US3608694A - Casing machine - Google Patents

Casing machine Download PDF

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Publication number
US3608694A
US3608694A US757876A US3608694DA US3608694A US 3608694 A US3608694 A US 3608694A US 757876 A US757876 A US 757876A US 3608694D A US3608694D A US 3608694DA US 3608694 A US3608694 A US 3608694A
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Prior art keywords
separator
shifter
partitions
tiering
containers
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Expired - Lifetime
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US757876A
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English (en)
Inventor
David F Schlueter
Myron C Noble
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FMC Corp
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FMC Corp
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65B—MACHINES, APPARATUS OR DEVICES FOR, OR METHODS OF, PACKAGING ARTICLES OR MATERIALS; UNPACKING
    • B65B5/00—Packaging individual articles in containers or receptacles, e.g. bags, sacks, boxes, cartons, cans, jars
    • B65B5/06—Packaging groups of articles, the groups being treated as single articles

Definitions

  • Upright containers are fed into the casing machine from a multiple-lane supply line, assembled into one tier, and the tier is transferred and reoriented by tiering fingers which deposit the containers in a tiering chamber.
  • The. open end of an empty case is manually positioned adjacent the tiering chamber, and pusher feet insert the tier in the case.
  • a feature of the casing machine is a rocking differential which [52] US. Cl 198/21, smoothly agcelerates and decelerates the timing fingers to 198/ prevent damage to the containers.
  • the present invention relates to container-handling machines, and particularly to machines which insert a tier or tiers of containers into a case. More specifically, the invention concerns casing machines of the type including sets of aligned tiering fingers which lift multiple-row tiers of upright containers from a centrally apertured separator adjoining the end of a container supply line, and which reorient and transfer the tier of containers to a tiering chamber from which they are inserted endwise into a case.
  • the present invention concerns a casing machine of the type disclosed in US. Pat. No. 2,650,009 to Kerr, and assigned to the assignee of the present invention.
  • One disadvantage of the Kerr apparatus is that undesirable shock loads are sometimes imparted to the containers and to the driving mechanism of the machine because of the sudden engagement of a single revolution clutch which drives the tiering fingers that transfer the containers, and due to the inertia of the fingers and their almost instantaneous acceleration to maximum speed.
  • the tiering fingers must travel upward approximately 3 inches before contacting the bottoms of each assembled tier of containers to allow time for a shifter mechanism to block the incoming containers that must be isolated from the tier.
  • the containers are subjected to shock and/or denting because the tiering fingers are moving near maximum velocity at the time they engage the containers. Additional shock and jarring is experienced by the containers as they are transferred onto the floor of a tiering chamber because the tiering fingers which effect the transfer, travel at a constant velocity.
  • containers whose height is approximately equal to or less than their diameter tend to become disoriented when entering the tiering chamber at a high velocity and the top rows of containers tend to tip forwardly.
  • Pusher feet in the patented structure transfer the tiers of containers into a case.
  • the pusher feet trace a path similar to a parallelogram in a vertical plane, and the forward and rearward cycles are identical.
  • the resulting motion is quite rapid, tending to upset tiers of short cans, and the case flaps are sometimes torn by the pusher feet due to their immediate lifting in the rearward stroke.
  • Kerr apparatus Another problem with the Kerr apparatus is the difficulty of changing the machine to handle other can sizes or to pack different numbers of tiers, because a large number of changeover parts and many hours of labor are required to accomplish a conversion.
  • the present apparatus is rapidly converted to handle different sizes of containers or to load various numbers of tiers either by adjustment only, or by addition or removal of common parts and with a minimum of parts peculiar only to one size of container. This is accomplished by means including unique timing, counting, sensing and inlet control mechanisms.
  • An important feature of the present invention is a rocking differential drive mechanism, by means of which the cans are smoothly accelerated from rest to maximum velocity, and are then decelerated as they are deposited on the floor of the tiering chamber where they are assembled into caseloads.
  • This eliminates undue shock which might otherwise damage the containers or their product.
  • the tendency for container mis orientation or spilling is eliminated by moving pusher feet slowly forward to transfer the tiers of containers into the case, but utilizing a rapid return stroke of the pusher feet so that the overall cycle is not prolonged. Further, the pusher feet are retracted to clear the case before being lifted at the beginning of the retracting stroke. This prevents the pusher feet from tearing a case.
  • Rapid changeover to handle a different can size is facilitated by forming the separator, where tiers of cans are assembled, of a plurality of similar divider units, each having its own can stop and mechanism that signals a full condition for a lane of cans associated with the divider unit.
  • the interspacing of the units and the can stops can be readily adjusted to handle a different diameter and number of cans without disturbing the signalling mechanism.
  • FIG. 1 is a perspective of the casing machine of the present invention, with the inlet end of the machine at the right.
  • FIG. 2 is a perspective of the casing machine viewed from the side opposite to the side shown in FIG. 1.
  • FIG. 3 is a perspective of the casing machine viewed from its inlet end.
  • FIG. 4 is a perspective of the drive train of the casing machine.
  • FIG. 5 is an enlarged, fragmentary elevation of a shifter mechanism which controls the flow of containers into the easing machine and is viewed in a downstream direction.
  • FIG. 6 is a section taken on lines 66 of FIG. 5.
  • FIG. 7 is a fragmentary perspective of two divider units which cooperatively define a lane for a row of cans in the area indicated by the arrow 7 on FIG. I.
  • FIG. 8 is an enlarged section taken along lines 8-8 on FIG. 7.
  • FIG. 9 is a perspective of a rocking differential indicated by the arrow 9 on FIG. 4.
  • FIG. 9A is a section, at reduced scale, taken through the center of the rocking differential shown in FIG. 9.
  • FIG. 10 is a diagram showing the input and output speeds of the rocking differential.
  • FIG. 10A is an elevation of a cam and follower arm, shown in the FIG. 4 drive train, for rocking the differential.
  • FIG. 11 is a perspective of pushers, and their mounting and actuating members, viewed from below, that push a tier of containers into a case.
  • FIG. 11A is a fragmentary plan indicated by the arrow 11A on FIG. 11.
  • FIG. 12 is a trace of the motion of the pushers shown in FIG. 1 1.
  • FIGS. l3l6 are fragmentary elevations of a synchronization control shown in FIG. 2, and illustrate successive operational positions of the control elements.
  • FIGS. 17 and 17A are enlarged fragmentary plans of an inactive and an active timing pin, respectively, which are part of the synchronization control.
  • FIG. 18 is a perspective primarily illustrating a lowerator which supports an empty case in filling position, and lowers the filled case to a discharge position.
  • FIG. 18A is an elevation of a lowerator cam which actuates the lowerator shown in FIG. 18.
  • FIG. 18B is a fragmentary elevation of a trip lever mechanism partially shown in FIG. 18.
  • FIG. 19 is a schematic electrical control diagram.
  • FIGS. 20 and 20A are fragmentary, diagrammatic elevation and plan views, respectively, which illustrate the inlet end portion of the casing machine and an associated supply conveyor.
  • FIGS. 21 and 21A are diagrammatic elevation and plan views, respectively, illustrating a mechanism for sensing when each of a plurality of longitudinal rows of cans in one assembled tier is complete.
  • FIGS. 22-26 are fragmentary diagrammatic elevations illustrating the operational sequence of assembling tiers of cans and loading the tiers in a case.
  • upright containers such as cans C
  • a 3 multilane feed conveyor 22 which is driven from the casing machine.
  • the cans are divided into multiple lanes on the conveyor by conventional means not shown and are separated by lane dividers 24 (FIG. 1).
  • the cans pass through a transversely movable shifter 26 whose vertical partitions 27 are initially aligned with the lane dividers 24.
  • the cans advance into a separator 28 having vertical partitions 29 in alignment with the lane dividers 24.
  • a can stop and sensing mechanism 30 in each lane is actuated to initiate a can transfer or tiering cycle.
  • Certain drive mechanism of the casing machine is now actuated, causing three sets of equally spaced tiering fingers 32 to rotate 120 about a common support shaft. This moves shifter mechanism 26 laterally to temporarily interrupt the flow of incoming cans.
  • the tier of upright cans is lifted from the separator 28 by one set of tiering fingers which reorients the tier 90 and deposits the tier on edge, with the cans in a lying down position, in a tiering chamber 34.
  • pusher feet 36 are actuated to move the tiers into a case A which has been manually positioned over a nozzle 38 and is supported by a lowerator 40.
  • the filled case is then lowered to a discharge conveyor or the like by the lowerator.
  • Power is supplied from a motor M (FIGS. 3 and 4) through a speed reducer R to a power shaft 42.
  • Shaft 42 rotates continuously and supplies power through a sprocket and chain drive 44 to the feed conveyor 22.
  • a tiering input shaft 46 and a pusher-lowerator shaft 48 are respectively driven by single revolution the clutches 50 and 52.
  • clutches On their driving sides, clutches have sprockets 54 and 56 (FIG. 4) which are connected by a chain 57 to a sprocket 58 mounted on the power shaft 42. Shafts 46 and 48 are driven only when their respective clutches 50 and 52 are engaged, but the sprockets 54 and 56 rotate continuously in the directions indicated by the arrows in FlG. 4.
  • the tiering input shaft 46 rotates in the same direction as the sprocket 54.
  • the shaft 46 rotates a shifter cam 60 and a differential cam 61 that-drives one side of a rocking differential 62.
  • the differential 62 operates the tiering fingers 32.
  • the output of the differential 62 drives a sprocket 63 freely mounted on shaft 46.
  • Sprocket 63 by means of a chain 67, drives a tiering sprocket 64 which is attached to one of two spaced spiders 65 that are mounted on a tiering shaft 66.
  • One set of tiering fingers 32 is mounted on each of three cross-shafts 68 which are carried by the spiders 65.
  • a three-toone speed reduction from the differential output sprocket 63 to the tiering sprocket 64 causes the tiering fingers 32 to be rotated 120 for complete revolution of the tiering input shaft 46.
  • a constant rotation is imparted to the pusher-lowerator shaft 48.
  • the vertical motion of the pusher feet 36 is controlled by a pusher lift cam 70 which is mounted on the shaft 48 and actuates a pusher lift arm 72 by means of a pivoted pusher lift lever 73 having a follower roller engaged with the cam.
  • the horizontal motion of the pusher feet 36 is effected by a pusher stroke cam 74 which is mounted on the shaft 48 and actuates a pusher stroke follower arm 75.
  • variable stroke shifter 26 (FIGS. 1 and 5) functions as a blocking device to interrupt the flow of containers from the feed conveyor 22.
  • a shifter bar 78 is displaced one-half of a can diameter so that each of a plurality of the vertical partitions 27 is placed in blocking relation to an incoming row of cans between the lane dividers 24 of the feed conveyor 22.
  • the shifter bar 78 (FIGS. 5 and 7) carries a depending shifter bracket 88, and slides on a spacer plate 80. Each end of the spacer plate 80 is supported by and secured to a block 81, as shown in FIG. 5. 'Downwardly open recesses 83 in the spacer plate 80 locate and retain a plurality of support arms 82, one of which is provided for each of the separator plate partitions 29.
  • the shifter bracket 88 has side ribs 89 (FIG. 6) that slide in grooved guide bars 90.
  • the guide bars 90 are mounted on a pair of transverse tie bars 84 that interconnect longitudinal side frame members 86.
  • the shifter bracket 88 (FIG. 5) includes a depending arm 91 having a series of holes 92 which provide for adjustment of the amount of lateral shifter stroke for various diameter cans.
  • a follower roller 94 is mounted in a selected hole 92 corresponding to the desired shifter bar displacement, and so mounted, rides in a slot 96 in a shifter cam follower lever 98.
  • the lever 98 is pivotally mounted to the frame of the machine at 99 and is oscillated between the phantom and full line positions shown by a cam follower 100 which is engaged with the shifter cam 60.
  • the separator 28 includes multiple divider units 102. Each divider unit is provided with a pair of the ramps 101, one of the partitions 29, and is removably mounted on the tie bars 84 by means of a bolt 104 recessed in the support arm 82.
  • the tie bars 84 cooperatively form a T-shaped slot 105, and a square nut 106 which fastens the bolt 104 is captured in the slot 105.
  • the divider units 102 are positioned to accept a particular diameter of can between adjacent partitions 29 by first removing the spacer plate 80, and then loosening the bolts 104 and sliding the support arms 82 along the tie bars 84.
  • the interspacing of the partitions 29 can be changed to accept a different can size.
  • the divider units 102 are readily removed by sliding the loosened unit along the slot 105 to a cross-slot 108 (H6. 7). The divider unit is then removed by sliding it forwardly out of the cross-slot.
  • Other units can be added in the obvious, reverse procedure.
  • one of the can stop and sensing mechanisms 30 is mounted on each divider unit 102. lts purposes are to control the number of cans allowed to accumulate in each lane of the separator 28, to control the longitudinal position of the row of cans so that the cans do not partially extend into the shifter 26, and to actuate a control circuit when this lane and the other lanes are full of cans.
  • the can stop and sensing mechanism 30 for each lane is actuated by the leading can in the row of cans pressing against an upstanding stop finger 110 which is mounted for limited displacement in a downstream direction.
  • the mechanism 30 actuates a flag 112 that interrupts a light beam LB projected across the casing machine.
  • a later-described photoelectric control unit is energized to initiate a loading of the assembled containers into the tiering chamber 34 (FIG. 1).
  • the can stop finger 110 is rigidly mounted on a support block 116.
  • the support block 116 is adjustable axially of a threaded rod 118 which is engaged with a threaded aperture in the block, and slides on a guide rod 120.
  • the ends of the threaded rod 118 are rotatably mounted in spaced carriage blocks 124 and 126, and the guide rod 120 is rigidly secured in the carriage blocks.
  • the support block 116 and the can stop finger 110 mounted thereon are moved along the guide rod 120 to longitudinally adjust the can stop finger 110 for the desired row length of cans to be accumulated in the corresponding lane. It is believed apparent that because the partitions 29 of two adjacent divider units 102 form the lateral limits of one lane of cans, the outermost divider unit at the left side of the casing machine (viewed in a downstream direction) does not require a can stop finger 110 or a flag 112.
  • each carriage block 124 and 126 depends from the support arm 82 in the manner shown for the carriage block 126 in FIG. 8.
  • each carriage block is provided with a central upstanding tab portion 125 that extends upward into a downwardly open milled slot 127.
  • the tab 125 is provided with a diagonal slot 133 and is retained by a roller 134, mounted on a pin 135, which is disposed in the slot.
  • the flag 112 is pivoted to the support arm 82 by the pivot pin 135, and is pivoted to the carriage block 126 by a pivot stud 136. Accordingly, when the lane of cans pushes against the can stop finger 110, the pivot stud 136 is moved away from the pivot pin 135 and the flag 112 swings about the pin 135 out of the light beam LB, as indicated by the arrow 1120..
  • the light beam LB originates from a photoelectric unit 137 (FIG. 3) which includes an integral lamp and receiving element and is mounted on one of the frame members 86.
  • the photoelectric unit 137 FIG. 3
  • the photoelectric unit 137 Since the light beam is interrupted by any one of the flags 112 in rest position, thus indicating that one or more lanes of cans is not yet complete, the photoelectric unit generates a control signal only when the separator 28 accumulates a complete tier of cans.
  • the signal from the photoelectric unit 137 energizes an adjacent solenoid 140 which is turn causes clutch 50 (FIG. 4) to engage and initiate the tiering cy-' cle.
  • the set of tiering fingers underlying the cans in the separator are smoothly accelerated upward to pick up cans from the separator and are smoothly decelerated as the cans are deposited in the tiering chamber by the tiering fingers.
  • this smooth acceleration and deceleration is performed by the rocking differential 62 (FIGS. 4, 9 and 9A).
  • the rocking differential 62 provides a variable-speed drive connection from the tiering input shaft 46 to the tiering shaft 66, via rotation of a pair of bevel gears 141 and 142 which are meshed with a spider gear 144.
  • the solenoid 140 (FIG. 3) actuates the tiering clutch 50 (FIG. 4) to transfer one tier of cans from the separator 28 (FIG. 1) to the tiering chamber 34
  • the tiering shaft 66 is turned 120 by the rocking dif ferential 62 and the drive train including sprockets 63 and 64, and the chain 67.
  • the spider gear 144 (FIG.
  • both the gear 141 at the input side of the differential and the differential cam 61 are keyed to the tiering input shaft 46.
  • the gear 142 at the output side is pinned to the sprocket 63.
  • the gear 142 and the sprocket 63 rotate together freely on the shaft 46, so that their motion can be modified by fore-and-aft motion of the spider gear 144.
  • the spider gear 144 rotates on a stub shaft 146 that projects from a spider gear hub 148, and the hub rotates freely on the shaft 46.
  • oscillation of the spider gear hub 148 will add to and subtract from the drive motion transmitted from the shaft 46, by means of the gears 141, 144 and 142, in accordance with known principles of differential gearing.
  • the oscillation of the spider gear hub 148 is provided by the differential cam 61 and associated linkage, as will now be described.
  • the cam has a track 151 which is eccentric to the shaft 46.
  • a cam follower 152 rides in the cam track and hence oscillates a cam follower lever 154 which is pivoted to the frame of the machine by a pivot shaft 156.
  • the lower end of the cam lever 154 is pivoted at 157 to one end of a cam link 158.
  • the other end of the cam link is pivoted at 159 to a cam crank 160.
  • the crank 160 depends from one end of a sleeve 162 that turns freely on the power shaft 42.
  • a companion crank 163 which is pivoted at 164 to one end of a spider link 165.
  • the other end of the spider link is pivoted at 166 to a spider crank 167 that depends from the spider gear hub 148.
  • the oscillation of the spider gear 144 is superimposed on the motion transmitted by the spider gear 144 to the chain 67 so that the tiering shaft 66 (FIG. 4) rotates with nonuniform motion to accelerate and decelerate the tiering fingers 32 in the manner previously described.
  • FIG. 10 is a diagram showing the speed change in revolutions per minute of the differential output gear 142, and hence the rotation of the shaft 66 which carries the tiering fingers 32, during one rotation of the differential input gear 141.
  • FIG. 10A illustrates the relation of the differential cam 61 to the FIG. 10 diagram; the degree markings on the cam are the same degree markings of the base line of the FIG. 10 diagram. Reference should also be made to the later-described FIG. 22 which illustrates the can transfer operation of the tiering fingers 32.
  • the abscissa of FIG. 10 is marked in 90 increments for one complete revolution of the input gear 141 and the differential cam 61.
  • the speed of the input gear 141 is seen to be 60 r.p.m.
  • the output gear 142 gradually accelerates from 0 to 90
  • the lowest point of the cam track 151 is at 90, and the cam follower 152 is at its extreme of movement inwardly toward the shaft 46.
  • the spider hub 148 is briefly motionless and the differential 62 transmits the full 60-r.p.m. rotation of the input shaft 46 to the output gear 142.
  • the cam follower 152 moves outward from the shaft 46 and drives the spider hub 148 (FIG. 9) forward in the direction of the arrow 144b. This adds to the linear speed of the chain 67 which powers the tiering fingers.
  • the 90180 portion of the cam track 151 is symmetrical with the -90 portion. Consequently, the 90- 180 rotation of the output gear 142 smoothly accelerates the tiering fingers from 60 r.p.m. to their maximum speed of 120 r.p.m. as the cam 65 rotates to its 180 position.
  • the hub 148 at this time has not attained its forward limit of movement in the direction of the arrow 144b.
  • the spider hub 148 is moved rearward in the direction of the arrow 144a and reduces the speed of the output gear 142 from 60 r.p.m. to 0 r.p.m.
  • the tiering fingers during this latter movement thus decelerate the can charge as it is deposited in the tiering chamber 34.
  • the cam follower lever 154 provides motion amplification such that the cam track 151 translates the spider gear hub 148 at half the velocity of the shaft 46 at 0 and at 180 in the cycle. Because the direction of movement of the hub is opposite at these points in the cycle, the output speed varies from 0 r.p.m. to 120, r.p.m. or twice the input speed of the shaft 46, and is readily provided for by means of the motion-amplifying linkage and cam arrangement shown.
  • the shifter 26 (FIGS. 1 and 4) and the rocking differential 62 are both driven from the shaft 46 in timed relation to each other.
  • the shifter stroke is initiated during the initial 40 of rotation of the input shaft 46.
  • the tiering fingers 32 rotate only about 1 about the tiering shaft 66.
  • the initial slow acceleration of the tiering fingers 32 allows sufficient time for the shifter 26 to block incoming cans so that the cans in the separator 28 are isolated before they are picked up by the tiering fingers.
  • Tiering The tiering steps comprise lifting the assembled tier of upright cans from the separator 28 and depositing the tier on edge in the tiering chamber 34 so that the cans are in a substantially horizontal position.
  • each of the three sets of tiering fingers 32 are mounted on a cross-shaft 68.
  • One tiering finger is provided for each lane of cans, and the cross-shafts 68 are rotatably mounted in two spaced spiders 65 that are secured to the tiering shaft 66.
  • a bellcrank 170 is attached to each cross-shaft and is provided with follower rollers 174 and 176 which engage a fixed tiering cam 172.
  • the bellcranks 170 pivot the crossshafts 68 and the attached tiering fingers 32 in the manner illustrated in FIGS. 22-26.
  • the lower cam' follower l76 engages the track 178 and pivots the cross-shaft 68 and the tiering fingers 32 into position to pick up the tier of cans C from the separator 28 for transfer to the tiering chamber 34.
  • the cam follower 174 of this same set of tiering fingers 32 later engages the track 180 and serves to pivot the tiering fingers (as illustrated for the leading set of fingers 32) rearwardly away from the cans.
  • the tier of cans is deposited on a plurality of slats 182 that form the floor of the tiering chamber 34, and the fingers retract while lowering to prevent disturbing the delivered cans.
  • the can transfer cycle is sequentially illustrated in FIGS. 22 through 24.
  • An adjustable thumb 183 (FIG. 22) is secured in a selected position along each tiering finger 32 to support the cans C as they are rotated through 90 from the upright position at the right of FIG. 22, to the lying-down position at the top of FIG. 22.
  • the tiering chamber 34 has side retaining plates 181 (shown in phantom in FIGS. 1, 2 and 3) which extend upward and downstream from the outside partitions 29 of the separator.
  • the retaining plates 181 serve to retain and guide the containers as they are lifted from the separator 28 and deposited on the floor of the tiering chamber.
  • each slat 182 (FIG. 18) of the tiering chamber floor has a slot 1820 which provides clearance for the tiering fingers 32.
  • the slats 182 are bolted to a crossmember 184 having a longitudinal slot 185 to allow lateral adjustment of the slats when the machine is readjusted to accommodate various container sizes.
  • FIG. 11 is a perspective of the pusher mechanism, looking from below, which inserts the tiers of cans into a case.
  • the single revolution clutch 52 (FIG. 4) is activated by a later-described control circuit.
  • the pusher feet 36 are moved through the path shown by the arrow 36a in FIGS. 24-26. This path is determined by the pusher stroke and the pusher lift cams 74 and 70 (FIG. 4) that are mounted on the pusher-lowerator shaft 48.
  • the pusher stroke follower arm 75 pivots about a shaft 185 and oscillates a pusher stroke arm 186 that is connected to a pusher stroke carriage 188 by a lengthwise ad-.
  • a square section pusher foot shaft 194 has end portions rotatably mounted in pillow blocks 195 on the carriage 188.
  • the lower end of the pusher lift rod 72 (FIGS. 4 and 11) is pivotally connected to the pusher lift lever 73, and the upper end of the lift rod 72 is pivotally attached to a pusher lift carriage 198.
  • the pusher lift carriage 198 (FIG. 11) includes a horizontal guideway 200, and is vertically slidable on a pair of vertical guide rods 202.
  • the carriage 198 oscillates the pusher foot shaft 194 to raise and lower the pusher feet 36.
  • the shaft 194 is provided with a crank arm 204 having a roller mounted in the vertically reciprocable guideway 200.
  • the horizontal guideway 200 allows the pusher feet 36 to be moved horizontally without affecting their vertical motion. Therefore, the vertical motion of the pusher feet can be varied independent of their horizontal movement.
  • FIG. 12 graphically illustrates the path of the pusher feet 36. Following the linear pushing stroke, the pusher feet retract slightly before following the arcuate return stroke. The significance of this retraction, as shown in FIG. 26, is that the

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US757876A 1968-09-06 1968-09-06 Casing machine Expired - Lifetime US3608694A (en)

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US (1) US3608694A (enrdf_load_stackoverflow)
DE (1) DE1937927A1 (enrdf_load_stackoverflow)
FR (1) FR2017546A1 (enrdf_load_stackoverflow)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3994386A (en) * 1975-06-02 1976-11-30 Toby Enterprises Apparatus for producing individually wrapped sliced stacks of a comestible product
US4413720A (en) * 1981-09-04 1983-11-08 Pfleger Frederick W Article handling apparatus
US4459794A (en) * 1981-06-01 1984-07-17 Standard-Knapp, Inc. Accelerated loading for case packer

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3110720C2 (de) * 1981-03-19 1986-08-21 Focke & Co, 2810 Verden Vorrichtung zum gruppenweisen Einschieben von Packungen in einen bodenseitig offenen Faltkarton
DE3301013A1 (de) * 1983-01-14 1984-07-19 Hans Paal KG Maschinenbau (GmbH & Co), 7056 Weinstadt Sammelpackmaschine

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2710089A (en) * 1951-02-23 1955-06-07 Fmc Corp Arrangement for dividing container supply lines
US3008563A (en) * 1959-05-26 1961-11-14 Meyer Geo J Mfg Co Charge-arresting device for article accumulators

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2710089A (en) * 1951-02-23 1955-06-07 Fmc Corp Arrangement for dividing container supply lines
US3008563A (en) * 1959-05-26 1961-11-14 Meyer Geo J Mfg Co Charge-arresting device for article accumulators

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3994386A (en) * 1975-06-02 1976-11-30 Toby Enterprises Apparatus for producing individually wrapped sliced stacks of a comestible product
US4459794A (en) * 1981-06-01 1984-07-17 Standard-Knapp, Inc. Accelerated loading for case packer
US4413720A (en) * 1981-09-04 1983-11-08 Pfleger Frederick W Article handling apparatus

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FR2017546A1 (enrdf_load_stackoverflow) 1970-05-22
DE1937927A1 (de) 1970-04-02

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