WO1994024033A1 - Bobineuse continue pour materiaux en bandes - Google Patents

Bobineuse continue pour materiaux en bandes Download PDF

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Publication number
WO1994024033A1
WO1994024033A1 PCT/US1994/004033 US9404033W WO9424033A1 WO 1994024033 A1 WO1994024033 A1 WO 1994024033A1 US 9404033 W US9404033 W US 9404033W WO 9424033 A1 WO9424033 A1 WO 9424033A1
Authority
WO
WIPO (PCT)
Prior art keywords
drum
core
core shaft
driving
roll
Prior art date
Application number
PCT/US1994/004033
Other languages
English (en)
Inventor
R. Duane Smith
Daniel F. Hould
Original Assignee
The Black Clawson Company
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 The Black Clawson Company filed Critical The Black Clawson Company
Publication of WO1994024033A1 publication Critical patent/WO1994024033A1/fr

Links

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
    • B65H19/2238—The web roll being driven by a winding mechanism of the nip or tangential drive type
    • B65H19/2253—The web roll being driven by a winding mechanism of the nip or tangential drive type and the roll being displaced during the winding operation
    • B65H19/2261—Pope-roller
    • 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
    • B65H2301/4148—Winding slitting
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2408/00—Specific machines
    • B65H2408/20—Specific machines for handling web(s)
    • B65H2408/23—Winding machines
    • B65H2408/236—Pope-winders with first winding on an arc of circle and secondary winding along rails
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2515/00—Physical entities not provided for in groups B65H2511/00 or B65H2513/00
    • B65H2515/12—Density

Definitions

  • This invention relates to apparatus and a method for the continuous winding of web materials.
  • the apparatus is of the general type shown in the co-owned Evans et al , U. S. Patent No. 2,703,683 of 1955 and
  • Such reels include a driving drum for surface driving each winding roll, and primary arms which support each successive new roll core while the web is starting to wind thereon, and wherein the new roll is then transferred to secondary means such as ways for completion of the winding.
  • Winders of this type have in the past been used most often to receive paper webs from a paper machine or from a converting line to form successive large rolls having the complete web width wound thereon, and these large rolls were then taken to a different station where they could be unwound, slit to desired smaller widths, and rewound with proper roll density control.
  • the modern trend is to slit wide webs before they are wound at all, and then to wind the resulting individual narrow webs into rolls of the proper quality.
  • the present invention was made as a result of realization of the fact that the existing technology did not provide adequate control of the density of wound rolls of relatively bulky web materials such as non-woven fabrics, particularly in conjunction with a slitting operation prior to winding the resulting multiple rolls.
  • the invention is not limited to bulky web materials and can be successfully utilized with other web materials.
  • the major novel characteristic of the invention is that it provides for driving each successively wound roll both by surface engagement with the driving drum and by a driving force applied to the axis of the roll from the start of the roll to its completion, i.e. during the interval wherein the new roll is being started on a core supported in the primary arms and also after it has been transferred to the secondary ways or other secondary supporting means.
  • the angular (rpra) speed of the roll constantly decreases as its diameter increases.
  • the invention provides for supplementing the surface driving of the winding roll throughout the complete winding cycle by applying a torque mode driving force to the core shaft which supports the winding roll both in the primary arms wherein the roll is started and on the secondary supporting means where winding of the roll is completed.
  • a special feature of the apparatus of the invention is that the center drive to the core shaft while it is supported in the primary arms originates from a stationary motor through a transmission system carried by one of the primary arms which is of such structure and mode of operation as to be equally effective in all positions of the core shaft in the primary arms as the shaft moves radially of the driving drum in response to the increase in diameter of the web material wound thereon.
  • the new segmented core in the primary arms which has segments corresponding to the width of each slit portion of the web is mounted on a common support, is brought up to the proper surface speed by its center drive before it is in contact with the web which is traveling around the drum to the roll winding on the secondary ways.
  • the core shaft is driven both by surface contact with the drum and by the center-applied drive, but the latter drive is shifted from maintaining the surface speed of the new slit roll matching that of the drum to applying predetermined torque to the winding roll that supplements the surface drive and thereby controls the hardness with which the web begins and continues to wind on the new core.
  • the apparatus of the invention includes a second torque mode drive associated with the carriages which support each successive winding roll on the secondary ways. Provision is made for transferring the center applied drive from the drive carried by the primary arms to the torque mode drive of the core shaft while it is carried by the secondary way carriages before the new roll is released from the primary arms so that they can return to the proper position for starting the next rol1.
  • Fig. 1 is a side elevation showing a winder installation in accordance with the invention
  • Fig. 2 is a side elevation, on a larger scale, of the primary arm assembly on the same side of the winder shown in Fig. 1;
  • Fig. 3 is an elevational view of the arm assembly, looking from right to left in Fig. 2;
  • Fig. 4 is a partial elevational view of the other side of the winder from the side viewed in Fig. 1;
  • Fig. 5 is a fragmentary view in elevation looking as indicated by the line 5—5 in Fig. 4;
  • Fig. 6 is an enlarged fragmentary section on the line 6—6 in Fig. 4;
  • Fig. 7 is a fragmentary view looking downward as indicated by the line 7—7 in Fig. 5.
  • Fig. 1 illustrates a continuous winder installation in accordance with the invention.
  • the driving drum 10 has its opposite end journals supported in end frames 11 and 12, and it is driven in conventional manner by a main drive 13 at a constant surface speed matching the speed at which a non-woven fabric web W is fed thereto.
  • the web feed may also be conventional, and those of its component parts shown in Fig. 1 include a pull roll 14 from which the web advances around a tension transducer roll 15, through a slitting section 16 and then around successive spreader rolls 17 and 18 to the drum.
  • Each of a pair of primary arm assemblies 20 includes an arm 22 mounted on the respective end frame 11 or 12 for pivotal movement about the axis of drum 10.
  • This movement is effected and controlled by a link 23 pivoted at 24 to the adjacent arm 22 and pivoted at 26 to a lever 25 on a shaft 27 rotatably supported in the adjacent end frame 11.
  • Shaft 27 extends across the machine and through the other end frame to operate the duplicate adjusting mechanism (not shown) for the other primary arm assembly. Rotation of shaft 27 may be controlled in any conventional manner to swing the arms 20 during roll changing as described hereinafter.
  • the remainder of the basic structure of the winder includes horizontal secondary ways 30 extending from the end frames 11 and 12 and supported near their outer ends by appropriate leg structure 31.
  • a carriage 33 is mounted by means of linear bearings 34 for sliding movement on each of these secondary ways, and each carriage 33 has a horn 35 pivotally mounted on its outer end for retaining the core shaft of each winding roll after it has been transferred from the primary arms 20. Movement of the carriages 33 is controlled by a fluid pressure cylinder 36 mounted in each of the ways 30 and having its piston rod 37 connected to the associated carriage.
  • the primary arm assembly 20 on the control side of the winder shown in Fig. 1 includes means for driving a new core by force applied to the axis thereof. The structure and mode of operation of this primary arm assembly are illustrated in Figs. 2-3.
  • the basic structural member is an arm 22 mounted by any suitable bearing structure 40 on the end frame 11 for rotation about the axis of drum 10 between approximately 11 o'clock and 3 o'clock positions as viewed in Fig. 1.
  • a slide 42 is movable lengthwise of the arm 22, and its movements are controlled by a fluid pressure cylinder 43 mounted near the radially inner end of arm 20 and having its piston rod 44 pivotally connected to the slide 42.
  • the slide 42 includes a portion forming a saddle 45 proportioned to receive and support the bearings 46 on one end of a core shaft 50 having a core C, or more probably a set of core sections C in end to end relation, mounted thereon in preparation for the winding of a new roll of web material W.
  • a core shaft 50 When a core shaft 50 is mounted in the saddle 45, it is rotatably held therein by the system of links and a fluid pressure cylinder shown in Fig. 2. More specifically, an arm 51 is pivoted at 52 to the slide 42, and it carries at its outer end a roller 53 which is movable into and out of rotatable engagement with a groove 54 in the bearings 47 on each core shaft 50 supported in saddle 45.
  • the arm 51 is moved into and out of the locked shaft-retaining position shown in Fig. 2 by a toggle linkage which includes a link 55 pivotally connected thereto and to a bell crank 56 pivotally mounted at 57 to the slide 42.
  • the bell crank 56 can be rocked back and forth about its pivot 57 by a fluid pressure cylinder 58 pivotally mounted to the slide 42 and having its piston rod 59 pivotally connected to the bell crank 56.
  • the arm assembly 20 incorporates a drive for directly driving a core shaft 50 mounted in the saddle 45 in all positions of the slide on the arm 22.
  • This drive includes a motor 60 mounted outboard of the end frame 11 by a bracket 61 as shown in Fig. 3. With the motor 60 mounted vertically as shown, its drive shaft 62 leads into a right angled transmission 63 having an output shaft 64 coaxial with the drum 10 and carrying a pulley 65 which drives a double-faced timing belt 66 and is therefore a sprocket, the belt 66 being omitted in Fig. 3.
  • the sprocket 65 rotates counterclockwise so that the belt 66 travels around an idler 70 journalled in the arm 22 to a second idler 71 journalled in the slide 42 and then around a sprocket 72 on a shaft 73 journalled in the slide 42. From the sprocket 72, the belt travels around an idler 74 journalled in the slide 42 to and around a rotary idler 75 mounted for vertical adjustment in the end of the arm 22 for take-up of the belt 66. From the take-up idler 75, the belt travels downwardly to and around an idler 76 journalled in the arm 22 to the drive sprocket 65.
  • the driving force applied to the sprocket 72 is transmitted directly to a core shaft 50 mounted in the saddle 45. More specifically, the sprocket shaft 73 extends into overlapping relation with the end portion of a core shaft 50, and the shaft 73 carries a spur gear 77 which meshes with a spur gear 78 on the adjacent end of the core shaft 50. Preferably, all of these drive parts will be enclosed by a suitable cover and therefore are not seen in Fig. 1.
  • this drive is provided on only one of the arm assemblies 20, and the other arm assembly includes only a slide 42 and the associated mechanism for moving that slide and for releasably mounting the other end of a core shaft in the saddle 45 on that slide 42.
  • a motor 80 is mounted separately from the winder at any convenient location along the secondary ways 30, such preferably as approximately mid-way between the position of the carriages 33 when a winding roll is first deposited thereon from the primary arms and the position of the carriages 33 when the roll is fully wound.
  • the motor 80 is located on the opposite (back) side of the winder from the primary arm drive because the drive of which it is a part requires a different component on the adjacent end of each core shaft 50.
  • the motor 80 is shown in Fig. 5 as mounted on a separate stand 81, although another mounting may be used as described hereinafter, and is omitted from Fig. 4 in the interests of clarity.
  • the motor 80 is connected through a belt or gear drive 82 with a relatively short drive shaft 83 mounted on the motor itself or on the stand 81 and extending at right angles to the length of the winder.
  • the shaft 83 is connected by a universal joint 84 with one end of a compound telescoping shaft 85 having its other end connected through a universal joint 86 with a spindle 88 which is selectively connected through a clutch mechanism 90 with a core shaft 50 supported on the adjacent secondary way carriage 33.
  • the clutch mechanism 90 includes a housing 92 supported by a bracket 93 on the carriage 33.
  • the spindle 88 is mounted by ball bearings 94 in a sleeve 95 supported for rotational and axial movement in the housing 92 by a sleeve bearing 96.
  • a female coupling member 99 is secured to the end thereof adjacent the carriage 33, and this coupling member is internally grooved and proportioned for a splined driving fit with a complementary male coupling member 100 which is provided on the adjacent end of each core shaft 50. It is accordingly necessary that the housing 92 be located to align the spindle 88 with a core shaft 50 supported on the associated carriage 33.
  • Movement of the clutch members 99 and 100 into and out of engaged position is effected and controlled by a fluid pressure cylinder 101 mounted on the bracket 93 and having its piston rod connected by an arm 102 with the spindle 88 through the bearings 94 at the adjacent end of sleeve 95.
  • Fig. 6 shows the clutch members in engaged position, and it will be understood that the cylinder 101 can be operated through a stroke of sufficient length -to pull the female clutch member 99 free of the male clutch member 100, i.e. to the right as viewed in Fig. 6.
  • the first step is to bring the new core C up to a surface speed matching that of the drum 10 while the core is held out of engagement with the drum by appropriate control of the cylinders 44.
  • the operation of cutting and transferring the web is preferably carried out by means of a knife 110 which is stationary during the roll changing operation in accordance with co-owned Tetro U.S. Patent No. 4,422,586 of 1983.
  • each new core 50 C may comprise a plurality of individual core sections mounted end-to-end on the shaft 50, each section for winding one of the split sections of the web W.
  • the core has one or more adhesive strips thereon to which the web adheres when the core is brought into engagement therewith against the drum 10, and as the web is thereby lifted away from the drum, it is drawn into contact with the knife 110 and thereby immediately severed and caused to start to wind on the new core.
  • the core is being driven, at the same surface speed, both through the drive carried in one of the primary arms and by surface engagement with the drum 10 through the web.
  • the control of the primary arm drive motor 60 is shifted from a speed mode to a torque mode to transmit predetermined torque to the core shaft 50 through the gears 77 and 78.
  • This torque is controlled in accordance with the nature of the specific web material being processed to maintain the desired torque while at the same time reflecting that the angular (rpm) speed of the core shaft constantly decreases as required by the increase in diameter of the winding roll. It is during this phase of the operation that the novel belt and gear drive of the core shaft is particularly important in making it possible for the core shaft to move upwardly in the arm assemblies 20 without affecting the drive thereto through gears 77 and 78. At the same time, the nip pressure of the winding roll against the drum is under the constant control of the cylinders 43, which can increase or decrease the gravitational load of the winding roll on the drum to establish and maintain desired nip pressure. When the fully wound roll R has been moved to the broken line position shown in Fig.
  • the winding roll is transferred to the secondary ways by swinging the primary arm assemblies through an arc in the usual manner, through shaft 27, levers 25 and links 23, until the bearings 46 on the core shaft are received on the secondary ways 30. While this movement is taking place, the drive motor 80 is actuated to bring the spindle 88 up to an angular speed slightly greater, preferably one percent, than the angular speed of the core shaft supporting the winding roll.
  • the cylinder 101 is actuated to engage the clutch members 99 and 100. Engagement and disengagement of these clutch members are preferably verified by means such as proximity switches 115 (Fig. 6).
  • the drive by motor 80 is then changed from a speed mode to a torque mode to apply the desired torque drive to the opposite end of the core shaft from its end connected with the drive in one primary arm, and the primary arm motor is switched from torque mode to speed mode.
  • the telescoping shaft 88 moves about its universal joint connections to compensate for the movement of the core shaft and the carriages 33, as illustrated in Fig. 7.
  • This arrangement is simpler than having the motor 80 mounted directly on one of the carriages 33, because it correspondingly reduces the weight carried by that carriage.
  • the linear bearings 34 are important to the operation of the winder by providing practical compensation for that weight load.
  • the motor 80 can be mounted by linear bearings on a stand parallel with the adjacent secondary way for movement with the adjacent carriage, in which case the motor shaft would be connected with the spindle 82 by a 90° gear box.
  • the complete cycle of starting and winding each new roll is initiated by driving the prepared core at a surface speed matching the surface speed of the driving drum until the web has been cut and transferred to the new core.
  • the axially applied separate drive which previously was regulated to match the surface speed of the drum is shifted to a torque mode wherein it will attempt to cause the winding roll to overspeed the drum.
  • This applied torque drive can be maintained in the same differential relation with the surface drive, while the rpm of the core necessarily decreases and the roll builds up, or it can be varied as determined to be appropriate to adjust the degree of hardness in the roll at different thicknesses.
  • the apparatus and method of the invention accordingly make it possible to drive each winding roll by both surface contact and center winding torque from start to finish for each core or set of cores on a common core shaft.
  • the resulting control of roll hardness and quality is definitely superior to what can be accomplished in this respect by the previous technology.
  • the complete cycle for the roll or rolls wound on each core shaft is under the control of a microprocessor 120 programmed in accordance with conventional computer technology as required to establish a predetermined relation between the angular speed of each drive applied to the core shaft and the actual angular speed at which it is driven by the drum. More specifically, the center drives are controlled to apply a torque which would cause the core shaft to rotate faster, by a predetermined percentage, than its actual rotational rate imparted by the drum, and thereby to develop greater tension in the web and to cause it to wind more tightly.
  • the differential between the rotational rates or torsional forces developed by the two drives can and should be varied in accordance with both the nature of the web material itself and the extent to which the degree of hardness (tightness) of a roll of that material should vary throughout the radius of the roll. It is therefore not practical to predict in advance the optimum operating condition for the winder of the invention in winding specific web materials, but in general it can be predicted that the center drive should be controlled to apply a torque to the core shaft which would drive it 3 to 5% faster than its actual speed as determined by the driving drum.
  • the differential between the two drives reflect the continuous decrease in the rotational speed of the core shaft as the radius of the winding roll increases while its surface speed remains constant, and this necessity is taken care of by maintaining the speed differential as a percentage.
  • the torque mode drive should be proportional to the radius of the winding roll, but the percentage differential between the two drives should remain the same. If, however, it is desired that the hardness or tightness decrease as the roll radius increases, the torque proportional to the roll radius should decrease as the roll radius increases. What is claimed is:

Landscapes

  • Replacement Of Web Rolls (AREA)
  • Winding Of Webs (AREA)

Abstract

L'invention concerne un appareil conçu pour le bobinage continu de matériau en bandes sur des mandrins successifs montés sur des broches d'enroulage successives et entraînés par mise en contact de leur surface avec un tambour d'entraînement (10) tournant à une vitesse constante, la broche d'enroulage étant supportée par des bras primaires pendant le démarrage et transférée ensuite sur des supports secondaires (30). Avec l'appareil selon l'invention, l'entraînement de la surface de la bobine est amélioré pendant le cycle complet par l'application d'une force d'entraînement directement sur chaque broche d'enroulage à la fois dans les bras primaires dans lesquels la bobine est démarrée et sur le moyen de support secondaire sur lequel le bobinage s'effectue. Avec un contrôle approprié du dispositif d'entraînement direct de sorte que la broche d'enroulage tourne plus rapidement que le tambour, le couple en résultant permettra à la bande d'être bobinée en conséquence de manière plus serrée.
PCT/US1994/004033 1993-04-13 1994-04-13 Bobineuse continue pour materiaux en bandes WO1994024033A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US4645593A 1993-04-13 1993-04-13
US08/046,455 1993-04-13

Publications (1)

Publication Number Publication Date
WO1994024033A1 true WO1994024033A1 (fr) 1994-10-27

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ID=21943548

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1994/004033 WO1994024033A1 (fr) 1993-04-13 1994-04-13 Bobineuse continue pour materiaux en bandes

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5645245A (en) * 1995-05-25 1997-07-08 Kremar; Djuro Center wind assist driving wheel mechanism
US5664737A (en) * 1995-10-10 1997-09-09 Beloit Technologies, Inc. Centerwind assist for a paper winder system
EP0905069A1 (fr) * 1997-09-17 1999-03-31 Albrecht Bäumer KG Spezialmaschinenfabrik Procédé et dispositif pour enrouler un matériau sous forme de bande
WO2000041959A1 (fr) * 1999-01-12 2000-07-20 Metso Paper, Inc. Procede de changement de charge lineaire sur une enrouleuse
WO2003033383A1 (fr) * 2001-10-15 2003-04-24 Windmöller & Hölscher Kg Dispositif d'enroulement de bandes de matiere sur des arbres d'enroulement
US7168651B2 (en) 2001-08-27 2007-01-30 Metso Paper, Inc. Method and device for power transmission in a reel-up
CN107108141A (zh) * 2014-12-20 2017-08-29 未来股份公司 用于生产卷筒纸的设备和方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1457822A (en) * 1918-12-16 1923-06-05 Albany Perforated Wrapping Pap Machine for and process of producing rolls of paper for towels, toilet paper, etc
US3103321A (en) * 1961-10-27 1963-09-10 Valley Iron Works Corp Paper machine reel
US5064131A (en) * 1990-06-05 1991-11-12 Quebec And Ontario Paper Company Ltd. Paper-making machine reeling operation
US5184787A (en) * 1990-03-08 1993-02-09 J. M. Voith Gmbh Winding machine for winding up a travelling web
US5251835A (en) * 1990-10-26 1993-10-12 Valmet Paper Machinery Inc. Reel-up and a method of reeling

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1457822A (en) * 1918-12-16 1923-06-05 Albany Perforated Wrapping Pap Machine for and process of producing rolls of paper for towels, toilet paper, etc
US3103321A (en) * 1961-10-27 1963-09-10 Valley Iron Works Corp Paper machine reel
US5184787A (en) * 1990-03-08 1993-02-09 J. M. Voith Gmbh Winding machine for winding up a travelling web
US5064131A (en) * 1990-06-05 1991-11-12 Quebec And Ontario Paper Company Ltd. Paper-making machine reeling operation
US5251835A (en) * 1990-10-26 1993-10-12 Valmet Paper Machinery Inc. Reel-up and a method of reeling

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5645245A (en) * 1995-05-25 1997-07-08 Kremar; Djuro Center wind assist driving wheel mechanism
US5664737A (en) * 1995-10-10 1997-09-09 Beloit Technologies, Inc. Centerwind assist for a paper winder system
EP0905069A1 (fr) * 1997-09-17 1999-03-31 Albrecht Bäumer KG Spezialmaschinenfabrik Procédé et dispositif pour enrouler un matériau sous forme de bande
WO2000041959A1 (fr) * 1999-01-12 2000-07-20 Metso Paper, Inc. Procede de changement de charge lineaire sur une enrouleuse
US6880779B1 (en) 1999-01-12 2005-04-19 Metso Paper, Inc. Method for changing linear load on a reel-up
US7168651B2 (en) 2001-08-27 2007-01-30 Metso Paper, Inc. Method and device for power transmission in a reel-up
WO2003033383A1 (fr) * 2001-10-15 2003-04-24 Windmöller & Hölscher Kg Dispositif d'enroulement de bandes de matiere sur des arbres d'enroulement
CN107108141A (zh) * 2014-12-20 2017-08-29 未来股份公司 用于生产卷筒纸的设备和方法
CN107108141B (zh) * 2014-12-20 2019-03-22 未来股份公司 用于生产卷筒纸的设备和方法

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