WO1987006218A1

WO1987006218A1 - Constant contact lay-on roll winder

Info

Publication number: WO1987006218A1
Application number: PCT/US1986/000730
Authority: WO
Inventors: Michael C. Perrigo
Original assignee: John Brown, Inc.
Priority date: 1986-04-08
Filing date: 1986-04-08
Publication date: 1987-10-22

Abstract

Turret type winder which incorporates articulated constant contact lay-on rolls (10a, 10b), which are mounted concentrically with the chucks (14a, 14b) at the ends of the arms (27) of the turret winder. These articulated constant contact lay-on rolls are continuously repositioned radially during winding and are able to either maintain constant pressure or to reduce lay-on roll pressure as the film bundle diameter increases. This winder also maintains an essentially constant wrap angle on the lay-on roll between the web (13) and the lay-on roll to minimize web tension variations during transfer operations. This is accomplished with the articulated constant contact lay-on roll by continuous circumferential repositioning during turret rotation when transferring to a new core (12a, 12b), so that the lay-on roll remains in contact with the surface of the bundle and maintains an essentially constant wrap angle during the entire 180 degree rotation of the turret arms. This feature virtually eliminates poor winding and the resulting formation of scrap during the turret arm rotation operation when a new core is loaded. This winder also incorporates an improved web feed-in mechanism to control web tension which incorporates a moveable float roll (91), a clutch driven bowed roll (96), driven feed rolls (95, 95') with free wheeling bearings and a mechanism to adjust the winding chuck speed in response to displacements of the float roll. This improved feed-in mechanism substantially reduces web tension variations due to drag forces normally encountered in the feed-in mechanism. This invention also includes an improved method for winding film bundles whereby the nip pressure is varied during winding and then maintained at an essentially constant value during turret rotation by maintaining an essentially constant wrap angle of the web on the lay-on roll during turret rotation.

Description

CONSTANT CONTACT LAY-ON ROLL WINDER BACKGROUND FIELD OF INVENTION

This invention deals with the field of devices called turre winders which are used to wind webs of film type materials o co es . A typical turret ^{^}winder is comprised of a rotatable turre containing two pairs of rotating chucks located 180 degrees apar from each other at the ends of a pair of turret arms. Thes turret winders can produce bundles of film up to 24 to 30 inche in diameter. Turret winders with three or four pairs of chuck are also available but these winders produce smaller bundles. The use of two pairs of chucks to hold two cores permits th web winding to be done essentially continuously. Winding begin on one core and then after a bundle is accumulated on the core the turret arms are rotated 180 degrees and the web i transferred to the second core and winding continue uninterrupted. Often the cores are surfaced with an adhesiv strip to facilitate web transfer to the new core. While the second core is accumulating a bundle, the firs core with it's bundle is removed, either manually o automatically, and a new core is loaded into the chucks . When th second core has accumulated a bundle, the turret is again rotate and the web transferred to the core in the first set of chucks These operations are then repeated until the desired number o bundles have been wound. When a web of film is wound, it forms a bundle o predetermined diameter corresponding to a particular length o the film material depending on the thickness of the film. During a typical winding operation, the web is wound on core approximately 3-5/8 inches in diameter at the rate of up t 1500 feet per minute. At the end of the winding cycle typica bundles contain 2000 to 6000 feet of film and range from 8 to 1 inches in diameter. These bundles of film are usuall accumulated in two to four minutes of winding. However large bundles containing as much as 40,000 feet of film are also woun in cycles of thirty minutes or more. In a typical operation, the web is a deformable elasti material which must be wrapped on the bundle without entrapmen of air between the accumulating layers . A lay-on roll is usually used to eliminate the entrapment o air when the web is wound on the bundle. This lay-on roll ride on the surface of the bundle as the web is wrapped and presse the web on to the rotating bundle to prevent air from bein trapped under the web as it is wrapped on the bundle. This lay on roll also influences the tension in the web and the hardnes of the bundle. The hardness is in part a function of th pressure exerted on the bundle by the lay-on roll and th force from web tension. The resulting pressure at the nip wher the lay-on roll actually presses the web onto the bundle and th tension in the web as it is wound determine bundle hardness. Th web tension is adjusted by conventional means in the web feed-i system. Proper web tension and lay-on roll pressure must b maintained to form a hard bundle without so much web tension i the bundle that the bundle telescopes or more typically, wit film that tends to cling, a barrel shaped bundle is formed. Whe telescoping occurs, the inner layers of a bundle are squeeze out axially resulting in a bundle width that is larger than th width of the web as it is wound. A barrel shaped bundle i narrower than the width of the unwound web and very often ha circumferential wrinkles in the bundle of film. In addition, i web tension and lay-on roll pressure are too low a soft bundle i produced with wrinkles from trapped air. If web tension and lay on roll pressure vary over too wide a range during winding, bundle will be produced with soft portions overlaid by har portions. When this occurs a bundle with ridges induced in th soft portions by the compression from the high tension har portions is produced. All of these irregularities can result i customer rejection of the bundle. As indicated above, when the desired bundle diameter ha been reached, the turret arms are rotated 180 degrees so that th second pair of chucks, which also hold an empty core, is move into position to begin the winding operation. In a typica application, winding of the web continues during the turre rotation operation. This turret rotation operation typically consumes 20 to 3 seconds and approximately 300 to 500 feet of web is wound on th bundle during this operation at web winding rates of 1000 to 150 feet per minute. During turret rotation on a typical turret winder, lay-o roll contact with the bundle is lost. For many types o materials, when this occurs, the web that is accumulated on th bundle during the turret rotation operation traps air betwee the successive layers. In addition, web tension often varie substantially. These factors cause unacceptable wrapping of th web during turret rotation. This poorly wrapped portion of th web must be removed manually from the bundle and discarded o reprocessed as scrap. At typical bundle sizes and web winding rates, this scra can represent 10 to 15 per cent of the total web actually woun on a core. The conventional web feed-in mechanisms which function t prepare the web for winding are also the source of variations i web tension, these variations contribute to unsatisfactory woun bundles of film. In a typical feed in mechanism the web travels over fee rolls which are driven by a variable speed motor. The web the travels over a bowed roll. The bowed roll has a rubbe cylindrical sleeve mounted on a number of bearings which ar supported on a cylindrical shaft which is curved or "bowed" alon its longitudinal axis. As the web passes over this bowed roll the film is stretched slightly in the direction transverse to it direction of travel and any wrinkles in the web are removed. In a conventional feed-in mechanism web tension i controlled by measuring or sensing the force exerted by the we on a float roll and using that force to adjust the speed of th core chuck drive motor. The speed of the motor which control the feed rolls is set at line speed, that is the average rat that the web is being processed. In practice, while these system function reasonably effectively, speed variation between th chuck core drive motor and the feed roll motor cause web tensio variations which adversely affect the winding operation. I addition, in conventional feed-in mechanisms inertia and frictio in the feed in rolls and the bowed roll, which stretches the we slightly as it traverses the bowed roll, induces furthe undesirable variations in web tension.

PRIOR ART

There are several approaches described in the prior ar relating to turret winders which incorporate lay-on rolls t control roll hardness, web tension and eliminate air entrapment The use of pivotally mounted pressure rolls for this purpos is known in the art. The U.S. Patent of ENGL No. 4,343,44 incorporates a pivotally mounted pressure roll as does the U.S Patent of PENROD No. 3_t478,975. Also included among these is an apparatus and metho described in the U.S. Patent of TETRO No. 4,431,140 incorporatin pivotally mounted pressure rolls with accompanying guide roll mounted on pivot arms which are mounted on plates concentric wit the turret shaft axis . This device also is configured to requir loading of cores on one side of the device and unloadin completed bundles on the opposite side. This loading arrangemen is contrary to the usual practice of loading and unloading at th same location. In addition, with the apparatus described i TETRO, when the turret is rotated from the winding position t the unloading position, the wrap angle of the web on the pressur lay-on roll is increased substantially from the angle occurrin during the winding operation. Finally, the TETRO apparatu requires that an adhesive strip must be placed on a new core t facilitate the transfer of the film web to the core at th beginning of the winding process . OBJECTS AND SUMMARY OF THE INVENTION

The present invention, the improved constant contact lay-o roll winder, was conceived to include the following objectives: 1. An improved turret type winder that maintains lay-on rol contact with the bundle throughout turret arm rotation durin the core transfer operation. 2. An improved turret type winder that maintains an essentiall constant wrap angle between the web and the lay-on roll durin core transfer operations. 3. An improved turret type winder that can reduce lay-on rol pressure as bundle diameter increases to avoid telescoping of th bundle of film. 4. An improved turret type winder that incorporates a articulated constant contact lay-on roll to virtually eliminat poor winding and scrap formation during core transfer operations 5. An improved turret type winder that provides for a constan contact lay-on roll and permits core loading and unloading fro the same location in accordance with conventional practices . 6. An improved turret type winder that provides for web transfe to new cores without the need for adhesive strips on the ne cores. 7. An improved turret type winder that maintains web tensio and lay-on roll pressure to minimize air entrapment and we tension variation to avoid wrinkles and ridges and the resultin film distortion in the wound bundle. 8. An improved turret type winder that incorporates a float roll, free wheeling driven feed rolls, a clutch driven bowe roll, a core drive control to maintain web tension and idle rolls which use air nozzles to initiate rotation. 9. An improved winding method in which nip pressure is varie during winding and then maintained essentially constant b maintaining an essentially constant wrap angle during turre rotation. These objects are accomplished by incorporating a constan contact lay-on roll mounted on articulated arms mounte concentrically with the core chucks on the arms of the turre winder. These articulated arms are rotatably mounted to permi continuously repositioning of the constant contact lay-on rol during rotation of the turret arms to enable core transfers to b accomplished. In addition, the portion of the articulated arms o which these constant contact lay-on rolls are mounted pivot t permit positioning of the constant contact lay-on rolls on th bundle as it is wound, while varying the pressure exerted on th bundle by the constant contact lay-on roll to reduce pressure a the bundle diameter is increased. Web tension is controlled by a a float roll . Tendenc driven feed rolls, which are free to rotate on their driv shafts, and a clutch driven bowed roll maximize float rol control responsiveness to core speed changes and minimize we tension variations due to speed variations between the speed o the chuck core drive and feed-in mechanism. BRIEF DESCRIPTION OF THE DRAWING

The following drawings depict the preferred embodiment o the invention. Fig. 1 is a side elevation view of the turret winder showin the articulated arms mounted on the turret arms in their positio near the end of a winding cycle. Fig. 2 is an end elevation view of the turret winder wit the turret arms in a vertical position. Fig. 3 is an elevation view of the turret winder showin the articulated arms in position for transfer of the web to a ne core. Figs. 4 through 9 show the articulated arms and the constant contact lay-on rolls at various positions durin the rotation of the turret arms during the core transfer operation as well as the path of the web. Fig. 4 illustrates the positions of the articulated arms an the constant contact lay-on rolls at the start of the transfe operation. The rotational index of the turret arms is 0 degrees, the turret arms are horizontal and the core mounted in the "A" chucks has a full bundle. Fig. 5 illustrates the position of the articulated arms an the constant contact lay-on rolls and the turret arms afte counter clockwise rotation to an index position of 45 degrees. Fig. 6 illustrates the position of the articulated arms, the constant contact lay-on rolls and the turret arms after counte clockwise rotation to an index position of 90 degrees. Fig. 7 illustrates the position of the articulated arms the constant contact lay-on rolls and the turret arms afte counter clockwise rotation to an index position of 135 degrees. Fig^'. 8 illustrates the position of the articulated arms the constant contact lay-on rolls and the turret arms afte counter clockwise rotation to an index position of 180 degrees with the J-arm in position to cut off the web to begin winding o a new core. Fig. 9 shows the position of the articulated arm after we cutting has been completed and the constant contact lay-on rol has been moved into contact with the core in the "B" chucks. Fig. 10 shows the position of the articulated arm a beginning of the winding cycle after completion of the cor transfer operation. Fig. 11 illustrates vanes and an air nozzle used t initiate rotation of idler rolls. Fig. 12 illustrates the articulated arm assembly. Fig. 13. and 13A illustrate the functioning of th articulated arm assembly. Fig. 14 illustrates the web feed-in mechanism and we tension control components. DETAILED DESCRIPTION OF THE INVENTION

This invention as shown in Fig. 1, a side elevation view which illustrates Turret Winder 1 mounted on Frame 2 whic supports Turret Cross Shaft 4 mounted on cross shaft bearing 5 Turret Arms 6 and 6' which are further comprised of right an left portions labeled 6A and 6A ' and 6B and 6B ' respectivel which are fixedly mounted on Turret Cross Shaft 4 and rotat clockwise when Turret Arm Positioning Motor 3 (Shown in Fig. 2 causes Turret Cross Shaft 4 to rotate. The entire Turret Ar Assembly 9 rotates as a unit in response to rotation of Turre Arm Positioning Motor 3. A pair of Core Chucks 14A and 14A' are mounted near the en of Turret Arms 6A and 6A ' respectively. Core Chuck 14A i fixedly attached to Chuck Drive Shaft 15A which is fixedl attached to Chuck Drive Pulley 20A. Chuck Drive Pulley 20A i driven by Drive Belt 17A which is in turn driven by Drive Pulle 18A which is rotatably mounted on Turret Cross Shaft 4 and i driven in turn by Drive Belt 19A. Drive Belt 19A is driven b Drive Pulley 21A which is fixedly attached to Shaft 22A on Chuc Drive Motor 23A. Tension in Drive Belt 17A is adjusted by repositionin Tension Pulley 24A which is moveably mounted on Turret Arm 6A. Tension in Drive Belt 19A is adjusted by raising or lowerin Chuck Drive Motor 23A on Motor Mounting Bolts 25A. Pivot Arm 16A is rotatably mounted on Chuck Drive Shaft 15A Pivot Pin 26A is mounted on Pivot Arm 16A on the end opposite t the point of attachment of Pivot Arm 16A to Chuck Drive Shaf 15A. Lever Arm 27A is rotatably mounted on Pivot Pin 26A. On end of Constant Contact Lay-on Roll 10A is rotatably attached t one end of Lever Arm 27A. At the other end of Lever Arm 27A on end of Counterweight 28A is fixedly attached at a point beyon the point at which Lever Arm 27A is mounted on Pivot Pin 26A. A this same end of Lever Arm 27A one end of Lever Positioner 29 is rotatably attached. The other end of Lever Positioner 29A i rotatably attached to Pivot Arm 16A. In this figure, Fig. 1, winding of Web 13 on Core 12B t form Bundle 8 is nearly complete and Turret Arm Assembly 9 ha already rotated 180 degrees from the normal winding position s that at this point Core 12A is positioned for the beginning o the winding operation. At this point in the operation Web 13 i carried over Transfer Lay-On Roll 40 which is rotatably supporte at each end by Transfer Arms 41 and 41 ' , which in turn ar pivotally mounted on Transfer Arm Shaft 42. Transfer Arms 41 an 41' are positioned by means of Positioner Device 43. In th preferred embodiment Positioner Device 43 is equipped wit Transfer Arm Damper 44, a hydraulic damper. Web 13 partiall wraps around Core 12A in a clock wise direction from Transfe Lay-on Roll 40 and then passes under Idler Roll 30 before passin over Constant Contact Lay-on Roll 10B to be wound on Bundle 8. J-arms 50 and 50' are pivotally mounted on J-arm Shaft 5 and are positioned by J-arm Positioning Devices 52 and 52 ' respectively which are driven by J-arm Positioner Drive 59. J arm Idler Roll 53 is rotatably mounted on the end of J-arms 5 and 50 ' . Web Knife 54 is mounted between J-arm 50 and 50 ' on We Knife Pivots 56 and 56' which are pivotally mounted on J-arms 5 and 50' and is activated by Knife Actuators 55 and 55' . Knif Actuators 55 and 55 ' , which are rotatably attached to one end Web Knife Pivot 56 and 56' respectively, are rotatably mounted respective J-arms 50 and 50 ' . A second pair of Core Chucks 14B and 14B ' are mounted at th opposite end of Turret Arm Assembly 9 on Turret Arms 6B and 6B ' Core Chucks 14B and 14B ' rotatably support Core 12B betwee Turret Arms 6B and 6B ' . Core Chuck 14B is rotatably attached t Turret Arm 6B on Chuck Spindle 32B. Pivot Arm 16B is rotatabl mounted on Chuck Spindle 32B. Pivot Pin 26B is mounted on Pivo Arm 16B on the end opposite to Pivot Arm 16B ' s attachment t Chuck Spindle 32B. Lever Arm 27B is rotatably mounted on Pivo Pin 26B. One end of Constant Contact Lay-On Roll 10B is rotatabl attached to one end of Lever Arm 27B. At the other end of Leve Arm 27B one end of Counter Weight 28B is fixedly attached at point beyond the point at which Lever Arm 27B is mounted o Pivot Pin 26B. At this same end of Lever Arm 27B one end o Lever Positioner 29B is rotatably attached. The other end of Lever Positioner 29B is rotatably attache to Pivot Arm 16B. Pivot Arm 16B is moved circumferentially around Chuc Spindle 32B relative to Turret Arm 6B by Pivot Arm Locating Moto 60B . Locating Motor 60B which is mounted on Turret Arm Assembl 9 is fixedly attached to Pivot Arm Locating Motor Output Shaft 63B. Motor Gear 61B is fixedly mounted on Locating Motor Output Shaft 63B. Motor Gear 61B engages Shaft Gear 62B which is fixedly attached to Drive Shaft 64B . Drive Shaft 64B is rotatably mounted on Turret Arm 6B and engages Pivot Arm Drive Gear 653 by means of Shaft Gear 66B . Pivot Arm Drive Gear 65B is fixedly mounted on Pivot Arm 16B . Fig. 2, an end elevation view of the invention, illustrates Turret Winder 1 with Turret Arm Assembly 9 in a vertical position. Turret Cross Shaft 4 is supported and driven by Turret Cross Shaft Positioning Motor 3 on one end and is supported on the other end by Turret Cross Shaft Bearing 5. Turret Arms ^' 6A' and 6B ' which are fixedly attached to Turret Cross Shaft 4, serve as mountings for Pivot Arm Locating Motors 60A and 60B . Pivot Arm Locating Motor 60A drives Pivot Arm Locating Motor Output Shaft 63A which is supported at the end opposite from Pivot Arm Locating Motor 60A by Support Bearing 67A which is mounted on Turret Arms 6A and 6B. Idler Roll 30 is rotatably supported by Pivot Arm Locating Motor Output Shaft 63 . A similar Idler Roll 31 is supported by Pivot Arm Locating Motor Output Shaft 63B. Motor Gears 61A and 61A' are fixedly mounted on Pivot Arm Locating Motor Output Shaft 63A and are positioned to engage Shaft Gears 62A and 62A ' respectively to rotate Pivot Drive Gears 65A and 65A ' via Drive Shafts 64A and 64A ' and Shaft Gears 66A and 66A ' around the axis of Core 12A. Since the pivot drive gears are fixedly attached to Pivot Arms 16A and 16A ' , rotatio of Articulated Arm Assembly 7A can be accomplished. Fig. 3 is also a side elevation view of the invention similar to Fig. 1, which illustrates the components of Turre Winder 1 in position for the transfer of web 13 to an empty cor 12A. In this figure, Fig. 3, a full bundle 8 is shown on cor 12B. Web 13 partially wraps around Transfer Lay-on Roll 40 whic is brought into contact with core 12A. Transfer Lay-on Roll 4 has been brought into contact with core 12A by counter clockwis rotation of Transfer arms 41 and 41' on Transfer Arm Shaft 42 b Transfer Arm Positioning Device 43. Web 13 is wound around Core 12A and from Core 12A partiall wraps around J-arm Idler Roll 53. From J-arm Idler Roll 53 We 13 passes under Idler Roll 30. From Idler Roll 30 Web 1 contacts Constant Contact Lay-on Roll 10B which is in contac with Bundle 8 on Core 12B . In this figure, Fig. 3, Lever Arms 27A and 27A' have bee raised to their maximum position away from Core 12A. This i accomplished by Lever Positioners 29A and 29A' .

THEORY OF WINDER OPERATION Figures 4 through 10 illustrate the functioning o Articulated Arm Assemblies 7A and 7B during bundle formation an core transfer operations. In Fig. 4 Turret Arm Assembly 9 (which is not shown) is i the horizontal position with Core 12A located on the right sid with a full Bundle 8 of film wound on Core 12 . At this point i the operation Web 13 is wound around Transfer Lay-on Roll 40 an travels to Constant Contact Lay-on Roll 10 . Constant Contac Lay-on Roll 10A is held in contact with the outer surface o Bundle 8 by Lever Arms 27A and 27A' . Pivot Arms 16A and 16A' ar approximately horizontal and Lever Positioners 29A and 29A' exer force on Lever Arms 27A and 27A" . This force is transmitted t Constant Contact Lay-on Roll 10A through Lever Arms 27A and 27A' On the left of Turret Arm Assembly 9 Core 12B is empty Constant Contact Lay-on Roll 10B is fully retracted away fro Core 12B and Lever Arms 27B and 27B' are approximately vertical As the transfer operation begins Turret Arm Assembly 9 is rotate in a clockwise direction. At the start of this transfe operation Pivot Arms 16A and 16A' are horizontal and align wit the horizontal axis of Turret Arm Assembly 9. The next figure, Fig. 5, illustrates the position of th various components after Turret Arm Assembly 9 has rotated 4 degrees in a clockwise direction. At this point in the transfe operation Constant Contact Lay-on Roll 10A remains in contac with the surface of Bundle 8. Tension in Web 13 is maintained b Lever Positioners 29A and 29A' acting through Lever Arras 27A an 27A' . Pivot Arms 16A and 16A' have rotated counter clockwis relative to the axis of Turret Arm Assembly 9. Because of thi rotation of Pivot Arms 16A and 16A', the angle of wrap that We 13 makes on Constant Contact Lay-on Roll 10A is essentially th same as the wrap angle illustrated in Fig. 4 at the beginning o the transfer operation. The next figure, Fig. 6, shows the components after 90 degrees of clockwise rotation of Turret Arm Assembly 9. Pivo Arms 16A and 16A ' have rotated further in a counter clockwise direction relative to the center line of Turret Arm Assembly 9. This rotation of Pivot Arms 16A and 16A' result in positioning o Constant Contact Lay-on Roll 10A so that it continues to maintai an essentially constant wrap angle of Web 13 on Constant Contact Lay-on Roll 10A. ; In Fig. 7 Turret Arm Assembly 9 has rotated 135 degrees clockwise from its initial position. At this point Web 13 has contacted Constant Contact Lay-on Roll 10B and Idler Roll 31. Pivot Arms 16A and 16 ' have rotated further in a counter clockwise direction relative to the center line of Turret Ar Assembly 9. Here again the wrap angle between Web 13 an Constant Contact Lay-on Roll 10A has been maintained and Constan Contact Lay-on Roll 10A has remained in contact with the surfac of Bundle 8. In the next figure, Fig. 8, Turret Arm Assembly 9 has rotated a full 180 degrees from its initial position. Here agai the wrap angle of Web 13 around Constant Contact Lay-on Roll 10 is maintained. After Turret Arm Assembly 9 has reached this 18 degree rotation, Transfer Lay-on Roll 40 is brought into contac with Core 12B and J-arms 50 and 50 ' are rotated clockwise by J- arm Positioners 52 and 52 ' to bring J-arm Idler Roll 53 in contact with Web 13 as shown in Fig. 8. At this point in the operation Web Knife 54 is actuated to cut Web 13 between Core 12B and J-arm Idler Roll 53. When this cut is made the cut end o advancing Web 13 is directed into nip 57 between Core 12B an Transfer Lay-on Roll 40 where Web 13 is picked up on Core 12B an winding commences. The sequence of operation illustrated i Figs. 4 through 8 shows that as Web 13 is wound on Bundle during the transfer operation the Wrap Angle 58 (as shown in Fig 4 ) made by Web 13 between the point that it first makes contac with Constant Contact Lay-on Roll 10A and the point that i reaches Nip 57 formed by Constant Contact Lay-on Roll 10A an Bundle 8 is maintained essentially constant throughout th transfer operation. Maintaining Wrap Angle 58 constant whil maintaining a constant tension in Web 13 and with constan pressure exerted by Lever Positioner 29A and 29A' through Leve Arm 27 and 27A' on Constant Contact Lay-on Roll 10A will produc constant pressure on Bundle 8 at Nip 57 and will produce a smoot bundle with the desired hardness. The remainder of cut off We 13 is wound onto Bundle 8 on Core 12A completing Bundle 8. As Web 13 begins to accumulate on Core 12B and J-arms 50 an 50' are retracted, Pivot Arms 16B and 16B ' are rotated counte clockwise and Lever Arm Positioners 29B and 29B ' extend fully an cause Lever Arms 27B and 27B' to bring Constant Contact Lay-o Roll 10B into contact with Core 12B as shown in Fig. 9. At thi point in the operation, Web 13 passes around Transfer Lay-on Rol 40, which is in contact with Core 12B., and then travels unde Constant Contact Lay-on Roll 10B as it accumulates on the ne bundle. In the next step in the operation Transfer Lay-on Roll 40 is retracted from Core 12B to its initial position as illustrated in Fig. 4. Pivot Arms 16B and 16B ' are rotated again counter clockwise relative to the axis of Turret Arm Assembly 9 so that the center line of Pivot Arms 16B and 16B ' are horizontal and in line with the center line of Turret Arm Assembly 9 as shown in Fig. 10. Winding of Web 13 on the bundle accumulating on Core 12B continues until Bundle 8 of satisfactory diameter is accumulated. The transfer operation is then repeated. Fig. 11 illustrates the use of Idler Roll Vanes 80 and Air Nozzle 81. Vanes of this type are located on both ends of Constant Contact Lay-on Rolls 10A and 10 B, Idler Rolls 30 and 31 as well as J-Arm Idler Roll 53. Air Nozzle 81 is mounted in close proximity to each set of Idler Roll Vanes 80. Compressed air is directed through Air Nozzle 81 towards Idler Roll Vanes 80 to cause the Idler Roll to rotate. Rotation of J-Arm Idler Roll 53 is accomplished just prior to the time at which J-Arm Idler Roll 53 comes in contact with Web 13 to initiate cutting of Web 13 by Web Knife 54. Rotation of Idler Rolls 30 and 31 are initiated in the same manner with compressed air through Nozzle 81. Rotation in each of these Idler Rolls is initiated just prior to roll contact with Web 13 during the transfer operation. This step in the operation occurs when Turret Arm Assembly 9 has rotated approximately 135 degrees from its initial horizontal position as illustrated in Fig. 7 above. Rotation of Constant Contact Lay-on Rolls 10A and 10B are initiated in the same manner with compressed air through Nozzl 81. Rotation in each of these Rolls is initiated just prior to roll contact with Web 13 during the transfer operatio as shown in Fig. 7. The initiation of rotation in all of these rolls durin various phases of the indexing and transfer sequence greatl minimizes wrinkles and tension spikes since the energy require to initiate roll rotation does not have to be transferred fro the web as in conventional practice. An important feature of this invention is the ability t control the pressure between the Constant Contact Lay-on Roll 10 or 10B and Bundle 8 as the bundle increases in diameter. Thi feature is accomplished by the following means. First Counte Weight 28A and 28B are designed to counter balance Constan Contact Lay-on Rolls 10A and 10B when mounted on their respectiv pairs of Lever Arms 27A and 27A ' and 27B and 27B ' . In th preferred embodiment the weight and approximate location o Counter Weights 28A and 28B are determined by conventional mean to counter balance the respective moments of Constant Contac Lay-on Rolls 10A and 10B and their respective Lever Arms 27A an 27A' and 27B and 27B' . Final balancing is accomplished b slideably positioning the ends of each of Counter Weights 28A an 28B in Counter Weight Slots 76A and 76A' and 76B and 76B ' locate in respective Lever Arms 27A and 27A" and 27B and 27B' a illustrated in Fig. 12. When this balance is accomplished th weight of the various components in Articulated Arm Assemblies 7 and 7B do not influence the pressure that Constant Contact Lay-on Rolls 10A and 10B exert on film Bundle 8 as it is formed. The pressure is determined by the geometric arrangement of various components, web tension and forces applied by Lever Positioners 29A and 29A' and 29B and 29B ' on respective Constant Contact Lay-on Rolls 10A and 10B . These arrangements are described in detail below. Fig. 13 depicts the position of the various components of Arm Assembly 7 and Transfer Lay-on Roll 40 beginning the winding operation with Core 12A just beginning to accumulate incoming Web 13. The center line of Core 12A is located at point 70, the center line of Constant Contact Lay-on Roll 10A is located at point 71, the center line of pivot pin 26A is located at point 72, the center line of the point of attachment of Lever Positioner 29A is located at point 73 , the opposite end of Lever Positioner 29 is mounted at point 74 on pivot Arm 16A and the center line of Counter Weight 28A is located at point 75 on Lever Arm 27A. Wrap Angle 58 is approximately 90 degrees at this state of the winding operation. Fig. 13A depicts the components described in Fig. 13 with an accumulation of film forming Bundle 8 on Core 12A. The force exerted by Constant Contact Lay-on Roll 10 on Core 12 and Bundle 8 is a function of the force applied to Constant Contact Lay-on Roll 10A from Lever Positioner 29A through Lever Arm 27A, the opposing force exerted on Constant Contact Lay-on Roll 10A by the tension in Web 13, and the relative location o the various center line points described above. Bundle 8 of approximately 24 inch diameter is depicted in Fig. 13A and Wra Angle 58 is approximately 45 degrees . The following terms are definitions for the purpose o illustrating how the invention disclosed herein accomplished th control of force exerted by Constant Contact Lay-on Roll 10 o film Bundle 8 as the bundle diameter increases . Term Definition F = Force exerted on bundle by Constant Contact Lay-on Rol a = angle made between point 70, 72 and 71 L = the distance between points 70 and 72 P = the Forces exerted by Lever Positioner 29 on Lever Arm 27 at point 73 T = Tension Force in Web 13 pulling against Constant Contact Lay-on Roll 10 M = the perpendicular distance between point 72 and the lin

F formed between points 73 and 74, (that is the line o action of force P). M = the perpendicular distance between points 72 and Web 13 a

T it passes from Transfer Lay-on Roll 40 to Constan Contact Lay-on Roll 10, (that is the line of action o web tension force T) . In accordance with the teaching of the present invention P(M ) - T (M )

F T F = cos (a/2)

Angle a increases as the diameter of Bundle 8 increases. A angle a increases Wrap Angle 58 decreases. In the preferred embodiment, L, the distance between point 70 and 72 is 15 inches and the distance between points 71 and 7 is 15 inches. In addition diameter of Core 12A is 3.625 inche and Constant Contact Lay-on Roll 10A is 4.5 inches in diameter These dimensions were selected for design convenience for windin bundles up to 24 inches in diameter and the invention is no intended to be limited thereby. In the preferred embodiment, if force P and force T ar maintained at constant values, force F acting on Constant Contac Lay-on Roll 10 remains nearly constant for bundle diameter up t approximately 10 inches. Thereafter force P gradually decline up to the maximum bundle diameter of 24 inches. The following table, Table 1, illustrates this variation i the preferred embodiment under the following conditions. Core Diameter = 3 5/8 inches P = 300 lbs . T = 24 lbs. L = 15 inches M = 5.54 inches at the start of winding

C M = 4.492 inches at a Bundle diameter of 24 inches

C M = 17.023 inches at the start of winding

T M = 11.197 inches at a Bundle diameter of 24 inches

T a = 15.56 degrees at the start of winding a = 56.72 degrees at a Bundle diameter of 24 inches Table 1

Bundle Angle Force on Ratio of initial

Diameter "a" Bundle Force at Core inches degrees "F" Diameter to Force lbs at Bundle diameter

3. 625 (Core) 15.5 82.9 1.00

4. 0 16.3 82.9 1.00

6. 0 20.2 84.0 1.01

8. 0 24.0 83.3 1.01

10 .0 28.0 82.4 0.99

12 .0 31.9 ^" 80.6 0.97

14 .0 35.9 79.0 0.95

16 .0 40.0 76.3 0.92

18 .0 44.0 73.2 0.88

20 .0 48.2 69.3 0.84

22 .0 52.4 64.8 0.78

24 .0 56.7 59.6 0.72

It is clear from the above description that there are two distinct methods of varying the pressure at Nip 57 with th tension in Web 13 constant. The first method includes variatio of the force exerted by Lever Arm Positioners 29A and 29A' a point 73 on Lever Arms 27A and 27A¹. The second method can be accomplished by varying Wrap Angle 58 by changing the relative position of Articulated Arm Assembly 7 relative to Transfer Lay- on Roll 40. By rotating Articulated Arm Assembly 7 as shown in Fig. 13 around the axis of Core 12A in a clockwise direction fro the horizontal position towards the vertically down position, Wrap Angle 58 will decrease and the perpendicular distanc between point 72 and Web 13 will also decrease the value of M and reduce the pressure at Nip 57. It can be seen that these methods of varying the pressure a Nip 57 can be combined using conventional means such as varyin pressure to pneumatic cylinders which are used as Leve Positioners 29A and 29A' in the preferred embodiment an simultaneously using the rotation of Articulated Arm Assembly 7, to regulate the force "exerted by Lever Positioners 29A and 29A' to produce virtually any type of pressure at Nip 57 while Web 13 is wound on Core 12A to form Bundle 8 while maintaining tensio in Web 13 constant. THEORY OF WEB TENSION CONTROL This invention also incorporates an improved means t control tension in Web 13 which is illustrated in Fig. 14. I this figure Web 13 passes over Secondary S Roll 111 and the passes over Primary S Roll 110. These S Rolls are driven throug S Roll Drive Belt 112 by S Roll Drive 113 as serve as the driv mechanism to pull Web 13 into Turret Winder 1 from an externa source of supply. By setting the speed of S Roll Drive 113 th line speed of Web 13 is set. Secondary S Roll 111 is driven b Drive Gear Assembly 120 from Primary S Roll 110 and in tur drives Drive Belt 116 which drives Transfer Pulley 117. Transfe Pulley 117 then drives Drive Belt 118 which in turn drive Transfer Pulley 119 and Drive Belt 99. As Web 13 continues through the feed-in mechanism fro Primary S Roll 110 Web 13 wraps around Idler Rolls 114, 115 an 90 before wraping around Float Roll 91. Float Roll 91 i rotatably supported by Float Roll Arms 92 and 92 ' which in tur are pivotally mounted on Float Arm Pivot 93. Web 13 passes fro Float Roll 91 over a pair of Feed Rolls 95 to Bowed Roll 96 an then to Transfer Lay-on Roll 40. Feed Rolls 95, 95' and Transfe Lay-on Roll 40 are rotated by Drive Belt 99 which is driven in conventional manner as described above from Roll Drive 113. Driv Belt 99 drives Feed Rolls 95 and 95 ' through Drive Shafts 103 an 103 ' on which Feed Rolls 95 and 95' are rotatably mounted. Bowe Roll 96 is also rotated via Bowed Roll Clutch Belt 98 which is i turn driven from the output Bowed Roll Clutch 97. The input o Bowed Roll Clutch 97 is rotated by Drive Belt 99 ' which is i turn driven by Drive Shaft 104. There are two important aspects of Web 13 that shoul'd b controlled as Web 13 is fed into Turret Winder 1 during windin operations; the first is maintenance of an appropriated tensio in Web 13 and the second is the removal of any wrinkles that ma be present in Web 13 before it is wound on Bundle 8. Th presence or absence of wrinkles in Web 13 is influenced b tension in Web 13. Often wrinkles are induced in Web 13 a tension is applied in the feeding of Web 13 to Turret Winder 1 Wrinkles are removed from Web 13 by Bowed Roll 96. As i conventional practice Bowed Roll 96 is curved slightly along it longitudinal axis so that the center of this roll is no concentric with its ends. In conventional practice Bowed Roll 9 is driven by Web 13 as it passes over Bowed Roll 96. Thi results in tension variations in Web 13 especially when there i a change in the velocity of Web 13 as it responds to change i the speed of Chuck Drive Motor 23A or 23B due to the fact tha Bowed Roll 96 must be sped up or slowed down by forces exerte through Web 13. In the present invention Bowed Roll 96 is drive through an adjustable Bowed Roll Clutch 97 to which it i connected by Bowed Roll Clutch Belt 98. The inclusion of Bowe Roll Clutch 97 permits Bowed Roll 96 to be adjusted to rotate a a speed that matches the speed of Web 13 and also follow variations in the speed of Feed Rolls 95 and 95 ' . This ability t adjustably drive Bowed Roll 96 substantially improves the remova wrinkles in Web 13 and avoids tension variations in Web 13 whic result from driving Bowed Roll 96 through Web 13. In addition to the use of Bowed Roll Clutch 97 the presen invention incorporates Float Roll 91, Float Roll Arms 92 and 92' which rotatably support Float Roll 91, Float Arm Pivot 93 t which Float Arms 92 and 92 ' are attached and Float Arm Tensione 102 and Float Arm Movement Sensor 94. In the preferre embodiment of the invention the distance between Float Arm Pivo 93 and the center line of Float Roll 91 is 15 inches and Floa Roll 91 which is normally horizontal is free to rotate in an ar approximately 30 degrees in either direction from this initia position in response to changes in tension in Web 13. Tension i Web 13 is initially adjusted by setting the pressure to pneumatic cylinder used as Float Arm Tensioning Means 102 an adjusting the feeding of Web 13 to position Float Roll Arm 9 vertically. After the initial adjustment to Float Arm Tensionin Means 102 and Float Arm 92 to set tension in Web 13 if th tension increases Float Roll 91 is displaced to the left as show in Fig. 14. This displacement is sensed by Float Arm Movemen Sensor 94 and a signal is generated and directed to Core Chuc Speed Control 100. Core Chuck Speed Control 100 responds to thi signal by reducing the rotational speed at which Bundle 8 i rotating thereby reducing the tension in Web 13. If the tensio in Web 13 decreases a displacement to the right will occur and signal will be generated to increase the rotational speed o Bundle 8 to restore the proper tension in Web 13. In th preferred embodiment Feed Rolls 95 and 95 ' which are rotatabl mounted on Drive Shafts 103 and 103 ' do not significantly dampe the response of Float Roll Arm 92 to change in tension in Web 1 or speed changes in Chuck Drive Motor 23 because of the abilit of Feed Rolls 95 and 95 ' to rotate independently from respectiv Drive Shafts 103 and 103 ^* . This feature coupled with th substantial travel over which Float Roll 91 is capable of movin and the fact that Bowed Roll 96 is driven through Bowed Rol Clutch 97 is a significant improvement over conventional practic in which the bowed roll is driven by the web and produces mor uniform tension and reduces wrinkles in Web 13. There is a further significant improvement over conventiona practice when rotation of the various idler rolls and lay-o rolls is initiated prior to contact with the web with the ai nozzles described above. From the foregoing description of the present inventio there is described, an improved Constant Contact Lay-on Rol Turret Winder which maintains Lay-On Roll contact with th accumulating bundle during the winding operation and the entir transfer operation. In addition, the wrap angle of the web o the Constant Contact Lay-on Roll is maintained essentiall constant during the transfer operation. There is also describe a mechanism which provides for the gradual reduction of Lay-o Roll pressure on the bundle of film as the bundle diamete increases . This reduction in pressure is accomplished withou the use of conventional pressure regulating means such as thos used to reduce air pressure on air cylinders as the bundl diameter increases. There is also described means fo simultaneously varying wrap angle, Lay-on Roll pressure and we tension during the winding operation. There is also described

_* web feed in mechanism which provides for improved control of we tension and wrinkle removal . The present invention has been described in connection wit the details of an illustrative embodiment. It is understood tha the present invention is not limited to the embodiment describe herein but is intended to encompass modifications incorporatin equivalent types of mechanisms that are within the scope of thi invention as defined herein. REFERENCE NUMBER LISTING 1 Turret Winder 2 Frame 3 Turret Arm Positioning Motor 4 Turret Cross Shaft 5 Cross Shaft Bearings 6A, 6A', 6B and 6B ' Turret Arms 7A and 7B Articulated Arm Assembly 8 Bundle

9 Turret Arm Assembly

10A and 10B Constant Contact Lay-on Rol l

11

12A and 12 B Core

13 Web

14A , 14A " , 14B and 14B' Core Chuck

15A and 15B Chuck Drive Shaft

16A, 16A' , 16B and 16B' Pivot Arm

17A and 17B Drive Belt 18A and 18B Drive Pulley 19A and 19B Drive Belt 20A and 20B Chuck Drive Pulley 21A and 2IB Drive Pulley 22A and 22B Shaft 23A and 233 Chuck Drive Motor 24A and 24B Tension Pulley 25A and 25B Motor Mounting Bolts 26A and 26B Pivot Pin 27A, 27A 27B and 27B' Lever Arm

28A and 28B Counter Weight

29A, 29A', 29B and 29B ' Lever Positioner

30 Idler Roll

31 Idler Roll

32A and 32B Chuck Spindle

40 Transfer Lay-on Roll

41 and 41' Transfer Arm

42 Transfer Arm Shaft

43 Transfer Arm Position Device

44 Transfer Arm Damper 50, 50' J-arm

51 J-arm Shaft

52 , 52 ' J-arm Position Device

53 J-arm Idler Roll

54 Web Knife

55 .and 55 ' Web Knife Actuator 56, 56' Web Knife Pivots

57 Nip

58 Wrap Angle

59 J-arm Positioner Drive

60A and 60B Pivot Arm Locating Motor

61A, 61A', 61B and 61B ' Motor Gear

62A, 62A' , 62B and 62B ' Shaft Gear

63A and 63B Pivot Arm Locating Motor Output Shaft

64A, 64A', 64B and 64B ' Drive Shaft

65A, 65A', 65B and 65B ' Pivot Arm Drive Gear

66A, 66A', 66B and 66B ' Shaft Gear

67A and 67B Support Bearing

70A and 70B Center line of Core 71A and 7IB Center line of Constant Contact Lay-on Roll 72A and 72B Center line of Pivot Pin 73A and 73B Center line of Lever position attachment point 74A and 74B Center line of Lever position attachment point 75 Center line of Counter Weight 76A and 76A ' Counter Weight Slots 80A, 80A' , 80B and BOB ' Idler Roll Vanes 81A, 81A' , 81B and 81B' Air Nozzle 90 Idler Roil 91 Float Roll 92 Float Roll Arm 93 Float Arm Pivot 94 Float Arm Movement Sensor 95 and 95 ' Feed Rolls 96 Bowed Roll 97 Bowed Roll Clutch 93 Bowed Roll Clutch Belt 99 and 99' Drive 3elt 100 Core Chuck Speed Control 102 Float Arm Tensioning Means 103 and 103 ' Drive Shaft 104 Drive Shaft 110 Primary S Roll 111 Secondary S Roll 112 S Roll Drive Beit 113 S Roll Drive 114 Idler Roll 115 Idler Roll 116 Drive Belt 117 Transfer Pulley 118 Drive Belt 119 Transfer Pulley 120 Drive Gear Assembly

BAD ORIGINAL

Claims

CLAIMS I claim: 1. An improved turret winding device, wherin said turre winder incorporates turret arms on which core chucks are mounted in which the improvement is comprised of : a. a constant contact lay-on roll; b. one or more lever arms on which said constan contact lay-on roll is rotatably mounted; c a pivot pin on which said lever arms are rotatabl mounted; d. one or more pivot arms which support said pivo pin and which in turn are rotatably mounted concentric with th core chucks mounted on the turret arms of the turret winder; e. one or more lever arm positioners which ar mounted at one end on said pivot arms and at the other end o said lever arms; and f. positioning means capable of positioning sai pivot arms rotatably about the center line of said core chucks.

2. An improved turret winding device as described in clai 1. wherein a counter weight is fixed to said lever arms t counter balance said constant contact lay-on roll.

3. An improved turret winding device in which th improvement is comprised of : a. a float roll; b. one or more float arms upon which said float rol is rotatably mounted; 87/06218 PCT/US86/00730

33 c. a float arm pivot upon which said float arms are rotatably mounted; d. tensioning means which are attached to said float arms to provide tension in a web of film being fed into said turret winder; e. a float arm movement sensor which is capable of detecting the displacement of said float arms; f. a core chuck speed control which varies core chuc rotational speed in response to the displacement of said float arms; g. a web feed drive; h. one or more free wheeling feed rolls, which are driven by said web feed drive at line speed; i. a bowed roll; and , j . an adjustable clutch drive which drives said bowed roll in response to said web feed drive.

4. An improved turret winding device, wherein said turret winder incorporates idler rolls, in which the improvement is comprised of : a. a float roll; b. one or more float arms upon which said float roll is rotatably mounted; c. a float arm pivot upon which said float arms ar rotatably mounted; d. tensioning means which are attached to said float arms to provide tension in a web of film being fed into said turret winder; e. a float arm movement sensor which is capable o detecting the displacement of said float arms; f. a core chuck speed control which varies core chuc rotational speed in response to the displacement of said float arms; g. a web feed drive; h. one or more free wheeling feed rolls, which ar driven by said web feed drive at line speed; i. a bowed roll; j . an adjustable clutch drive which drives said bowed roll in response to said web feed drive; k. vanes which are attached to one or more idler rolls; and 1. one or more air nozzles which direct compressed air at said vanes to impart rotation to said idler roll just prior to said roll coming into contact with said web. 5. An improved turret winding device, wherein said turret winder incorporates turret arms on which core chucks are mounted, in which the improvement is comprised of : a. a constant contact lay-on roll; b. one or more lever arms on which said constant contact lay-on roll is rotatably mounted; c. a pivot pin on which said lever arms are rotatably mounted; d. one or more pivot arms which support said pivot pin and which in turn are rotatably mounted concentric with the core chucks mounted on the turret arms of the turret winder; e. one or more lever arm positioners which are mounte at one end on said pivot arms and at the other end on said leve arms; f. positioning means capable of positioning said pivo arms rotatably about the center line of said core chucks; . g. a float roll; h. one or more float arms upon which said float rol is rotatably mounted; i. a float arm pivot upon which said float arms ar rotatably mounted; j. tensioning means which are attached to said floa arms to provide tension in a web of film being fed into sai turret winder; k. a float arm movement sensor which is capable o detecting the displacement of said float arms; 1. a core chuck speed control which varies core chuc rotational speed in response to the displacement of said floa arms; m. a web feed drive; n. one or more free wheeling feed rolls, which ar driven at line speed by said web feed drive; o. a bowed roll; and . an adjustable clutch drive which drives said bowe roll in response to said web feed drive. 6. An improved turret winding device, wherein said turre winder incorporates turret arms on which core chucks are mounte and idler rolls, in which the improvement is comprised of : a. a constant contact lay-on roll; b. one or more lever arms on which said constant contact lay-on roll is rotatably mounted; c. a pivot pin on which said lever arms are rotatably mounted; d. one or more pivot arms which support said pivot pin and which in turn are rotatably mounted concentric with the core chucks mounted on the turret arms of the turret winder; e. one or more lever arm positioners which are mounted at one end on said pivot arms and at the other end on said lever arms; f. positioning means capable of positioning said pivot arms rotatably about the center line of said core chucks; g. a float roll; h. one or more float arms upon which said float roll is rotatably mounted; i. a float arm pivot upon which said float arms are rotatably mounted; j . tensioning means which are attached to said float arms to provide tension in a web of film being fed into said turret winder; k. a float arm movement sensor which is capable of detecting the displacement of said float arms; 1. a core chuck speed control which varies core chuck rotational speed in response to the displacement of said float arms; m. a web feed drive; n. one or more free wheeling feed rolls, which ar driven at line speed by said web feed drive; o. a bowed roll; p. an adjustable clutch drive which drives said bowe roll in response to said web feed drive. q. vanes which are attached to one or more idler rolls and or constant contact lay-on roll; and r. one or more air nozzles which direct compressed air at said vanes to impart rotation to said roll just prior t said roll coming into contact with said web. 7. An improved turret winding device in which ^' th improvement is comprised of : a. a constant contact lay-on roll; b. one or more lever arms on which said constan contact lay-on roll is rotatably mounted; c. a counter weight which is fixed to said lever arm to counter balance said constant contact lay-on roll; d. a pivot pin on which said lever arms are rotatabl mounted; e. one or more pivot arms which support said pivo pin and which in turn are rotatably mounted concentric with th core chucks mounted on the turret arms of the turret winder,- f. one or more lever arm positioners which ar mounted at one end on said pivot arms and at the other end o said lever arms; g. positioning means capable of positioning said pivot arms rotatably about the center line of said core chucks; h. a float roll; i. one or more float arms upon which said float roll is rotatably mounted; j . a float arm pivot upon which said float arms are rotatably mounted; k. tensioning means which are attached to said float arms to provide tension in a web of film being fed into said turret winder; 1. a float arm movement sensor which is capable of detecting the displacement of said float arms; and m. a core chuck speed control which varies core chuck rotational speed in response to the displacement of said float arms; n. a web feed drive; o. one or more free wheeling feed rolls, which are driven at line speed by said web feed drive; o. a bowed roll; and p. an adjustable clutch drive which drives said bowed roll in response to said web feed drive. 8. An improved turret winding device, wherein said turret winder incorporates idler rolls, in which the improvement is comprised of : a. a constant contact lay-on roll; b. one or more lever arms on which said constant contact lay-on roll is rotatably mounted; c. a counter weight which is fixed to said lever arms to counter balance said constant contact lay-on roll; d. a pivot pin on which said lever arms are rotatably mounted; e. one or more pivot arms which support said pivot pin and which in turn are rotatably mounted concentric with the core chucks mounted on the turret arms of the turret winder; f. one or more lever arm positioners which are mounted at one end on said pivot arms and at the other end on said lever arms; g. positioning means capable of positioning said pivot arms rotatably about the center line of said core chucks; h. a float roll; i. one or more float arms upon which said float roll is rotatably mounted; j . a float arm pivot upon which said float arms are rotatably mounted; k. tensioning means which are attached to said float arms to provide tension in a web of film being fed into said turret winder; 1. a float arm movement sensor which is capable of detecting the displacement of said float arms; and m. a core chuck speed control which ^'varies core chuck rotational speed in response to the displacement of said float arms; n. a web feed drive; σ. one or more free wheeling feed rolls, which ar driven at line speed by said web feed drive; o. a bowed roll; p. an adjustable clutch drive which drives said bowe roll in response to said web feed drive; q. vanes which are attached to one or more idler rolls and or constant contact lay-on roll; and r. one or more air nozzles which direct compressed air at said vanes to impart rotation to said roll just prior t said roll coming into contact with said web. 9. An improved turret winding device as described in claim 1., 2.,

5.,

6.,

7. or 8. in which the force exerted by th constant contact lay-on roll on the bundle is essentiall constant up to a desired bundle diameter and decreases graduall

_* with further increases in bundle diameter when the force exerte on said lever arms by said lever arm positioners is maintained a a constant value. 10. An improved method for winding bundles of film on turr winders, which incorporates a lay-on roll, in which nip pressur at the line of contact between the lay-on roll and the bundle is maintained at an essentially constant value during turre rotation by maintaining an essentially constant wrap angl between the web and the lay-on roll. 11. An improved method for winding bundles of film on turret winders such as that described in claim 10. wherein the wrap angle is maintained constant by continuously repositioning the lay on roll during turret rotation. 12. An improved method for winding bundles of film o turret winders in which a web is wound on a rotating core and th pressure maintained on a lay-on roll, where said lay-on roll i in contact with the surface of the bundle, is varied durin winding of the web to maintain constant hardness of said bundle and further said lay-on roll is repositioned during turre rotation to maintain contact between the constant contact lay-o roll and the bundle during turret rotation to maintain a essentially constant wrap angle between said web and sai constant contact lay-on roll during said turret rotation.