US2890000A - Winder drive - Google Patents

Description

' June 9, 1959 E. D. BEACHLER WINDER DRIVE 2 Sheets-Sheet 1 Filed Sept. 26. 1955 EYZ E'NYZIF I z A 0 Z 2 4 L a fl 1 I a r F 1111 2 3 6% J ii i i l i A a 1 ww w 4 an E EDWARD D. BEACHLER June 9,1959

Filed Sept. 26, 1955 E. D. BEACHLER WINDER DRIVE 2 Sheets-Sheet 2 Ill fiWEHZZfiF EDWARD Q BEACHLER United States Patent WINDER DRIVE Edward D. Beachler, Beloit, Wis., assignor to Beloit Iron Works, Beloit, Wis., a corporation of Wisconsin Application September 26, 1955, Serial No. 536,432 Claims. (Cl. 242-66) This invention relates to a machine for winding web material, such as paper, to produce a roll of the desired hardness irrespective of the size or weight of the roll, and more particularly, to an improved drum winder.

Although the invention may have application in a number of fields involving the formation of rolls of flexible sheet material, the instant invention may be used to particular advantage in the formation of rolls of paper. In the so-called under drum winders the winding drums are positioned so as to define a winding nip therebetween and means are provided to guide a paper web beneath one of the winding drums and up through the winding nip whereat the web is wrapped around a core. The core with the initial wrap of web thereon rests on both of the winding drums and the winding drums are rotated so as to rotate the core and draw the web up through the winding nip and around the core thereby building up a roll of paper web on the core.

Drum winders characteristically produced wound rolls of web material which increase in hardness as the weight of the roll increases and the paper immediately adjacent the core is ordinarily only loosely wound. In the case of lightweight webs which are preferably wound to form relatively soft rolls, lifting mechanism for the cores has been provided so that the full weight of the roll does not rest on the winder drums as the roll increases in size. This, however, does not help in the case of rolls which are to be wound reasonably tightly.

In accordance with the teachings of the instant invention, means are provided for driving the winder drums at slightly difierent speeds during the initial build up of the roll in order to obtain a more firm roll portion immediately adjacent the core. After the roll has built up to appreciable weight, this will serve to compact the outer wraps of web so as to make the roll firm throughout. During start up of roll formation, however, it has been found that it is important to drive the winder drum which is not wrapped by the web (from beneath) at a slightly greater speed than the winder drum which the web passes beneath before coming up through the winding nip. In this way additional tensioning of the paper web is effected between the point of contact with the faster driven winder drum and the region of contact of the web beneath the other drum. The difiiculty here is that a change must take place in the driving of the winder drums during the windup operation so that, as the wound paper roll builds up to substantial size, the winder drums will finally be driven at substantially the same speed. One reason for this is that the rather great weight of the large substantially completely wound paper roll applies such forces against both of the winder drums that differences in peripheral speeds therebetween will result in damage to the paper roll. When the weight of the initially wound roll is smaller relative slippage between the drums and the roll can take place to a limited extent without damaging the roll; but when the roll nears its maximum size the frictional drag between the roll ice and the winder drums is too great for such slippage without damage to the roll.

In view of the foregoing it is necessary to effect a change in the winder drum speeds during the actual winding operation for each roll of paper.. The use of separate drives for the two drums with appropriate adjustments therebetween are not practical and a single main drive mechanism appears to be the only practical solution to this problem. Interconnecting drive mechanisms such as belts permitting slippage also leave something to be desired because of the typical problems which arise from continuous slippage between parts, such as slippage between belts and pulleys. The instant invention afiords a unique mechanical connection between the two winder drums involving a differential gearing assembly which is operated so as to effect an initial diiferential between the drum speeds; but the driving control of the difierential gearing assembly is arranged to yield to the driving effect provided by the increased size of the paper roll, when the size of the paper roll is such that differences in speed between the winder drums become impractical or harmful to the paper roll.

It is, therefore, an important object of the instant invention to provide an improved winder machine.

It is a further object of the instant invention to provide'an improved drive mechanism for a winder machine whereby desired differences in winder drum speeds may be obtained during an initial phase of roll buildup and such diiferentials in winder drum speed may be eliminated during the final phases of roll buildup, all by automatic operation of the drive mechanism.

Other and further objects, features and advantages of the instant invention will become apparent to those skilled in the art from the following detailed disclosure thereof and the drawings attached hereto and made a part hereof.

On the drawings:

Figure 1 is essentially a diagrammatic view in elevation of a drum winder during the initial phases of roll windup;

Figure 2 is another diagrammafical view of the drum winder of Figure 1, showing the winder during the final stages of roll buildup;

Figure 3 is a top plan view with parts shown in section of a drive mechanism embodying the instant invention; and

Figure 4 is a top plan view, with parts shown in section, of another drive mechanism embodying the instant invention.

As shown on the drawings:

In Figures 1 and 2, an underdrum winder machine, indicated generally by the reference numeral 10, is shown. The machine 10 comprises a first underwinder drum 11 and a second underwinder drum 12 defining a winding nip N therebetween. The winder drums 11 and 12 are aligned in generally parallel relationship, or generally horizontal alignment and spaced only slightly therefrom so as to permit the web W to pass freely up through the winding nip N. The web W travels from a suitable source through guide means, or under a guide roll 13, over a guide roll 14, and over a tensioning shoe 15, until the web reaches the second winder drum 12. The web W then passes beneath the second winder drum 12 following the surface thereof up through the winder nip N and then over the top of the core C, or the roll R of web already wrapped around the core C.

As shown in Figure 1, the core C has only a small roll R formed thereon. In Figure 2, the core C has a large roll R of paper wrapped thereabout.

During the initial windup shown in Figure 1, the weight of the roll R is quite smalland the paper wraps initially applied to the core and to the small roll R tend to be rather loose. Accordingly, the first drum 11 is driven at a speed greater than the speed of the second drum 12. The drums 11 and 12 are ordinarily of the same size, but it is the peripheral or surface speed of the drum 11 which is greater than the peripheral speed of the drum'1 2 during'theinitial phases of windup. This serves to tension the web from the point of contact 16 between the "drum 11 and the roll Rand perhaps the initial point of contact 17 between the web W and the second drum 12, orat least between the firstpolnt of contact 16 and a point of contact 18 at which the Web W leaves the surface of the second drum 12. In any event, this tensioning effect serves to build up a harder paper roll R during the initial phases of roll buildup.

When the paper roll finally reaches a substantlal size, such as the roll R of Figure 2, the weight of the paper roll R is applied at the points of contact 16 and 18 between the roll R and the drums 11 and 12, respectively; and this weight is very substantial so that the frictional engagement between the roll R and the drums 11 and 12 is: appreciable. In this situation, if the drum 11 was to be driven at a speed greater than the speed 'of the drum 12, injury of the paper on the outer surface of the roll R would be caused at the points 16 and/or 18. In the practice of the instant invention, the drive mechanism here provided for causing the drum 11 to rotate at a speed greater than the drum 12 yields to the frictional forces created between the roll R and the drums 11 and 12 to the extent that the torque imparted by the drive mechanism to the drum 11, which in turn is imparted to the drum 12 to the roll R, is sufficiently great to overcome the torque tending to drive the roll 12'at a different speed. Of course the drive mechanism of the instant invention can be arranged so that the main drive is connected to the second drum 12 and the effect of the roll R serves to overcome the secondary torque tending to drive the roll 11 at a different speed.

' Referring to Figures 3, it will be seen that the winder drums 11 and 12 are shown only partially in plan view, with certain other parts shown diagrammatically. The winder drum 11 has a stub shaft 20 extending therefrom through a suitable bearing 21 (shown diagrammatically) to a coupling 22, whereat it is corotatably connected to a drive shaft 23 directly connected to main drive means 24, shown here in the form of an electric motor. The main drive means '24 imparts'a substantial amount of torque to the drum 11 so as to rotate the drum 11 at a predetermined speed during the entire roll buildup. This speed is faster than the speed of the drum 12 during initial roll buildup by virtue of the mechanismwhich will be described contained within a housing outlined in dotted lines and indicated generally by the reference numeral 25, but the driving eifect of the mechanism within the housing 25 is ultimately overcome by the frictional engagement between the roll R of substantial size and the drums 11 and 12, so that the driving torque imparted to the drumll by the main drive mechanism 24 is ultimately imparted also to the second drum 12 'through the large paper roll R (which functions almost as a gear in view of the substantial frictional engagement therebetween) Referring now to the mechanism within the housing 25, it will be seen that a gear 26 corotatably mounted on the drive shaft 23 is meshed with a second gear 27 (carried on ashaft 28) which in turn is meshed with a gear 29 corotatably mounted on a shaft 30.

The shaft 30 also carries a (beveled) pinion 31 corotatably mounted thereon. The pinion 31 is, of course, in driven connection with the main drive mechanism 24 through the gears 26, 27 and 29, and the shaft 30. It will be. appreciated that bearings for the shafts 23, 28 and 30 have been omitted from the drawing for the purpose of simplifying thedrawing.

The pinion 31 is the first of three rotary gear elements which cooperate to define a differential gearing assembly. The other two elements are a (beveled) pinion gear 32 opposed to the pinion gear 31 and a planetary gear housing or frame 33, here shown as a T-shaped member having (beveled) pinion gears 33a and 33b meshing with the pinion gears 31 and 32. The planetary pinion gears 33a and 3312 are mounted at the extremities of the arms: of the T-shaped member 33 which is corotatably connected to the stem. of the T-shaped member 33 which forms a rotatable shaft 34. The pinion gear 32 opposed to the first mentioned pinion gear 31 is corotatably mounted on a sleeve 35 which carries a plain or spur gear 36 corotatably thereon. The sleeve 35 is freely rotatable on the shaft 34, so that when the shaft 34 is held against rotation, rotation of the first mentioned pinion 33 eifects rotation in the opposite direction of the opposed pinion 32, via the planetary pinions 33a and 33b, which in turn effects rotation of the sleeve 35 and gear 36 mounted thereon. The gear 36 is meshed with a gear 37 on a drive shaft 38. The drive shaft 38 is connected by a coupling 39 to a stub shaft 40 on the second drum 12 (suitably mounted in bearings 42 shown diagrammatically). It will thus be seen that the second opposed pinion 32 is in driving connection with the second drum 12 through the sleeve 35, gears 36 and 37, and the drive shaft 38.

As will be appreciated, if the planetary pinions 33a and 33b are held against rotation about the shaft 34 (although freely rotatable about the arms 34a) the input to the first pinion 31 is transmitted directly to the opposed pinion 32 and, using properly sized gears throughout the mechanism, the rate of speed at which the first drum 11 is rotated will be the same as the rate of speed at which the second drum 12 is rotated. In the instant differential gearing assembly 31, 3'2, 33, the rotary gear element 33 is the control element, and rotation of the shaft 34 carrying the control element 33 in one direction serves to impart a greater speed to the pinion 32 than the driven speed of the pinion 31, while rotation of the shaft 34 in the opposite direction will impart a slower speed to the pinion 32 than that of the driven pinion 31. The shaft 34 carrying the control element 33 is actuated by a corotatably mounted gear 43', which meshes with a smaller gear 42 corotatably mounted with a gear 44 on another shaft 45. The gear 44 meshes with'a driving gear 46 directly connected to an auxiliary drive means 47, here shown as a small motor.

It will be appreciated that, in the operation of the differential gearing assembly 31, 32, 33, the control element 33 has torque applied thereto. This torque may be merely that sufiicient to hold the shaft 34 against rotation, or the torque may be sufiicient to rotate'the shaft 34 in either direction. In any event the torque thus applied afifords the'variable control for driving the second drum 12. It will be'appreciated that the remaining gears in'the connection between the main drive shaft 23 and the secondary drive shaft 38 for the second drum 12 afford no variation in torque or speed except through the torque applied to the control element 33, assuming the gear sizes to remain fixed in each case. The torqueapplylng means (in this case the motor 47) thus applies torque to the control element 33 to impart to the second element or pinion 32 a driving torque which must, as has been explained, be yieldable to the driving torque applied to the first drum 11. Or expressed in other terms, the torque-applying means 47 imparts to the control element 33 a torquewhich, in turn, imparts a driving torque to the second drum 12, via the differential gear assembly 31, 32, 33. i This torque imparted to the second drum 12 is yieldable to the torque imparted to the first drum 11 and does, in fact, yield thereto when the size and weight of the paper roll R becomes so great that the frictional efiiect amounts to a substantially direct mechanical driving connection between the first drum 11 and the second drum 12. This is made possible by the use of a small D.C. motor 47, but it may also be I made possible by the use of braking mechanism, such as a hydraulic brake, or by generators in place of the motor 47. The essential feature is that mechanism must be provided for applying torque to the control element 33, either as positive or negative torque; and the torque thus applied is yieldable to the torque ultimately applied to the second drum 12 through the large sized paper roll R. The torque applied to the control element 33 can, of course, be varied to suit particular operations, or even varied easily during the wind up of an individual roll, although an advantageous feature of the instant invention provides for automatic operation whereby the torque thus applied is overcome at the desired roll weight and size.

Referring now to Figure 4, it will be seen that a somewhat diiferent differential gearing assembly arrangement is shown. The first winder drum 111 and the second winder drum 112 are shown only partially in plan view. The first winder drum 111 has a stub shaft 51 suitably carried in bearings 52 (shown diagrammatically) and connected through a coupling 53 to a drive shaft 54 carried on bearings 55 and 56.

Main drive mechanism 57 is provided in the form of a motor (although it will be appreciated that any other type of drive mechanism such as a combustion engine, etc. may be used) and the drive mechanism 57 is connected to a driven shaft 58. The driven shaft 58 is carried by bearings 60 and 61 and corotatably mounts a sleeve 62 carrying a spur gear 63 which meshes with a spur gear 64 corotatably mounted on the first drum drive shaft 54. In this manner, the main drive mechanism drives the first drum 111 at a desired speed.

The sleeve 62 corotatably mounted on the main drive shaft 58 carries a sun gear 65. An opposed sun gear 66 is carried on a second sleeve 67 that is freely rotatable on the main drive shaft 58. The third element of the instant differential gearing assembly is a cage 67a rotatable on bearings 68 about the shaft 58 and carrying freely rotatable planetary gears 69 which mesh with both of the sun gears 65 and 66. The cage 67a carries peripheral gear teeth 70 which mesh with a gear 71 on an auxiliary torque-applying shaft 72 carried by bearings 73 and 74. The shaft 72 is controlled by any of the previously mentioned torque-applying devices, but in this case by means of a drive unit P in the form of cone pulleys P-l (on the shaft 58) and P-Z (on the shaft 72) interconnected by on adjustable belt B. The freely rotatable sleeve 67 carrying the sun gear 66 also carries a spur gear 80 which is meshed with a gear 81 corotatably carried on a drive shaft 82. The drive shaft 82 is mounted on bearings 83 and 84 and is connected through a coupling 85 to a stub shaft 86 directly connected to the second drum 112 (and carried on a bearing 87).

It should be further noted that only a slight speed differential (relative to the speed of rotation of the rolls) is required to obtain the proper tensioning or compacting of the web in the roll R, and the power applied or absorbed by the control element in the differential gearing arrangement of the invention bears substantially the same ratio to the total power required to drive the speed controlled roll as the speed differential bears to the speed of the speed controlled roll, neglecting friction in the gearing assembly. Accordingly, the controlling element, in this case the unit P or the small motor 47, may be very small in size and power and readily controlled. If a separate speed controlled prime mover were used in conjunction with the prime mover for the speed controlled roll, such would have to be large in size and difiicult to control.

It will be understood that modifications and variations may be effected without departing from the spirit and scope of the novel concepts of the present invention.

I claim as my invention:

1. In a winder machine in which a web is formed into a wound roll, a first underwinder drum and a second underwinder drum defining a winding nip to support the wound roll therebetween, and means for driving said drums at relative rotational speeds such that there is a differential in the peripheral speeds of the drums in the initial stages of the formation of the wound roll with such speed differential being decreased as the size of the wound roll increases, said driving means comprising: main drive means, means connecting said main drive means to said first drum, a differential gearing assembly having three rotary elements, the first of said elements being connected to said main drive means, the second of said elements being connected to said second drum, the third of said elements being a control element, and rotatable driven means applying torque to said control element in a direction to tend to drive the same at a speed such as to establish a differential in the peripheral speeds of said drums.

2. In a winder machine, a first underwinder drum and a second underwinder drum defining therebetween a winding nip, a main drive imparting a predetermined torque to said first drum to rotate the same, a first rotary gear element in driven connection with said main drive, a second rotary gear element in driving connection with said second drum, a control rotary gear element arranged with said first and second elements to define a differential gearing assembly, and rotatable driven means applying torque to said control element to impart to said second element a driving torque less than said predetermined torque tending to create a speed differential between said drums.

3. In a winder machine, a first underwinder drum and a second underwinder drum defining therebetween a winding nip, a main drive imparting a predetermined torque to said first drum to rotate the same, a first rotary gear element in driven connection with said main drive, a second rotary gear element in driving connection with said second drum, a control rotary gear element arranged with said first and second elements to define a differential gearing assembly, and rotatable driven means applying torque to said control element to impart, via said differential gear assembly, to said second drum a driving torque less than said predetermined torque tending to create a speed differential between said drums.

4. In a winder machine, a first underwinder drum and a second underwinder drum defining therebetween a winding nip, means guiding a paper web beneath one of said drums and up through the nip to be wound around a core resting in the nip, a shaft rotatably mounting said first drum, a motor connected to said shaft imparting a predetermined torque to said first drum to rotate the same, a first rotary gear element in driven connection with said shaft, a second rotary gear element in driving connection with said second drum, a control rotary gear element arranged with said first and second elements to define a differential gearing assembly, and a secondary motor driving said control element to impart, via said second element to said second drum a driving torque less than said predetermined torque, tending to create a speed differential between said drums.

5. In a winder machine in which a web formed into a wound roll, a first underwinder drum and a second underwinder drum defining a winding nip to support the wound roll therebetween, and means for driving said drums at relative rotational speeds such that there is a differential in the peripheral speeds of the drums in the initial stages of the formation of the wound roll with such speed differential being decreased as the size of the wound roll increases, said driving means comprising: main drive means, means connecting said main drive means to said first drum, a differential gearing assembly having three rotary elements, the first of said elements being connected to said main drive means, the second of said elements being connected to said second drum, the

7 8 third of said elements being a control element, and rotateffects direct mechanical driving connection between the able means applying torque to said control element in t an 's ond drumsa direction to tend to drive the same at a speed such as to establish a diiferential in the peripheral speeds of said drums, the torque applied to said second drum by said 5 References Cited in the file of this patent V 'UNITED STATES PATENTS difierential gearing assembly being overcome by the 1,266,942 Hendfirson y 21, 1918 torque applied to said first drum by said main drive 1 3 MPBanl 1932 means when the Wound roll reaches such size that it Klmpton et 1935 2389,047 Heinz Nov. 13, 1945

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