleau sans mandrin de feuille absorbante et son procédé de fabrication
WO2020245319A1 (fr) 2019-06-05 2020-12-10 MTorres Tissue S.r.l. Procédé et dispositif pour dénuder un mandrin de bobine d'un cylindre
US11046540B2 (en) 2017-11-29 2021-06-29 Paper Converting Machine Company Surface rewinder with center assist and belt and winding drum forming a winding nest
US20210403266A1 (en) 2020-06-26 2021-12-30 Paper Converting Machine Company Method for Producing Coreless Roll Products
US11247863B2 (en) 2018-11-27 2022-02-15 Paper Converting Machine Company Flexible drive and core engagement members for a rewinding machine
US11261045B2 (en) 2019-03-01 2022-03-01 Paper Converting Machine Company Rewinder winding methods and apparatus
US20230010524A1 (en) 2021-07-06 2023-01-12 Rongzhi Cui Children's Ride-On Vehicle Assembly

Patent Citations (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1554619A (en) 1976-05-19 1979-10-24 Moelnlycke Ab Roll of web material
US4487378A (en) 1982-05-19 1984-12-11 Masashi Kobayashi Coreless toilet paper roll and method for manufacture thereof
US5186099A (en) 1988-12-23 1993-02-16 China Henan Light Industrial Products Import And Export Corporation Method of saving space occupied by toilet rolls in transportation and storage processes and related special devices
US5027582A (en) 1989-04-14 1991-07-02 The Procter & Gamble Company Compact, core-wound paper product and method of making
US5730387A (en) 1992-09-25 1998-03-24 Yamazaki; Tokushichi Apparatus for making coreless roll of web material
US6056229A (en) 1998-12-03 2000-05-02 Paper Converting Machine Co. Surface winder with pinch cutoff
US6422501B1 (en) 2000-11-27 2002-07-23 Paper Converting Machine Company Core infeed apparatus for winder
US6838187B2 (en) 2002-05-10 2005-01-04 National Starch And Chemical Investment Holding Corporation Water based adhesive composition with release properties
JP3777150B2 (ja) * 2002-11-15 2006-05-24 株式会社不二鉄工所 巻芯成形機能を備えた巻取機の巻芯軸
US9290347B2 (en) 2011-02-23 2016-03-22 Fabio Perini S.P.A. Device and a method for extracting winding spindles from a log of web material
US9284147B2 (en) 2012-09-21 2016-03-15 Paper Converting Machine Company Method and apparatus for producing coreless rolls of paper
US11383947B2 (en) 2012-09-21 2022-07-12 Paper Converting Machine Company Method and apparatus for producing coreless rolls of paper
US9919888B2 (en) 2012-09-21 2018-03-20 Paper Converting Machine Company Method for producing coreless rolls of paper
US9975720B2 (en) 2012-09-21 2018-05-22 Paper Converting Machine Company Method for producing coreless rolls of paper
US10676304B2 (en) 2012-09-21 2020-06-09 Paper Converting Machine Company Method and apparatus for producing coreless rolls of paper
US20160137398A1 (en) 2014-11-17 2016-05-19 Georgia-Pacific Consumer Products Lp Compressed Hollow Coreless Re-Formable Roll Products
US10213066B2 (en) 2016-04-01 2019-02-26 Essity Operations France Coreless roll of absorbent sheet and method for manufacturing the same
IT201600073544A1 (it) 2016-07-14 2018-01-14 Paper Converting Machine Company Italia S P A Metodo per mantenere la forma circolare del foro centrale di rotoli coreless di carta tissue e relativo rotolo
EP3688226A1 (fr) 2017-09-29 2020-08-05 Essity Hygiene and Health Aktiebolag Rouleau sans mandrin de feuille absorbante et son procédé de fabrication
EP3688224A1 (fr) 2017-09-29 2020-08-05 Essity Hygiene and Health Aktiebolag Rouleau sans mandrin de feuille absorbante et son procédé de fabrication
US11046540B2 (en) 2017-11-29 2021-06-29 Paper Converting Machine Company Surface rewinder with center assist and belt and winding drum forming a winding nest
US11247863B2 (en) 2018-11-27 2022-02-15 Paper Converting Machine Company Flexible drive and core engagement members for a rewinding machine
US11261045B2 (en) 2019-03-01 2022-03-01 Paper Converting Machine Company Rewinder winding methods and apparatus
WO2020245319A1 (fr) 2019-06-05 2020-12-10 MTorres Tissue S.r.l. Procédé et dispositif pour dénuder un mandrin de bobine d'un cylindre
US20210403266A1 (en) 2020-06-26 2021-12-30 Paper Converting Machine Company Method for Producing Coreless Roll Products
US20230010524A1 (en) 2021-07-06 2023-01-12 Rongzhi Cui Children's Ride-On Vehicle Assembly

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