US3116890A

US3116890A - Web winding apparatus

Info

Publication number: US3116890A
Application number: US128434A
Authority: US
Inventors: Ernst D Nystrand
Original assignee: Paper Converting Machine Co
Current assignee: Paper Converting Machine Co
Priority date: 1961-08-01
Filing date: 1961-08-01
Publication date: 1964-01-07
Anticipated expiration: 1981-01-07

Description

Jan. 7, 1964 E. D. NQYSYTRAND WEB 'WINDING APPARATUS 5 Sheets-Sheet 1 Filed Aug. 1. 1961 Jan. 7, 1964 E. D. NYSTRAND WEB WINDING APPARATUS 5 Sheets-Sheet 2 Filed Aug. 1. 1961 ATTORNEYS.

.Jan. 7, 1964 E. D. NYSTRAND WEB WINDING APPARATUS Filed Aug. 1, 1961 5 Sheets-Sheet 3 /N V! N 703,.

I I EP/YsZQ/WJI/MNP BYM %W 44/ Jan. 7, 1964 E. D. NYSTRAND 3,116,890

WEB WINDING APPARATUS Filed Aug. 1, 1961 5 Sheets-Sheet 1.

By m www ATTORNEYS.

1964 E. D. NYSTRAND 3,116,890

WEB WINDING APPARATUS Filed Aug. 1. 1961 5 Sheets$heet 5 gig 52 C l/VVENTO/Z.

United States Patent 3,1165% it? WENDENG APPARATUS Ernst l). Nystranc, Green Bay, Wis, assignor to Paper Qonverting Machine Gm, line, Green Bay, Win, a corporation oi Wisconsin Aug. l, 1961, gt!!- No. 128,434 is Claims. pi. 242-54 This invention relates to a Web winding apparatus and, more particularly, to a rewinder in which a web such as paper is rewound from a large roll into a number of smaller rolls.

The invention described herein can be used with a multiple stage winder of the character described in Kwitek and ystrand U.S. Patent No. 2,769,600, and reference is hereby made to that patent.

This application is a continuation-in-part of my copending application, Serial No. 724,358, filed March 27, 1958, now Patent No. 2,995,314.

Multiple stage rewinders of the character described in the above-mentioned patent and with which this invention has to do, are used in large numbers in the paperproducing industry, Paper coming from a paper-making machine is most conveniently stored in large rolls, sometimes five feet in diameter or more. Before the paper can be marketed to the ultimate consumer, as would particularly be the case in toilet tissue, toweling, etc., it is necessary to provide much smaller rolls. To make the unrolling and rerolling as economical as possible, high speed rewind rs have been developed. These machines take the paper as it is unwound at a constant rate of speed and slit it into narrower widths and rewind the narrower widths continuously on small paperboard cores. When it is considered that the paper is traveling at speeds often well in excess of 1009 feet per minute, it will be appreciated that a large number of problems arise in rewinding.

Prominent among the many problems present is that of regulating the rotational speed of the rewinder element or mandrel on which the paper is to be rewound. This could be avoided if the mandrel on which a web is rewound could be driven independently of the tension in the web, and the provision of such an apparatus constituted an important object of my earlier application.

Another object of the instant invention is to provide an improved version of the apparatus disclosed in the earlier applicationapparatus which is particularly improved relative to operations other than normal rewinding.

For example, in threading the winder (interchangeably termed rewinder), it is most desirable to limit the amount of paper waster. The first log or batch of wound rolls (if the paper web is slit on the rewinder) must be discarded. These represent loss of paper and take up space where space may be ill aiforded. Also, this is a crucial time in winder operation and the more scrap paper to be handled, the more the operator must be concerned with unproductive functions which could take his attention away from the machine.

The provision of significantly less paper in the initial winding is achieved through the instant invention and the provision of a novel mechanism for this constitutes a more specific object of this invention.

More generally, the invention has as its object the provision of novel mechanism for regulating portions of the rewinder during indexing of the mandrels other than during normal high speed continuous rewinding. As such, it permits power indexing of the mandrels when the main portion of the rewinder is inoperative. This has been found advantageous in the normal day-to-day commercial operation.

it should be pointed out that rewinders justify themselves economically because of the high output resulting from high speed, continuous operation. Anything that 3,ll6,8% Patented Jan. 7, 1%84 avoids extended down-time is especially desirable. This can be appreciated from the fact that as little as a few years ago, rewinders were normally operating at about 700 f.p.m., while now they are approaching 2000 f.p.m., and even higher speeds are contemplated. This has meant more complex machines with potential increase in troubles-troubles minimizable by the instant invention.

Other objects and advantages, both general and specific, may be seen in the details of construction and operation seen as this specification proceeds.

This invention will be explained, in an illustrative embodiment, in conjunction with the accompanying drawing, in which- FIG. 1 is a side elevational view of a winder which is equipped with a variable speed drive embodying teachings of this invention; FIG. 2 is an enlarged fragmentary view of the portion of the drive seen in the lower right-hand portion of FIG. 1; FIG. 3 is an enlarged fragmentary sectional view, taken along the line 33 of FIG. 1; FIG. 4 is an enlarged fragmentary plan view as would be seen along the line 4-4 of FIG. 1; FIG. 5 is an enlarged fragmentary cross-sectional view of one of the mandrels with which the rewinder is equipped; FIG. 6 is a view similar to FIG. 5 but showing a different mandrel arrangement; FIGS. 7 and 8 are wiring diagrams for the rewinder; and FIG. 9 is an air piping diagram.

In the illustration given, a web winding apparatus (commonly referred to as a rewinder) is designated generally by the numeral ill. Rewinder in includes a frame 11, on which is rotatably carried a multiple mandrel turret generally designated by the numeral 12. The frame ll also provides a rotatable mounting for bedroll 13, over which a web 14 travels on its way to being wound on mandrels 15.

In the illustration given, the turret 12 is provided with six web winding mandrels 15. One web winding mandrel, designated by the numeral 15a, is shown in a web winding station. The mandrel designated 15b is shown in a roll-removing station; that designated 15c in a core-receiving station; that designated 15d in a core-cutting station; that designated 15:: in a glue-applying station; and that designated 15 in a station at which the mandrel has been brought up to the proper rotational speed at which the web winding operation on that particular mandrel is ready to begin. The turret 12 as illustrated is equipped with six mandrels, and such is considered an optimum number. However, a greater or lesser number may be satisfactorily employed in the practice of this invention, provided, however, that an even number are employed.

To initiate a rewinding on a particular mandrel, for example, mandrel 15 in the illustration given, the turret 12 is rotated counterclockwise and mandrel 15f is brought near to bedroll 13 which feeds the leading edge portions of the web against the core with which mandrel i5 is equipped. During the course of winding the web on a given mandrel, the turret is rotated further so as to position the mandrel at the end of a particular winding operation in the position occupied by mandrel 15a. For this purpose, it is necessary that the turret structure be swingably mounted in order to permit a mandrel to pass the bedroll 13. An intermediate position of a mandrel between the positions designated 15f and 15a is designated by the numeral lid. All of the foregoing is well established in the paper-producing art, and, in particular, is set forth in the above-identified Patent No. 2,769,600. A full explanation of the sequence of operations as the turret is indexed can be found therein.

Each mandrel 15 is equipped with a pair of pulleys or

sheaves

17 and 18, as can be best seen in F165. 5 and 6. Sheaves 17 and 18 are grooved for the receipt of belts such as V-belts, and are identically positioned longitudinally of each mandrel. Of the two sheaves provided on each mandrel, one sheave, that designated 17, is fixed unrotatably to the mandrel as by a setscrew 19, while the other sheave, that designated 18, is journaled on mandrel for rotational movement therewith, as by bearing 20. In each adjacent mandrel, the chanacter of the seating of the sheaves 1'7 and 13 thereon is reversed. For example, in mandrels 115a, 15c and 152, the rotatable sheave 18 is outboard, while in mandrels 15b, 15d and 15;, the fixed sheave i7 is outboard. As will be described hereinafter in greater detail, this arrangement permits two belts to contact the sheaves on two adjacent mandrels simultaneously. One belt has a decreasing speed characteristic and is employed for driving the mandrel during the web winding period from station 15 to 150 and until the mandrel at 15a has its rolls completely wound. The other belt, at the time the first-mentioned belt has a decreasing speed characteristic, has an increasing speed characteristic and is employed for bringing. the mandrel immediately behind the web-winding mandrel up to the proper web-engaging speed, the mandrel brought up to speed being designated by the numeral 15 in FIG. 1. The travel of both belts can be seen in FIG. 1, in which the belts 21 are seen contacting the sheaves on mandrels 15a and 151.

Each mandrel-driving belt 21, besides being entrained in the aligned

sheaves

17 and 18 in adjacent mandrels, is entrained in a sheave 22 or 22a which is part of a variable speed drive designated generally by the numeral 23. A portion of this variable speed drive can be seen in FIG. 4, wherein two sheaves are designated 22 and 22a and are employed for varying the speed of belts 21. In addition, a number of belt-tensioning sheaves or pulleys are provided and are designated by the numerals 24, and 26 in PEG. 1, the

sheaves

24 and 25 being pivotally mounted as at 24a and 25a, respectively, while the sheave 26 is mounted in a pivotal, air cylinder loaded fashion to be described in greater detail hereinafter.

Referring now to FIG. 4, the sheave 2,2; is secured to a shaft 27 journaled in bearings 28 and 28a mounted on baseplate 11a which may be provided as part of frame 11. The sheave 22a (seen only in FIG. 4) is secured to shaft 27a which is journaled in bearings 29 and 29a. It will be seen that the shaft 27 is positioned within the shaft 27a to provide both pulleys 22 and 22a on one side of the drive 23. Each shaft 27 and 27a is also equipped with a frusto-conical member 3t} and Biia secured in non-rotative relation thereto by means of suitable setscrews and keys. The frusto-conical members 30 and 30a are oppositely oriented. In the illustration given, the larger ends are adjacent and each frusto-conical member 30 and 3th: is of considerable length in contrast to its change in diameter. Baseplate Illa also rotatably carries shaft 32 coupled to an electric clutch coupling 31, the shaft 32 being suitably journaled in bearings 33 and 34, the shaft 32 being disposed parallel to the shafts Z7 and 27a carrying the frusto-conical members 30 and 39a. Shaft 32 carries two frusto-conicai members 35 and 35a which are identical to the frusto-conic-al members 3% and 3% mounted on shafts 27 and 27a, the frusto-conical members 35 and 35:: carried by shaft 32 being oppositely oriented to each other and to the frusto-conical members 3% and 39a carried by shafts 27 and 27a. The shaft 32 is equipped with extensions going beyond the bearings 33 and 34, one for coupling to a special drive generally designated 3-6 and the other carrying a sheave 37. The sheave 37 is suitably powered through a belt 37a (see now FIG. 1) from a sheave 37b mounted on drive shaft 370 of the rewinder, drive shaft 370 being geared to bedroll 13 as at 37a.

Riding over the frusto-conical member 3%) and its radjacen-t frusto-conical member 35, is a belt 33, which conples the rotative motion of frusto-conical member 35 induced by sheave 37 to frusto-conical member 30. As can be seen in FIG. 1, the belt 38 is also entrained over a sheave 39, two of which are provided, one for each belt 33, as can be seen in PEG. 3. dual purpose in providing tension for the belts 38 through The sheaves 39 serve a the action of springs 44) on levers 4 3a fixed on shafts 43, and, by being movable in a direction parallel to the axis of shafts 32 and 27, provide for changing the position of belts 3%}. For this purpose, the sheaves 39 are rotatably mounted on stub shafts 41 (best seen in PEG. 3), which in turn are secured within arms 42 slidably carried on shafts 4-3. Shafts 43 are rotatably mounted in bearings 43a on base plate 11a.

By moving sheaves 39, the position of belts 33 can be changed and thus the speed of frusto-conical members 30 and 3th: changed. For example, by moving one sheave 39 outwardly (i.e., away from the common end of oppositelyoriented members St? and 3%), the rotationai speed of the member 35) or Site, as the case may be, associated with the pulley 39 as moved is increased. In FIG. 4, movement of the right-hand belt 38 to the right increases the speed of frusto-conical member Eda and its associated puliey 22a. Inward movement provides the reverse in speed change. This occurs in the left-hand portion of the system, since the two pulleys 3? are connected together by means of a cable and spring system generally designated %4 and in which the numeral 4-5 refers to a coiled spring connecting arm 42, as can be best seen in FIG. 3. Thus, movement to the right of the pulley 39' over which the right hand belt 38 in FIG. 4 is entrained increases the rotational speed of the right-hand frusto-conical member Eda, while movement to the right of the left-hand belt rovides an opposite change in speed in its associated frusto-conical member 39. As can be appreciated from what has gone before, the increase in speed of the righthand frusto-conical member 3% is employed to bring mandrel 15; up to web-engaging speed, while the decrease in speed of the other frusto-conical member 30 is employed to decrease the speed of mandrel 15a during the course of a rewinding operation.

To achieve movement of each pulley 39" and thereby change the speed of the two mandrels 15a and 157', speed variation control means are employed which operate through the cable and spring system designated 44 and which derives a signal from cams on and 47. Cams 46 and 47 are secured to a shaft 43 (best seen in FIG. 3), which is suitably journaled in frame it as at 59 and 56. Also secured to shaft 48 is a sprocket 51 which is suitably connected by intermediate chain 52:: to a sprocket 525 on the main indexing shaft 52.

The main indexing shaft 52 (seen only in FIG. 1 and at the extreme upper right-hand corner thereof) is em ployed in rewinders to provide timing signals for the indexing of turret 12. As in the Patent No. 2,769,600 mentioned above, this indexing of turret can be achieved through a Geneva arrangement (not shown). In any event, one rotation of shaft 52 produces, in the machine illustrated herein, a one-sixth rotation of turret 12, thus bringing another mandrel into the web winding position. It will be appreciated that the residence time of a mandrel in the fixed position in a given station does not extend for all the entire one-sixth rotation of shaft 52, but only for a fractional part thereof, it being necessary, for example, to have a mandrel remain in the station identified as the core-loading station and to which the numeral 15s is aflixed for only so long as it is necessary to mount an elongated core thereon. The remainder of the cycle of shaft 52 (corresponding to a one-sixth revolution of turret '12) is employed for bringing the mandrels into a subsequent station, i.e., mandrel 15] being moved downwardly and into engagement with bedroll I3, while mandrel 15a is being moved away from bedroll 1'3 and ultimately into the station designated by the numeral 151) for removal of the wound roll.

The chain 520 connecting main indexing shaft 52 and shaft 48 which carries sprocket 51 is so arranged as to provide a two-to-one speed reduction, so that cams 46 and '47 make only one-half a revolution for each complete revolution of the main indexing shaft 52. This provides for cams 46, for example, to reduce the speed of mandrel- 15a during winding, and on the next cycle of main indexing shaft 5.2, for bringing the speed of belt 21 to engage the sheave on mandrel 15:2 up to the required value.

Pivotally mounted on frame 11 as at 53 (see FIG. 2) are cam follower arms 54 and 55, each of which is equipped with a cam follower roller designated respectively 54a and 55a. Cam follower arm 54- is shown in a position perpendicular to the control cable 56, and in this position the portion of the cam in contact with the cam follower roller 54a is about to initiate the beginning of a winding of a new roll, i.e., the point of transfer. It is to be noted that the high point of the cam designated 46a has already passed in contact with cam follower roller 54a, so that the point of transfer of web 14 to a new mandrel 15 occurs during the rapid decrease in speed of the mandrel that is just coming into the winding station. The movement of cam follower roller 54a in following cam 46 is transmitted from cam follower arm 54 to the left-hand sheave 39 in FIG. 3 by means of cable 56. Correspondingly, the motion of cam follower roller 55a derived from cam 47 is transmitted to the right-hand sheave 39, as seen in FIG. 3, through cable 57. Each cable is suitably entrained in sheaves 58 in order to change the direction thereof, and the ends of cables 55 and 57 are secured to bolts 59 extending into sleeve portion 6% of the arms 42 which support the sheaves 39.

The ends of

cables

56 and 57 which are secured to cam follower arms 54 and 55' are equipped with turnbuckles 55a and 57a, respectively, for initial positioning of sheaves 39 at the transfer point. The upper end of each cam follower arm 54 and 55 is equipped with an elongated slot 54b and 55!) which extend transversely therethrough. Each slot 541) and 551) carries a block designated Sdc and 55c, respectively, which is positionable longitudinally of its associated slot by means of a

control knob

54d and 55d which is threadedly received within t3. threaded opening in the top of each cam follower arm 54 and 55. The ends of turnbuckles Sda and 57b not secured to the associated

cables

56 and 57 are pinned to blocks 54c and 55c, respectively. Thus, by rotating

control knobs

54d and 55d, the associated blocks 54c and 550 can be moved upwardly or downwardly in slots 54b and 55b, as the case may be, and thus change the effective length of the cam follower arms 54 and 55. For example, by rotating control knob 54d clockwise and thus moving block 540 upwardly, the length of cam follower arm 54 is effectively increased, the length of cable 56 remaining constant, so that on movement of the cam follower arm in a counterclockwise direction, greater travel of the associated sheave 39 is afforded from the same starting point. The starting point corresponds to the transfer point of the web to the mandrel 15 just entering the web winding station designated 15f, and at this point the rotational speed of the mandrel must always be the same for any given web velocity. However, it is desirable to be able to change the terminal speed, i.e., the speed of mandrel 15a at the end of a web Winding operation. Where, for example, a higher caliper (i.e., thickness) sheet is being run, it may be necessary to have a lower terminal speed than that employed on a normal caliper sheet in order to produce a roll of larger diameter. Conversely, with lower caliper sheets, the terminal speed may be required to be higher, producing a roll of smaller diameter. Both of these requisites can be met in the foregoing apparatus merely by adjusting the blocks 54c and 55c upwardly for a larger diameter roll or downwardly for a smaller diameter roll than was previously being run.

The diameter can be changed independently of the paper caliper within the limits of paper or web strength, stretch, and softness. The diameter remains constant until manual adjustment of the terminal speed is made; changing the caliper of the web does not itself change the terminal speed or diameter. Changing the diameter of the finished roll is at the discretion of the operator, and may or may not be required to compensate for sheet caliper changes, depending upon finished roll quality standards of the user of the machine.

It is believed that a brief description of the apparatus thus far described will further aid in understanding the invention, therefore such a description follows.

Continuous Operation The apparatus is shown in a condition in which a transfer winding operation is about to take place. In FIG. 1, it can be seen that very slight counterclockwise movement of turret 12 will bring mandrel 15 near to bedroll 13. At this instant, a knife transversely severs web 14 between mandrels 15 and 15a so that the glue-equipped surface of the core on mandrel 15 picks up the leading edge of web 14 for winding. Mandrel 15 is being driven through its sheave 17 by belt 21, which is entrained over the sheave 39* shown in the left-hand portion of FIG. 3 and which derives a continuous signal from cam as. Cam 46 has been contoured to provide the change in speed necessary to maintain a constant linear surface speed on mandrel 15 during the enlargement of the diameter of the roll being wound thereon. in the illustration given, cam 46 rotates counterclockwise, as can be appreciated from the arrow shown in FIG. 2, and gradually permits cam follower arm 54% to pivot counterclockwise about its pivotal mounting at 53 on frame ill. This movement of cam follower arm 54 permits the left-hand sheave 39 in FIG. 3 to move toward the right and to a position which entrains a greater portion of belt 33 about the left-hand frusto-conical element Ed in FIG. 4.

Inasmuch as belt 38 is driven by frusto-conical member 35, which is moving at a constant speed, the rightward movement of the left-hand belt 3%; in FIG. 4 reduces the speed of the ieft-hand frusto-conical member dd and thus the speed of its associated pulley 22. The pulley 22 carries belt 21 which provides the drive for mandrel 15 through its sheave 17. The same belt that is driving sheave 17 of mandrel 157 is also entrained to the position previously occupied by mandrel lie but does not affect the rotation of mandrel 15c inasmuch as the sheave 18 thereof is rotatably mounted thereon. The movement to the right of the left-hand sheave 39 is brought about through the cooperation of spring 45 and cable 57 in cooperation with the movement of cable 56, since cable 57 is being drawn to the right in FIG. 2 under the influence of the clockwise movement of cam follower arm 55 as seen in FIG. 2. The movement of cable 57 moves the right-hand sheave 39 also toward the right in FIG. 3, which changes the position of its belt 38- to a position Where more of belt 38 is wrapped about its associated frusto-conical member 35a and less about frusto-conical member 3%. This means that the associated sheave 22;: has an increasing speed characteristic. The belt 21 entrained over this sheave will be operating on sheave 1% of mandrel 15f and have no effect thereon. However, as mandrel 15c moves into the position occupied by mandrel 15f, the belt having the increasing speed characteristic will operate against the sheave 17 of the next adjacent mandrel so as to bring that mandrel up to the proper webengaging speed.

Having thus described the usual or continuous operation of the apparatus, the special features of the equipment will now be described and with particular reference to Power indexing Equipment.

Power Indexing Equipment Referring now to FIG. 4, the special drive 36 will now be described. It will be seen that the shaft 32 at its lefthand end carries a sheave 61 which is releasably coupled to the shaft 32 by means of an overrunning cam clutch 62. The bed plate 11a also supports a down-time or auxiliary motor 63 which is equipped with a sheave 6d acting 7 as a companion for the sheave 6i. E-ntrained over the sheaves 6i and 64 is a V-belt 65.

When the rewinder is operating as outlined above, the clutch 62 is disengaged and the motor 63 is shut down. Likewise, the electric clutch 311 is engaged so that the variable speed drive system 23 is driven through belt 37:: through sheave 37. When it becomes necessary to index the mandrels and where the main portion of the rewinder is shut down (the main drive shaft 370 being stopped), this can be advantageously achieved through disengaging the electric clutch 3i, engaging the cam clutch 62, and activating the auxiliary motor 63. It will be appreciated that the main indexing shaft 52 may be operated independently of the main drive shaft 370 as by motor 520 (shown only fragmentarily in FIG. 1), and this is employed for indexing the mandrels into proper position, as at the beginning of a winding operation of when it is necessary to repair the machine. The motor 52c operates through a belt drive 52d and a clutch pulley 52a to selectively rotate the shaft 52.

During this operation, the rotation of the main indexing shaft 52 causes movement of the cam shaft %as through the chain 521;. Thus, as the mandrels index, the earns 46 and 4'7 move the belts 38 along the various conical members in accordance with the program established by the contours of the cams i6 and 47.

Under such circumstances, the main drive shaft 370 of the rewinder is stopped. The gear connection G between shaft 37c and shaft 52 is rendered ineifective through the use of a clutch 52, coupled to indexing shaft drive gear 525;. When this occurs, there is no rotational movement of the cones 3%, Ella, 35 and 35a normally developed by belt 37a. This further means that the belts 38 would have to slide along stationary surfaces, which would tend to destroy the frictional engagement of the belts 38 with the various conical members 3% and 35. It will be appreciated that a predetermined amount of friction is essential so that the drive cones 35 and 35a will produce the right speed in the various mandrels. The possibility of undue stressing of the belts 38 arises when the belts are shifted over stationary conical members. This is avoided in the inventive construction through the employment of a special drive motor 63 intermittently coupled to the shaft 32 for selective rotation of the drive cones 35 and 35a. When this intermittent character is established (as where the indexing shaft 52 is operated independently of the main drive shaft 37), the electric clutch 31 is simultaneously disengaged-this precluding the drive motor 63 attempting to drive the entire rewinder through the belt 37a.

it is further believed that a brief resume of the special operation just described will be further helpful in understanding the invention, and therefore the same is set down hereinafter under the heading Power Indexing Operation.

Power Indexing Operation From time to time, it is found advantageous to specially index the turret 12; independently of operation of the remainder of the rewinder. Ordinarily, it will be appreciated that the main indexing shaft 52 is responsive to the rotational movement of the main drive shaft 37c via gears 52 and 52g, and the faster the rewinder operates, the faster the indexing must occur. When the main indexing shaft 52 is operated independently of the rewinder drive shaft 37c (as by motor 52c), there is power indexing. Although the main drive shaft 37c is stopped and the indexing shaft 52 is separately powered, the rotational motionof the indexing shaft 52 is still transmitted to the cam shaft 43 by means of the chain 52a. This results in programming of the cam systems involving earns 46 and The programming established by the earns 46 and 47 results in the shifting of the belts 38 associated with the variable speed drive 23 over predetermined courses. During this operation, the auxiliary motor 63 is coupled to i 8 the drive shaft 32 by means of a clutch and V-belt drive

system including elements

61, 62, 64 and 65. Thus, the various cone elements 3d, Etta, 35 and 35a will rotate to facilitate shifting of the belts 38 thereover. At the same time, however, the electric clutch 31 is disengaged so that the auxiliary motor 63 is not then attempting to drive the rewinder through the V-belt drive system including sheaves 37 and 37b and belt 37a.

it will be apparent, however, that there is no interference with the program established by the cams 46 and 47, since the belts 38 will follow through their predetermined courses. In this fashion, the mandrels can be advanced utilizing the least amount of paperfor example, the mandrels can be indexed at a speed corresponding to 1500 feet per minute, while the paper coming to the mandrels is traveling only a few hundred feet per minute. Power indexing, that is, rotation of the turret carrying the mandrels 15 independently of any bedroll linkage, is advantageous even when the bedroll is completely stopped. For example, this makes it possible to load cores on empty mandrels for the subsequent receipt of paper. Also, after the machine has been down for a time, the glue on cores may be dried so that it is necessary to introduce a newly-glued core into the transfer point mandrel. It is also advantageous to utilize power indexing of the mandrels independently of any bedroll operation so as to properly position a mandrel at the correct transfer point, thereby eliminating scrap.

The electrical circuitry for the auxiliary motor 63 can be seen in FIG. 7, where a power source such as 440- volt, 60-cycle, three phase is designated by the symbol V. The circuit generally designated A in PEG. 7 provides the current to a switch S. The switch S in turn energizes the starter 63a for the auxiliary motor 63 and a relay 31a. The relay 31a is interconnected with the clutch 31 to deenergize the same.

Also seen in FIG. 7 is the electrical circuitry associated with the power indexing motor 52c. The starting circuitry for the motor 520 is essentially conventional. However, the pushbutton B also energizes a relay R; which is associated with an air control circuit to be described hereinafter. The air control circuit is provided for tensioning the belts 21, and the equipment for this purpose will be described below under the heading Belt Tensioning Equipment.

Belt T ensioning Equipment Referring now to FIG. 1 and in particular to the idler pulley 26, it will be seen that this pulley is rotatably mounted on a transverse shaft 66. The shaft 66, in turn, is carried by a bracket member 67 which is pivotally mounted on the frame 11 as at 68. Provided on the frame 11 as by a pivotal mounting at 70, is an air cylinder 71. The piston rod 72 of the cylinder 71 is pivotally connected to the bracket 67 as at 73. It will be seen that extension of the piston rod 72 pivots the bracket 67 to tension the belt 21. Two such assemblies are provided, one for each belt 21.

Reference to PEG. 9 shows the two cylinders employed for tensioning the belts 21, the cylinders being designated 71 and 71a. Each cylinder is equipped with an arr line 74 and 740, respectively, which supplies pressurized fluid to one end of the cylinder-the end tending to extend the associated piston rod. The operation involved here contemplates that the cylinders 71 and 71a will always be under pressure, but that the value of the pressure will be varied so as to achieve relaxation of the belt tension or increase thereof, as desired. For this purpose, a source of compressed air 75 is provided, coupled by suitable piping to a high pressure regulator '76 and a low pressure regulator 77. Conduits from both regulators 76 and 77 communicate with three-way valve 78 and 73a associated, respectively, with cylinders 9 71 and 71a. Each of the valves '78 and 78a is equipped with a solenoid actuator '79 and 7%, respectively.

in the condition seen in FIG. 9, the solenoids 7 and 9a are energized and position the valves '78 and 78a to silver high pressure air to the cylinders 71 and 71a. This results in maximum tensioning of the belt, which is c .cterisic of th ordinary or continuous operation of the rewinder.

During power indexing, as described above, it is advantageous to relax the tension on the belt 21, especially if paper is being Thus, the previred to the mandrels. ously-rnentioned relay R is provided, the relay R being 've to open the contacts C of HS. 8. In FIG. 8, the wiring diagram associated with the solenoid valves 79 79a is shown, power for the valves coming from a source V in ordinary Operation, the contact C as well as contacts C an C are closed, so that the solenoids '79 and 7% are energized and the cylinders 71 and 71a communicated with high pressure regulator 76 (see PEG. 9). However, when the pushbutton B (see 1G. 7) is pushed, both solenoids are deenergizcd and the valves 73 and 78a are switched from the position shown in FIG. 9 so as to communicate with the low pressure reg ator W. This is the condition of the system during power ind Reduction of the tension or the belts 21 allows a slight page in the belt system so that the mandrel or mandrcls contacted by the belts are operated at wer speeds than they would it full frictional contact Were present. The degree of relaxation of belts 2 1 is only such as e nit the web speed to control the rotational speed of the mandrel in the web winding station. In other words, the incremental torque on the mandrel urging it to a faster speed is not as great as the sheet strength. For any given machinewherein sheets of substantially similar strengths are being wound from day to day--a single setting of the low pressure regulator 77 will sufiice.

The tensioning apparatus can be used advantageously aside and apart from ower indexing, as, for example, when -andrel 35a in the web winding station is winding a log T at becomes oversized as would result from wedded panel, and the like. Reference to FIG. 8 shows the electric" cir uitry for achieving selective relaxation of the t tension. in FIG. 8, there is provided a pushbutton E which can be actuated by the machine on or r upon the appeared-ice of a wad, or the like, and this results in the energization of relay R The relay R upon energi tion opens the normally closed contacts C C t on persisting until the switch S is opened by cut-oil knife (not sh wn), which indicates the completion winding of a roll on given mandrel. be seen that current is still provided to of the solenoids 79 and by wrote of a switch S ich can also be seen in EEG. 3. The switch S is actasted a earn 3 fixed to the shaft 452, which also carries the progr mining cams El.

Adva eously, the is clamped to the shaft rews so that it can be adjusted into correct ti ion with the program cams 4'7 and $1. This p c selector switch to change its selection of solenoid valves T9 or at the transfer of the web to a new mandrel. Also the cam is preferably split into two discs so the duration of the cycle that the selector r holds each set of contacts closed, can be accurately adjusted. operation of the tensioning system relative to m rel operation on an oversized log is described below r the heading Too Large Log Operation.

Too Large Log Operation ma-lly closed contacts C and C so that the cam and selector limit switch S can control the flow of electrical power to whichever of the solenoid air-operated control valves is associated with the mandrel immediately adjacent the Web winding station. in other words, the belt will be tensioned on the mandrel coming up to speed and approaching the web winding station, while the belt on the mattdrel in the web winding station is under slack tension. ln H6. 8, the mandrel in the web winding station would be associated with valve 7?.

The cam and selector switch S coordinate with the procams as and 47 to deenergize the control valve "79 which controls the air supply .to the air cylinder ii-this cylinder controlling the tension in that mandrel drive belt which is driving the mandrel 15a (the mandrel which is receiving the web being wound at the time when the operator presses the too large log pushbutton B This supplies low pressure air to the cylinder 71 and reduces the tension in the associated mandrel drive belt 21 to permit friction unwinding instead of metered winding, the other mandrel drive belt being maintained at full metered winding tension.

The transfer of the cut-off limit switch S interrupts the too large log operation by decnergizing relay R and returns the unit to normal running conditions with high pressure air supplied to both mandrel belt tension air cylindersrendering the cam and selector limit switch inoperative. Thus, the operator may again press the too large log pushbutton B if he Wishes, but there is no Way for him to signal the machine not to return to normal conditions at cut-0E.

While, in the foregoing specification, a detailed description of an embodiment of the invention has been given for purpose of explanation, it will be readily appreciated by those skilled in the that the details herein may be varied widely without departing from the spirit and scope of the invention.

I claim:

l. ln web winding apparatus for the cyclic winding of webs, a frame, an even numbered plurality of mandrels rnovably, rotatably mounted on said frame, each of said mandrels being equipped at the same longitudinal positions with a pair or" pulleys, one of said pair of pulleys being fixed to said n1 ridrel and the other rotatable thereon, the positions of said one and said other pulley being reversed in adjacent mandrels, drive means simultaneously engag able with two adjacent mandrels, s id drive means comprising a pair of belts entrained in the pulleys of said two adjacent inandrels, a mechanical variable speed drive 0pcrative to provide one belt with an increasing speed characteristic while providing the other belt with a decreasing speed characteristic, a bedroll rotatably mounted on said frame adiacent the belt-engaged mandrels, means for rotating said bedrol-l, means for indexing said mandrels, said indexing means normally being coupled to and responsive to said bedroll-rotating means, and means for indexing said mandrels independently of said bedrol -rotating means.

2. in web winding apparatus for the cyclic winding of webs, a frame, on even numbered plurality of mandrels mo /ably, rotatably mounted on said frame, each of said mandrels being equipped at the same longitudinal positions with a pair of pulleys, one of said pair of pulleys being fixed to said mandrel and the other rotatable thereon, the positions of said one and other pulley being reversed in adjacent mandrels, drive means simultaneously engageable with two adjacent mandrels, said drive means comprising a pair or" belts entrained in the pulleys of said two adjacent mandre-ls, a mechanical variable speed drive operative to provide one belt with an increasing speed characteristic while providing the other belt with a decreasing speed characteristic, Ia bedroll rotatably mounted on said frame adjacent the belt-engaged mandrels, means for rotating said bedroll, means for indexing said mandrels, said indexing means normally being coupled to and responsive to said bedroll-rotating means, means for inexing said mandrels independently of said bedroll-rotating means, said variable speed drive being releasably coupled to said bedroll-rotating means and deriving power therefrom, said variable speed drive being coupled to said mandreldndexing means and being responsive thereto, means for powering said variable speed drive independent of said bedroll-rotating means, and means for uncoupling said variable speed drive and bedroll-rotating means responsive to the powering of said variable speed drive by said independent powering means.

3. In web winding apparatus for the cyclic winding of webs, a frame, an even numbered plurality of mandrels movably, rotatably mounted on said frame, each of said mandrels being equipped at the same longitudinal positions with a pair of pulleys, one of said pair of pulleys being fixed to said mandrel and the other rotatable thereon, the positions of said one and said other pulley being reversed in adjacent mandrels, drive means simultaneously engageable with two adjacent mandrels, said drive means comprising a pair of belts entrained in the pulleys of said two adjacent mandrels, a mechanical variable speed drive operative to provide one belt with an increasing speed characteristic while providing the other belt with a decreasing speed characteristic, a bedroll rotatably mounted on said frame adjacent the beltengaged mandrels, means for rotating said bedroll, means for indexing said mandrels, said variable speed drive being equipped with a pair of programming cams adapted to vary the speed of said belt-engaged mandrels, means coupling said variable speed drive with said bedrollrotating means for transmitting power to said drive, means for selectively uncoupling said bedroll-rotating means and said drive, and means for transmitting power to said drive responsive to the means for selectively uncoupling said bedroll-rotating means and drive.

4. In web Winding apparatus, a frame, a mandrelsupporting turret rotatably mounted on said frame and operative to position each mandrel in a Web winding station, an even number of mandrels rotatably carried by said turret, each of said mandrels carrying a pair of pulleys at aligned positions along the length thereof, one of each pair of pulleys being fixed with the other rotatable With respect to the associated mandrel, corresponding pulleys in alternate mandrels being fixed and the remaining corresponding pulleys being rotatable, a pair of belts entrained in the pulleys of two adjacent mandrels, a pair of variable speed drives for said belts, one of said drives increasing the speed of its associated belt while the other of said drives decreases the speed of its associated belt, means for controlling said drives, said controlling means being operative to cause the fixed pulley on a mandrel positioned in a web winding station to be coupled to the belt having a decreasing speed characteristic, each of said variable speed drives including a conical member rotatably mounted on said frame and having a driving pulley axially secured thereto in which the said associated belt is entrained, separate powered belt means for each of said members positionable along the length thereof and transmitting motion to the conical surface thereof, the conical member associated with one belt being oppositely oriented from the conical member associated with the other of said belts, the said separate powered belt means being entrained over sheaves on said frame for movement parallel to the axes of said conical members, said sheaves being so interrelated that movement in one sheave is accompanied by corresponding movement in the other, a bedroll rotatably mounted on said frame adjacent the belt-engaging mandrels, means for rotating said bedroll, means coupling said variable speed drives with said bedroll-rotating means for transmitting power to said drives, means for selectively uncoupling said bedroll means and said drives, and means for transmitting power to said drives responsive to the means for selectively uncoupling said bedroll-rotating means and drives.

5. In web winding apparatus, a frame, a mandrelsupporting turret rotatably mounted on said frame and operative to position each mandrel in a web winding station, an even number of mandrels rotatably carried by said turret, each of said mandrels carrying a pair of pulleys at aligned positions along the length thereof, one of each pair of pulleys being fixed with the other rotatable with respect to the associated mandrel, corresponding pulleys in alternate mandrels being fixed and the remaining corresponding pulleys being rotatable, a pair of belts entrained in the pulleys of two adjacent mandrels, a pair of variable speed drives for said belts, one of said drives increasing the speed of its associated belt while the other of said drives decreases the speed of its associated belt, means for controlling said drives, said controlling means being operative to cause the fixed pulley on a mandrel positioned in a web winding station to be coupled to the belt having a decreasing speed characteristic, each of said variable speed drives including a conical member rotatably mounted on said frame and having a driving pulley axially secured thereto in which the said associated belt is entrained, separate powered belt means for each of said members positionable along the length thereof and transmitting motion to the conical surface thereof, the conical member associated with one belt being oppositely oriented from the conical member associated with the other of said belts, the said separate powered belt means being entrained over sheaves on said frame for movement parallel to the axes of said conical members, said sheaves being so interrelated that movement in one sheave is accompanied by corresponding movement in the other, a bedroll rotatably mounted on said frame adjacent the belt-engaging mandrels, means for rotating said bedroll, means coupling said variable speed drives with said bedroll-rotating means for transmitting power to said drives, means for selectively uncoupling said bedroll means and said drives, means for transmitting power to said drives responsive to the means for selectively uncoupling said bedroll-rotating means and drives, each of said sheaves being coupled by cable means to a cam follower arm pivotally mounted on said frame, and separate identical cams associated with each arm, the cam associated with one arm being reversely oriented to the cam associated with the other arm, means on said frame for indexing said mandrels, means coupling said cams with said indexing means for rotating said cams in step with the said indexing means, and means for releasably coupling said indexing means with said bedrollrotating means.

In web winding apparatus, a frame, a bedroll rotatably mounted on said frame, an even-numbered plurality of mandrels movably, rotatably mounted on said frame, a variable speed drive for said mandrels adapted to drive said mandrels independently of the tension of a web being wound thereon, means on said frame for indexing said mandrels, means for rotating said bedroll, means releasably coupling said indexing means and the means for rotating said bedroll, said drive comprising two pairs of cones mounted for rotation in said frame with the axes of the cones in each pair being disposed in parallel relation with the cones of each pair being oppositely oriented, belt means supported on each pair of cones, means" on said frame for moving each of said belt means axially of said cones in a predetermined cyclic fashion, said beltmoving means including a sheave movably supported on said frame for each of said belt means, cam means on said frame, means connecting said cam means with said indexing means, means connecting said sheaves with said cam means, said connecting means being adjustable to provide a variation in the terminal speed of the drive at the end of a winding cycle without affecting the initial speed at the beginning of a winding cycle, means on said frame coupling said bedroll-rotating means and one frame a of each pair of cones for rotating said one frame of each pair of cones, clutch means in the means connecting said bedroll-rotating means and said cones for disengaging said cones from said bedroll-rotating means, belt means coupling the other cone of each pair of cones sequentially with pairs of adjacent mandrels, each mandrel being equipped with a pair of pulleys for entrainment of said belts, one of said pulleys being rotatably mounted while the other pulley is fixed to said mandrel, the positions of said pulleys being reversed in adjacent mandrels, and motor means on said frame for rotating said one of each pair of cones responsive to said clutch means.

7. In web winding apparatus for the cyclic winding of webs, a frame, an even numbered plurality of mandrels movably, rotatably mounted on said frame, each of said mandrels being equipped at the same longitudinal positions with a pair of pulleys, one of said pair of pulleys being fixed to said mandrel and the other rotatable thereon, the positions of said one and said other pulley being reversed in adjacent mandrels, drive means simultaneously engageable with two adjacent mandrels, said drive means comprising a pair of belts entrained in the pulleys of said two adjacent mandrels, a mechanical variable speed drive operative to provide one beltwith an increasing speed characteristic while providing the other belt with a decreasing speed characteristic, a bedroll rotatably mounted on said frame adjacent the belt-engaged mandrels, means for rotating said bedroll, means for indexing said mandrels, said indexing means normally being coupled to and responsive to said bedroll-rotating means, means for indexing said mandrels independently of said bedroll-rotating means, means releasably coupling said variable speed drive to said bedroll-rotating means, means for powering said variable speed drive responsive to the uncoupling of said releasably coupling means, and means for adjusting the tension of said belts to permit the web speed to control the mandrel speed on which the web is being wound.

8. The structure of claim 7 in which said tension adjusting means comprises a pressure fluid cylinder for each belt, a tensioning pulley rotatably movably mounted on said frame for each belt and having a belt entrained therein said cylinder and tensioning pulley being operatively connected to tension the belt entrained therein, and means for varying the fluid pressure in said cylinder.

9. The structure of claim 7 in which said tension adjusting means includes means responsive to means for indexing said mandrels independently, whereby the belt tension is relaxed during independent indexing.

10. In web winding apparatus, a frame, a mandrelsupporting turret rotatably mounted on said frame operative to sequentially position each mandrel in a web winding station, an even number of mandrels rotatably carried by said turret, each of said mandrels carrying a pair of pulleys at aligned positions along the length thereof, one of each pair of pulleys being fixed with the other rotatably with respect to the associated mandrel, corresponding pulleys on alternate mandrels being fixed and the remaining corresponding pulleys being rotatable, a pair of endless belts entrained in the pulleys of two adjacent mandrels, a pair of variable speed drives for said belts, one of said drives increasing the speed of its associated belt while the other of said drives decreases the speed of its associated belt, means for controlling said drives, said controlling means being operative to cause the fixed pulley on a mandrel positioned in a web winding station to be coupled to the belt having a decreasing speed characteristic, a bedroll rotatably mounted on said frame adjacent the belt-engaged mandrels, means for rotating said bedroll, means for indexing said mandrels, said indexing means normally being coupled to and responsive to said bedroll-rotating means, and means for indexing said mandrels independently of said bedrollrotating means.

11. The structure of claim 10 in which means are provided on said frame for relieving the tension of said belts to produce slippage between said belts and pulleys.

12. In web winding apparatus, a frame, a mandrelsupporting turret rotatably mounted on said frame operative to sequentially position each mandrel in a web winding station an even number of mandrels rotatably carried by said turret, each of said mandrels carrying a pair of pulleys at aligned positions along the length thereof, one of each pair of pulleys being fixed with the other rotatable with respect to the associated mandrel, corresponding pulleys on alternate mandrels being fixed and the remaining corresponding pulleys being rotatable, a pair of endless belts entrained in the pulleys of two adjacent mandrels, a pair of variable speed drives for said belts, one of said drives increasing the speed of its associated belt while the other of said drives decreases the speed of its associated belt, means for controlling said drives, said controlling means being operative to cause the fixed pulley on a mandrel positioned in a web winding station to be coupled to the belt having a decreasing speed characteristic, a bedroll rotatably mounted on said frame adjacent the belt-engaged mandrels, means for rotating said bedroll, means for indexing said mandrels, said indexing means normally being coupled to and responsive to said bedroll-rotating means, means for indexing said mandrels independently of said bedroll-rotating means, said variable speed drives being releasably coupled to said bedroll-rotating means and deriving power therefrom, said variable speed drives being coupled to said mandrel-indexing means and being responsive thereto, means for powering said variable speed drives independent of said bedroll-rotating means, and means for uncoupling said variable speed drives and said bedrollrotating means responsive to the powering of said variable speed drives by said independent powering means.

13. In web Winding apparatus, a frame, a mandrelsupporting turret rotatably mounted on said frame operative to sequentially position each mandrel in a web winding station, an even number of mandrels rotatably carried by said turret, each of said mandrels carrying a pair of pulleys at aligned positions along the length thereof, one of each pair of pulleys being fixed with the other rotatable with respect to the associated mandrel, correspending pulleys on alternate mandrels being fixed and the remaining corresponding pulleys being rotatable, a pair of endless belts entrained in the pulleys of two adja cent mandrels, a pair of variable speed drives for said belts, one of said drives increasing the speed of its associated belt while the other of said drives decreases the speed of its associated belt, means for controlling said drives, said controlling means being operative to cause the fixed pulley on a mandrel positioned in web winding station to be coupled to the belt having a decreasing speed characteristie, a bedroll rotatably mounted on said frame adjacent the belt-engaged mandrel, means for rotating said bedroll, means for indexing said mandrels, said indexing means normally being coupled to and responsive to said bedrollrotating means, means for indexing said mandrels inde pendently of said bedroll-rotating means, means releasably coupling said variable speed drives to said bedrollro-tating means, means for powering said variable speed drives responsive to the uncoupling of said releasable coupling means, and means for adjusting the tension of said belts to permit the web speed to control the speed of the mandrel on which the web is being wound.

14. In web winding apparatus, a frame, a mandrelsupporting turret rotatably mounted on said frame operative to sequentially position each mandrel in a web winding station, an even number of mandrels rotatably carried by said turret, each of said mandrels carrying a pair of pulleys at aligned positions along the length thereof, one of each pair of pulleys being fixed, with the other rotatable with respect to the associated mandrel, corresponding pulleys on alternate mandrels being fixed and the remain ing corresponding pulleys being rotatable, a pair of endless belts entrained in the pulleys of two adjacent mandrels, a pair of variable speed drives for said belts, one

of said drives increasing the speed of its associated belt While the other of said drives decreases the speed of its associated belt, means for controlling said drives, said controlling means being operative to cause the fixed pulley on a mandrel positioned in a web winding station to be coupled to the belt having a decreasing speed characteristic, a bedroll rotatably mounted in said frame adjacent the belt-engaged mandrels, means for rotating said bedroll, programming means coupled to said variable speed drives for controlling the speed of said belt-engaged mandrels, means on said frame for adjusting the tension of said belts to produce slippage between said belts and the puileys on said belt-engaged mandrels, switch means coupled to said tension-adjusting means for actuating said tension-adjusting means for producing said slippage, and means responsive to said programming means and coupled to said tension-adjusting means for eliminating said slippage, whereby said apparatus can be selectively operated for tension-controlled winding of a given mandrel.

15. n web winding apparatus, a frame, a mandrel-supporting turret rotatabl mounted on said frame operative to sequentially position each mandrel in a web winding station, an even number of mandrels rotatably carried by said turret, each of said mandrcls carrying a pair of pulleys at aligned positions along the length thereof, one of each pair of pulleys being fixed, with the other rotatable with respect to the associated mandrel, corresponding pulleys 15 on alternate mandrels being fixed and the remaining corresponding pulleys being rotatable, a pair of endless belts entrained in the pulleys of two adjacent mandrels, a pair of variable speed drives for said belts, one of said drives increasing the speed of its associated belt while the other of said drives decreases the speed of its associated belt,

means for controlling said drives, said controlling means being operative to cause the fixed pulley on a mandrel positioned in a web winding station to be coupled to the belt having a decreasing speed characteristic, said controlling means including programming means coupled to a mandrel in the web winding station for decreasing the speed thereof at a predetermined rate, electrical means including a switch for uncoupling said programming means from said :web Winding station mandrel, and means responsive to said programming means for recoupling said programming means to said web winding station mandrel at the end of a web winding cycle whereby actuation of said switch is operative to provide tension-controlled winding for only the remaining portion of the winding cycle in which said web winding station mandrel is engaged.

References Cited in the file of this patent UNITED STATES PATENTS

Claims

1. IN WEB WINDING APPARATUS FOR THE CYCLIC WINDING OF WEBS, A FRAME, AN EVEN NUMBERED PLURALITY OF MANDRELS MOVABLY, ROTATABLY MOUNTED ON SAID FRAME, EACH OF SAID MANDRELS BEING EQUIPPED AT THE SAME LONGITUDINAL POSITIONS WITH A PAIR OF PULLEYS, ONE OF SAID PAIR OF PULLEYS BEING FIXED TO SAID MANDREL AND THE OTHER ROTATABLE THEREON, THE POSITIONS OF SAID ONE AND SAID OTHER PULLEY BEING REVERSED IN ADJACENT MANDRELS, DRIVE MEANS SIMULTANEOUSLY ENGAGEABLE WITH TWO ADJACENT MANDRELS, SAID DRIVE MEANS COMPRISING A PAIR OF BELTS ENTRAINED IN THE PULLEYS OF SAID TWO ADJACENT MANDRELS, A MECHANICAL VARIABLE SPEED DRIVE OPERATIVE TO PROVIDE ONE BELT WITH AN INCREASING SPEED CHARACTERISTIC WHILE PROVIDING THE OTHER BELT WITH A DECREASING SPEED CHARACTERISTIC, A BEDROLL ROTATABLY MOUNTED ON SAID FRAME ADJACENT THE BELT-ENGAGED MANDRELS, MEANS FOR ROTATING SAID BEDROLL, MEANS FOR INDEXING SAID MANDRELS, SAID INDEXING MEANS NORMALLY BEING COUPLED TO AND RESPONSIVE