US3312408A - Live collar assembly for winding machines - Google Patents

Description

April4, 1967 T. M. OWENS 3,312,408. 7

LIVE COLLAR ASSEMBLY FOR WINDING MACHINES Filed Oct. 12, 1964 2 Sheets-Sheet 1 WWI INVENTOR.

THOMAS M. OWENS Ewen- Q 26 lBb PRIOR ART April 4, 1967 T. M. OWENS LIVE COLLAfi ASSEMBLY FOR WINDING MACHINES 2 Sheets-Sheet 2 Filed Oct. 12, 1964 I INVENTOR.

THOMAS M. OWENS x N E h a m. EU .1 \%F% k BMM United States Patent Ofifice 3 ,3 12,408 Patented Apr. 4, 1967 3,312,408 LIVE COLLAR ASSEMBLY FOR WINDING MACHINES Thomas M. Owens, Wanakena, N.Y. 13695 Filed Oct. 12, 1964, Ser. No. 403,317 1 Claim. (Cl. 242-66) This invention relates to high speed winding machines, and more particularly to the type of machine having a pair of winding drums for driving and supporting the roll of material wound and a removable aligning shaft which is displaceable with respect to the drums for guiding the roll during the winding process.

In the manufacture of paper, particularly high quality paper having a coated surface, a tubular metal core, on which the paper is wound, is employed in the various coating processes. With recent improvements in paper making, higher speeds are required and longer and heavier rolls are used.

In winders particularly, modern processes require speeds twice that of other machines so that the winding process can be completed in sufficient time for the operator to remove the wound rolls and install a new core, to adjust slitters and cutters, and to do all the other work required between runs. When other machines are run at speeds up to 2,000 feet per minute, a winder must be capable of speeds up to 4,000 feet per minute. When rolls as long as twelve feet are wound, the weight of the completed roll may be as much as 2 tons, requiring more time, as well as equipment, to handle.

' Older winding machines, although equipped to handle the larger rolls, rarely can be run at speeds as high as 1,500 feet per minute.

One of the primary objects of the present invention, accordingly, is to provide means for adapting older winding machines for satisfactory operation at higher speeds as well as means in new machines adapting them for high-speed operation. Another important object is to provide means for the elimination of vibration when such machines are run at high speeds.

-. A further object is to cut the time required for unloading the machine after the roll is wound.

A still further object is to reduce the frequency of necessary repairs such as replacement of bearings.

Other objects and advantages will be apparent from the following description taken in conjunction with the accompanying drawings, in which:

FIGURE 1 is a fragmentary perspective and diagrammatic view of a winding machine in which the device of the invention may be installed; 1

FIGURE 2 is a fragmentary longitudinal sectional view of one end of the winding shaft of the machine of FIGURE 1 showing the collar usually employed to mount the core on the shaft;

FIGURE 3 is a fragmentary longitudinal sectional view of a winding shaft showing the live collar assemblies according to the invention at either end of the shaft, the assembly at one end being shown rotated 90 from that at the other end;

FIGURES 4 and 5 are end views of a collar assembly as viewed in the direction of the arrows 4-4 and 55, respectively, of FIGURE 3; and

FIGURE 6 is a greatly enlarged sectional view of the collar member and core at one end of the shaft of FIG- URE 3.

Referring particularly to FIGURE 1, the winding machine 10 includes two winding drums 11 and 12 supported side-by-side in suitable bearings on the frame 13 of the machine. The drums are driven, by means not shown, to rotate in the same direction as indicated by the arrows in FIGURE 1. The paper 14 is wound into rolls 15 on a tubular metal core 16 mounted coaxially on a winding shaft 17 by means of collars 18 at either end of the core.

The winding drums are mounted on parallel axes and are spaced apart a sufficient distance to feed the web of paper 14 up between the drums to the core 16 on which it is wound. Slitters and cutters for cutting the web into narrower widths and for cutting the web at the end of the rolls may be mounted beneath the drums.

' Shaft 17 is displaceable upward as the web 14 is wound on the rolls 15, and is held in parallel relation with the axes of the drums 11, 12 by means of verctically extending guide tracks 20 at either end of the shaft. One of two slides of carriers 21 is shown at one end of shaft 17. The slides 21 are slidably mounted on the tracks 20, 20 and carry bearing means 22 for the shaft 17.

At least one of the bearings 22 is of the split-boX-type and shaft 17 can be withdrawn from the core 16 when the rolls 15 have been wound so that the rolls on core 16 can be removed from the machine. The bearing 22, shown in FIGURE 1, has a cover or top portion 22 normally held in place by the latch 23, but which may be swung up and away from the bottom portion on the hinge 22b when the latch is released. Thrust rings 24 may be removably secured on shaft 17 on either side of the bearing 22 to prevent end play of the shaft during the winding operation.

A top-pressure or rider roll 25 is usually provided on top of the rolls 15 to give the latter a downward pressure on drums 11, 12 before the paper rolls have attained sufficient weight to have proper frictional engagement with the drums. Means for lessening the pressure of the rider roll as the weight of rolls 15 builds up is usually provided in the means, not shown, which secure roll 25 in the guide tracks 20.

In FIGURE 2 is shown the conventional means for securing the core 16 on shaft 17. A collar 18 has a slide fit on the shaft 17 and has a reduced portion 18a having a slide fit within the end of core 16. A shoulder 18b is adapted to abut against the end of core 16 when a collar is secured at each end of the core to shaft 17 by means of a setscrew 26.

It has been found that, aside from scarring the shaft 17, the set screws 26 cause an offsetting or drawing away of the axis of core 16 from its coaxial relation with the shaft as is exaggeratedly indicated in FIGURE 2. While this offsetting may not be noticeable at slower speeds, it causes excessive vibration when the winder is run at speeds exceeding 1500 feet per minute.

Furthermore, the split bearing 22 has been found to be unsuited for use at higher speeds in that it becomes worn and must be replaced at frequent intervals.

FIGURES 3-6 illustrate the live collar construction of the present invention which has been found to overcome the foregoing disadvantages. A new winder shaft 27 is provided for the machine 10 and the bearings 22 are replaced with new ones, if worn. Shaft 27 may have reduced ends to provide a shoulder 28 at either end for abutting against the bearings 22 to prevent end play without the need for thrust rings 24. To cut costs and to lighten the shaft, the latter is preferably provided with solid end portions 27a, and a tubular part 2717 connecting the end portions and comprising the major portion of the shaft. Annular rings 27c, welded or otherwise secured to the end portions 27a and tubular portion 27b, are employed to-secure the portions of the shaft 27together.

A live collar assembly 30 is provided at either'end of core 16 and each assembly includes a collar member 31 which is frictionally engaged coaxially within the end of the core 16. Member 31 has a radially projecting flange 32 at the end of the core for securing the core endwise of the shaft 27.

As' best seen in FIGURE 6, the inner end of member 31 has an inwardly tapered end 31a for facilitating its insertion within the end of the core. The remainder 31b of the portion inserted within the core 16 is given a carefully machined sliding fit with the inner wall of the core end, which is also carefully machined. To assure good frictional engagement of the member 31 with core 16, the outer end of portion 31b is given a very slight outward taper exaggeratedly shown at 31c in FIGURE 6.

The inside of the member 31 has an undercut recess, or enlarged inside diameter, at 33 and the outer race 34a of a ball or other rolling-member type bearing assembly 34 is pressed into the recess 33 so as to be firmly secured in the recess. No portion of the collar member 31 engages the shaft 27.

The inner race 34b of the bearing assembly 34 has a sliding fit with the end portion 27a of the winding shaft and is Wider than the upper race, having an annular portion 340 extending axially outward beyond the collar member 31.

Also outward of the member 31, a split-ring annular clamp 35 has its two semi-circular halves adjustably secured together by the screws 36, as shown, so as to be removably secured to the end portion 27a of the shaft 27. Clamp 35 has an annular portion 35a, also split, projecting toward the member 31 and undercut to loosely overlie the projecting portion 340 of the inner bearing race 34b.

As best seen at the right hand end of FIGURE 3 a pair of pins 37, carried in clamp member 35 midway between screws 36, have a drive fit in diametrically opposite, axially aligned holes in the clamp portion 3511 which overlies the inner race portion 340. Pins 37 project inwardly and have a slide fit in appropriate holes in the inner race member so that the clamp 35, bearing assembly 34 and collar 31 become a unitary assembly with the collar being rotatable relative to the clamp and inner race 340, see FIGURES'4 and 5.

In operation, a new core 16 is placed in position on top of drums 11 and 12 after any wound rolls have been removed. Shaft 27 is inserted in the core and the live collar assemblies 39 are slid onto the shaft at either end of the core. The outer ends of shaft 27 are then secured in bearings 22 in conventional manner. However, since bearings 34 form a part of the collar assemblies 30, a pin 40 may be passed through bearing 22 and shaft 27, as indicated in broken lines in FIGURE 1, to prevent shaft 27 from rotating.

The assemblies 30 are then inserted with their collar members 31 within the ends of core 16. The tapered ends 31a of the collar members facilitate their insertion and the taper at 31c is so slight that the flanges 33 can be forced up against the ends of core 16 as shown in FIG- URE 3.

The screws 36 are then tightened to clamp the assemblies 30 in position. The paper 14 is then started around the core 16 and the winder is started in the usual manner.

It has been found that,-since the shaft 27 does not rotate, less mass must be put in motion and higher speeds may be more quickly reached. Moreover, the decreased bearing friction provided by the roller member bearings 34, as compared to the older type bearings 22, permits the winder core 16 to be rotated by the drums 11, 12 at high speeds before a heavy load of paper wound thereon is built up and the rider roll 25 need not be employed. It has also been found that the ball bearings 34 provide such lowfriction, regardless of load or speed, that the pin 40, to keep shaft 27 from rotating, may be dispensed with as unnecessary.

The collar portion 31 is self-centering when it is insorted in the core 16 so that there is no offsetting of the core axis from the axis of rotation as is the case when the setscrew-clamped collar 18 is used. Moreover, there isno scarring of the shaft 27 when the clamps 35 are tightened. The halves of each split ring clamp 35 have extensive surface contact with shaft 27 when the screws 35 are tightened and, since the pins 37 extend parallel to the screws 36, there is no distortion of the inner race 34b.

Since the shaft 27 does not rotate, there is less mass to rotate and fewer parts to cause imbalance and hence vibration. Furthermore, any sagging or deflection of the shaft, however slight, has little effect on the rotating core, collar member and outer race which are supported only at the two ends of the shaft. The bearings 22 are used only as clamps to secure the ends of shaft 27 on the slides 21 and hence do not require replacement or renewal. Since bearings 34 can be replaced by simply supplying new assemblies 31) for the machine, work stoppages to renew bearings are eliminated. Wear due to end play or thrust in the ball bearings, 34 are minimal in contrast to that in older, split-type bearings 22. Nevertheless, shaft 27 does extend across the machine to give a rigidity to the rollaligning mechanism which would be impossible if only stub-shafts were used.

When the rolls 15 are built up on core 16, the machine is stopped, paper web 14 is cut and the core and rolls removed from the machine as follows: The split bearing 22 shown in FIGURE 1 is opened and carrier 21 lowered out of the way. The clamp 35 at the far end of the machine in FIGURE 1 is then loosened by simply backing off one of the screws 36 a quarter turn. The collar member of the live collar assembly 36 at the near end shown in FIGURE 1 is easily dislodged from engagement with the ends of core 16 by striking the protruding far end of shaft 27 with a rawhide or rubber hammer.

Shaft 27 is then withdrawn from the core 16 without loosening the clamp 35 of the near assembly 30 and the paper rolls on the core 16 may then be rolled, or otherwise removed from their position on the winding drums 11, 12. The assembly 30 at the far end is removed from the core in any convenient manner. When another core 16 is installed for the next operation of the machine, this live collar assembly 30 at the far end of the machine is the only one which has to be replaced on shaft 27.

The preferred construction of shaft 27, using the tubular portion 27b for the major length of the shaft, shown in FIGURE 3, provides means for lightening the weight of the shaft, which is usually manually installed and withdrawn, without sacrificing rigidity.

As will be apparent to those familiar with the art, the invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof, The embodiment disclosed is therefore to be considered in all respects as illustrative rather than restrictive, the scope of the invention being indicated by the appended claim.

What is claimed isz A high speed paper winding machine having a tubular core on which the paper is wound and a pair of rotatably driven winding drums for supporting the core and the paper thereon, a non-rotating shaft displaceable upward With respect to the drums; guide means at each end of the shaft for maintaining the shaft in alignment with the drums, the shaft being removably secured to the guide means; and a collar assembly at each end of the core securing the core coaxially on the shaft; each assembly including a collar member having a tubular portion frictionally and removably engaged coaxially within the core and having a radially-projecting thrust-resisting portion at the end of the core, and rolling member type bearing means having an outer race member secured coaxially within the collar member and having an inner race member slidably and coaxially mounted on the shaft, the inner race member having an annular portion projecting axially and externally of the collar member, a pair of semicircular clamp members forming a split annular ring about the shaft, screw means extending on either side of the shaft at a right angle to the shaft securing the clamp members together and removably securing them to the shaft, each clamp member having a portion overlying the projecting portion of the inner race, and pin means disposed radially on either side of the shaft and extending in a direction at a right angle to that of the screw means and pivotally securing the inner race member to the clamp members.

References Cited by the Examiner UNITED STATES PATENTS 1,821,877 9/1931 Bowne 308236 6 2,613,881 10/1952 Kottmann 24268.4 2,665,930 1/1954 Stanley 308236 X 3,079,101 2/ 1963 Rockstrom 24266 FOREIGN PATENTS 73 6,537 9/ 1955 Great Britain.

FRANK J. COHEN, Primary Examiner.

STANLEY N. GILBREATH, Examiner.

2,148,065 2/ 1939 Farmer 24268.4 10 W. S. BURDEN, Assistant Examiner.

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