US2407313A - Wrapping machine - Google Patents

Description

Sept. 10, 1946. J, MALHIO 4 2,407,313

WRAPPING MACHINE Filed July 5, 1940 '14 Sheets-Sheet 2 ,4 j /Gf .2:

J55 J60 J61 164 M6?" mH HUN-I65 J55 INVENTOR. BY: 610mm Mahat ATTORNEYJ.

Sept. 10, 1946.- c. J. MALHIOT 2,407,313

WRAPPING MACHINE FiledJuly 5, 1940 14 sheets-sheet 5 1N VENT OR.

ATTORNEY J Sept. 10, 1946. v c. .1. MALHIOTQ ,3

WRAPPING MACHINE Filed July. 3, 1940 14 sheets-sheet 4 v E OR. a BY. t H 2W /0A TTORNEY}: I

C. J. MALHIOT WRAPPING MACHINE J Sept. 10, 1946.

Filed July 5, 1940 14 Sheets-Sheet 5 INVENTOR. Clare nae Q/M ,mwm)

ATTORNEY.

Sept. 10, 1946.

c. J. MA LHI OT WRAPPING MACHINE l4 Sheets-Sheet 6 INVENTOR.

, a v fix BY: Clara we Sept. 10, 1946. c. J. MALHIOT WRAPPING MACHINE Filed July 3; 1940 l4 Sheets-Sheet 7 INVENTOK ATTORNEYJ.

Y. Clarerwe JlMaZ/aot l a, M/QM Sept. 10, 1946. c. J. MALHIOT 2, 7,

I 'WRABPING AdHINE I Filed July '3, 1940 1.4 Sheets-Shet s INVENIOR.

ATTORNEYJ.

Sept. 10, 1946. v c. J. MALI-HOT I 2,407,313

WRAPPING MACHINE ATTORNEY6.

Clarence Sept. 10, 1946. c J. MALHIOT 2,407,313

' WRAPPING MACHINE Filed July 3, 1940 14 Sheets-Sheet 10 INVENTOR.

Chrerwe JIMalMZ' z @a M/Qs'afl) ATTORNEY 5.

4 aza Sept. 10, 1946. c. J. MALHIOT' I 2,407,313

WRAPPING MACHINE Filed July 3, 1940 14 Sheets-Sheet 11 Ill Sept. 10, 1946. -no I Q 2,40%313 I WRAPPING MACHINE 7 Filed July 3, 1940 14 Sheefs-Sheet 12 INVENTOR.

ATTORNEY l Sept. 10, 1946. c. J. MALHIOT WRAPPING MACHINE 14 Sheets-Sheet 15 m WEI/4&6 4. 1 WW 4 in o Mm m y IINVENTOR. B Clarence m M ATTORNEY;

Sept..10, 1946. .c. J. MALHIOT WRAPPING MACHINE.

' Filed July 3. 1940 14 Sheets-Sheet 14 Patented Sept. 10, 1946 Clarence J. Malhiot, Oak Park, Ill., assignor to F. B. Redington Co., Chicago, 111., a corporation of Illinois Application July 3, 1940, Serial No. 343,849

33 Claims.

This invention relates to packaging or wrapping machines, and more particularly to such machines of the high speed automatic type.

It is an object of the invention to provide a packaging or wrapping machine of improved construction and operating characteristics, and more specificallyto provide an automatically operable machine adapted for the high speed packaging or wrapping of frangible or relatively easily damaged articles.

A further object of the invention is to provide a machine of the foregoing type wherein various conveyor elements thereof areadapted for varia ble speed motion, as distinguished from uniform or intermittent operation, whereby to facilitate the passage ofthe articles or packages through the machine at highspeed, but without shock or jar, and insuring a sufficient time interval of article or package movement at the various operating stations to permit adequate and complete operation of the mechanisms disposed at such stations.

More specifically stated, an object of the invention is to provide, in a machine of the foregoing type, continuously operable article or pack age conveying means such as conveyors, wrapping wheels, and the like, having alternate high and low speed cycles of operation, the high speed cycle providing for a maximum rate of travel of the articles along a predetermined path, and the low speed cycle insuring a suflicient time interval of article movement at a predetermined station or stations to permit the operation of the various operating mechanisms thereon.

Another object of the invention is to provide continuously movable variable speed packaging or wrapping elements having alternate high and low speed cycles of operation, the high speed cycle facilitating the approach of the elements into operative article or package engaging position, and the low speed cycle insuring the proper movement of the elements as they engage and operate upon the articles.

Still another object of the invention is to provide, in a packaging or wrapping machine, article engaging transmission elements of resilient construction whereby to allowfor possible variations in the necessary movements of th articles as they are engaged by such elements and thereby obviate the possibility of damage to the articles by the elements.

Still another object of the invention is to provide, in a packaging or wrapping machine, a processing conveyor structure which may be operated independently of the machine and while other machine elements are not in operation.

A still further object of the invention is to provide a conveyor structure in a packaging 'or wrapping machine particularly adapted for the handling of frangible articles, which conveyor is operable to move the articles along a predetermined path in spaced relation, independent motive means being provided for each. article,,wl 1ereby even though the conveyor may be relatively long, no cumulative crushing effect is appliedto the articles in their transmission movement.

Various further objects, advantages and features of the invention will appear from the following specification when. taken 'in connection with the accompanying drawings, wherein certain preferred embodiments of the invention are set forth for the purposes of illustration.

In the drawings, wherein like reference. numerals refer to like parts throughout:

Figure 1 is ,a general assembly view, in front elevation, of a wrapping machine constructed in accordance with the principles of the present invention.

Fig. 2 is a partial detail view of the outer end of the feeding conveyor structure.

Fig. 3 is an end view of the machine, as. seen from the left in Fig. 1, the outer end of the feeding conveyor being brokenaway.

Fig. 4 is a sectional view of the feeding conveyor, taken on the line 44 of Fig. 3. g

Fig. 5 is a partial rear view 'of the machine, more particularly illustrating the drive gearing.

Fig. 6 is a sectional view through the machine, taken generally along the line 66 of Fig. 5 and more particularly illustrating the article feeding mechanism and associated drive, for feeding the articles from the feeding conveyor into the wrapping wheel. 7

Fig. '7 is a sectional view of the feeding mechanism, on the line l-1 of Fig. 6.

Fig. 8 is a detail sectional view of the feeding mechanism, on the line 8-8 of Fig. 7.

Figs. 9 and 10 are detail perspective views of two of the slide members associated with the feeding mechanism.

Figs. ll'and' 12 are sectional views of the feeding. mechanism illustrated in Fig. 7, taken along the line llll thereof and showing two of the operating positions of the mechanism.

Figs. 13 and 14 are detail perspective views of the wrapper paper guide means and clamping means, res ectively, associated with the feed mechanism.

Fig. 15 isa detail view of the wrapping wheel and associated wrapping mechanisms, as seen from the front of the machine as in Fig. 1.

Fig. 16 is a sectional view of the wrapping mechanism, taken on the line 1 61 6 of Fig. 15.

Figs. 17 and 18 are detail view of two of the wrapping elements of the wrapping mechanism.

Fig. 19 is a sectional view of the wrapping wheel and associated wrapping mechanism, on the line Iii-19 of Fig. and also illustrating the associated drive structure, as indicated by the section line |9-|9 of Fig. 5.

Fig. 20 is a sectional view through the mechanism of Fig. 19 on the line 2U20 thereof.

Fig. 21 is a sectional view through the wrapping wheel and mechanism on the line 2l2| of Fig. 19.

Fig. 22 is a sectional view through the mechanism of Fig. 21 on the line 22-22 thereof.

Figs. 23, 24 and 25 are detail views of various wrapping mechanism parts.

Fig. 26 is a sectional view through the machine, on the lines 26-26 of Figs. 5 and 15, more particularly illustrating the ejector elements for moving the articles from the wrapping Wheel to the transfer wheel, and the associated drive mechanism.

Fig. 27 is a sectional view more particularly illustrating the overrunning clutch and independent drive for the processing conveyor, taken on the line 2121 of Figs. 5 and 26.

Fig. 28 is a partial detail view of the ejector elements, transfer wheel, and infeed end of the processing conveyor as seen from the front of the machine as in Fig. 1.

Fig. 29 is a sectional view of the mechanism of Fig. 28 on the line 29-29 thereof.

Fig. 30 is a detail perspective view of one of the transfer wheel package support platforms.

Fig. 31 is a detail perspective View of one of the processing conveyor feed links.

Fig. 32 is a sectional view through the mechanism of Fig. 28, and associated drive, on the lines 32--32 of Figs. 5 and 28.

Fig. 33 is a detail View of the discharge end of the processing conveyor and the infeed end of the associated removal conveyor, as seen from the front of the machine.

Fig. 34 is a sectional view through the mechanism of Fig. 33 on the line 34--34 thereof.

Figs. 35 and 36 are sectional views through the processing conveyor on the lines 35-35 and 3636 respectively of Fig. l; and

Figs. 3'7 to 44, inclusive, are diagrammatic views illustrating the several steps in the wrapping of the articles as performed by the machine.

Referring more particularly to the drawings, the machine illustrated comprises a high speed automatic machine for packaging or wrapping bars of soap, such as laundry soap or the like. In the use of a machine of this type,,it is desirable that the soap bars be fed to the machine as they come from the molding presses, at which time they are in soft, semi-plastic and frangible condition. Problems are presented in the handling of the semi-plastic bars to effect the high speed wrapping thereof without damage to the bars, which problems are solved by the present invention. While the machine as illustrated is thus particularly adapted for the high speed wrapping of semi-plastic soap bars, it is to be understood that the various features of the invention are adaptive for other uses and purposes, including the wrapping or packaging of other types of articles.

General machine structure Referring to Fig. 1, the machine in general wheel, the wrapper is folded and the bars are wrapped by suitable wrapping or packaging devices, later to be described; and upon reaching transmission or ejector rolls 53, the wrapped bars are ejected from the wrapping Wheel to a transfer wheel 54 which transfers them to a processing conveyor, generally indicated by the numeral 55. In the processing conveyor, the bars are passed along suitable processing elements, which in the particular machine illustrated are heating and cooling elements for sealing the wax paper wrapper in which the bars are wrapped and, after processing, the bars are ejected from the processing conveyor onto a removal conveyor 56 operable to deliver them to a suitable point of delivery.

Drive mechanism The various mechanisms of the machine are all adapted to be driven in synchronized, timed relation by means of a main electric driving motor 60, Fig. 1, and a drive gearing mounted on the rear of the machine and best illustrated in Fig. 5. More particularly, referring to Figs. 1, 3, 5 and 6, the motor 69 drives a main drive shaft 6| through the intermediary of a flexible belt 62, belt pulleys 63 and 64, and a clutch mechanism 65. The pulley 53 is loosely mounted on the shaft BI, and the clutch mechanism 65, which may be any suitable form of disk clutch, is provided for connecting and disconnecting the driving engagement between the pulley and the shaft. The clutch is controlled by means of an oscillatable shaft 66 and a linkage 61 leading to a clutch control handle 68 mounted on the front of the machine in a position to be conveniently manipulated by the machine operator. It will be seen that while the pulley 63 is constantly operated so long as electric motor 60 is in operation, the main drive shaft 61 is operated only when the clutch 65 is engaged.

Drive shaft 6! carries a pinion 69 in driving engagement with a gear ill mounted on a shaft H. The gear Ill may be connected to the shaft H through an overload driving arrangement as indicated at 12. Such overload device may be of any suitable construction, and is provided for permitting the gear Ill to slip on the shaft H in the event of overload conditions in the machine. It is to be understood that overload mechanisms, for safety purposes, may be elsewhere provided in the drive connections if desired. Normally, however, the gear '16 efiects the rotation of the shaft H 'as the gear is driven. This shaft projects forwardly through the machine frame 49, as best shown in Fig. 6, and near its front end carries three control cams l3, 14,,and 15, forming the driving means for the feeding mechanism 5|, as will be later described.

The shaft H, at its rear end, also carries a gear 16 in driving engagement with a gear "i1 mounted upon a shaft 18, see particularly Figs. 5 and 19. Gear 17 carries a block 19 provided with a longitudinal track 89. A shaft 8|, offset with respect to the axis of shaft 18, carries a crank member 82, which crank is provided with a pin 83 engageable within the track 86 of the block I9. Accordingly, it will be seen that as. the. gear 11 is rotatably driven, moving the block 1.0 which is mounted thereon in a circular path, the crank pin 83 which is engaged in the block track will cause the rotation of the crank 02 and its associated shaft 8I. But it is to be noted that while the gear TI and the shaft [8 are driven at con.- stant speed, the driving movement which is imparted to the crank 82 and its associated shaft ill will be a variable speed motion, clue to the offset displacement of the axes of the shafts I8 and 8|. While the rotation of shaft M will be continuous, it will be at variable speeds comprising alternate fast and slow cycles of operation the slow cycle of rotation being imparted thereto when the parts are in the position illustrated in Fig. -5, and the rapid cycle of operation being imparted when the crank and block I9 assume a position displaced 180 degrees from the position shown. While the, rotation of the shaft IN is alternately fast .and slow, it is further to be noted that the acceleration and deceleration of the shaft BI is gradual, whereby to avoid imparting shocks to the shaft or to the mechanisms operated therefrom. During operation, the pin 83 slides longitudinally in the track. and maintains driving engagement between the parts notwithstanding the offset relation of the shafts I8 and BI. The variable speed drive mechanism thus providedis well suited for the purposes of the present invention, but it is to be understood that other suitable forms-of variable speed drives could be substituted.

Shaft BI carries a pinion 85., Figs. 5 and 19, in engagement with a gear 86 mountedon a shaft 07, which shaft also carries a bevel gear 88 adapted 'to drive a cooperating bevel gear 89 mounted on one end of a shaft. 90. The other end of shaft 90 carries a gear SI, Figs. 3, 5 and 6, which through gearing 52 and 93 drives the feed ing conveyor 50. It will thus be seen that the feeding conveyor, to which more specific reference will hereinafter be made, is driven at variable speed through the several driving connections described.

Variable speed shaft 81 also carries a pinion 95, Figs. 5 and 19, in driving engagement with a gear 96 secured to a. shaft 81 which extends for wardly through the machine frame and on its front end carries the wrapping. wheel 52. The wrapping wheel is thus also driven at variable speed through its driving connections.

Constant speed shaft I8 also extends forwardly through the frame 49 of the machine and is provided on its front end with a gear I forming a part of the driving means for the wrapping mechanism, as will be later described. Adjacent its rear end, the shaft carries a gear IOI in driving engagement with gear I02 secured to shaft I 03, extending forwardly through the frame of the machine and provided at its front end with a block I04 forming another driving element for the Wrapping mechanism, as will be also later described. The gear I00 and the block I04, being driven from the shaft I8, are operated at constant speed.

Driving gear 11, further referring to Figs. 5 and 19, also meshes with an idler gear I05 which is loosely mounted on the shaft 81. This idler gear drives a gear I06 which in turn drives a gear I01 forming the driving mechanism for the paper feeding and cutting rolls diagrammatically indicated at I03 and I09 on Fig. 1. The specific construction of these paper feed and cutter rolls and their driving means forms no part of th present 6 invention, and is only diagrammatically indicated. Constant. speed .idler gear I05 also drives a gear I10, Fi s.;5. and 26, secured to a shaft III. This shaft also extends forwardly through the machine frame and carries a crank H2 at its front end, which crank constitutes another of the driving elements for the wrappin mechanism.

Gear IIO meshes with a gear II3 associated with a. shaft II4 also extending through the machine frame and provided on its front end with a hand wheel II5, Fig. 1. Axial movement of shaft I I 4 serves to connect th gear II3 thereto by suitable clutch means, not shown, after which the shaft and the. gear may be rotated by the hand wheel whereby to manually operate the drive gearing as for setting up purposes and the like.

Constant speed gear IIO further meshes with and drives a gear H6, Figs. 5 and 26, secured to a stub shaft Ill, the gear H5 in turn being arranged to drive a gear II8 Which is loosely mounted on a shaft I I9, the latter extending forwardly through the frame of the machine and being provided at its forward end with a pair of bevel gears I20 and I2I adapted to drive the ejector rolls 53, and with a hand wheel I22. The arrangement is such that the shaft II9 may be driven either from the gear I I0 or from a supplementary independently operable power source which-in the particular embodiment of th mechanism disclosed comprises an electric motor I24. To this end a gear I25 is pinned to the shaft H9, and clutch devices are provided so that the gear and the shaft may be driven selectively either from the power gear I I8 or the electric motor I24, as will best be understood by reference to Figs. 26 and 2'7 of the drawings, seel also Figs. 3 and 32. More specifically, the motor shaft is provided with a worm I26 adapted to drive a worm gear I21 mounted on a stub shaft I28. This shaft is connected by means of a coupling I20 to one part of a one-way overrunning clutch device I355 which may be of any suitable construction, the other part of the clutch being rigidly associated with the gear I25. Similarly an overrunning clutch assembly I3! forms a one-way driving connection between the hub sections of gears I I8 and I25. It will thus b seen'that the gear I25 and its associated shaft I I9'may be driven selectively either from the power gear I I8 or the electric motor I24, the motor I24 remaining stationa'ry'when the shaft is driven from gear H0, and similarly the gear II8 being uninfiuenced when the shaft is independently driven by the motor I24. By this means it will be seen that the shaft I I9 as well as gears driven from the gear I25, later to be described, may be independently operated by the motor I24 while the gear H8 and the various mechanisms associated therewith heretofore described are not in operation. The hand wheel I22 furnishes a hand power means for the shaft H9 and its associated structures.

Referring further to Figs. 5, 2'? and 32, the gear I25 meshes with and drives a gear I 33 mounted on a stub shaft I34, the shaft also earrying a gear I35 adapted to drive a gear I36.

Gear I36 is mounted on a shaft I37, the forward end of which carries a sprocket I38 forming the driving means for the processing conveyor. Gear I35 also meshes with and drives a gear I39 which in turn drives a gear I40, the latter being mounted upon a shaft I4I which at its front end carries the transfer wheel 54. It will thus be seen that the gear I25, selectively operable, as previously described, is adapted to drive the ejector rolls 53,

a the transfer wheel 54, and the processing conveyor 55 by means of the connections described. Gear I33 also meshes with and drives a gear I43 adapted to operate a cooling water pump I44 associated with the processing conveyor.

Referring to Figs. 33 and 34, it will be seen that the sprocket I45 at the discharge end of the processing conveyor is provided with a gear I46 which, through gearing I41, I48, is adapted to drive a gear I49 associated with and forming the driving means for the removal conveyor 56.

Having described the drive mechanism of the machine, the several mechanisms operated thereby Will now be more specifically considered.

Feeding conveyor Referring to Figs. 1 to 6 inclusive, it will be seen that the feeding conveyor, generally indicated by the numeral 50, more specifically comprises an elongated frame structure I53 carrying an endless belt or the like I55 adapted to be driven at alternately fast and slow speeds by its drive gear 93. An adjustment screw I55, Fig. 2, may be provided for positioning the end roller I51 for the outer end of the conveyor, thus providing for the proper tensioning of the conveyor belt. Fig, 2 shows the outer end of the conveyor, such end being cut away from the views illustrated by Figs. 3 and 6. In this connection it is to be understood that the conveyor may be of any length suitable for the particular machine. A pair of pressure rollers, preferably rubber, I58 and I58 carried by arms I50 and I6I pivoted to a bracket I62 are provided for engaging the upper faces of the soap bars I03 as they are fed into th machine on the conveyor. The pressure rollers are urged into engagement with the soap bars by gravity, their downward movements being limited by adjustment screws I54 and I65. The pressure rolls aid in maintaining the soap bars against undesired slippage on the surface of the conveyor belt, the rectangular bars preferably being fed to the conveyor, as best shown in Fig. 2 so that they are in longitudinally alined and abutting relation.

Feed mechanism As the soap bars, being fed inwardly on the feeding conveyor, reach a feeding or loading station adjacent the wrapping wheel 52, they are fed or loaded into the Wrapping wheel from the conveyor by the feed mechanism generally indicated by the numeral 5|, and best shown in Figs. 1, 3 and 6 to 14 inclusive of the drawings.

The feeding mechanism derives its power from the three control cams 13, 14 and 15, driven from the main drive mechanism of the machine at constant speed as previously described. Cams 13 and 15 control the movements of a main pusher bar or feeding member I which transfers the soap bars from the feeding conveyor belt into the wrapping wheel, whereas cam 14 operates and controls a pair of paper clamp members or arms HI and I12, Fig. 14, which holds the wrappers in proper position against the soap bars as they are fed by the pusher into the receiving pockets of the wrapping wheel.

More specifically, control cam 13 is provided with a cam slot I13, Fig. 7, which operates and controls the movements of a pivoted bell-crank lever I14. The upper end of this bell-crank lever is provided with a, bracket I15 which threadedly receives a shaft I16 connected to and adapted to operate a slide I11 to which the pusher bar I10 is pivotally connected by a pivot connection I18, Fig. 7. The detailed construction of the slide I11 10 shaft I04 also being carried by the frame of the machine. Shafts I19 and I84 form a track structure for guiding the slide in its horizontal movements. Normally the slide moves as a unit with the shaft I16 and to this end. a compression l5 spring I85 normally holds the bracket I80, which is pivoted to the slide as indicated at I81 and through which the shaft I15 extends, in engagement with a collar I88 fixed to the shaft. However, in the event that the pusher I10 engages 2O abnormal resistance, as for example in the jamming of articles in the machine, the spring I85 will yield permitting shaft I16 to move idly within the bore of the bracket I 80.

To control the vertical movements of the pusher, control cam 15 is provided with a cam track which operates a lever I90 pivoted as indicated at I9I, Fig. 7, a second lever I52 being associated with the lever I90 for movement therewith. Lever I92 is pivotally connected to a vertically reciprocable bar I93 which is guided in its vertical movements by a stationary guide bracket I94 secured to the frame of the machine. As best shown in Figs. 7, 8, l1 and 12, the vertically reciprocable bar I93 carries a U-shaped bracket I95 having a horizontally extending trough track in which a roller I95 carried by the pusher or feeding member I10 is adapted to reciprocate. It will be seen that by means of the mechanism described the vertical pivoting of the pusher I10 may be controlled by the movements of bar I93,

While the pusher is simultaneously horizontally reciprocated by the slide I11. The slide I11 and the bar I93 are so timed in their movements that a substantially horizontal motion will be imparted to the pusher I10 as it moves to the right as seen in Figs. 7, l1 and 12 to eject the soap bar I63a which is at the feeding station from the conveyor into the wrapping wheel, the end of the pusher being returned in an upwardly directed 0 generally elliptical path so as to clear the succeeding soap bar I63b which is being fed to the feeding station by the feeding conveyor belt as the pusher feeder is being retracted for its next succeeding feeding operation. As the succeedin 5 bar reaches the feeding station, it is brought into engagement with and positioned by an adjustable stop member I51, Figs. 11 and 12.

The fast and slow movements of the conveyor belt I are also so timed with respect to the 0 movements of the pusher I10 that the slow movement of the belt takes place as the soap bar at the feeding or loading station, such as bar I63a, is being ejected from the belt, the rapid belt movement taking place after the bar has been re- 5 moved to bring the next succeeding bar, such as bar I631), quickly into position at the feeding station and into engagement with the stop I91. This type of belt movement constitutes an important feature of the invention. The rapid belt movements facilitate high speed operation of the machine, the mechanism being adapted to wrap bars at speeds in excess of two hundred bars per minute. At the same time, during the time that the bar at the feeding station is being removed from the belt conveyor by the pusher I10, the belt is moving at a relatively slow speed thus minimizing the crushing eifect of the succeeding bars against the bar being ejected. As has been previously stated, the bars are received by the machine in a wet and soft semi-plastic readily frangible condition, and if excessive pressures exist between the trailingedge of the bar being removed and the leading edge of the succeeding bar, the corners of these edges, as indicated at I63a' and [63W in Fig. 11, may be easily damaged. Additionally, the acceleration and deceleration of the belt is gradual so that no jerks or shocks are transmitted to the articles and uncontrolled slipping is minimized, the rubber pressure rolls I58 and I59 aiding in maintaining the driving relation between the belt and the bars superimposed thereon. I

As the soap bar is fed from the conveyor into the wrapping wheel it is pushed against cut outer and inner wrappers, the initial enclosing of the bars in the wrappers being accomplished as the bars are moved into the Wrapping wheel pockets. Suitable inner and outer wrapper sheets 200 and as! may be mounted in web-form upon rolls 232 and 293 respectively carried on the upper frame portion of the machine, Fig. 1, the webs being fed to the feeding station by feeding rolls Hi8 and severed into suitable wrapper lengths by cutter rolls 533 diagrammatically indicated on Fig. l, as previously described. Mechanism may also be included for causing the end o-fthe outer wrapper to extend beyond the inner wrapper end, Figs. 37 and 38, to facilitate the outer wrapper sealing, as Will be later described. As best shown in Figs. '7 and 13, as the wrappers are fed to the feeding station they are aligned and held in position by a series of adjustable positioning devices. These devices comprise a pair of adjustable brackets 205 and and a series of finger stops 231, 288 and N59 carried by a support bracket 2H] adjustably carried on the frame of the machine and adjustable by a series of adjustment screws 2| l, as best shown in Figs. 6 and 15. In addition to theseista tionary guide brackets there are the two movable clamp members ill and I12 controlled by the movement of the cam id, as previously indicated. More specifically, control cam 14 carries a cam track adapted to operate a bell-crank lever 2l5, Figs. 6 and 'l, the upper end of which is connected by means of a link, 213, adjustable'as to length, to a slide bracket 2|! shown in perspective detail in Fig. 10. This slide bracket is provided with alined openings 2i8 and 2!!! adapted to receive the bar H9 and with a bifurcated bracket portion 22%) adapted to receive the square bar I84, the bars l 19 and I 8 guiding the slide .2 ll in its horizontal movements as in the case of the slide l'l'l previously described. The slide 2H carries the movable paper clamps by means of arms 22! and 222, Fig. 14,- extending forwardly therefrom, the clamp-s themselves being provided with springpressecl presser blocks 223 and 224 at their upper ends' As will be best understood by reference to Figs. 11 and 12, the slide 2!! is so controlled by its control cam as to maintain the presser blocks in contact with the wrappers, holding them in The initial folding of the wrappers around the bar as it is moved into the wrapping wheel is diagrammatically indicated in Figs. 37 and 38 of the drawings.

Conveyor or wrapping wheel and packaging mechanism The conveyor or wrapping wheel 52 and its associated packaging or Wrapper folding mechanism is best illustrated in Figs. 1 and to 25 inclusive of the drawings. The wrapping wheel, Figs. '15,

10 21 and 22, moves counterclockwise as seen in Figs.

15 and 21. It is provided with a series of circumferentially disposed article or package receiving pockets 230, the trailing wall 23! of each pocket being fixed and the leading wall 232 of each 5 pocket being in the form of a pivoted lever springurged by compression springs 233 into pocketclosing or bar-gripping position. Each lever '232 i pivoted a indicated at 234 and is provided with an extending arm 235 carrying a roller 2 36 at its end adapted to bear against the'periphery of a fixed cam 23?. Referring .to Fig. 21, it will be seen that the contour of cam 231 is such as to permit springs 233 to move the levers 232 into pocketclosing positions as each pocket becomes alined with the feeding pusher I 10 at the loading station to receive the soap bar and wrapper therefrom, the pocket remaining closed in bar-gripping posi. tion as the bar and wrapper are moved past the several wrapping devices until the pocket is moved a distance of approximately I80 degrees to a discharge position at the transfer wheiel 54-whereupon the cam causes the pocket lever to be opened so that the wrapped bar may be readily withdrawn by the ejector rolls 53. I

As has been previously explained, the Wrappin wheel being driven from the speed variator devices 19, 82, it is moved at gradually accelerating and decelerating alternate fast and slow speeds. By this means the movements of the wheel pockets 4() will be slowed down at predetermined points to facilitate the loading or unloading of the pockets and the operation of the various wrapping mechanisms upon the bars and wrappers carried thereby, and speeded up in their transit between such points to increase the speed, of operation of the machine. At the same'time the entire mechanism moves without jerks or shocks, thedriving arrangement thus preserving the advantages of an intermittently operable wrapping wheel structure '50 without the disadvantages thereof. More specific cally, the wrapping wheel is operated at its slow point of travel when in the position illustrated in Figs 15 and 21, when the soap bars are being fed thereto by the pusher I10 and removed therefrom 55' by the ejector rolls 53.

After the bars have been loaded into the wrap ping wheel pockets, and as the pocketsmove counterclockwise from the loading or feeding station, the side edges 240 and 24! of the wrappers 6 project radially outwardly from the bars as best indicated in Figs. 21 and 38. The wrapping wheel has a fixed guide 242, Fig. ,21, associated therewith, the advance or left edge of which is'provided with a folding lip 243 which is adapted to.

understood byreference to Fig. 21, and also to the diagrammatic views, Figs. 39 and 40. The tucking member 244 is pivotally mounted upon one arm of a lever 245 which lever is in turn pivotally mounted on the frame of the machine as indicated at 246. Fig. 24. A spring 241, Fig. 40, yieldingly urges the tucking member into engagement with the surface of the soap bar during the wrapper tucking operation. The lever 245 is'operated by a link 248, adjustable as to length, and pivotally connected to the lever arm 245a as indicated at 249, Figs. 22 and 24. The link 243' is 'in'turn-pivotally connected to and operated by the crank member H2, Figs. 21 and 26, driven from the main drive mechanism of the machine,-as previously described. It will be seen that gas the crank is rotated, lever 245 will be oscillated upon its axis 246 to reciprocate the tucking member 244 and effect the tucking action'described. After the side edges of the wrapper. have thus been folded into position, they are maintained in folded position continuously while the soap bars are in the wrapping Wheel by the fixed guide 242.

As the partially wrapped soap bars reach a position displaced approximately 90 degrees from the feeding or loading station, a series of end folding members become operative upon the projecting end portions of the wrapper, performing the necessary folding operations upon the projecting wrapper ends and thus completing the folding of the wrappers. The sequence of the end folding operations will be best understood by reference to Figs. 41, 42, 43 and 44. It will be seen that upper and lower end folding members 255 and 256 are first simultaneously operable to effect the creasing and forming of the underlying end folds. Just as folders 255 and 256 start to withdraw, a rotary folder 251 becomes operative to form the trailing overlying fold, and substantially simultaneously as the package continues its' movement in the wrapping wheel a stationary folding pin 258 becomes operative to partially 'fold the leading overlying end fold into position; the folding being completed and the completed end folds being held in folded position upon continued movement of the package by'a side wall section 259 formed as a part of the guide structure 242, previously described. It is to be understood that similar end folding and holding devices are provided for operation upon the projecting wrapper ends at bothends of the package.

More specifically, referring to Figs. 15, 16 and 19, it wil be seen that the upper endfolding member 255 is carried by a bracket 265 mounted on the upper end of a crank arm 266, th lower end of which is pivotally connected as indicated at 261 to a crank disc 268 carried at one end of.

a shaft 269. The other end of the shaft carries a gear.216 which is adpated to be driven by the gear Hill which is operated at constant speed by the main drive mechanism of the machine, as previously described. Crank arm 266 carries a roller21l adapted to slide within a substantially vertical guide track 212 formed in guide block 213 mounted upon the frame of the machine. It will beseen that as the crank disc 268 is rotated clockwise, as seen in Fig. roller 211 will be vertically reciprocated Within the guide track of the guide block 213, thus imparting a generally elliptical motion to the folding member 255. The major axis of this elliptical path of travel is vertical, and the horizontal component of the movement allows the folding member to move with the package as it is transported by the wrap ping wheel. In other words, as the folding member 255 is moved downwardly, as seen in Fig. 15, into engagement with the wrapper end to effect the folding operation, itsimultaneously moves to the right while in contact with the package to accommodate the movement of the folding member to the translation of the package in the pocket of the wrapping Wheel. The wrapping wheel is preferably arranged to be moving at its slow rate of travel during the engagement of the folding member, thus allowing sufficient time for its operation and without requiring a rapid horizontal component of movement. Referring more particularly to Fig. 41, it will be noted that the folding member 255 is provided with two fingers 215 and 216, the former constituting the folding member for the upper underlying end fold and the latter being a guide for the trailing edge of the wrapper.

The folding member 288 which performs the functions of folding member 255 upon the other end of the package wrapper is similarly shaped and partakes of similar movements. To this end it is carried at the upper end of a crank arm 23f, the lower end of which is pivotally connected as indicated at 282 to the gear 216, the construction being best understood by reference to the detail View of this mechanism as shown in Fig. 13. Crank arm 28! is also provided with a roller 233, Figs. 16 and 18, slidable within the substantially vertical guide track of a guide bracket 284, so that as the gear 21%! is rotated clock-wise as seen in Fig. IB, an elliptical movement is imparted to the folding member 282 in a manner and for a purpose as previously described with reference to folding member 255.

The lower end folding member and its manner of operation will be best understood by reference to Figs. l6, 19, 21 and 23. It will be seen that this folding member, generally indicated by the numeral 296 in Fig. 23, not only carries the folding plate 256, previously described, but is also provided with a second folding plate 29f for cooperation upon the opposite end of the package, the folding plates 25% and 29! being carried by support arms 292 and 223 respectively. The lower end of folding member 296 is pivotally connected as indicated at 294 to the gear I06, and the arm 293 of the member is provided with a roller 295 operable within a generally vertical guide track formed in a guide block 296 as best shown in Figs. 16 and 21. It will be seen that as the gear Hill is rotated counterclockwise, as seen in Fig. 21, a generally elliptical path of movement will be imparted to the folding members or plates 256 and 29! and more specifically as the folding members are raised into engagement "with the projecting Wrapper ends to effect the folding operation, the folding plates will be simultaneously moved to the right, as seen in Fig. 21, while in contact with the wrapper whereby to accommodate for the move ments of the package with the wrapping wheel as previously described in connection with the action of the upper end folding members 256 and 280. 'As also previously described, the upper and lower end folding members may be substantially simultaneously operable at the slow point of movementlof the wrapping wheel. It i to be noted that the folding plates 256 and 29! are provided with directly operable foldin fingers 291 and 228 as well as With guide fingers 299 and 3336 respectively engageable with the trailing wrapper edge portions.

The rotary end folding members and their as-

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