KR20010114223A - Continuous Winder And Method Of Winding Slit Rolls Of Large Diameter On Small Diameter Cores - Google Patents

Abstract

The drum-type continuous winding machine for winding the slit sections of the web on the individual cores on the core shaft 20 has a core shaft having a core coupled with the moving web on the main winding drum 22 for web cutting and new core conveyance. It comprises a pair of primary support arms 24, 25 with radial slots 28 which receive the core shaft from a fixed cam plate 29 which permits movement. Since driven nip rolls 30 supported on arms 24 and 25 engage the core on the core shaft during valve conveyance, the core shaft is interposed between the nip roll 30 and the primary drum 22 so that a critical speed limit is achieved. To provide a return of the web on the core without. The secondary arms 50, 51 which receive the core shaft support the secondary winding drums 52 in the guide tracks 55 which are moved radially to engage the rolls to be wound.

Description

Continuous Winder And Method Of Winding Slit Rolls Of Large Diameter On Small Diameter Cores}

In winding a roll of large diameter, shippable, high quality web material, including film, nonwoven material, paper, paperboard material, and composite material, onto the core, slitting and winding operations are web forming and converting. It is appropriate to arrange in series with the process. This continuous winding device reduces production costs and waste, and allows for quick identification of process control problems. Continuous winding smoothly handles line rolls, handoff of finished rolls, high speed conveyance of individual slit webs onto corresponding core segments, and initiation of winding processes on new core segments. Requires that.

Continuous winding of large diameter slit rolls on a wide machine presents significant problems. A particular problem arises from the fact that long small diameter core shafts are bent by their own weight and exhibit critical speed limitations during acceleration prior to web conveyance. This critical speed limit is the main cause of deflection of the core shaft causing harmonious and dynamic imbalance. These critical velocity conditions generate vibrations that interfere with web reflections and can result in inaccurate or incomplete start and initiation where the roll does not have sufficient hardness. In addition, deflection of the shaft can cause roll quality problems when winding the slit roll to a large diameter. The problems described above include, for example, a shaft for supporting a core of 0.076 m (3 in) over a wide width that may exceed 5.08 m (200 in) and a roll diameter that may exceed 1.524 m (60 in). This is particularly important when the core shaft is very compact, such as a shaft for winding up.

Large diameter slit rolls are wound with wide machine width in continuous operation, core shaft deflection and critical speed conditions are controlled, and the set of rolls formed is controlled in density throughout the entire winding process. Is required.

The present invention relates, in particular, to a continuous drum-shaped surface winder and a winding method applied for winding a slit web material onto individual core segments supported on a common core shaft, and more particularly to a wide relatively small diameter core. A method and a winder applied to wind the slit web into discrete rolls of significant diameter of at least 1.524 m (60 in) on the shaft.

1 is a partially broken perspective view of a continuous winding machine according to the present invention.

FIG. 2 is a partially broken end view of the winder of FIG. 1 as seen from the off running side, with some parts moved relative to the position of FIG. 1 for illustration; FIG.

3 is a side view of the winder of FIG.

4 to 9 are views sequentially showing the operation and method of the winder,

4 shows a new core shaft in a position where the knife sugar roll changeover position is indicated and the primary nip roll is moved to the core acceleration position.

Figure 5 moves the core against the drum and moves the accelerating core to the -25 ° position where it contacts the web on the primary drum such that the primary arm is rotated to the -20 ° position to spray the adhesive onto the web and spring loaded A diagram showing a primary arm ready to be moved to a roll changeover position that operates to convey a knife onto a new core.

6 shows a take-up roll that is stopped by the associated support drum while the knife shoe is in the stop position after being transferred to the braking position on the secondary arm.

FIG. 7 shows that the latch assembly on the secondary arm is retracted to raise the take-up roll by the lift table relative to the shaft puller and recording position, with the support arm pointing in the counterclockwise direction of FIG. 4 relative to the conveying position, A diagram showing the primary arm after slowly directed to the + 30 ° position, stopped at this position by sensing proximity switching.

FIG. 8 shows that the rolls continue to be stacked to a predetermined diameter under equilibrium, the primary nip roll is released, and the support drum on the support arm has a predetermined hardness while the primary drum is directed back to the shaft loading position shown in FIG. A support arm returned from the primary arm to the conveying position ready to receive the core shaft, increasing pressure for the sake of brevity.

9 shows the primary arm in a -30 ° core shaft loading position positioned on the cam shaft surface when the lamination roll is supported between the drum and the driven support roll.

The present invention provides a continuous surface drum winder and method for winding a slit web into a large diameter roll on a small diameter core on an individual core segment of highway wide web material. In particular, the winder and the winding method provide for conveying the slit web at line speed on a core supported on an elongated core shaft as described above.

The first or primary driven drum has a driven primary nip roll rotatably mounted on a support arm. The arm is pivotally mounted on a primary arm that rotates about or with the axis of the drum. The primary arm also has other means for supporting the slots, recesses or ends of the core shaft and leading to the initial winding stage, wherein the core shaft is interposed between the driven primary nip roll and the driven primary drum, thereby conveying the web. And to prevent resonance and sagging of the core shaft, which may cause critical speed limitations and wrinkles at startup.

Buildup of roll segments, ie individual rolls, is initiated on the core shaft while the core shaft is supported on the primary arm. The geometry of the arm, primary or main drum and nip roll ensures that the core shaft and core are straight or parallel to the surface of the primary drum and that a good starting point is obtained by proper loading by the primary nip roll. In this way, the core shaft is formed to be supported during web conveyance and during initial roll lamination.

Also, during the roll lamination step, the primary arm is programmed to move from the roll switching position to the roll conveying position where the core shaft and the rolls thereon are conveyed to a pair of support arms, referred to herein as secondary support arms. The secondary arm is movable on the secondary arm and associated with the support arm so as to supportably engage with the lamination roll while the roll is in progress each time it engages the main winding drum. In addition, the primary nip roll is combined with the take-up roll so that the winding of the roll continues in a form in which two drum take-ups on which both drums are driven are driven at a predetermined speed or torque mode and are nipped by the driven rider roll. Continue. The primary nip roll is released after supplying sufficient nip loading to the supporting drum by the weight of the winding roll.

The change in roll diameter is always known by reading the inclined transducer integrated into the pivot arm for the primary nip roll and by the position of the secondary support drum on the secondary arm. The loading of the primary nip roll and the loading of the secondary support arms can be controlled by the roll diameter as well as weighted to provide roll density and deflection control.

When transporting the primary arm to the delivery position of the secondary or support arm, the slow movement of the take-up roll set causes little change in the web length and therefore little change in the web tension, and the roll set causes the take-up roll sag. Allows winding of the entire roll set diameter while partially retaining on the main drum to assist in minimizing.

At the start of winding after web conveyance, the winding set is interposed between the main drum and the driven primary nip roll, and the core shaft is held in a slot formed in the primary arm. After the complete set of rolls has been loaded, the secondary arm returns to the starting position so that the primary arm is partially wound up with the secondary arm while maintaining contact with the driven nip roll through a total rotation of about 60 °. Allow to transport the set. The winding rolls are stacked until initiating contact with the balanced secondary support drum driven at line speed. This three roll or three point engagement state is maintained through the main portion of the stack of rolls of roll slots while the secondary arm and the support drum cooperate with the primary drum to support the weight of the take-up roll.

Once a sufficient set of rolls is achieved where the rider roll is no longer needed, the primary arm and associated nip rolls are fully retracted to place the new shaft into the core, with the ends of the shaft held in the slots of the primary arm. It is supported on the surface of the fixed cam. The conveying shoe-type web cutting system is pivotally mounted on an axis common to the axis of the main drum, is rotated under an on-running web, and is located upstream of the nip and It is located between the new core and the lamination roll on the core shaft. The primary nip roll drive is in speed mode to accelerate the new core and core shaft. The primary arm is then about 5 ° such that the core is moved from the cam surface into the arm slot at which the core is at line speed by driving engagement with the web on the drum just before (upstream) the point where the web is lifted from the drum by the conveying shoe. Is rotated.

An adhesive spray applicator is mounted between the primary arms and has a separate spray head that is operated upstream of the core shaft to spray onto the web surface with adhesive. The primary arm is then rotated about 5 ° further to activate the adhesive spray. At the same time a precision grinding cutting knife emerges from the shoe into the slit web and secures the web. The momentum of the web tension and lamination rolls pulls the web through the knife, thus creating a complete straight cut while conveying the individual web onto a new core by the adhesive. At the same time, the adhesive on the cutting tail causes the tail to adhere to the surface of each finished roll.

The secondary arm then points to a complete winding set of rolls to the braking position where the braking torque is regeneratively applied by the secondary drum to be spaced from the primary drum to stop the roll rotation. Next, the winding roll set is moved to the dropping position. At the same time, the shoe-shaped web cutting system is pivoted by its arm to the lowered stop position, and the new core set with the web is held on the primary arm and is continuously wound and loaded onto the primary drum by the driven primary arm nip roll. do. In this interposed position, the core shaft remains substantially sag-free and the rigid winding of the individual slit webs on each core, with the hardness controlled by the torque and pressure supplied by the primary nip roll. Provide an initiation. Natural deflection of the core is excluded or controlled, otherwise wrinkling of the web at the initiation can occur and create critical speed problems.

The apparatus and method of the present invention are contemplated to provide unique features and advantages to this kind of winder. These features and advantages include the exclusion or control of critical speed problems and the exclusion or control of related core shaft deflection problems for the continuous winding of wide and / or large slit rolls.

The interposition of the new core shaft and the next roll transition between the main driven drum and the driven nip roll excludes the natural speed that causes creases at the critical speed and winding start.

The conveying shoe system with a pop-up knife ensures straight and clean conveying regardless of web speed.

The driven primary arm nip roll ensures a good hard start and a suitable hard profile by means of programmed nip and programmed torque control as a function of the diameter of the take-up roll via a position sensor on the pivot of the driven primary nip roll. .

Slow controlled movement of the winding roll set from the vertical centerline through the main drum to the winding position of about -20 ° to + 30 ° provides excellent roll support and changes the web length hardly and thus reduces web tension deflection. Rarely does not occur and allows winding to the diameter of the entire roll set while being supported on the main or primary drum to assist in minimizing the deflection of the core shaft and the winding roll.

The driven support drum supports the winding roll set in the winding position to further assist in minimizing the deflection of the winding roll.

The driven support drum ensures that the lamination roll has a suitable density profile by programming the nip pressure and the torque control of the follower. This system is similar to the known two-drum winding system widely used in the art for stop / start slitting and rewinding operations.

A driven support drum is also used to support and stop the winding set after conveying by providing regenerative braking.

Primary support arms with nip rolls provide safety, ensure that the roll roll set is contained within the working surface of the two winding drums, and the lateral movement of the roll roll set until it is transferred to the secondary arm To prevent.

The shaft sensing device is integrated into the secondary support arm to prevent excessive loading of the core shaft by excessive loading of the supporting drum.

The secondary arm is used for safety to ensure that the set of winding rolls is received inside the two winding drums. The secondary arm prevents lateral movement of the winding roll set and is also used to eject the finished roll set.

The position sensing device is integrated with the secondary arm pivot to balance the arm assembly through the support arm cylinder to prevent excessive loading of the core shaft by the support arm, which may cause shaft deflection.

Therefore, an important object of the present invention is a continuous two-drum surface type winding, in which the core shaft is supported throughout the entire winding process leading to web conveyance, initiation and completion in a manner that eliminates bending and deflection and reduces critical speed problems. It is to provide a odor and winding method.

It is a further object of the present invention to provide a two-drum type winder, in which the layers on the roll are operable to provide three-point winding control through the main part of the winding of the slit web to individual core segments on the core shaft.

Another object of the present invention is that, as described above, the secondary winding drum is controlled on the second arm in such a way as to support the weight of the lamination roll on the core shaft so that the core shaft can remain relatively straight through the entire winding process. It is to provide a winder.

Other objects and advantages of the invention will be apparent from the following detailed description and the accompanying drawings and claims.

With reference to the drawings that show suitable embodiments of the present invention, a continuous winder, specifically designed and configured for winding the slit web on small cores in individual rolls of large diameter, is generally indicated by reference numeral 10. The winder 10 comprises an apparatus supported on a frame 12 having a second side frame 14 spaced apart from the first side frame 13. A rectangular tubular cross member 15 extends between the frames 13, 14 adjacent to the on running side of the winder. The process progress direction is shown by the arrow 17 of FIG.

The winder is wound around a core shaft having a diameter of 0.076 m (3 inches) or less and a width of 5.08 m (200 inches) or more. The diameter of the individual roll segments wound on the core shaft 20 can exceed 60 inches.

The winder 10 may be used in a process line which may have an upstream slitter and may have a spreader similar to a spreader roll disposed at the inlet end of the winder as shown in FIGS. 1 and 3. It is intended to be. The apparatus may include a conventional process tension separator and control roll to guide the slit web to the winder for winding onto a core (not shown) supported on the core shaft 20. A typical core shaft 20 used in the present invention is shown in FIG. Also, as is known in the art, core shaft removal and loading mechanisms can be used.

The first or primary winding drum is rotatably mounted between the side frames 13, 14 and is driven by a floor mounted electric drive, not shown. A pair of primary arms 24, 25 are pivotally mounted on the side frames around a pivot axis concentric with the axis of rotation of the drum 22 and are disposed at each transverse end of the drum.

The primary arms are each formed with radially extending core shaft receiving recesses or slots 28 which receive the ends of the core shaft 20 during the initial winding stage. Using the vertical line of the radial line through the centerline of the slot 28 as the neutral position, the arms 24, 25 are moved from the -30 ° position as shown in FIG. 4 to the +30 degree position as shown in FIG. It is rotatable by the cylinder 260 around the axis of the main winding drum 22.

The fixed cam plate 29 is provided on each of the side frame members 13 and 14. Each cam plate 29 has a front facing inclined surface 31 that is inclined at an angle parallel to the slot 28 about the -25 ° position of the arm, and the upper horizontal core shaft support cam surface 32. In addition, at least a portion of the cam surface is exposed when the primary arm 22 is rotated to about -30 degrees.

The primary arms 24, 25 support the driven primary arm nip rolls 30 in turn. The nip roll 30 is supported on a nip roll support arm 33 that is pivoted at pivot point 35 on the primary arm 24. The pivot point 35 includes a shaft angle encoder such that the diameter of the lamination roll on the drum 22 can be determined. The primary nip roll is coated with silicone rubber or plasma discharge coated. The positions of the arm 33 and the supported primary nip roll 30 are controlled such that one is on both sides of the winder by the actuator or cylinder 36. The cylinder 36 is nip rolled from the raised position as shown in FIGS. 2 and 3 to the fully lowered position, for example engaging the core on the core shaft 20 as shown in FIGS. 1 and 6. 30 can be moved. The roll 30 is driven by the drive motor 37 and the belt 38.

3 and 5, the web conveyance and cutting shoe 40 extends transversely adjacent the outer surface of the drum 22 between the frames 13, 14, and the drum ( Is rotated about an axis common to the axis 22). The shoe 40 is movable on the support arm 41 between the lowered or retracted position as shown in FIG. 3 and the rotated operating position as shown in FIGS. 1, 4 and 5, and the web And a web cutting knife 42, which can extend over the shoe and the path of the web across the drum 22 to cut off.

The shoe 40 provides an upper curved surface that is designed to operate with the web extending over the surface. The arm 41 is connected to the drive motor 39 shown in FIG. 1 by a common shaft, whereby the shoe 40 is in the lowered non-operating position shown schematically in FIG. 3, and FIGS. 4 and 5. It may be arranged between elevated operating positions comprising a cutting knife as shown in FIG.

Spray bar 44 is fixedly mounted on cross member 45 and supports a plurality of adjustable adhesive spray nozzles 46. The spray nozzle is connected to the adhesive source, and basically only the web segments can be aligned to be sprayed by the adhesive to be returned to the new core.

A pair of support arms 50, 51, referred to herein as secondary arms, is pivotally mounted to the off running end of the side frames 13, 14. Encoder 50A is integrated with the pivot support for reading each position of the support arm.

Secondary arms 50 and 51 have a number of functions. Firstly, the primary arm provides a means by which the core shaft 20 is supported during the main stage of winding. The arms 50, 51 also provide support for the driven support drum, referred to herein as the secondary winding drum 52. The drum 52 is mounted on secondary support plates 53, 54 that are vertically movable on pairs of guide tracks 55 supported on the inward surfaces of each rotatable arm 50, 51. The secondary plates 53, 54 effectively form a movable carriage coupled by the cross frame member 71 and move on parallel tracks 55 (FIG. 3), whereby the secondary arms 52 For example, it may be moved vertically between the lowered position of FIGS. 1 and 2, and the intermediate position and the raised position shown in FIGS. 8 and 9, respectively. The movement and position of the support drum 52 extends between the arms 50, 51 and is controlled by a pair of cylinders 58, 59 adjacent at the U-link clevis by the secondary roll support plates 53, 540. The secondary support plates 53 and 54 are mutually coupled to the rotationally movable pinion gear 56A together with the rack and pinion mechanisms 56 and 56A and the racks 56 associated with the respective plates 53 and 54. It is integrally moved by the connecting rotatable shaft 61, thereby ensuring uniform movement of the drum 52 by excitation cylinders 58, 59.

The rotational movement of the secondary arm itself is pivotally fixed to one of the side frames 13, 14 with the actuator extending to a U-link 66 attached to one of the arms 50, 51, respectively. Controlled by cylinders 63 and 64. The secondary arm is movable between the two extreme positions by the cylinders 63 and 64, which are shown in FIGS. 7 and 8, respectively.

The motor 70 and the gear reducer 72 drive the driven support drum 520 through the timing belt drive 74 clearly shown in Figures 2 and 3. The motor 70 has been completed, which will be described in detail below. In order to stop the rotation of the roll set, regenerative braking is possible The motor 70 and the reducer 72 are part of a secondary frame structure with secondary support rolls 52 for the cross frame member 71 for vertical movement. ) Is mounted.

The upper and upstream facing edges of the secondary arms 50, 51 have a rear facing notch 80 assigned to receive the ends of the core shaft 20. The cylinder 82 actuates a notch closing slide 84 mounted on the arms 50, 51, whereby the core shaft can be fixed in place in the receiving notch 80, or the core shaft is removed from the notch. Can be removed.

The operation of the continuous winder 10 will be well understood with reference to FIGS. 4 to 9. First, referring to FIG. 4, a complete winding roll set 100 is attached to a slit-in supply web 102, supported on a secondary arm between the main drum 22 and the supporting drum 52, and a roll set Since the substantial weight of 100 is balanced by the hydraulic pressure in the cylinder 63, the core shaft 20 is kept straight in the neutral position. The end 20A of the core shaft 20 is captured in the notch 80 by the closing plate 84.

The new core shaft 20 is located on the fixed upper cam surface 32 of the cam plate 29, and the pre-shrinked nip roll 30 is lowered to engage the core shaft and the new core to allow the placement of the core shaft. Is placed on the core shaft ready to accelerate. The knife conveying shoe 40 is rotated from the lowered stop position to the upper operating position of the lower part of the on-learning web 102, raising the on-learning web to the upper part of the upper surface, and then the main drum and roll set 100. Down into the nip 105 formed therebetween.

Referring to Fig. 5, at the start of the roll switching procedure, the primary arm is rotated + 5 ° from the -30 ° position shown in Fig. 4 to the -25 ° position shown in Fig. 5. In this position, the slot 28 is aligned with the front cam surface 31, with the core shaft 20 with the core on top dropping to the bottom of the slot 28, where the core is of the on running web 102. It is in contact with the top surface of the individual sections. In this position, the nip roll and core shaft rotate at substantially web speed.

The web cutting and conveying process is initiated as the secondary arm moves from -25 ° to the -20 ° position in FIG. 5. The adhesive is sprayed through the spaced nozzles 46 to the exposed top surface of the running web 102, while the knife 42 is triggered in the path of the overlapping web from the shoe 40. The inertial motion of the slit web causes the web sections to be cut on the knife, and individual web strips are bonded to each core on the core shaft 20 to initiate the winding process. The adhesive remaining on the web, ie the upper surface of the web tail, serves to glue or fix the web tail to the outer circumference of the roll of the roll set 100.

After cutting and conveying is completed, the completed roll set 100 can be moved to the position shown in FIG. 6 by the cylinders 63 and 64, and the rotation of the roll set is carried out by the motor 70 and the supporting drum 52. It is stopped by regenerative braking through In this position, the load of the roll set is supported by hydraulic cylinders 58 and 59.

At this point, at the beginning of winding on a new set of cores, the core shaft has its length on the outer surface of the primary drum 22 with the core shaft end captured in the arm slot 28 of the primary arm. It is important to note that while the nip is supported along, the nip is loaded by the driven primary nip roll 30. When the primary nip roll 30 is lowered, the nip roll is driven in a speed mode that matches or nearly matches the speed of the new core to the line speed. The new core shaft is interposed between the rolls 30 and 22, is retained in the slot 28, and is maintained in a straight axial position, thus eliminating the critical speed problem. The roll 30 limits the radial movement and the slot 28 limits the axial movement of the core shaft. After the web is cut, the primary nip roll 30 switches from web speed to speed limit adjustment torque (SLAT) mode and continues to be wound. The nip relief system is actuated by controlling the pressure in the cylinder 36 such that the nip between the core and the drum 22 as a function of the roll diameter measured by the shaft angle encoder at the pivot point 35 of the nip roll arm 33. Load it.

In addition, after the conveyance is completed, after the movement of the secondary arm toward the vertical position shown in FIG. 6, the knife cutting and web conveying shoe assembly 40 is about 180 to 185 ° by the motor and gear boxes 23 and 23A. It can be rotated clockwise on the support arm to stop in position.

The new roll set 100A continues to be stacked between the nip roll 30 and the primary drum 22, and the core shaft moves radially in the slot 28 by the stack diameter of the roll set, if necessary. This state is shown in FIG. At this time, after the roll set 100 is regeneratively braked to the stop by the supporting drum 52, the secondary arms 50 and 51 can be moved to the fully clockwise dropping position as shown in FIG. The core retainer notch 80 is opened by the contraction of the plate 84. The lift table raises the take-up roll to a free position for the secondary arm to pivot to the primary and secondary conveying positions 110 as schematically shown in the position shown in FIG. The core shaft can be pulled and recorded, and the recorded shaft can be returned to be ready for placement in the slot 28 and the primary arm 24 of the cam 29 by core handling devices known in the art. Can be.

In addition, after regenerative braking by the supporting drum 52, the ratio of the supporting drum pressure can be added to the supporting drum to prevent slipping during braking, and upon dropping of the completed roll set 100, the secondary supporting drum ( The carriage subassembly for 52) is fully lowered to the lowered position by the relative motion of the plates 50, 51 on the track 55 of the secondary arm. The complete lowered position is shown in FIG.

During the continuous winding of roll set 100A, primary arms 24, 25 continue to rotate and slowly move the winding set to + 30 ° from the vertical position as described above. After the primary arm is positioned at the 30 ° position, as shown in FIGS. 7 and 8, the winding roll 100A reaches a specific diameter of 0.4572 m (18 in), and the secondary or support arm is the primary drum. Slowly moving backwards toward and stopped by proximity switch 120 on the end of the arm at notch 80. During this time, the secondary support arm 52 is positioned in the raised position in the velocity mode. Proximity switch 120 indicates that core shaft 20 is located in the notch, which is shown in FIG. At this time, the latch plate 84 is actuated by the cylinder 80 to lock and secure the core shaft in the notch 80 of the secondary arm. As shown in FIG. 8, a winding process is performed in which a laminated roll set is wound on a secondary drum and the bonding by the nip roll 30 is maintained. The upper position of the support drum 52 reduces the upward pressure in the cylinder 59 to the equilibrium pressure applied by the cylinder 59 to zero the load on the roll 100A or to increase the primary nip roll 20 load. It can be ignored to dominate.

In a suitable embodiment in which a 15.24 m (60 in) diameter roll 100 is formed, the initial engagement of the secondary arms as shown in FIG. 8 and described above can occur at a minimum of about 0.4572 m (18 in) diameter and the next winding This is continued by continuing to drive the secondary drum 52 in the speed mode in which the nip roll 30 is engaged. This may continue for example at a predetermined intermediate position having a diameter of 0.6096 to 0.762 m (24 to 30 inches). At this time, the nip roll 30 is retracted while winding continues as shown in FIG. 9, the support drum 52 is switched from the speed control mode to the SLAT mode, and from the equilibrium pressure, the support drum is moved to the cylinders 58 and 59. Is converted to the programmed support pressure as applied.

After the primary arm nip roll 30 is fully raised and the drive is stopped, the primary arm can be rotated to return to the loading position shown in FIG. 9, which is -30 °.

The nip of the programmed support pressure by the secondary arm 52 can be adjusted to control the roll hardness. The other proximity switch 130 on the support arms 50, 51 applies excessive support pressure and senses whether to raise the winding set. This may be a proximity switch also disposed within notch 80. When the proximity switch senses the core shaft indicative of upward movement of the core shaft in the notch, the support drum pressure can be gradually reduced until the core shaft and the roll are lowered from the proximity switch. Winding continues until the maximum selection diameter as shown in FIG. 9 where roll switching is ready is achieved.

The width of the slots 28 formed radially within the arms 24, 25 is formed in such a way that they are forced fit with one of the support surfaces adjacent the ends of the core shaft 20. The core shaft 20 is shown in elevation at the top of FIG. 2, with each end of the core shaft having a pair of support surfaces 20a, 20b at each end. The slot 28 is tightly fitted with the core shaft surface 20a and limits the lateral movement of the core shaft. The alignment of the slots in the arm is similar to the circular motion of the stack on the roll 30 in the starting position as shown in FIG. Thus, at certain times, the ends of the core shaft 20 are limited in lateral motion by the walls of the slots 28.

The lamination diameter of the roll segment as formed by the individual cores is achieved by the radial outward movement of the core shaft in the slot 28 with respect to the force of the lamination on the roll 30.

The primary arms 24, 25 are received in the core shaft inside the two pairs of support surfaces 20a, and the transfer of the secondary arms in the slots 80 is carried in the cores in the slots 80 at the outer support surfaces 20b. By receiving the shaft.

The transfer of the stack roll 100A from the primary arm to the secondary arm achieved as shown in FIGS. 7 and 8 occurs when the stack roll has a sufficient diameter, so that the core shaft is released from the slot 28. Can be. This is a function of the design of the machine, but typically can be a function of a diameter of 0.4572 m (18 inches) or more. After dropping the first roll set 100, the secondary arms 50, 51 are moved to the receiving position as shown in FIGS. 7 and 8, coupling the core shaft to the adjacent support surface 20b, and the sensor Stop the rotation of the secondary arms 50, 51 by means of 120 and equilibrate pressure programmed primary as the position of the secondary arms 51, 52 by the sensors 50A provided in the cylinders 63, 64; The conveyance is made smooth by closing the slot 80 by the cylinder 82 and the slot retainer 84 which are moved in the non-interfering adjacent relationship with respect to the arm.

Working order

1. While the winding set is between the driven main winding drum 22 and the driven supporting drum 52 and the driven primary arm nip roll 30 is in the retracted state, the new core shaft 20 is in the vertical centerline position. Are automatically loaded onto the cam 32 around the slot 28 in the primary arm at -30 °.

2. At the start of the roll changeover process, the knife shoe 40 is directed around the drum at the bottom of the web and stopped at the cut position on the other side of the core.

3. The driven primary arm nip roll 30 is lowered to the core shaft and is in speed mode to accelerate the new core close to the line speed. See FIG. 4.

4. Adhesive spray applicator nozzles 46 are located proximate each web 102.

5. The primary arms 22, 25 are moved from 5 ° to -25 ° position from the vertical centerline, and the core shaft 20 is lowered from the cam 28 onto the web 102 and the drum 22 so that the natural Straightens deflection.

6. When the primary arm is moved to the 20 ° position, the adhesive is sprayed onto the web and attaches the tail on the slit winding roll 100. See FIG. 5.

7. The primary arm stops at the -20 ° position, allowing the finely ground cutting knife to come out of the shoe 40 and secures the web. The momentum of the web tension and winding rolls pulls the web through the knife and causes a complete straight conveyance to the new core slightly folded.

8. The driven primary arm nip roll 30 switches from the speed mode to the speed limit adjustment torque (SLAT) mode.

9. The nip reduction system is activated and provides nip loading as a function of roll diameter from the angular encoder at the pivot point of the arm 33 which senses the position of the nip roll.

10. The support arms 50, 51 direct the winding set 100 of the slit roll from the drum 22 to the braking position. See FIG. 6.

11. The knife shoe 40 is rotated around the drum, the knife is retracted and the shoe is stopped at the bottom of the drum.

12. The driven support drum 52 is kept pressed against the roll set and regenerated to stop the winding set. The proportion of support drum pressure is added to the support drum to prevent slippage.

13. When the support drum 52 reaches zero speed, the support drums 50 and 51 are moved to the dropping position. See FIG. 7. In this position, the weight of the winding rolls and the shrinkage of the drum cause the winding rolls to sag. The degree of deflection is limited by the upper edges of the roll set that come into contact with each other. When the roll set is supported by the lift table, the core shaft occupies a straight position.

14. The table 110 ascends and automatically stops until it supports the winding set.

15. The support arm latch 84 is retracted.

16. The winding set of rolls is raised to the core shaft retracted position.

17. The primary arms 24, 25 slowly move the winding set to + 30 ° from the vertical position.

18. After the primary arm is positioned at the + 30 ° position, and after the winding set reaches a minimum diameter of 0.4572 m (18 in), the support arms 50, 51 rotate again towards the drum 22, It stops when it senses that the proximity switch on the arm 50 has approached the new winding shaft. See FIG. 8. Switch 140 is shown in FIG. 4.

19. Support arm latch 84 extends and accesses an interlocking portion that allows the support arm to retract under equilibrium pressure.

20. The support drum 50 is raised when the support arm pivots toward the drum 22 in speed mode under the elevated pressure, and is converted to an equilibrium pressure of 0.6096 m (24 in), the winding set being wound on the equilibrium support drum. do.

21. When the roll is wound, the position sensor 50A on the support arm pivot point is used to program the equilibrium pressure of the support arm by the cylinders 58, 59 to prevent excessive bending of the core shaft during the winding operation.

22. When the winding set reaches a diameter of 0.6096 to 0.762 m (24 to 30 in), the driven primary arm nip roll 30 is raised and the support drum 52 is switched from the equilibrium pressure to the programmed support pressure. The drive switches from speed mode to SLAT mode.

23. After the primary arm nip roll 30 is fully raised and the drive is stopped, the primary arms 24, 25 are rotated back to the stowed position. See FIG. 9.

24. The nip of the programmed bark pressure is adjusted to control the roll hardness. Proximity switch 130 on the support arm senses whether the support drum supplies excessive support pressure and raises the winding set. When the switch senses the core shaft, the support drum pressure is gradually reduced until the roll and core shaft are lowered from the switch.

25. After step 15, the shaft puller is automatically engaged with the core shaft and extracted at inflation pressure.

26. The shaft 20 is then retracted from the winding set 100 by an automatic shaft puller.

27. The table 110 lowers the roll onto a roll platform (not shown) and is inclined to eject the roll onto the platform.

28. A new cutting core is loaded on the table manually or automatically.

29. After the table detects that a new core has been loaded, the table is raised to the shaft insertion position.

30. The shaft is inserted automatically and expands automatically.

31. Next, when the overhead hoist picks up the shaft and the primary arm is rotated back to the loading position, the shaft is automatically loaded again on the cam around the slot 28 in the primary arm.

32. After reaching the programmed full length or diameter on the take-up roll, the take-up is ready for the next automatic roll changeover.

Although the method described herein and the form of apparatus for carrying out the method constitute an effective and suitable embodiment of the present invention, the present invention is not limited to the method and apparatus form, but is defined in the appended claims. It will be appreciated that changes may be made without departing from the mind.

Claims (18)

A method of continuously winding a slit web with a plurality of correspondingly large diameter rolls on individual cores supported on a common elongated shaft, comprising conveying the slit web on a core from a fully wound roll at a line speed. , (a) arranging a core shaft having a core in surface contact with the slit web supported on a winding drum and bringing the core shaft and the core thereon at a line speed; (b) applying a driven nip roll to the core at a line speed while simultaneously limiting the end of the core shaft with respect to the lateral movement of a radial line from the axis of rotation of the drum through the core shaft; (c) cutting the slit web at a position downstream of the contact area of the web and the core by the drum while limiting the core shaft as above, while simultaneously simultaneously cutting the web to a corresponding core on the core shaft. Returning, and (d) continuing winding the frying web on the core while laterally limiting the core shaft by the driven nip roll against core shaft deflection that may cause a critical speed limit. How to wind up continuously. The method of claim 1, wherein the core shaft and the core thereon is at a web line speed by the driven nip roll prior to contacting the core with the slit web on the winding drum. 2. The method of claim 1, wherein the limiting step comprises the step of the core in an elongated slot providing a path through which the core shaft radially extending and having a core loaded thereon moves in contact with the slit roll on the drum. Securing the core shaft at the end with respect to the lateral movement by capturing the end. 2. The winding machine of claim 1 wherein the winder has a movable secondary support drum that is movable to contact the rolls stacked on the core in a spaced relationship relative to the winding drums and maintains contact between the stacking rolls and the driven nip rolls. And contacting said secondary drum with said roll while said roll obtains a predetermined diameter. 5. The method of claim 4, wherein the limiting of the core shaft to lateral movement is terminated after joining the secondary drum and the lamination roll. The method of claim 4, wherein the nip roll is in contact with the lamination roll until at least the secondary drum is in contact with the lamination roll. The method of claim 1, wherein the nip roll is driven in speed mode prior to the cutting step and is switched to speed limit adjustment torque mode after conveying the web to a core on the core shaft. 7. The method of claim 6, wherein the pressure of the nip rolls on the lamination roll is increased as the diameter of the rolls increases. The method of claim 1, wherein an adhesive is sprayed onto the inner surface of the web leading to the complete winding roll immediately prior to the cutting step for simultaneously gluing the tail segments of the cutting web onto each of the winding rolls. Providing an adhesive surface for attaching the individual webs to the core. 5. The secondary support drum of claim 4, wherein the secondary support drum is mounted on a secondary support arm that operates independently of the primary drum and the nip roll, the secondary support arm receiving a core shaft with a partial winding roll thereon. A core shaft support for said secondary drum, said secondary drum being in contact with said partial winding roll when said core shaft is supported on a support arm having a partial winding roll simultaneously supported between said primary and secondary drums; Moveable on the primary arm, the method further comprising equilibrating the weight of the roll by the secondary arm. 11. The method of claim 10, wherein said step of equilibrating comprises varying the balance force of said secondary drum and measuring the angle of said secondary arm to prevent excessive bending of said core shaft. 5. The method of claim 4, further comprising applying a braking force to the take-up roll through the secondary drum to stop rotation after the conveying step. In a drum type winder for continuously winding a slit web with a large diameter roll on an individual core supported on a core shaft, A frame, a main winding drum positioned on the frame, a pair of arms mounted on the frame to rotate about an axis common to the axis of the main winding drum, and three for supporting a plurality of cores thereon. An elongated core shaft and a lamination roll supported on the arm and engageable with the core on the core shaft, The arm has a radially extending slot through which the end of the core shaft extends through the core when the core is received in the slot, the slot being in the radial direction of the drum along the slot and the rotation of the core shaft on the arm. Forming a wall that limits the lateral movement of the core shaft end while allowing movement of the core shaft of the slot, wherein the slot is simultaneously coupled by the lamination roll to convey the web onto the core on the core shaft. Has a radial length for moving the core shaft radially to position the upper core to engage a web supported on the surface of the drum while maintaining the core shaft in a straight position for A drum type winder opened at each outer diameter end for receiving. 14. The apparatus of claim 13, further comprising a cam located on the frame, each adjacent to each of the arms, wherein each cam is configured to support the core shaft before the core shaft enters the slot open end. A drum-type winder forming a radially outwardly disposed surface of the arm slot open end. 14. The apparatus of claim 13, further comprising: a pair of secondary arms rotatably mounted on the frame, secondary support drums mounted between the secondary arms, and the radial movement of the secondary drums. Further comprising a radially extending guideway located on the secondary arm supporting the secondary support drum, The secondary support drum is movable by engagement of the stacking roll on the core shaft with the secondary arm at a position spaced apart from the joining position of the stacking roll and the main support drum, thereby stacking the stack between the drums. Drum type winder for placing rolls. 16. The method of claim 15, further comprising a cylinder located on the secondary support drum that provides lift force to the secondary support drum, wherein the weight of the lamination roll on the core shaft is to maintain the core shaft in a straight line. At least a substantial portion of the drum type winder being supported by the cylinder to the secondary supporting drum. The method of claim 15, wherein the secondary arm is formed with a core shaft receiving notch on its end, and after the lamination roll has been laminated to the point where the core shaft reaches the open end of the slot of the primary arm. The core shaft end is received in the notch, and the core shaft and the upper roll are movable around the secondary support drum to a stowed position spaced apart from the primary arm by the secondary arm. 18. The drum-type winder according to claim 17, further comprising motor driving means for the secondary drum for dynamically braking the rotation of the roll to drop the lamination roll from the winder.