Patent Publication Number: US-3879246-A

Title: Laminating apparatus and method

Description:
United States Patent [1 1 Walker 1 1 LAMllNATlNG APPARATUS AND METHOD {76] inventor: Robert J. Walker, 2942 Linden Ave., Berkeley, Calif. 94705 [22] Filed: Sept. 11, 1972 [21] Appl. No.: 287,678  
 [52] U.S. Cl 156/265; 156/519 [51] Int. Cl B32b 31/00 [58] Field of Search 156/256, 264, 265, 259. 156/519 [56] References Cited UNITED STATES PATENTS 2,254,217 9/1941 Grupe 156/265 2,289,336 7/1942 Bamford 156/519 2,726,975 12/1955 Hoag 156/259 2,990,081 6/1961 DeNeui et al.... 156/519 3,232,808 2/1966 Dries et a1. 156/519 Laminating apparatus 1 Apr. 22, 1975 11/1973 Radzins 1. 156/264 9/1966 Canno 156/259 Primary E.\&#39;aminerDouglas J. Drummond Attorney, Agent, or F inn-Stanley Bialos [57] ABSTRACT and method, particularly adapted for continuously adhesively bonding relatively narrow elongated strips of flexible material cut from a parent sheet, to a web of material and applying such strips in spaced apart relationship on the web. The parent sheet is continuously fed from a roll in one general direction to a continuously rotating vacuum drum. Cutting means, desirably rotary cutting means, contacts the drum and cuts the strips from the parent sheet in spaced apart relationship on the drum.  
 16 Claims, 33 Drawing Figures WENTE&#39;Z 8221975 SHEET UEUF 1O PHENTEB AFR 2 215. 5  
 SHEET U3UF 10 EfHEEAFRZZiSYS SHEET 0h HF 10 w rw Kw Q wow m kow g5 mop l mmm 111 II ll mow wmw MOP  
 SHEET 08 0F 10 PS-EEHTEBAFR221975 SHEET GBUF 10 hl lu Nmm VEEIHEBAFR 22 m5 SHEET 09 0F 10 Fig.22  
 Fig. 21  
 means and the drum, which controls the time intervals.  
 between intermittent contacting of the cutting means on the drum. Arcuate length of the strips on the drum is determined by the feed velocity of the parent sheet relative to the peripheral velocity of the cutting means. Adjustment of the spacing on the web can be effected by varying the web speed relative to the peripheral velocity of the drum.  
  The freely rotatable pinch roll has the same velocity as the peripheral velocity of the drum when in pinching engagement therewith. Web distortion will occur when the web velocity is not the same as the peripheral velocity of the drum. Stress caused by such distortion is relieved by spaced apart flat portions on the drum between spaced apart arcuate portions so that the web may return quickly (snap) to a neutral position intermittently during dwell periods which the flats provide. As an alternative, the pinch roll may be intermittently moved up and down, into and out of engagement-with the drum in timed relationship to provide such dwell periods.  
  In the case of non-stretchable film or other nonstretchable web material, stress is relieved by including yieldable drive means in the drive mechanism for feeding the web, in combination with means for intermittently providing dwell periods. Where spaced rows of strips are applied to the web, individual rolls of parent sheet material may be provided for the strips. As an alternative, a single roll may be provided and split into narrower bands which are subsequently spaced apart and then individually cut into the strips.  
  In an embodiment of the invention, the laminating apparatus may be used in combination with a conventional so-called side-weld bag making machine, the strips being adhered to opposite faces of the bag adjacent its mouth to form a twist type closure. Means is provided for synchronizing operation of laminating apparatus with the bag making machine.  
  In another embodiment, the apparatus may be in combination with a conventional so-called back seal terial which will assume a dead-set position when folded, are employed, as is disclosed in applicants U.S.  
 Pat. No. 3,402,052, dated Sept. 17, 1968. Metal foil,  
 desirably aluminum foil, is most suitable.  
  A problem exists in cutting said material into such narrow strips from a parent sheet, and handling the strips. To overcome this problem, a rotary vacuum drum is provided which releasably retains the strips, and on which the strips are cut by a crush-cutting action (nonshearing action). Advantageously, a continuous uninterrupted vacuum is employed, thus eliminating valving and automatic controls for applying and releasing the vacuum. Cutting means at one location, advantageously rotary cutting means, which includes at least one cutting blade, intermittently contacts the drum and cuts the parent sheet into the strips when it is held on the drum by the vacuum. The center to center line spacing between adjacent strips on the drum is. determined by the relative peripheral velocity between such rotary cutting means and the drum, while the arcuate length of the strips on the drum is determined by the velocity of the parent sheet relative to the peripheral velocity. of the cutting means.  
 type bag making machine wherein the bottom ofthe bag is welded with which the laminating apparatus is I also synchronized. In a further embodiment, the web to which the strips are applied adjacent each edge thereof,  
 is continuously wound into a roll which may be severed into lengths for the forming of twist type wrappers.  
 SUMMARY AND OBJECTS OF THE INVENTION.  
  At the time the parent sheet is&#39;t&#39;ed to the drum it has adhesive on&#34; its outer face with reference to the drum. The adhesive may be initially precoated on the parent sheet, such as a heat activatable adhesive, or an adhe- -sive coating may be applied by the apparatus, such as freely journalled so that its peripheral velocity is the same as the peripheral velocity of the drum at the location where the pinching and strip transfer occur.  
  In order to vary the center line to center line spacing between the&#34; strips on the web, provision is made to vary the feed velocity of the web relative to the peripheral velocity of the vacuum drum. At the time of pinching, such difference in drum and web velocity will cause web distortion consisting of tension or slack in the web. To prevent such distortion of the web, stress caused by tension or slack is intermittently relieved by providing flats between arcuate portions on the vacuum drum which provide dwell periods allowing the web to assume intermittently a neutral position. Such means may also be a pinch roller mounting which is automatically moved intermittently into and out of engagement against the drum, thus, providing the neutral dwell periods when the web is not being pinched. Under certain circumstances, yieldable means is provided in the drive for the web which is employed in combination with the aforementioned flats or intermit- I strips on the web can be varied by altering the speed of the web relative to the peripheral velocity of the vacuum drum. A variable speed transmission could be used for this purpose but, advantageously, the transmission is a fixed gear transmission which drives the web at a constant speed, and differential mechanism is employed which is of a common type providing up to about 6 percent continuous speed variation. For greater variation, different change gear combinations may be substituted in the fixed gear transmission while still employing the differential mechanism.  
  In one embodiment of the invention, the laminating apparatus lays the strips in elongated form at each side ofa moving web transversely to its edges with their axes substantially parallel to the vacuum drum axis (trans verse lamination), in association with a so-called sideweld bag making machine. In such machine, a web of plastic material is moved in the same direction as a fold line which provides a hinge connection for two opposite sides of the web; and the web is severed and heatsealed transversely to form the side-welds. In the invention hereof, where the laminating apparatus is employed in combination with such side-weld bag making machine, means is provided for longitudinally folding the web after the strips have been applied thereto, and feeding the thus folded web into the side-weld machine, the operation of the laminating apparatus being coordinated or synchronized with the bag making machine.  
  In another embodiment of the invention, the strips are cut in elongated form and bonded to the web with their lengthwise direction extending transversely to the axis of the vacuum drum and with groups of spaced apart strips, spaced apart longitudinally of the direction of movement of the web (longitudinal lamination). It is then folded and longitudinally sealed into tube form in a conventional bag making machine wherein the bag side edges are folds and the bottom is sealed and severed from the resultant tube.  
  The parent sheets from which the strips are formed may be on individual rolls, or it may be on a wide roll which is cut into narrower bands which are then separated and fed to the vacuum drum. For transverse lamination of the relatively narrow elongated strips, a relatively wide sheet of parent material is employed and the elongated strips are formed by crosswise cutting of the sheet with their lengthwise direction extending transversely of both the web and its direction of travel; and the vacuum drum has rows of vacuum holes extending parallel to the drum axis.  
  For longitudinal lamination, the vacuum drum has rows of circumferential vacuum holes extending transversely to the drum axis to which the individual bands are fed and which retain the cut strips thereon. For the manufacture of wrappers, the web to which transversely extending strips have been applied may be wound into a roll which is then severed by the consumer into individual sections to form the wrapper.  
  From the preceding, it is seen that the invention has as its objects, among others, the provision of an improved simple and economical apparatus and method for the lamination by adhesive bonding of elongated and narrow strips of flexible material, especially metal foil, in spaced apart relationship to a continuously moving web, particularly plastic film, either in a direction extending transversely to the direction of movement of the web or longitudinally of such direction; which are particularly adapted for the manufacture of twist type closures for wrappers, and for bags in association with conventional bag making machines; performable at a high speed; and in which the apparatus is provided with means for varying the spacing between the strips on the web and also the width of length of the strips.  
 Other objects will become apparent from the following more detailed description and accompanying drawings, in which:  
 DESCRIPTION OF FIGURES The present invention is illustrated as to particular preferred embodiments thereof in the accompanying drawings wherein:  
  FIG. 1 is a schematic plan view of a laminating and bag making machine in accordance with the present invention;  
  FIG. 1A is a partial enlarged view illustrating edge detecting mechanism;  
  FIG. 2 is a side elevational view taken in the planes 22 of FIG. 1;  
  FIG. 3 is an end elevational view taken in the direction of arrow 3 of FIG. 1;  
  FIG. 4 is a top plan view of a pair of laminating heads as employed in the mechanism of FIG. 1;  
  FIG. 5 is a schematic elevational view of a laminating head and web handling apparatus of the present invention; looking in the direction of arrow 5 in FIG. 4;  
  FIG. SA on sheet 10 is a sectional view of laminating speed control apparatus taken in the plane 5A of FIG.  
  FIG. 58 on sheet 10 is a sectional view taken in the plane 58 of FIG. 5A;  
  FIG. 6 is an enlarged longitudinal vertical sectional view of a laminating head taken in the plane 66 of FIG. 4;  
  FIGS. 6A and 6B are enlarged illustrations of cutting means of the laminating head immediately prior to and at the point of severing a foil strip for laminating;  
  FIG. 7 is a developed plan illustration partially in section illustrating drive elements and connections for a laminating head in accordance with the present invention;  
  FIG. 8 is a schematic perspective view illustrating the relationship of certain of the drive means of the present invention;  
  FIGS. 9, 10, 11 and 12 are enlarged partial schematic sectional illustrations of actual laminating steps with the apparatus illustrated in FIG. 6;  
  FIG. 13 is a longitudinal elevational view partially in section of a conventional differential drive mechanism as may be employed in the present invention;  
  FIG. 13A is a sectional view taken in the plane 13A of FIG. 13;  
  FIG. 14 is a schematic perspective illustration of speed control means as may be employed with the differential of FIG. 13 to control the feed speed of a web to the laminating heads of the present invention;  
  FIG. 15 is a perspective view of web folding mechanism as may be employed between the laminating mechanism and bag making machine of the present invention;  
 FIG. 16 is a longitudinal view partially in section of I a vacuum drum of the laminating head of the present invention;  
  FIG. 17 is a central longitudinal sectional view of the foil feed roll of FIG. 6;  
  FIG. 18 is a schematic illustration of a hot melt adhesive applicator and associated mechanism in accordance with the present invention;  
  FIG. 19 is a schematic illustration of conventional back seal type (bottom-weld) bag manufacture;  
  FIG. 20 is a schematic perspective illustration of alternative foil handling and laminating apparatus in accordance with the present invention; 5  
  FIG. 21 is a partial side elcvational view of the pinch roller and vacuum drum engagement in the embodiment of FIG. 20&#39;,  
  FIG. 22 is a partial schematic end elevational view of the vacuum drum and pinch roller of the embodiment of FIG. 20, looking in the direction of arrow 22 in FIG. 21;  
  FIG. 23 is a perspective illustration of a side-weld bag as may be formed in carrying out the present invention;  
  FIG. 24 is a perspective illustration of a bottom-weld bag as may be formed in carrying out the present inventron;  
  FIG. 25 is a perspective illustration of a wrapper sheet formed in accordance with the present invention;  
  FIG. 26 is a perspective illustration of the wrapper sheet of FIG. 25 secured about an object;  
  FIG. 27 is a schematic plan view of laminating and handling equipment producing the sheet of FIG. 25; and  
  FIG. 28 on sheet 6 is a schematic illustration of what may be termed a yieldable drive mechanism applicable to the apparatus of the present invention wherein a non-stretchable web is laminated in the apparatus.  
 DESCRIPTION OF PREFERRED EMBODIMENT The present invention is particularly applicable to the laminating of flexible elongated strips, such as a metallic foil, to a flexible web of film, such as, for example, stretchable polyethylene film or non-stretchable biaxially oriented polyester film, for the manufacture of bags with twist type closures as disclosed in applicants aforementioned US. Pat. No. 3,402,052, or for the manufacture of wrappers disclosed in applicants copending application, Ser. No. 261,315, filed June 9, I972, for Wrapper For Comestibles Or The Like, And Method And Package Thercfor. The strips are capable of assuming a dead set position when folded, to thus provide a tight closure by interlocking.  
  However, the invention has a wide range of applicability in laminating by adhesive bonding other types of strips to webs. The utility of the resultant product has been briefly noted above and is again commented upon in connection with certain figures in the drawings. There are encountered certain problems in the application of narrow, elongated, small pieces of flexible material, such as foil, to a moving web, and the mechanism of the present invention is particularly directed to the facile accomplishment of such application or lamination. and to overcoming the problems associated therewith.  
  Referring now to FIGS. 1 through 3, there will be seen to be illustrated therein mechanism for affixing or laminating small elongated strips of foil 51 to a moving web 52 of a thin plastic film for the production, for example, of thin film bags or sheets having the foil strips thereon in particular predetermined spaced apart locations. In FIGS. 1. through 3 there is illustrated means for producing conventional side weld bags having foil strips disposed about the bag mouth and extending lonwhere the web is folded longitudinally and the direction of travel changed by a plow mechanism 59 for feeding the folded web longitudinally in the direction of the fold into a conventional side weld bag making machine 61. In this embodiment of the present invention the bag making machine 61 receives the web from the laminating unit and through the conveyor means. The plow mechanism 59, as illustrated in FIG. 15 will be seen to be comprised as a top roller 62 over which the web passes with a pair of closely adjacent parallel rollers 63 disposed below the top roller perpendicularly thereto at the center of the web. A V-shaped plate 64 is disposed with the end thereof extending from the upper roller 62 downward and away from such roller. The point of the plate 64 is disposed adjacent the far end of the pair of transversely disposed rollers 63. The web 52 is drawn over the plate 64 and and downwardly between the rollers 63 to thus fold the web in half and this folded web is then passed about a further roller 66 to enter the bag making machine 61.  
  The bag making machine 61 is a conventional socalled side weld bag making machine, and includes a plurality of rollers, including pinch rollers 71, between which the laminated web is passed. Conventional cutting and sealing means 72 are provided for transversely cutting the folded web and sealing the cut folded edges to form a succession of bags generally indicated at 73, having, as shown in FIG. 23, a bottom formed with a fold 293 and sealed side edges 292.  
  One of the problems of handling a web of material 52 fed from a laminating unit 56 is the necessity of maintaining edge alignment of the web. This is herein accomplished by the provision of a conventional edge guide vacuum sensor 74 illustrated in FIG. 1A as comprising inner and outer vacuum holes to produce control signals upon variation of the web edge a predetermined amount from a desired position as the web moves past the sensor. The laminating unit 56 is mounted for transverse movement upon V-shaped rails 76 by caster wheels 77 each formed with a peripheral V-groove fitting the V-shaped rail. The laminating unit is rigidly affixed by brackets 83 to an unwind stand 78 which is used with a bag making machine, and which has freely rotatable rollers extending thereaeross. Stand 78 is mounted upon slide rails 79 on base 81 for controlled lateral movement together with the laminating unit 56. The web leaving the laminating unit passes about rollers on the unwind stand and thence about roller 62 on the V-former shown in FIG. 15 which is disposed in fixed position. The edge guide sensor 74 produces signals indicating lateral movement of the web in either direction from a predetermined edge line, with such signals being transmitted to conventional edge guide control means 82, which is connected to the conventional unwind stand and through brackets 83 to the laminator to move same laterally in either direction to the extent required to maintain the web centered in passage through edge guide sensor 74.  
  Considering now the laminating unit 56 and referring to FIGS. 4 and 5 there will be seen to be illustrated one preferred embodiment of the laminating apparatus. It is noted at this point that numerous variations and modifications of the present invention are possible and thus the illustrations of FIGS. 4 and 5 relate only to one embodiment. For example, in FIG. 4 there are shown two laminating heads 53 and 54 for the purpose of applying foil strips to opposite edges of a web passing through the laminating unit. However, it is noted that these strips may also be applied in accordance with the present invention in a manner generally illustrated in FIG. and described subsequently. Additionally, the embodiment of FIGS. 4 and 5 employs a foil strip hav ing a heat activatable adhesive coating on one side thereof, and alternatively, the strips may be affixed to the web by a hot melt operation by employing for example, structures such as illustrated in FIG. 18 of the drawings. At least certain other variations in the embodiment of the present invention illustrated in the FIGS. 4 and 5 are noted in the course of the description thereof.  
  A flexible laminating material, such as a parent sheet of metal foil 86, is provided on a rotatably mounted supply roll 87 and fed about a plurality of rotatable guide rollers 88 and thence about a drive roll 89 with a spring pressed pinch roll 91 pressing against sheet 86 as it passes about the drive roll for withdrawing the sheet from supply roll 87. The sheet is passed from the drive roll 89 to a vacuum laminating drum 92 where it is cut into strips by a cutter roller 93 having cutting blades engaging the surface of the vacuum drum 92, as is subsequently described in more detail. Strips 51 cut from the parent sheet 86 are carried by vacuum drum 92 into engagement with web 52 passing over a freely rotatable laminating pinch roll 94 disposed to press the web against arcuate portions on the vacuum drum to be described. Adhesion of the strips to the moving web may be accomplished with a variety of different types of adhesives, such as, for example, heat activatable adhesive precoated on the foil or a liquid adhesive applied by the apparatus.  
  The web of film 52 is fed from rotatably mounted supply roll 57 between film drive and pinch rolls 96 and 97, respectively, and thence over the laminating pinch roll 94 to pass through a dancer mechanism 98 and thence about a guide roller 99 out of the laminating unit 56. Dancer mechanism 98 is provided for controlling the web feed from the laminating unit to a bag making machine and includes speed control mechanism 101 connected to control the speed of a variable speed main laminatingunit drive motor 102 through a gear box 103. This main drive motor drives all parts of the laminating unit including the film drive roller 96.  
  Although dancer mechanisms are known in the art, it is believed of interest at this point to briefly comment upon the mechanism 98 of FIG. 5. This dancer mechanism 98 includes a pair of parallel arms 106 pivotally mounted on opposite sides of a frame 107 carrying the web rollers. A pair of freely rotatable rollers 108 and 109 is mounted between the pivotally mounted arms 106 with the web passing beneath the lower roller 108 and over the upper roller 109. The arms 106 are spring loaded as by means of springs 111 to tension the tops of the arms toward the laminating pinch roller 94 and the web passes first about the lower dancer roller 108 and thence about the upper roller 109 from whence it passes into the bag making machine where it is drawn by web drive means therein from the laminating unit initially faster than it is fed by the film feed or drive roll 96. This pivots the arms 106 counterclockwise in FIG. 5 by the pull of the web and this is herein employed to control the speed of the main drive motor 102 of the laminating unit, and also stopping and starting of the laminating apparatus by pull of the web through the dancer mechanism.  
  The speed control may be accomplished by a simple speed control mechanism 101 additionally illustrated in FIGS. 5A and 5B appearing on sheet 10 of the drawings. This mechanism may simply include a pulley wheel 112 connected by a belt 113 about a wheel on the axle of the dancer mechanism arms 106 so that this pulley wheel will be angularly displaced in accordance with angular displacement of the dancer arms 106. The speed control mechanism itself may be comprised as a housing within which there is disposed a conventional speed control device 114 such as a potentiometer in the circuitry of a common silicon control rectifier variable speed motor control unit. Control device 114 has extending therefrom an operating arm 115; pulley wheel 112 is mounted on the housing by a shaft extending therethrough and carrying a pair of angularly separated arms 116 and 117 extending radially outwardly of the pulley wheel shaft in position to engage the operating arm 115 upon angular displacement of pulley wheel 112.  
  Movement of the pulley wheel will thus rotate the arms 116 and 117 in an arc to thus engage the operating arm 115 to move same to the left or right to increase or decrease the speed of the main drive motor 102. In this connection, the provision of the angularly separated arms 116 and 117 obviates hunting of main drive motor 102 which might otherwise occur by insignificant motions of dancer mechanism 98. Electrical connection from the control device 114 may be provided by electrical conductors 118. In the illustrated embodiment of the present invention counterclockwise pivoting of the dancer arms 106 will rotate the pulley wheel 112 in a counterclockwise direction to thus swing the arm 117 to the left in FIG. SE to engage the operating arm 115 and speed up main drive motor 102. This will then feed the web of film at a slightly greater rate to thus return the dancer mechanism to normal position and, consequently, swing the arms 116 and 117 back to a neutral position such as illustrated. Clockwise rotation will produce slowing of the motor drive.  
  Considering now actual lamination of foil strips to a moving web of plastic film, or the like, reference is made to FIGS. 6, 6A and 68. An individual laminating head 54 includes the rollers, drums and the like described in connection with FIG. 5 in general, mounted for rotation between a pair of parallel vertically disposed side plates 121 with integral crosspieces 122 forming a rigid frame. The laminating unit 54, for example, is slidably mounted upon a pair of transverse shafts secured to the frame 107, so that the lateral position of the laminating heads may be adjusted to laminate strips in predetermined relation to the edges of film 52 passed beneath the laminating heads.  
  The parent sheet of foil 86 is withdrawn from foil supply roll 87 by driven rotation of the driver roller 89. The foil pinch roll 91 is mounted for free rotation upon pivoted arms 123 biased by one or more springs 124 to urge the pinch roll against the foil passing about the drive roll 89. Pinch roll 91 preferably has a rubber cover, as illustrated. The foil passes from drive roll 89 to vacuum drum 92 which is rotated by means described below. In the embodiment of the invention illustrated in FIG. 6, it is desired to cut narrow transverse strips 51 from the foil sheet 86 and to this end the vacuum drum 92 is provided with spaced axially extending rows of vacuum openings 126 about the periphery of vacuum drum92. Foil engaging the vacuum drum will be held flat upon the surface thereof and successive strips of foil are cut from the sheet on the drum by cutter blades 127 mounted on the rotatable cutter roll 93.  
  In FIG. 6 there is illustrated six blades 127 on the cutter roll 93 and these blades may be mounted on the roll, as illustrated in FIG. 6A, for example, by placing each blade in a peripheral groove in the roll together with a clamp bar 128 and tightening a set screw 129 against the clamp bar. This provides means for adjusting the blades for contact with the drum. The vacuum drum 92 and cutter roll 93 are driven to rotate in synchronism, and a freely rotatable blade wiper roll 131 is provided with a soft wiping surface such as oil impregnated felt 132 in position to be lightly engaged by the tips of the blades 127 as the cutter roll 93 is rotated, for lubricating the blades.  
  In the interests of simplicity of manufacture and operation, vacuum drum 92 has a continuous uninterrupted vacuum drawn through the peripheral parallel rows of openings 126 and with the drum rotating in a clockwise direction, as indicated in FIG. 6, there is preferably provided a vacuum shield 133 extending about the lefthand portion of the drum, as illustrated, in relatively close proximity thereto and preferably carrying a flexible sheet 134 of cloth or the like secured to the lower portion of the shield and extending about the concave side thereof to be held against the rotating vacuum drum by the vacuum connections thereof in order to limit loss of vacuum on the side of the drum which is not carrying foil strips. There may be also provided a thin scraper blade 136 secured, for example, to the bottom of shield 133 and disposed to lightly engage the periphery of the vacuum drum in order to remove any foil strips that may not have been transferred to web 52 from the vacuum drum because of possible operation failure to engage pinch roll 94 against the vacuum drum by the mechanism described follows.  
  Laminating pinch roll 94 is mounted for free rotation upon a shaft 137 and preferably has a resilient&#39;cover of rubber, or the like, and a slick surface formed, for example, of a Teflon cover 138 to provide minimum web friction. Pinch roll shaft 137 is mounted upon one or more pivot arms 139 carried by a pivot pin 141 and adjusted by an eccentric mechanism 142. This mechanism 142 is provided for the purpose of adjustably fixing the position of the laminating pinch roll 94 against the vacuum drum to apply adequate pinching pressure, and to allow disengagement of the pinch roll to permit threading of the web through the laminator as well as to relieve pressure when the apparatus is shut down. For this purpose, a fixed shaft 143 is provided having a circular cam 144 eccentrically mounted thereon for rotation within a circular bearing aperture 146 in pivot arm 139. A handle 147 extending from cam 144 provides for manual rotation of the cam to thus pivot the arm 139 to move pinch roll 94 toward or away from vacuum drum 92.  
  In operation, the pinch roll is disposed in position to press web 52 passing over the pinch roll against the vacuum drum or at least portions thereof, as described later. The degree of pressure is adjustable by the eccentric mechanism 142. The strips to be successively laminated to the web have tacky adhesive coated on their outer faces with reference to the vacuum drum; consequently, the pinch roll pressure effects transfer of the successive strips to the web. In this connection, the vacuum which is maintained is insufficient to overcome the bonding strength of the tacky adhesive.  
  In the illustrated embodiment of FIGS. 6, 6A and 6B, the vacuum drum 92 has a circular exterior configuration with flat or planar portions 148 disposed between equally spaced arcuate portions 149. The vacuum connections 126 extend to the peripheral arcuate portions 149 of the vacuum drum which as the drum rotates hold successive leading edges of the foil sheet being fed to the drum for cutting into strips, as well as holding the cut strips in place until they are carried by the drum to the location of lamination onto the web at pinch roll 94. The provision of six cutter blades on cutter roller 93 and six arcuate flat portions on the vacuum drum 92 is not critical, but has been found desirable.  
  Before proceeding with a description of the laminating procedure with the apparatus illustrated in FIG. 6, it is noted that attachment of foil strips to a film is accomplished by the provision of adhesive in tacky state, herein provided upon the foil strips. As previously noted various types of adhesives may be employed, such as pressure sensitive adhesive or heat activatable adhesive. In the circumstance wherein the foil is precoated with a heat activatable adhesive, provision is herein made for heating the foil prior to lamination and maintaining the foil at a sufficiently elevated temperature upto the point of lamination so that the adhesive is tacky and bonds the foil strips to the film. In this respect, reference is made to FIGS. 16 and 17, which illustrate details of a vacuum drum and foil drive drum incorporating heating means. The foil drive drum 89 may, as illustrated in FIG. 17, be mounted for rotation upon a fixed hollow shaft 15! extending between the laminating head side plates 121 as by means of bushings 152 which may also be employed as thrust bearings to maintain the roller in position between the side plates.  
  The feed roller 89 is driven by a gear 153 connected to one end of the roller. Heating of the foil feed roller 89 may be accomplished by the provision of a heating element 154 coiled about the shaft 151 and mounted thereon. Electrical connections 156 for heater 154 may extend through an open end of the fixed shaft 151 with the wires thereof connected to opposite ends of the heater through openings in the shaft as illustrated. A conventional thermostat is employed for controlling temperature. It is noted at this point that foil feed roller 89 may be provided with heating means under those circumstances wherein it is necessary to apply heat to the foil in passage about such roller; however, for many applications of the present invention, it is either not necessary to apply heat to the foil orsuff cient heat may be applied by the vacuum drum itself.  
  Reference is now made to FIG. 16 wherein the vacuum drum 92 is illustrated as including a hollow shaft 157 extending from one end of the drum and closed at the other end of the shaft. The drum shaft 157 is journalled in the side plates 12] of the laminating unit frame, and carries a drive gear 158 secured to the shaft.  
 The peripheral vacuum openings 126 of vacuum drum 92 are connected to an end chamber 159 in the drum which communicates with the interior of hollow shaft 157. At the outer end of this hollow shaft there are provided radial openings 161 in the shaft into an annular vacuum chamber 162 having the housing thereof sealed to the shaft in rotatable relation thereto. Vacuum chamber 162 communicates through a vacuum pipe 163 to a vacuum source 164 so that there is continually drawn a vacuum through the parallel rows of vacuum openings 126 in the arcuate portions 149 of the periphery of the vacuum drum.  
  Also provided within drum 92 are electrical heater elements 166 disposed, for example, in longitudinal bores 167 in the solid material of the drum and communicating with the end chamber 159 of the drum. Electrical connections from heater elements 166 extend through this chamber 159 and through hollow shaft 157 radially outward of the shaft into connection with annular slip rings 168 mounted in an annular insulating connector block 169 secured to the shaft for rotation therewith. Exteriorly of the vacuum drum shaft there are provided a pair of fixed brushes 171 disposed in position to engage the electrically conducting slip rings 168 as the vacuum drum shaft rotates, and brushes 171 are electrically connected to a heater power source 172 for energizing heater elements 166.  
 In order to control the temperature of the vacuum drum there may also be provided one or more temperature sensors 173 disposed within the drum adjacent the periphery thereof and connected, similarly to the connection of the heater elements, through hollow shaft 157 to slip rings 174 in an insulating connector block 176. Exteriorly of the drum and shaft there are provided electrical brushes 177 engaging slip rings 174 as they rotate with the vacuum drum shaft and electrically connected to temperature control means 178 that in turn controls the output of the heater power source 172. It is again noted at this point that it may only be necessary for particular types of adhesives to provide for heating of the vacuum drum and that heating of the foil feed roll 89 is optional.  
  Considering now the general operation of the lamination unit as primarily illustrated in FIGS. and 6, at the location of the freely journalled pinch roll 94 where it presses web 52 against arcuate portions 149 of the vacuum drum, the web will be driven by the vacuum drum and thus be moved over the laminating pinch roll 94 at the same velocity as the peripheral velocity of vacuum drum 92. With the foil feed roll 89 driven at a predetermined velocity foil sheet 86 is fed to the vacuum drum. As the leading edge of the foil touches an arcuate portion 149 of vacuum drum 92 having a row of vacuum openings 126, it is gripped by the vacuum applied to such openings and held to the drum. As vacuum drum 92 rotates cutter roll 93 also rotates and in FIG. 6A there is illustrated the condition of these elements just before a strip 51 of the foil is cut from the parent sheet 86 thereof. In FIG. 6B there is illustrated the relationship of a blade 127 and vacuum drum at the instant strip 51 is cut from the parent sheet, from which it will 7 be noted that the strip is cut while it is over a row of vacuum holes 126.  
  It will be noted that the present invention provides for crush cutting on the drum in immediate proximity to a row of vacuum openings, rather than shear cutting. Actual severing of the strip from parent sheet 86 occurs by cutter blade 127 crushing the sheet to engage the vacuum drum surface, thereby cutting from the sheet a strip 51 which has necessarily been firmly gripped by the vacuum prior to its severance as shown in FIG. 6A, and maintained gripped during severance as shown in FIG. 6B. This then obviates one of the major problems in handling of very narrow elongated strips of flexible material in transverse lamination inasmuch as the strips may be as narrow as approximately A; inch in width, and the foil of very light gauge of about 0.001 to 0.002 inch (1 to 2 mils). It is to be understood that the vacuum opening 126 diameter is less than the width of a strip 51 to be cut.  
  After severance, a strip 51 cut from the sheet is retained by the vacuum of the vacuum drum as it rotates to thus move the strip around into position for engagement with web 52 which is pressed against the outer surface of the strip with reference to the drum by laminating pinch roll 94. As previously noted, a suitable adhesive is provided on the outer surface of foil strip 51. When the strip and web are pressed together this adhesive in tacky state attaches the strip to the web, and  
 thus as the web passes beyond pinch roll 94 it carriesthe strip with it. The strip is thus releasably retained on the vacuum drum, and becomes adhesively bonded to the web and is thus transferred from the vacuum drum against the force of the vacuum. The foil sheet 86, al-  
 though flexible, has sufficient rigidity that the cut leading end of the sheet adjacent the vacuum drum remains supported on the drum as is illustrated in FIG. 6B.  
  Actual lamination of a strip 51 to a web of film 52 is illustrated in FIGS. 9 and 10 wherein strip 51 held on the vacuum drum 92 by the vacuum applied through openings 126, is illustrated to approach the film as drum 92 and pinch roller 94 rotate together. It is again noted that the pinch roller 94 is journalled for free rotation and is thus driven by the vacuum drum when the I two are in engaging relationship. This relationship pertains during each period that an arcuate portion 149 of the vacuum drum is in position to engage the pinch roll through film 52 over the pinch roll. The pinch roll, being formed of a resilient material such as rubber, or the like, is actually compressed at the area of engagement with the vacuum drum as indicated in FIG. 9, and a pressure is exerted between foil strip 51 and film 52. This then transfers the foil strip from the vacuum drum to the web of film 52 by the bonding action of the adhesive.  
  The foil sheet 86 is fed toward the vacuum drum by foil feed roll 89 at a constant predetermined velocity less than the peripheral velocity of the drum, to thus dispose the same predetermined length of parent sheet upon each arcuate section 149 of the vacuum drum as the drum rotates. It is to be noted that the width (arcuate length on the vacuum drum) of each strip of foil 51 to be laminated .on the web is basically determined by the relative peripheral velocities of the foil feed drum 89 and cutter roll 93, although a synchronous fixed relationship exists between the peripheral velocities of the cutter roll and vacuum drum in order that the successive severed strips 51 will always be held by a row of vacuum holes.  
  The center line to center line spacing between strips on the vacuum drum is determined by the frequency of cutting of the strips by the cutting blades intermittently contacting the vacuum drum, as the vacuum drum rotates. In the embodiment of FIG. 6 this then is determined by the relative rotational velocity of the cutter roll with respect to the vacuum drum and the peripheral spacing of the cutting blades on the cutter roll. In  
 this embodiment these elements (the tips of the cutting blades, and the periphery of the vacuum drum) are rotated at the same peripheral velocity, and are substantially the same diameter. Further, in the embodiment of FIG. 6 if, for example, the peripheral spacing between the six tips of adjacent cutting blades is 2 inches, the center line spacing between strips 51 on the vacuum drum will be an arcuate distance of 2 inches. With every other blade omitted, the frequency of cutting becomes less, and the center to center line spacing will be increased to 4 inches; with only two oppositely positioned blades the spacing will be 6 inches; and with only one blade, the spacing will be 12 inches. Alternatively, varying the relative speed of rotation between the cutter roll and the vacuum drum will produce similar effects of varying the center to center line spacing of strips on the vacuum drum.  
  The center to center line spacing between strips affixed to the web is determined by the peripheral or circumferential spacing between strip positions on the vacuum drum and the relative velocity of the web to the vacuum drum. Thus, by varying the speed of the web, spacing of the strips on the web may be varied, such that if the average rate of travel of the web as determined by the velocity of web feed roll 96, is less than the peripheral velocity of the drum, the center to center spacing of the strips on the web will be increased as compared with their spacing on the vacuum drum prior to transfer onto the web. Conversely, if the average rate of travel of the web is more than that of the drum, the spacing of the strips on the web will be decreased.  
  It will be understood that during the repetitive intervals when the web is intermittently pressed or pinched by the arcuate portions 149 of the vacuum drum against pinch roll 94 whereby the pinch roll is intermittently driven, such differences in velocities between the web and the drum necessarily result in web tension or slack being created in that portion of the web between drive roller 96 (FIG. and pinch roll 94. In order to avoid the disadvantageous effects of tension or slack accumulating in the web, such as nonregistry of the strips relative to printed matter on the web, the flats 148 between the arcuate drum portions 149 serve such purpose by providing breaking of contact between the vacuum drum and the pinch roll 94 following each strip lamination onto the web passing over the pinch roll and whereby the web is intermittently in non-driving engagement with the drum and the freely journalled pinch roll becomes an idler roll, thus allowing the web to return to a neutral position.  
  While an arcuate drum portion 149 is in pressure contact with the web and pinch roll beneath for transfer of a strip onto the web, and additionally under such conditions that the average web feed velocity is less than the peripheral velocity of the vacuum drum, the web will be placed under tension on the input side of the pinch roll. Under such circumstances, if the web is formed of a material having elasticity such as, for example, polyethylene film or the like, the web will be stretched between pinch roll 94 and the film feed roller 96. In the instance wherein the web is formed of a material having substantially no elasticity or stretchability such as, for example, biaxially oriented polyester film (Mylar), there may be provided a yieldable drive connection such as a lost motion system to relieve partially stress caused by such web tension. Apparatus providing such capabilities is illustrated in FIG. 28 as described later.  
  Similarly it will be understood that while an arcuate portion of the vacuum drum is pressing against the web and pinch roll, but the average web feed velocity is however, in this instance, greater than the peripheral velocity of the vacuum drum, slack will be produced in the web on the input side of the pinch roll.  
  As the vacuum drum rotates slightly further, a flat portion 148 of the drum faces the pinch roll so that a neutral state or dwell period occurs wherein the web is no longer pressed against the drum and forced to travel at the drums peripheral velocity. During such dwell period, and depending upon which of the two states of web velocity to drum velocity obtains, the web will *snap&#34; (move quickly) either forward by the pull of the spring loaded dancer mechanism 98, relieving slack produced in the web, or the webwill snap back through its elastic properties or by reason of a yieldable drive connection relieving, in this case, tension produced in the web. The web thereby regains its original unstressed or unstretched condition.  
  By such cooperating features discussed above, successive strips can be placed on the web at relatively increased or decreased center to center spacing as compared with their spacing on the vacuum drum prior to transfer onto the web.  
  For example, referring to FIGS. 9 through 12, it will be seen that rotation of the vacuum drum rotates the laminating pinch roll 94 and presses strip 51 onto the web 52 over the pinch roll to attach the strip to the web. FIG. 10 illustrates strip 51 laminated on the film web 52. In the circumstance wherein the average rate of travel of the web is less than the peripheral velocity of the vacuum drum, during each laminating operation the web will be pulled toward the left in the drawings, and the web tensioned on the right or input or feed side of the pinch roll. As soon as the vacuum drum has rotated sufficiently to present a flat surface 148 to the pinch roll, the web is freed from constraint between drum and roll so that it resiliently contracts or snaps back toward the right thereby actually moving the laminated snaps back around the pinch roll as illustrated in FIG. 11 by the solid strip 51 on the web 52. It is to be appreciated that the illustration in FIG. 11 is exaggerated to show a marked difference between the strip 51 and the strip position 51 that would have been the strip location if the drum and the web were at all times moving at the same velocity. FIG. 12 illustrates the next lamination operation following the one illustrated in FIGS. 9 through 11, the just laminated strip being closer to the previously laminated strip 51 than would have been the case if the web and drum velocity were the same.  
  It will be seen that the present invention provides dwell time wherein the web is not maintained in tight contact against the vacuum drum. These dwell times may be provided by the aforementioned flats or flat areas 148 on the vacuum drum, as illustrated and described above, or may be alternatively provided. Thus, for example, it is possible to move the pinch roll into and out of engagement with the drum as by a reciprocating motion of the pinch roll by structure as illustrated in FIG. 22 and described subsequently.  
  The present invention is particularly adapted to the continuous application of spaced strips to a moving web of material that then may be formed into a bag or the like. The embodiment of the present invention described above incorporates drive means and speed control means to provide the described capabilities of the laminating apparatus. The relationship of driving and driven elements of a laminating head 54 is schematically illustrated in FIG. 8 wherein the same numerals are employed as in FIG. 5. FIG. 7 illustrates additional components of the drive mechanism. The elements of the laminating head are powered or driven from the main drive motor 102 through the gear box or transmission 103.  
  As schematically illustrated in FIG. 7, the vacuum drum shaft 157 and the cutter drum shaft 157 are rotated at the same velocity, and in the above described embodiment of theh present invention the foil sheet feed roll 89 is rotated to feed the foil substantially oneeighth of the peripheral velocity of the blade tips on the cutter roll 93 to provide the desired width (arcuate length on the drum) of strips 51 to be cut from the parent foil sheet 86.  
  Using the parameters given before as an example of possible spacing of cutting blades 127 on cutter roll 93 of 2 inch peripheral separation between blade tips, it will be seen that when foil feed roll 89 feeds the foil at substantially one-eighth of the velocity of the blade tips which intermittently contact vacuum drum 92 at regular 2 inch intervals on its surface, the strips of foil cut from the parent sheet will be substantially A inch in width upon severance.  
  Considering now the drive mechanism of the present invention in somewhat greater detail, reference is madefirst to FIG. 7 which is a developed view illustrating drive connections. The same numbers are employed in FIG. 7 as in FIGS. 6 and 8; and it will be seen that the main drive motor 102 and attached gear box 103 are connected by a belt or chain 181 to a main drive shaft 182 that is mounted for rotation in the frame 107 in extension transversely thereacross. This shaft 182 extends rotatably through laminating head side plates 121. A multiple gear element 183 is disposed about main shaft 182 and is adapted to be releasably affixed thereto by clamping means 184. As previously noted, the laminating head is adapted to be moved laterally of the main frame 107 upon transverse shafts 125. This lateral adjustment of the laminating head is accommodated by the drive mechanism by means of gear element 183 cutter roll 93. Rotation of the vacuum drum 92 is provided by an idler gear 188 mounted for free rotation on cutter roll shaft 157&#39; and meshing with a gear 189 of gear element 183 and a gear 191 on the end of vacuum drum shaft 157. The vacuum drum is mounted for rotation in side plates 121 of the laminating head, as illustrated. As previously explained, in the embodiment of the present invention described above, cutter roll 93 and vacuum drum 94 have the same operative diameter and are rotated at the same angular velocity by the means described above.  
  Also mounted for rotation between side plates 121 is the foil feed roll 89. This roll 89 has a gear 192 affixed to the shaft and engaging a first gear 193 of an idler gear unit 194 mounted for free rotation on one of the side plates 121. This idler gear unit also includes a second gear 196 which meshes with a drive gear 197 on one end of a shaft journalled in one side plate 121 and carrying a sprocket wheel 198 connected by a chain drive 199 about a sprocket wheel 201 of the main gear element 183. It will be seen that, with rotation of the main drive shaft and and consequent rotation of the gear unit 183, foil feed drum 89, cutter roll 93, and the vacuum drum 92 will be rotated in synchronism.  
  The main drive motor 102 also rotates the web feed roll 96, and provision is herein made for varying the rate of rotation of the web feed roll in relation to the rate of rotation of the main drive shaft and previously mentioned drums and rolls. To this end there is provided a conventional controlled differential unit 206 (shown in detail in FIGS. 13 and 13A) having an input shaft 207 rotated by a chain or belt drive 208 from the gear box 103 and an output sprocket wheel 209 connected by a chain drive 211 to a sprocket wheel 212 on the shaft 96 of web feed roller 96. Differential 206 does not reverse directions of rotation but does provide a limited adjustement of the speed of rotation of web drive roller 96 relative to the rate of rotation of vacuum drum 92.  
  It will be&#39; seen from referring to FIGS. 7 and 8 that clockwise rotation of the main drive shaft 182 will produce a clockwise rotation of the vacuum drum 92 and counterclockwise rotation of the cutter roll 93 so that foil fed onto the vacuum drum by clockwise rotation of the foil feed drum 89 intermittently cut into strips for transportation by the vacuum drum into engagement with the web of film fed by the clockwise rotation of the web feed roll 96. Provision is made for urging th freely rotatable web drive pinch roll 97 against web feed roll 96 as, for example, by spring biased slide blocks 218 (FIG. 7) mounted in the frame 107. It will be seen that the directions of rotation of the drums and rolls described immediately above coincide with the directions of rotation identified in FIGS. 5 and 6, for example. It is again to be noted that the drive train is illustrated in FIG. 7 by a developed view wherein certain elements are moved from their normal position inorder to be able to illustrate in a single drawing the relationship of elements in their driven connections.  
 Differential 206 may be controlled from differential control unit 213 (FIG. 14 described later in detail) mounted on frame 107 (FIG. 7) and rotated or&#39;driven by a chain or belt 214 from&#39;main drive shaft 182. The output of control unit 213, as schematically illustrated in FIG. 7, is applied by electrical means 216, 238 and 236, to ratchet means 217 of th differential for varying the differential output velocity relative to the input velocity thereof. This differential and the control afforded thereby are described in further detail later.  
  It has. been briefly noted above that provision is herein made for varying the speed of rotation of web feed roll 96 by differential control unit 206. It is possible with this control means to vary the center to center spacing between strips on the web (not on the vacuum drum) in the embodiment of the present invention under discussion. Although it will be appreciated that various types of means may be employed for this purpose, the conventional one illustrated in FIGS. 13, 13A and 14 is found highly desirable. Referring to these Figures, there will be seen to be illustrated a differential mechanism and control therefor. This particular system is a well-known type commercially identified as Mark III Control System, manufactured by Deitz Company, Inc. of Wall, New Jersey.  
  The input shaft 207 is mounted for rotation in hearing mounts 221., and this shaft extends into integral connection at 219 to a frame or housing 222 for rotation of the same with the shaft; shaft 207 being driven from main gear box 103 (FIG. 7). A worm gear 223 is rotatable about shaft 207 within the housing, and worm gear 223 and output gear 209 are inteegrally connected together by a hollow shaft 224. Thus output gear 209 and worm gear 223 rotate in unison. The frame 222 will be seen to be journalled for rotation about hollow shaft 224.  
  Within the frame 222 there is provided a worm 226 mounted for rotation in the frame, in position to mesh with worm gear 223 and extending through the frame to terminate in a small gear 227 at the end of the worm shaft. Exteriorly of the frame gear 227 is connected through an idler gear 228 to a gear 229 having a shaft 230 thereof extending into the frame and rotatably mounted in the frame thereby. The inner end of the shaft 230 is provided with a bevel gear 231. A differential drive shaft 232 extends through the opposite end of the frame from the input shaft 207 and is provided at the inner end thereof with a bevel gear 233 meshing with the bevel gear 231 within the frame. At the outer end of differential shaft 232 there is provided a toothed wheel 234 secured to the shaft which is in turn rotatably mounted in frame 222. In order to control the rotation of output gear 209 there is provided, as a portion of this control unit 206, a solenoid actuated latching mechanism. This latching mechanism is fixedly mounted and includes a solenoid 236 connected to wir ing 236, and reciprocal latch member 237 adapted to be moved into and out of engagement with teeth in the wheel 234 soas to prevent it from rotating. At any time the toothed wheel 234 is prevented from rotating by the latch mechanism, there is produced a relative rotation between frame 222 and differential drive shaft, 232. This then causes the bevel gear 231 to travel about the differential shaft bevel gear 233 as the frame is rotated by input shaft 207; and this motion is transmitted back to rotate worm 226. Rotation of worm 226 is transmitted through worm gear 223 and shaft 224 to output gear 209. It will be seen that with this structure it is possible to change the relative speed of rotation of output gear 209 with reference to input shaft 207, and thus adjust the web speed. Such adjustment is accomplished by controlling the solenoid operated latching mechanism by control means 213 illustrated in FIG. 14 and described below.  
  Such control means 213 includes a frame or housing 241 within which there is provided a rotatable cam 242 having a curved outer surface. This cam is mechanically connected to the drive 214 from main drive shaft K82. It will thus be seen that rotary cam 242 is rotated in synchronous relationship with vacuum drum 92. There is also provided in control unit 213 a pair of fixed spring-return switches 243 and 244 along the arc of the circle described by the movement of rotary cam 242. There is additionally provided an adjustable springreturn switch 246 which is shown to be mounted on an arm 246&#39; carried by shaft 247 extending from frame 241 and having a control knob 248 thereon for manually adjusting the angular position of switch 246. A set screw or the like 249 may be provided for fixing the position of switch 246. It will be seen from FIG. 14 that angularly adjustable switch 246 is movable along an arc coinciding with the path of rotary cam 242, and thus the angular position of switch 246 at the time of its actuation by cam 242 may be adjusted by the operator of the machinery.  
  Further reference to FIG. 14 will indicate electrical connections from switches 243, 244 and 246 to control amplifier 238, which is of any suitable design to actuate differential 206 by amplifying signals from control means 213 and from a photoelectric sensor 245 (FIG. for a purpose to be described, such amplifier being part of the aforementioned Deitz Mark 111 system. From the control amplifier wires 236 lead to solenoid 236 of FIG. 13, and wires 245 lead from photosensor 245.  
  With the main drive shaft rotating in a clockwise direction, movable cam 242 will actuate in succession switches 246, 243 and.244. Actuation of switch 244 causes solenoid 236 to actuate reciprocal latch member 237 thereby producing a difference in speed between input shaft 207 and output gear 209. The difference in speed so produced is such that the output speed will be decreased relative to the input speed, withthe result that the film web speed will be retarded relative to the peripherial velocity of the vacuum drum. This actuation of the differential will continue until cam 242 has further rotated to actuate switch 246, which discontinues operation of the solenoid and allows the input and output speeds of the differential 206 to return to their normal relationship. Therefore, by positioning movable switch 246 in different angular posi tions relative to switch 244, the duration of the period during which the web velocity is retarded relative to the vacuum drum may be controlled by the operator.  
  In the present embodiment of the invention, the conventional units employed in the Deitz Mark III system are so chosen as to provide an amount of web velocity retard reltive to that of the vacuum drum which is continuously variable from approxitmately zero to 6 percent depending upon the angular disposition of movable switch 246 as well as the condition of photoelectric sensor unit 245 when it is utilized, as will be explained subsequently. Such possible variations in the amount of web retard (slowing of web velocity) provides means for adjusting the center line to center line distance between strips on the web to any desired spacing within the limits of the particular embodiment of the invention. This is important in obtaining proper registry with printed matter on the web.  
  Thus, as was taken as an example noted previously with regard to the embodiment in FIG. 6, the peripheral disposition of the cutting blades may be on 2 inch centers between their tips, thereby placing the individual strips on 2 inch centers on the vacuum drum. With no velocity differences between the web and the vacuum drum, the distance between strips on the web will also be 2 inches after their transfer and lamination thereon.  
 It follows, however, from the above description of the differential control means that up to a 6 percent retard in velocity of the web relative to the vacuum drum may be introduced by the angular positioning of switch 246 relative to switch 244 of the control mechanism 213 (FIG. 14). This amount of retard is continuously variable up to the approximate 6 percent limitation. Consequently, the strips on the web may be positioned from their normal 2 inch spacing up to 6 percent less in center to center distance, or 1.88 inch by the snap laminating principle described previously.