US3191883A

US3191883A - Winder for web material

Info

Publication number: US3191883A
Application number: US343009A
Authority: US
Inventors: Edward R Wells
Original assignee: Procter and Gamble Co
Current assignee: Procter and Gamble Co
Priority date: 1964-02-06
Filing date: 1964-02-06
Publication date: 1965-06-29
Anticipated expiration: 1982-06-29

Description

June 29, 1965 E. R. WELLS WINDER FOR WEB MATERIAL Filed Feb. a, 1964 6 Sheets-Sheet 1 INVENTOR.

Edward R. Wells M 7 l k ATTORNEY June 29, 1965 E. R. WELLS WINDER FOR WEB MATERIAL 6 Sheets-Sheet 2 Filed Feb. 5, 1964 ATTORNEY E. R. WELLS WINDER FOR WEB MATERIAL June 29, 1965 6 Sheets-Sheet 3 Filed Feb. 6, 1964 June 29, 1965 E. R. WELLS WINDER FOR WEB MATERIAL 6 Sheets-Sheet 4 Filed Feb. 6, 1964 INVENTOR. Edward R. Wells ATTORNEY June 29, 1965 E. R. WELLS WINDER FOR WEB MATERIAL 6 Sheets-Sheet 5 Filed Feb. 6, 1964 INVENTOR.

Edward R. Wells ATTORNEY June 29, 1965 R. WELLS WINDER FOR WEB MATERIAL 6 Sheets-Sheet 6 Filed Feb. 6, 1964 s R H mm ma Wm 10 w d E ATTORNEY United States Patent 3,191,883 WHNDER FGR WEB MATERIAL Edward R. Wells, Green Township, Hamilton County, ()hio, assignor to The Procter & Gamble Company,- Cincinnati, Ohio, a corporation of Ohio Filed Feb. 6, 1964, Ser. No. 343,009

11 Claims. (Cl. 24256) This invention relates to continuous winding machines for paper and other web material. More particularly, the invention relates to winding machines which are designed to receive a web from a paper making machine or other source without interruption and to wind the paper continuously into successive rolls of a given diameter, both with and without prior slitting into multiple widths.

Highspeed paper making processes, presently in commercial use, are capable of producing a continuous web of paper at rates of up to and exceeding 3,000 feet of paper per minute. Winding the web and severing it when a full roll is completed has long been a problem at these speeds because it is necessary to simultaneously initiate winding on a new, empty core shaft. When transferring the winding operation from the full roll to the new core shaft a considerable amount of paper is often made unusable through lack of concise transfer and resulting uneven rolls. When attempts are made to alleviate the web transfer problem by interrupting or replacing the surface winding method, another type problem is encountered in that wound rolls have distinct or graduated hard and soft layers because of changes in paper web tension thus leading to later paper fmishing difficulties.

In the usual paper machine reel or surface winding device, the empty core shaft is supported in close proximity to the Winding drum as the roll being wound nears com pletion. The new core shaft is brought into winding relation by moving it from a first position at which it is out of contact with the paper moving over the winding drum into a second position where it contacts the winding drum before the paper Web is severed. The paper is severed and caused to wrap around the new core shaft 'by such uncertain means as air blasts and the billowing of the web induced by finished roll deceleration. These methods are of such unreliability, especially on webs which must be slit into short widths before winding, that such slitting and winding for finished rolls is accomplished in a separate operation.

In otf-machine web processing such as laminating and coating, it is desirable to rewind continuously. :The usual center shaft driven rewinders used for this purpose 'because of their ability to incorporate flying web cutoff and transfer therein, lack the inherent web tension and roll density control ability of the horizontal drum surface winder.

The principal object of the invention is to provide an improved winder and transfer mechanism for severing a continuously moving web as it is being wound to complete a full roll or multiple narrow rolls and simultaneously initiating winding 'on an empty core shaft, the whole transfer operation being carried out automatically.

Another object of the invention is the provision of a machine for controlling even and smooth transfer of continuously moving web material for winding on a new core shaft without any loss in web speed or tension.

A further object of the invention is the provision of a horizontal drum type paper web winding machine which is cap-able of achieving continuous accurate control of roll density and uniformity.

Still a further object of the invention is the provision of a paper Winding machine having the above mentioned advantages which is also capable of receiving a continuously moving multiple sli-t or full width web directly from a paper making machine thereby eliminating the need for rewinding equipment as a consequence of which the capital investment for rewinding equipment is eliminated as is the expense of the manpower needed for operation of rewinding equipment.

The nature and substance of the invention can be summarized briefly as comprising a winding drum having trunnion shafts at its ends mounted for rotation in a machine wherein it is supported by suitable bearings. A pair of enveloping arms are mounted for rotation around the trunnion shaft, one arm of the pair being mounted on either side of the winding drum.

During normal winding, the enveloping arms are stationary and inactive below the winding drum while the core shaft being wound is held against the Winding drum. The core shaft is supported by a pair of spaced way members which extend rearwardly from the main frame of the winding machine. When a new core shaft is to be started, the enveloping arms are rotated forewardly from below to a position above the winding drum where one or more driven idler rolls raise the web from the winding drum while not interfering with the winding which is continued on the core shaft which has been almost fully Wound.

An empty core shaft is moved to a position in close proximity to the winding drum where it is picked up and moved to a position over the winding drum and in contact therewith after it has been accelerated to proper rotating speed so that its surface speed substantially matches that of the winding drum. In this position, the web is in substantial arcuate contact with the new core shaft and web winding tension control is retained at the drum :but moved to its line of contact with the new core shaft. A pair of side arms having a cutting device incorporated therebetween are pivoted to the enveloping arms. The side arms are moved downwardly so that the cutting device severs the web. Immediately, the leading end is urged to completely encircle the new core shaft and reenter the nip between the winding drum and the new core shaft. The side arms are then raised and the enveloping arms are rotatedto their neutral position. The new core shaft on which winding has been initiated is then deposited on the spaced way members by the primary arms after the previously completed roll 'has been moved rearwardly thereon for removal.

While the specification concludes with claims particularly pointing out and distinctly claiming the subject matter regarded as forming the present invention, it is believed the invention will be better understood from the following description taken in connection with the accompanying drawings in which:

FIGURE 1 is a side elevation of the apparatus showing the parts in normal-winding position. Certain portions of the appartus have been broken away in order to better illustrate the structure. 7

FIGURE 2 is a side elevation, with portions broken away, showing the relative position of the parts of the apparatus after a roll has been completely wound and new core shaft is to be brought into position for winding.

FIGURE 3 is a side elevation of the apparatus similar to FIGURE 2, with portions removed for clarity of illustration, except that a new core shaft has been moved to the position where winding is initiated thereon.

FIGURE 4 is a side elevation, similar to FIGURE 3, showing the relative position of the several parts of the apparatus when the paper web is severed to initiate winding on the new core shaft. The position of the finished roll illustrates the subsequent movement of the finished roll away'from the Winding mechanism to permit the new core shaft to be placed in the normal winding position.

FIGURE 5 is a side elevation, partially broken away and with portions removed for clarity of illustration, showing the new core shaft in normal winding position. This view also shows the position of the enveloping arms a when they are inoperative beneath the winding drum as the paper web is being wound upon the new core.

FIGURE 6 is an end elevation, partially broken away and partially in cross section, looking at the apparatus with its parts in the position of FIGURE 3. The view is taken from the end at which the new core shafts are introduced.

In order to provide for a better understanding of the structure of the apparatus, the various parts and elements, which are assembled to define the structure will now be explained with particular reference, at least initially, to FIGURES 1 and 6.

The entire apparatus is mounted on the baseplates 16 and 11 which support, respectively, the frames 12 and 13. A cross member 14 supports the

end brackets

14a and 14b which receive the shaft ends of the spreader roll assembly 17. As shown in FIGURE 1, the web of paper 18 is received in finished condition from a paper making machine or any equivalent source and is initially guided under the spreader roll 17. A winding drum 19 having trunnion shafts 2i) and 21 extending from their respective ends (FIGURE 6) is supported in the bearing housings 22 and 23 mounted on the frame members 12 and 13, respectively. A bracket 24 secured to the frame 13 supports a variable speed motor 25 which directly drives the winding drum 19 through the coupling 26.

The core shaft ways 27 and 28 are used to support each new core shaft 29. As shown in FIGURES 1 and 6, each new core shaft 29 is initially maintained at the position shown in FIGURE 1 by means of the pivot locks 36 and 31 which are secured to the shaft 32. The shaft 32 is mounted for pivotal movement in the core shaft ways 27 and 28. Release levers 33 and 34 are provided and are attached to the shaft 32 to release the pivot locks 30 and 31 when desired. A spring 35 (FIGURE 1) is provided to normally maintain the pivot locks 36 and 31 substantially in a vertical position thereby keeping the new core shaft 29 away from the winding apparatus.

During normal Winding, the web of paper 18 is guided over the winding drum 19 and then around the core shaft 23a as shown in FIGURE 1. The roll being wound is held against the winding drum 19 by means of the pivoted arm 36 which has a freely rotating roller 37 bearing against the core shaft 29a at one end there being a similar arm (not shown) at the other end of the core shaft 29a. A double acting fluid pressure cylinder 38 is secured to the frame 12 by means of the block 39 at one end is attached to the pivoted arm 36 at the other end to pull the roller 37 toward the winding drum 19 so that the paper being wound on the core shaft 29a is maintained against the winding drum at substantially constant pressure to provide for even Winding. The similar arm (not shown) on the far side of the machine is maintained against the core shaft 29a by similar means. The core shaft 29a is supported by the core shaft way 46 on the near side of the machine, there being a similar way 41 (not visible) on the far side. The ways 4% and 41 support the core shaft 29a throughout the winding operation and even after it is ultimately moved away from the winding drum when the paper roll is completed.

Enveloping

arms

42 and 43 are mounted on either side of the winding drum 19 and are capable of free rotation on the trunnion shafts 20 and 21, respectively. As best illustrated in FIGURES 2 and 6, the enveloping

arms

42 and 43 have

side arms

44 and 45 pivoted thereto around the shaft 46. A bracket 47 (FIGURE 2) is attached to the enveloping arm 42 and one end of tension spring 48 is attached thereto as shown. The other end of the spring 48 is attached to the end of the side arm 44 at the member 49. The spring 48 normally maintains the side arm 44 in the position illustrated in FIGURE 2. The side arm 44 includes a bracket 50 on which a roller cam follower 51 is mounted for free rotation. The other side arm 45 is provided with a similar spring arrangement for keeping it in balance with the arm 44. As seen in 4 FIGURE 6, the side arm 45 has a bracket 52 having a roller cam follower 53 similar to the bracket and cam follower 51 mounted on the side arm 44.

As previously explained, the enveloping

arms

42 and 43 are mounted for free rotation on the trunnion shafts 20 and 21, respectively. As shown in FIGURE 6, the outer ends of the enveloping

arms

42 and 43 are provided with drive gears 54 and 55, respectively. The drive gears 54 and 55 are engaged, respectively, by the bull gears 56 and 57 which are mounted for free rotation on the shaft 53, the ends of which are supported in the frames 12 and 13. The bull gears 57 and 56 are engaged, respectively, by the pinions 59 and 60 which are secured to the drive shaft 61. The drive shaft 61 is driven from the gear box 62 located inside the frame housing 12 (FIGURES 1 and 6). The gear box 62 is in turn selectively and intermittently driven by the motor 63 from a suitable control, the details of which are not illustrated for the purpose of describing this invention as they will be known to those skilled in the art. The left end of the shaft 61 (as seen in FIGURE 6) is mounted for free rotation in a bearing (not shown) within the frame 13.

The primary arm 64 is mounted for free rotation in the groove 66 of the hub of the enveloping arm 42 as best seen in FIGURE 6. The primary arm is mounted in similar fashion with respect to the enveloping arm 43. As shown in FIGURE 1, a core shaft clamp member 68 is pivoted to the primary arm 64 at 69 and has a roller 70 at its outer end. An air cylinder 71 has one end secured to the primary arm 64 as at 72. The piston rod 73 is attached to the core shaft clamp member 68 at 74. A tension spring 75 is provided to normally pivot the core shaft clamp member 68 to its inoperative position as shown in FIGURE 1 when the air cylinder 71 is inoperative. An identical core shaft clamping arrangement is provided on the primary arm 65 and those of its elements which appear in the drawing are identified by like reference numerals in FIGURE 6.

The primary arms 64 and 65 are provided with drive gears 76 and 77, respectively, as best seen in FIGURE 6. The drive gears 76 and 77 are driven by the bull gears '78 and 79, respectively, which are mounted for free rotation on the idler shaft 58 and are in turn driven, respectively, by the pinions 80 and 81 as shown in FIG-

URES

1 and 6. As best seen in FIGURE 1, the pinions 80 and 81 are secured to the shaft 82 which is driven by the gear box 83 mounted within the frame 13 (FIGURE 6). The gear box 83 is selectively and intermittently driven by a motor (not shown) in similar fashion as the drive for the gear box 62 although the two gear boxes are not driven in unison as will be appreciated as the description of the operation of the machine proceeds.

Referring again to FIGURES 2 and 6, it will be noted that a driven idler roll 84 is mounted on the shaft 46 between the enveloping

arms

42 and 43. Similarly, a driven idler roll 85 is mounted for rotation in the

bearings

86 and 87 attached to the

side arms

44 and 45, respectively. A saw tooth knife 88 is mounted between the

side arms

44 and 45 intermediate the idler rolls 84 and 85.

A stud shaft 89 (FIGURE 6) is secured to the enveloping arm 42 and has the double idler pulley 90 mounted for free rotation thereon. A drive pulley 91 is attached to the trunnion shaft 20 and rotates the idler pulley 90 by means of the belt 92. A belt 93 is provided to drive the pulley 94 from the idler pulley 90. The pulley 94 is secured to the shaft 46 thereby providing a positive drive for the idler roll 84. A pulley 95 also attached to the shaft 46 drives the idler roll 85 by means of the belt 96 which runs over the pulley 97. The pulley 97 is secured to the support shaft 98 for the idler roll 85. The purpose of the drive system just described is to rotate the idler rolls 84 and 85 so that their respective surface speeds correspond approximately to the speed of the moving Web 18. This is advantageous as will be better understood as the description proceeds.

The spreader roll 17 is driven from a pulley 99 (FIG- URES 1 and 6) secured to the trunnion shaft 21. The pulley 99 drives the belt 100 which runs over the pulley 101 mounted on the input side of gear reducer 102. Pulley 103 on the output shaft of reducer 102 drives belt 104 which in turn drives pulley 105 on jack shaft assembly 16, Belt rotates spreader roll 17 and is driven by the second pulley 106 on jack shaft 16. Again, the drive from the trunnion shaft 21 to the spreader roll 17 is provided to turn the spreader roll 17 at approximately the same surface speed as the speed of the moving web 18.

Means are also provided for bringing the new core shaft 29 to proper rotating speed before it makes contact with the winding drum 19. This is accomplished by the core shaft accelerating chain 107 (FIGURES 1-5 inclusive), which engages sprocket 11'7 fixed on one end of all core shafts 29. The core shaft accelerating chain 107, as best seen in FIGURE 3, driven by sprocket 129, also engages the idler sprockets 108 and 109 while its upper periphery runs over chain guide 110. Sprocket 129 is coupled to pulley 127 through air operated clutch 128.

Pulley 127 is in turn driven by timing belt 126 and pulley 125 fixed to trunnion shaft 20. Both ends of core shaft 29 are equipped with anti-friction bearings 130 and 131 (see FIGURE 6) which roll on contoured guide supports 132 and 133 and which are similar in contour to chain guide 110. The rearmost sections of the guides permit core shaft 29 to gradually move. radially inward under load of clamps 68 to contact drum 19 after acceleration, as will be appreciated by viewing FIGURE 3.

Referring again to FIGURE 1, a pivoted arm 111 having a freely rotating roller 112 at its end is actuated by a double acting fluid pressure cylinder 113. One end of the cylinder 113 is attached to the bracket 114 while the other end is attached to the arm 111 as shown. A similar pivoted'arm (not shown) is also provided on the far side of the machine to work in unison with the arm 111 and for the purpose to be hereinafter described.

Operation During normal winding the web 18 is led into the apparatus under the spreader roll 17 as shown in FIGURE 1. From there it is guided over the winding drum 19 and around the core shaft 29a supported for free rotation on the core shaft ways 40 and 41. The core shaft 29:: is held against the winding drum 19 by the action of the cylinder 38 pulling on the arm 36 on one side and the similar arm (not shown) on the other side which has a similar actuating mechanism. The enveloping

arms

42 and 43 are inactive and rest in the inoperative position below the winding drum 19 as shown in FIGURE 1. The previously finished roll 115 has been moved to the right from where it is removed from the apparatus before the next roll has been built up to a large diameter.

As the paper roll 116 is built up to a diameter approaching the finished diameter shown in FIGURE 2, the enveloping

arms

42 and 43 are rotated clockwise (as viewed in FIGURES 1 and 2) by actuating the motor 63 until the

arms

42 and 43 arrive at the position illustrated in FIGURE 2. The motor63 drives the gear box 62 to rotate the shaft 61 and thus, the gears 54 and 55 so that the enveloping

arms

42 and 43 are moved to the desired position where winding is to be initiated on a new core shaft. In this position, the'web 18 runs over the driven idler rolls 85 and 84 and thence to the nip between the winding drum 19 and the roll 116.

Next, the primary arms 64 and 65 are rotated through a bottom arc to the position illustrated in FIGURE 2. The primary arms 64and 65 are rotated by the drive to the gear box 83 which through the previously described gear train causes the arms 64 and65 to move into the position for picking up the new core shaft 29.

'each of the primary arms 64 and 65 are pivoted around the points 69 by actuating the cylinders 71 until the clamp members 68 assume the position shown in phantom in FIGURE 2, in which position the core shaft 29 is grasped so that it can be carried to the web transfer position by the primary arms 64 and 65.

The core shaft 29 is provided with a sprocket 117 and support bearings 130 and 131 at either end as shown in FIGURE 6. After the core shaft has been grasped by the primary arms 64 and 65, the sprocket 117 is engaged by the core shaft accelerating chain 107 and support bearings 130 and 131 contact shaped

guides

132 and 133 as the core shaft is moved by the primary arms 64 and 65 from the position shown in FIGURE 2, to the position shown in FIGURE 3. .Thus, when the core shaft 29 approaches the position of FIGURE 3, it is rotating so that its surface speed approximately matches the speed of the drum 19 and the moving web 18 which is being guided around the core shaft 29 as illustrated. As arms 64 and 65 continue to pivot, the core shaft 29 and its wrapping web become contiguous with drum 19. Subsequently, the surface speeds equalize asfirm contact is made and shaft 29 loses contact with chain 107 and guides 132 and 133. a

The next continuous sequential step in the web winding and transfer operation is the pivoting of the

side arms

44 and 45 to the phantom line position illustrated in FIGURE 3 as Well as the full line position in FIG- URE 4. This is accomplished by means of the cams 119 and which are secured to the primary arms 65 and 64, respectively, and are positioned so that they engage the

cam follower rollers

53 and 51, respectively, to cause the

side arms

44 and 45 to be pivoted to the full line position illustrated in FIGURE 4. As the

side arms

44 and 45 move to this latter position, spring loaded knife 88 is cocked and fired severing the web 18 and causing the new leading end to be thrown into the nip between the new core shaft 29 and the winding drum 19. Simultaneously, the air pressure is reversed in air cylinder 38 causing the arm 36 to move finished roll 116 to the right as shown in phantom line position in FIGURE 4 with the same action occurring on the similar arm mechanism (not shown) on the far side of the machine. This releases the newly completed roll 116 which is moved to the right by pivoted L shaped bracket 122 attached to arm 36 as shown in FIGURE 3. Bracket 122 equipped with rollers is made to contact core shaft 29a by pivoted inclined guide 123 and fixed horizontal guide 124. The arm 111 actuated by the cylinder 113 completes the movement of completed roll 116 toward stops 121 at the end of ways 40 and 41. A similar and equivalent mechanism (not shown) on the far side of the machine assists in moving the roll 116 to that position.

The

side arms

44 and 45 are quickly restored to their original position (see phantom lines in FIGURE 4) by the springs 48 as soon as the

cam follower rollers

53 and 51 are out of contact with the cams 119 and 120.

' After winding on the new core shaft 29 has been started the enveloping

arms

42 and 43 are moved to their inactive position beneath the winding drum 19 as shown in FIGURE 5. Next, the new core shaft 29 is deposited on the ways 40 and 41 by means of the primary arms 64 and 65 as also shown in FIGURE 5. The core shaft clamp members 68 are disengaged by means of the springs 75 after the air in the cylinders 71 is released. The core shaft clamp members 68 are not released, however, until the pivoted arm 36 and the similar arm (not shown) on the far side of the machine have been returned by the air cylinder 38 and the similar means (not shown) on the far side of the machine to hold the new core shaft 29 against the winding drum 19. During this return rollers on L bracket 122 remain below guide 124 and pass through to the left of pivoting guide 123. Pivoted arm 111 is also returned to a position near the drum.

Thus, the transfer cycle has been completed and the primary arms and the enveloping arms remain inactive below the winding drum 19 while the new roll is being wound. When it again reaches the proportions of the previously wound rolls these arms with their associated mechanisms will be actuated to initiate winding on another core in the same fashion as heretofore described.

It will be obvious to the skilled worker that various forms of mechanical, pneumatic, hydraulic or electrical actuating devices may be employed for the various operating components of the device and that the actuating or operating circuits for these components will vary accordingly. However, with these teachings as a guide the necessary circuit means for carrying out the objectives of the invention will be readily apparent to the skilled worker in the art.

While particular embodiments of the invention have been illustrated and described, it will be obvious to those skilled in the art that various changes and modifications can be made without departing from the spirit and scope of the invention and it is intended to cover in the appended claims all such changes and modifications that are within the scope of this invention.

What is claimed as new is:

1. A continuous winder and transfer mechanism fo web materials comprising a pair of spaced frame elements, a winding drum having trunnion shafts supported in bearings mounted on said frame elements, web transfer means including a pair of enveloping arms mounted on each of said trunnion shafts, means for intermittently rotating said enveloping arms 360 around said trunnion shafts, at least one idler roll mounted for rotation between the extremities of said pair of enveloping arms, web severing means mounted between said enveloping arms, said means for rotating said enveloping arms being actuated so that said idler roll and web severing means are moved and thereafter stationed above the winding drum during web transfer and means for actuating said web severing means and to initiate winding on a new and empty core shaft contacting said winding drum.

2. A continuous winder and transfer mechanism for web materials comprising a pair of spaced frame elements, a winding drum having trunnion shafts supported in bearings mounted on said frame elements, web transfer means including a pair of enveloping arms mounted on each of said trunnion shafts, means for intermittently rotating said enveloping arms 360 around said trunnion shafts, a side arm pivoted to each of said enveloping arms, at least one idler roll mounted between said side arms, web evering means mounted between said side arms, said means for rotating said enveloping arms being actuated so that the side arms come to rest above the winding drum during web transfer and means for pivoting the side arms to increase arcuate web contact about the new core shaft and to actuate the web severing means and initiate Winding on an empty core shaft.

3. A continuous winder and transfer mechanism for web materials as claimed in claim 2 including drive means for said idler roll to rotate said idler roll so that its speed is approximately matched with the speed of the moving web.

4. A continuous winder and transfer mechanism for web materials as claimed in claim 3 wherein the enveloping arm rotating means are actuated to move the enveloping arms to an inactive position beneath the winding drum after winding has been initiated on the new core shaft.

5. A continuous winder and transfer mechanism for web materials as claimed in claim 2 wherein the enveloping arm rotating means are actuated to move the enveloping arms to an inactive position beneath the winding drum after winding has been initiated on the new core shaft.

6. A continuous winder and transfer mechanism for web materials comprising a pair of spaced frame elements, a winding drum having trunnion shafts supported in bearings mounted on said frame elements, means for rotating said winding drum, web transfer means including a pair of enveloping arms mounted on each of said trunnion shafts, means for intermittently rotating said enveloping arms 360 around said trunnion shafts, a side arm pivoted to each of said enveloping arms, a pair of idler rolls mounted for rotation between said side arms, web severing means mounted between said side arms, a pair of primary arms mounted for rotation around said trunnion shafts, said means for rotating said enveloping arms being actuated to move the side arms into web transfer position above the winding drum so that the idler rolls raise the moving web above the winding drum, said primary arms having means for grasping a new core shaft, said primary arms being rotated into position to grasp a new core shaft and thereafter move it into transfer position between the idler rolls and the winding drum, and means for pivoting said side arms to increase arcuate web contact about the new core shaft and to actuate the web severing means and initiate winding on the new core shaft held in transfer position by said primary arms.

7. A continuous winder and transfer mechanism for web materials as claimed in claim 6 including means for first rotating said enveloping arms to inactive position beneath said winding drum, means for thereafter rotating said primary arms to deposit the new core shaft on a pair of finished roll ways extending rearwardly from said frame elements, means for holding the new core shaft against the winding drum and means for thereafter causing the primary arms to release the new core shaft so that the primary arms can be moved to their inactive position.

8. A continuous winder and transfer mechanism for web materials as claimed in claim 7 including means for driving said idler rolls so that their surface speed is approximately matched with the speed of the moving web, and means for accelerating said new core shaft as it is moved into the web transfer position so that its surface speed is approximately matched with the speed of the moving web.

9. A continuous winder and transfer mechanism for web materials as claimed in claim 6 including means for accelerating said new core shaft as it is moved into the web transfer position so that its surface speed is approximately matched with the speed of the moving web.

10. A continuous winder and transfer mechanism for web materials as claimed in claim 6 including means for driving said idler rolls so that their surface speed is approximately matched with the speed of the moving web.

11. A continuous winder and transfer mechanism for Web material comprising spaced frame elements, a pair of finished roll ways extending rearwardly from said frame elements, a single winding drum having trunnion shafts projecting into bearing supports mounted on each of said frame elements, means for continuously feeding web material around said winding drum, a pair of primary arms spaced and mounted for rotation around said trunnion shafts, said primary arms including means for grasping a core shaft and moving it into position to initiate winding of the web thereon, a pair of enveloping arms mounted inwardly of said primary arms for free rotation on said trunnion shafts including means for rotating said enveloping arms 360 in increments as they go through a complete transfer cycle, a side arm extending from each of said enveloping arms, at least one driven idler roll extending between said side arms, web severing means extending between said side arms, means for rotating and positioning said enveloping arms so that the said idler 9 16) roll lifts the web from the winding drum for a portion of References Cited by the Examiner its arc of contact therewith, means for pivoting said side UNITED STATES PATENTS arms downwardly toward said winding drum to increase arcuate web contact with the new core shaft and to cause 11679343 8/28 Aldnch said web severing means to out said web and initiate wind- 5 2,475,480 7/49 l at 242 65 ing on a new core shaft held in web transfer position by 2,581,242 1/52 Dlckhaut 242-65 said primary arms, means for rotating said enveloping 2,703,683 3/55 EYans al 242*65 arms to a neutral position beneath said winding drum, 3,103,321 9/63 mek 24265 and means for rotating said primary arms to deposit the 3,116,031 12/63 new core shaft on the said finished roll ways to complete 10 winding of web material thereon. MERVIN STEIN Primary Examiner

Claims

1. A CONTINUOUS WINDER AND TRANSFER MECHANISM FOR WEB MATERIALS COMPRISING A PAIR OF SPACED FRAME ELEMENTS, A WINDING DRUM HAVING TRUNNION SHAFTS SUPPORTED IN BEARINGS MOUNTED ON SAID FRAME ELEMENTS, WEB TRANSFER MEANS INCLUDING A PAIR OF ENVELOPING ARMS MOUNTED ON EACH OF SAID TRUNNION SHAFTS, MEANS FOR INTERMITTENTLY ROTATING SAID ENVELOPING ARMS 360* AROUND SAID TRUNNION SHAFTS, AT LEAST ONE IDLER ROLL MOUNTED FOR ROTATION BETWEEN THE EXTREMITIES OF SAID PAIR OF ENVELOPING ARMS, WEB SEVERING MEANS MOUNTED BETWEEN SAID ENVELOPING ARMS, SAID MEANS FOR ROTATING SAID ENVELOPING ARMS BEING ACTUATED SO THAT SAID IDLER ROLL AND WEB SEVERING MEANS ARE MOVED AND THEREAFTER STATIONED ABOVE THE WINDING DRUM DURING WEB TRANSFER AND MEANS FOR ACTUATING SAID WEB SEVERING MEANS AND TO INITIATE WINDING ON A NEW AND EMPTY CORE SHAFT CONTACTING SAID WINDING DRUM.