US2119024A - Registering apparatus - Google Patents

Description

May 31, 1938. R. E. PIERCE ET AL REGISTERING APPARATUS Filed May 9, 1955 4 Sheets-Sheet 1 II I FIG. 2.

May 31, R E PlERCE ET AL REGISTERING APPARATUS Filed May 9, 1955 4 Sheets-Sheet 2 FIG3.

May 31, 1938.

R. E. PIERCE ET AL REGISTERING APPARATUS Filed May 9, 1935 M/N/ MUM I/EL 0 C/ 7') WHEN l/EAT/ CA 1.

4 Sheets-Sheet 3 May 31, 1938. R. E. PIERCE ET AL REGISTERING APPARATUS Filed May 9, 1935 4 Sheets-Sheet 4 H Hun MET-722.1%) M M m m V .Lfi IW aZ-Id .LEEH) ava ELLSvd d0 SUI-13:18 avaNl-l 99% 4 Patented May 31, 1938 UNITED STATES PATENT OFFICE REGISTERING APPARATUS Application May 9, 1935, Serial No. 20,586

2 Claims.

This invention relates to registering apparatus, and with regard to certain more specific features, to adjustable registering apparatus for spacedly imprinting or otherwise operating upon a web traveling at adjustable speeds and which is to be subsequently cut or otherwise operated upon at intervals.

Among the several objects of the invention may be noted the pro-vision of means for applying an adhesive imprint or the like to a traveling web, at suitable intervals which are to correspond to certain intervals of cutting of the web to provide predetermined blank lengths carrying the imprints, the linear speed of said web being adjustable in order to provide for different blank lengths under conditions of a constant rate of cutting; the provision of apparatus of the class described which shall operate under ideal conditions for bulk output of blanks of average length, and which shall operate well for outputs of all other blank lengths within its range; the provision of apparatus of this class which shall not require overspeeding and consequently excessive vibration of the machine on which it is mounted for producing any output; and the provision of a device of this class which is simple in construction, operation, and adjustment. Other objects will be in part obvious and in part pointed out hereinafter.

The invention accordingly comprises the elements and combinations of elements, features of construction, and arrangements of parts which will be exemplified in the structures hereinafter described, and the scope of the application of which will be indicated inthe following claims.

In the accompanying drawings, in which is 11- lustrated one of various possible embodiments of the invention,

Fig. 1 is a front elevation of the device;

Fig. 2 is a plan view;

Fig. 3 is an end elevation, viewing Fig. 1 from the right;

Fig. 4 is a vertical section taken on line 44 of Fig. 2;

Fig. 5 is a cross section taken on line 55 of Fig. 1;

Fig. 6 is a kinematic diagram corresponding to the adjustment of Fig. 1 for shortest bag and slowest speed of web;

Fig. 7 is a view similar to Fig. 6 showing another adjustment for longest bag and fastest speed; and,

Fig. 8 is an illustrative set of curves drawn on rectangular coordinance, in which lineal speeds (Cl. i l-69) of one element are plotted against angular positions of a driving arm or member.

Similar reference characters indicate corresponding parts throughout the several views of the drawings.

Referring now more particularly to Fig. 1, there is shown at numeral I a web of material which is threaded over a guide roll 3 and under impression roll 5. The web 1 moves to the right in the directionof the arrowat one of various adjusted speeds. 10 The web passes on to a tubing and cutting mechanism. The cutting apparatus on the tubing mechanism for cutting the continuous tubing into tubular blanks of predetermined length is operv ated at a constant speed but the web may be 15 drawn therethrough at various rates. Tubing and cutting apparatus of this class is known. Hence, it will be seen that if the velocity of the webbing I be changed, that the cut lengths of tubing Will'accordingly be changed. For instance, 20 with a high speed of webbing (and tubing) longer blanks will be cut by the constant-speed cutter, and with a low speed of webbing (and tubing) shorter blanks will be cut.-

It is the purpose, per se, of the present mecha- 5 nism to apply to the webbing, before it reaches the tubing and cutting machine, suitable spaced areas of adhesive which are used later in operations carried out for transforming the blanks into bags or the like. It will be understood that the 30 application of adhesive is exemplary of the operations that may be carried out by the present machine and that other impressions may be made, as with ink, or even without material, and plain indentations or other impressions or operations 5 may be accomplished.

The exemplary operating device herein described is a paste bar 1 having an operating end 61 which, is provided with a facing of adhesive upon each revolution of which, as the bar 1 40 turns, comes up to a vertical, position (from its lowermost point) to contact tangentially with the web I as it passes under the impression roll 5 to transfer the adhesive to the web I. It will be appreciated that it is desirable to have the 4,5 peripheral speed of the operating face 61 at the end of the paste bar I equal to the linear speed, or at least nearly equal to that of the web I, in order that accurate or substantially accurate impressions or application may be obtained. At 50 the same time, provision must be made for changing the peripheral speed of the end of paste bar I (when it contacts with the web I) in order to match various linear speeds at which the web I may run. It is also desirable that the paste bar 1 55 able to any of various linear speeds to provide various blank lengths and requiring-a" corresponding peripheral speed of the part that makes the impression; and for mechanicalgsimplicityj the impressing means should preferably remainv at a constant radius about its center of rotation.

One method of solution heretofore used has" been to drive the paste bar or like mechanism by a set of elliptic gears. Such a drive, when connected in the mechanical train between'the cutter and paste bar produced the desired corresponding equal periodic motion of paste bar and cutter. It also produced the varying peripheral speed of the end 61 of the paste bar .Land by ad= vancing or retarding the elliptic gear positions relatively to the remaining parts of the train, the speed of the end 61 of the paste bar 1 adjacent to the roll 5, could be brought to approximately'that oftheweb I. H The disadvantages of. the elliptic gear, construction were (1) the end 61 of the paste bar I was required to travel at its maximum' linear velocity at the maximum velocity of the web :I (thus providing maximum blankv lengths), and then when the gears were adjusted" so that the linear velocity of the end of the paste bar 1 was matched to areduced linear velocity of the web I, the end of the paste bar was still traveling at one portion of its period of movement ata speed higher than required by thetravel of the web I and at onepoint in its movement at lower speeds; and; (2) 'at'all butjmaximum and minimum fadjustments, the velocity of the end of the paste bar Twas accelerating or-decelerating in its action on the web! at'the roll 5: p 1 q The above is illustrated in FigJS'Wherein the dashed curve I indicates how-the paste bar end linear speeds vary with angular positions of the constant speed e1liptic"'gear' driving member which makes one revolution per cutof the cutter mentioned above. In view of the fact that the lengths of the abscissas represent angles of the driving mechanism and thezlatter nioves'at a constant rate, the abscissas also represent time; The ordinates represent tangential speeds of the paste bar end. Since 'acceleratiorris' defined as rate of change of velocity, any slopes on curves drawn on the coordinates .shown,'indicate'tan gential acceleration.

Referring now to the curve I representing the paste bar end linear speeds when driven from a constant speed driving mechanism through elliptic gears, it will be seen thatfto'p'roduce the proper linear speed of 290 feet perminutewhich' is proper for producing 36inch tubes, the curve must be shifted (gears set), so that thecu'rve crosses the 180 ordinateat the 290 value which means crossing the 180 ordinate with the sloping part of the curve, and this indicates an' undesirable accelerating action by thebar while ap'-* plying the impression. This curve also shows that while the velocity of the paste bar is 290 feet per minute at the 180 ordinate, the velocity of the bar isabout 430 feet per minute at about the 273 point in its cycle, and this must be, in order to take care of 54 inch tubes made at high est tube speed of 430 feet per minute with the same set of gears.

The present mechanism overcomes all the above difficulties and provides for no excessive speed of the end of the paste bar 1, substantially no vibrating action occurring under the adjustments for average. output and only slight vibration at maxim'um'and'minimum adjustments, with substantially no acceleration or deceleration at criti- "cal operating points at any adjustment.

Referring to Figs. 1-5, there is shown at numeral 9, a main drive shaft having a gear H meshed with a gear l3, the latter being mounted v.xupona countershaft l5 with a driving sprocket I1. The sprocket I"! is adjustable with respect to its ownhub"'and'shaft l5 by means of adjusting members .19. A chain 2|, driven by the sprocket I! passes over a sprocket 23 which is attached to a driving disc 25; the latter being rotatable on bearings 21 which are carried on a gudgeon 29. Theigudgeon 29 extends from a carriage 31 slidable in guides-33 on frame 39. The carriage may be locked in any adjusted position in the guides 33 by locking bolts 35 passing through slots 31 in the frame 39.

A lead screw borne in frame 39 is'controlled froma hand wheel 43, the screw being threaded into the carriage 3| to control the position there: of when the lock bolts 35 are loosened. A-pointer 45 cooperating with a scale 41 provides means for reproducing a given adjustment, the bolts 35 being again tightened after-the adjustment has beenmade. I

The chain 2| passes under 'fixed idling sprockets and over a vertically slidable and adjustable idlin sprocket 5|. The sprocket 51 is carried on an adjustable gudgeon 53 which may be tightened in. any position in a slot 55. By this means the chain 2| may be properly tensioned for anyjadjustment in position of the carriage 3|.

From the above, it will be seen that the center line of rotation ffA of the driving disc 25 may be adjustedlaterally'. o

The driving disc 25 also carries an eccentrically located gudgeon 51 upon which'is'rotatable'a slider block 59, "the latter being also slidably mounted in a' groove 6| formed in the face of the driven disc 63, the latter being attached to a shaft,65. The shaft '65 carries the paste bar I which carries at its end the face pad 61 workin against the web I where the latter is backed by the impression roll 5. In Fig. 3 is shown a paste pan 69 with a paste roller 1| dipping therein and delivering paste to the paster pad 61 by means of an intermediate roll 13. The center line B'upon which the driven disc 63 rotates is fixed with respect to the frame 39.

From the above, and from diagrammatic Figs. 6 and 7, it may be seen that the center of 'rotation of the driving disc 25 may be adjusted with respect to the center of rotation of the driven disc 63, both to the right and to the left. When the center of rotation A is set to its maximum right-handposition, such as shown in Figs; 1, 2, and 6, the end of paster bar 1 moves with minimum velocity when it reaches its upper verticaliposition, andunder these conditions moves with its maximum velocitywhen it reaches its lower'vertical position T When the center line A is set to its maximum, left-hand position, such as shown in Fig. 7, then .the paster bar 'Treache's' its maximum velocity' when in its upper vertical position"'ahd under these conditions its minimum velocity when in its lower vertical position.

It will be understood that the upward vertical position of the paster bar I is the critical one because it is at this time that the paste pad 61 contacts with the web passing under the impression roll 5. This corresponds to the heavy line at the 180 ordinate in Fig. 8.

When the center line A is set to coincide with the center line B, then the angular velocity of the paster bar I is constant throughout its entire cycle, and under these conditions, the velocity of its end B? is designed to equal that of the running web i when the latter is running at a speed for producing, in conjunction with the constantly moving cutter, the average sized blank which is 30 inches long and which constitutes most of the output of the machine. It will be seen thatunder these conditions, the mechanism is operating ideally because there is no variation in the angular velocity of the driven disc 63. In Fig. 8, the heavy horizontal straightline (curve II) at 240 feet per minute indicates the constant speed of the end 61 of the paster I under the coincident adjustment of centers- (A7! (B7,-

Fig. 8 also shows by means of curve III, the paster bar end speeds corresponding to the setting shown in Fig. 6 for lowest speed of web I. It will be seen that at the 180 point where the paste bar is slowest and effective in applying paste, there is no slope to the curve. That is, a tangent thereto is horizontal. This means that the bar is not substantially accelerating or decelerating during the application of paste to the web.

Curve IV shows the paste bar speeds corresponding to the setting shown in Fig. 7 for highest speed of web I, wherein at the 180 vertical position, the paster bar end reaches its maximum velocity. Here again it may be noted that a tangent to the curve is horizontal, indicating zero acceleration.

It is to be understood that the zero acceleration at the operating point is instantaneous, and that there is a very slight acceleration and/or deceleration under approach and recess conditions of the paster bar I, but that it is of such a small degree in the region. of the 180 angle that it is inconsequential, the curves being substantially flat over the narrow angular range during which paste is applied.

Fig. 8 also shows a curve V which crosses the 180 ordinate at the same point as curve I for the elliptical gears; that is to say, the mechanism of Figs. 6 and 7 has been adjusted to provide for the end of paste bar 1 when it is in vertical position a speed of 290 feet per minute. This curve V shows that the end of the paste bar I never exceeds the linear speed of 290 feet per minute, although in the case of the elliptical gear drive, excess was necessary at an angle of about 273. In other Words, with the present mechanism, for a given speed adjustment, the speed of the end of the paste bar is a maximum or a minimum when it is operating to apply paste and no ex- :essive high or low speed thereof is necessary at any point in the cycle. Whether it is a maximum or a minimum depends upon which side of center B the setting of center A is made.

The operation of the device is as follows:

The mechanism which drives the tuber and cutter (not shown) also drives the main drive shaft 9, thus driving the shaft 15 through gears II and I3. The sprocket I! on shaft 15 drives the sprocket 23 by way of the chain 2|, said chain having been adjusted to proper tension. The adjustment at H! is effected so that the end 61 of the paste bar 1 applies. paste at proper points on the web I, that is, With'respect to the action of cutter. When the drive is set into motion, the sprocket 23 receives a constant angular movement, thus delivering a constant angular movement to the driving disc 25 which drives the gudgeon 51 to transmit motion to the disc 63. The sliding action of the slider 59 in the groove 6! accommodates the eccentricity (if any) between centers A and B.

With the eccentricity between said centers A and B shown in Figs. 1, 2, and 6, the paster bar end velocities shown in curve III of Fig. 8 are obtained. The paster bar velocities shown in. curve IV of Fig. 8 are obtained underthe conditions of setting shown in Fig. 7. The paster bar velocities shown in curve II of Fig. 8 are obtained when the center lines A and B are coincident. The paster bar velocities shown in curve V of Fig. 8 are obtained upon adjustments intermediate the adjustments shown in Fig. 7 (curve IV) and a condition of coincidence between the centers A and B (curve II, Fig. 8).

The curve V of Fig. 8 indicates the setting for manufacturing 36-inch tube blanks. proximately per cent., of the tubes required are between the 30-inch and 36-inch blanks. The 36-inch blanks are made by a setting giving the curve V, and the 30-inch blanks are made by a setting giving the curve II. For curve II there is no eccentricity and for curve V, there is but a slight eccentricity. Thus, no, or only slight, eccentricity is necessary for producing about 80 per cent., of the product required. And even for the greatest eccentricities (for the remaining 20% of products) indicated in Figs. 6 and 7, there is substantially no accelerating condition at maximum and minimum Velocities. And, for all settings, there is no period in the cycle of the paster bar at which it has a higher velocity than that required for making a proper application of the impression to the web, in the case of adjustments of center A to the left of center B (Fig. 7); or a lower velocity than required for making proper application of the impression to the web in the case of adjustments of center A to the right of center B (Fig. 6) J The broad outlines of what is considered to be novel in the present construction are characterized in Figs. 6 and 7, although narrower novel features are shown in the other figures. The mechanism between driving and driven elements comes within the class known as quickreturn mechanisms. What is considered to be novel, under the present circumstances, in connection with this mechanism is (1) its arrangements so that maximum or minimum velocities of the bar 1 are always attained at a predetermined position coincident with the position necessary for applying an impression on the passing web; (2) the setting of the centers A and B, in such a direction and along such a line that the requirement (1) is attained at all settings of eccentricity (see line CL (Figs. 6 and 7) which is normal to the line V-T; and (3) the provision of such a setting that the center A is not only adjusted on one side of the center B but crosses the center B and goes through a range of settings on the other side thereof whereby a range of settings above the constant average is obtained, as well as a range of settings below, an-d a coincident setting.

In order to simplify'the claims, the driving member rotating about center A may be characterized as a driving crank, the driven member rotating about center B as the driven crank and the centers of rotation of these cranks may be characterized as being relatively set along such a line that a given element such as the paster bar 1 may reach a predetermined position to give maximum velocities at zero acceleration when one center is adjusted with respect to the other on one side of the latter, and to give minimum velocities at said positions when the center which is reset crosses the other to give another range of settings on the other side of the latter center.

In view of the above, it will be seen that the several objects of the invention are achieved and other advantageous results attained.

As many changes could be made in carrying out the above constructions without departing from the scope of the invention, it is intended that all matter contained in the above description or shown in the accompanying drawings shall be interpreted as illustrative and not in a limiting sense.

We claim: r

1. In apparatus of the class described, a driving crank, a driven crank, sliding means between said cranks whereby the driving crank drives the driven crank, and means for relatively resetting the centers of rotation of said cranks, said resetting being along a line passing through the centers of crank rotations, and the center of the driving crank being adapted to coincide with and be set on either side of the center of the driven crank, the latter center being fixed.

2. In apparatus of the class described, a driving crank, a driven crank, sliding means between said cranks whereby the driving crank drives the driven crank, and means for relatively resetting the centers of rotation of said cranks, said resetting being along a fixed straight line passing through the centers of crank rotations and the center of the driving crank being adapted to coincide with and be set on either side of the center of the driven crank, the latter center being fixed.

ROBERT E. PIERCE. FRANK R. LINDA.

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