US2497124A - Mechanism for handling production from cup forming machines or the like - Google Patents

Description

Feb, 14, 19% L. M. HARVEY 2,497,124 MECHANISM FOR HANDLING PRODUCTION FROM cup FORMING MACHINES OR THE LIKE Filed March 28, 1944 12 Sheets-Sheet l gum i lgum 5 Feb. 14, 11950 M. HARVEY 2,497,124

MECHANISM FOR HANDLING PRQDUCTION FROM CUP FORMING MACHINES OR THE LIKE Filed March 28, 1944 12 Sheets-Sheet 2 Feb. 14% 11950 M. HARVEY 2,497,124

MECHANISM FOR HANDLING PRODUCTION FROM CUP FORMING MACHINES OR THE LIKE Filed March 28, 1944 1?. Sheets-Sheet 3 Feb M, 11950 L. M. HARVEY 2,497,124

MECHANISM FOR HANDLING PRODUCTION FROM cup FORMING MACHINES OR THE LIKE Filed March 28, 1944 12 Sheets-Sheet. 4

Feb. 114-, 1950 HARVEY 2,497,124

MECHANISM FOR HANDLING PRODUCTION FROM CUP FORMING MACHINES OR THE LIKE Filed March 28, 1944. 12 Sheets-Sheet 5 //7 ew/0r A e0 M Hm" may Feb. 14,3950 L. M. HARVEY 2,497,124 MECHANISM FOR HANDLING PRODUCTION FROM cup FORMING MACHINES OR THE LIKE Filed March 28, 1944 x12 Sheets-Sheet 6 Feb. 14, 1195@ HARVEY 2497 124- MECHANISM FOR HANDLING PRODUCTION FROM CUP FORMING MACHINES OR THE LIKE I 12 Sheets-Sheet 7 Filed March 28, 1944 h men/ ar X60 lf l/ar veg Feb, M 1956) L. M. HARVEY MECHANISM FOR HANDLING PRODUCTION FROM CUP FORMING MACHINES OR THE LIKE l2 Sheets-Sheet 8 Filed March 28, 1944 //7 Mania 1 M. f/Or my Fi e/wee Feb, M 1195i? 1.. M. HARVEY 29497791124 MECHANISM FOR HANDLING PRODUCTION FROM CUP FORMING MACHINES OR THE LIKE Filed March 28, 1944 1 .2 Sheets-Sheet 9 Feb. M, 195% L. M. HARVEY 2,497,124

MECHANISM FOR HANDLING PRODUCTION FROM 00? FORMING MACHINES OR THE LIKE Filed March 28, 1944 12 Sheets-Sheet 1O Feb. 114%, 1950 L M HARVE Y 2,497,124 MECHANISM FOR HANDLING PRODUCTION FROM CUP FORMING MACHINES OR THE LIKE Filed March 28, 1944 12 Sheets-Sheet ll //7renf0r Z60 M. flarve y MECHANISM FOR 'HANIDLING PRODUCTION FROM OUR FORMING MACHINES OR THE LIKE Filed March 28, 1944 12 Sheets-Sheet 12 Feb. M, 1950 M HARVEY 2,497,124

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Patented Feb. 14, 1950 MECHANISM FOR HANDLING PRODUCTION FROM CUP FORMING MACHINES OR THE LIKE Leo M. Harvey, La Canada, Calif.

Original application December 17, 1942, Serial No.

Divided and this application March 28, 1944, Serial No. 528,384

13 Claims. 1

This invention relates to a construction or mechanism for handling the output or production of a cup forming machine or the like and it is a general object of the invention to provide such a mechanism which is effective and practical for the removal of cups when finally formed by the cup forming machine and for stacking such cups in nested formation.

This application is a division of my copending application entitled Machine for making paper cups, filed December 1'7, 1942, Serial No. 469,306, which has matured into Patent No. 2,435,308.

Another object of this invention is to provide an improved paper cup machine having novel and very effective cup transferring means for transferring the finished cups from the die means to the cup stacking means.

Another object of this invention is to provide a machine of the character referred to embodying a novel stacking means for stacking the cups one within the other at any selected degree of compression or tightness, thus facilitating the packaging of the finished cups.

The various objects and features of my invention will be fully understood from the following detailed description of a typical preferred form and application of my invention, throughout which description reference is made to the accompanying drawings, in which:

Fig. l is a front elevation of the machine provided by this invention. Fig. 2 is, a side elevation of the machine showing the paper supply and feed means. Fig. 3 is an enlarged plan l vation .of the machine with the most elevated parts appearing in horizontal cross section. Fig. 4 is an enlarged fragmentary vertical detailed ect a v w il tra in he ie me ns in the operated condition and showing adjacent parts of the machine. Fig. 5' is a view similar to Fig. 4 illustrating the cup ejecting .or stacking means, a portion of the paper feed means, the scrap cutting means, etc. Fig. 6 is an nlarged longitudinal detailed sectional view of the main clutch of the machine. Fig. 6 is an elevation View of one of the cams of the clutch shown in Fig. 6. Fig. 7 is a transverse detailed sectional view taken as indicated by line i! on Fig. 6. Fig. 8 is an enlarged longitudinal detailed sectional view of a sprocket and clutch assembly embodied in the paper feed means of the invention. Fig. 8 is a fragmentary transverse detailed sectional view of the free running clutch means of the structure shown in Fig. 3. 9 is an enlarged fragmentary vertical detailed sectional view of a portion of the paper feed means. Fig. 1.0 is an enlarged fragmentary horizontal detailed sec.- tional view illustrating the cup transferring means. Fig. 11 is a plan View of certain elements of the cup transferring means showing the two positions of the cups during the stage trans.- ference and illustrating the different positions of the transferring elements. Fig. 12 is a fragmentary vertical detailed sectional View illustrati-Ilg a portion of the means for actuating the cup transferring elements. Fig. .13 is an enlarged fragmentary vertical detailed sectional view showing the mechanism foroperating the cup transferring means. Fig. 13 is a vertical dc.- tailed sectional view of the adjustable connection between the walking beam and the chains. Fig. 14 is an enlarged fragmentary vertical detailed sectional view illustrating the several means for operating the dies. Fig. 15 is an enlarged fragmentary vertical detailed sectional view taken as indicated by line l5-i5 on Fig, 14. Fig. 16 is an enlarged fragmentary vertical detailed sectional view showing the dies in the position preceding the bead forming operation. Fig. '17 is a View similar to Fig. 16 showing the dies in position at or near the completion of the bead. Fig. 18 is a diagrammatic viewil'lustrating the paper feed means and the cup transferring means. Fig. 19 is a fragmentary diagrammatic view of the paper feedin means, Fig. 20 is a vertical detailed sectional view of the flute forming die removed from the machine. Fig. 21 is a view similar to Fig. 20 illustrating the flute forming punch. Fig. 322 is a bottom elevation of the flute forming die. Fig. 23 is ,a plan elevation of the flute forming punch. Fig. 24 is a vertical sectional view of the scrap cutting means apart from the other elements of thefmachine with certain of the members in side elevation. Fig. 25 is an enlarged plan View of a cup blank after the flutes have been formed therein. Fig. 26 is an enlarged side elevation of the blank provided with the flutes. Fig. 27 is a side elevation of the cup following the flute forming, cup shaping and ironing operations and Fig. 23 is a fragmentary side elevation of the completed cup.-

The cup forming machine embodying the present invention may be said to comprise, generally, a supporting and housing case It, a power means or drive means H for driving or operatingth'e various mechanisms of the machine, a paper feed means iii, a die mechanism 13 which receives the paper from the feed means i2 and cut-s it into blanks and forms paper cups therefrom, a cup transferring and stacking mean I4 for withdrawing the completed cups from the mechanism l3, and scrap handling means I5.

The case I supports the various elements of the machine and houses portions of the drivin means II and associated parts. The case ||l may be a generally square or rectangular upright boxlike structure. The opposite sides of the case II] are provided with access Openings closed by hinged doors l6. The top of the case I0 is flat and horizontal to carry certain elements of the paper feed means l2, the die mechanism l3, etc. The walls of the case are closed and sealed to prevent the escape of the lubricant for the driving mechanism. The lower portion of the case It may be provided with a suitable base l1 adapted to rest on th floor or other support.

In the preferred form of the invention the machine is entirely self-contained and embodies its own power means. In the construction illustrated the power means includes a suitable electric motor M mounted on a bracket l8 secured on a wall of the case H]. The motor M is mounted on, what I will term, the rear side of the case I. The drive means II is characterized by a single crank shaft 9 and all of the working parts of the machine are driven from this single crank shaft. In the preferred construction illustrated, the motor M is mounted to have its shaft horizontal and the crank shaft I9 is rotatably mounted in the lower portion of the case I9 to be below the shaft of the motor M and to extend at right angles to the motor shaft. The crank shaft I9 is rotatably supported by suitable spaced bearings in the case. A clutched worm drive is provided between the motor M and the crank shaft I9.

The clutched drive includes a flanged mounting plate or carrier 2| secured to the rear wall of the case ID by screws 22 and having a hub 23 which projects freely through an opening 24 in the case wall, see Figs. 6 and 7. The hub 23 has an inward extension 25 which projects some distance into the case It]. A horizontal shaft 26 extends longitudinally through the hub 23 and its extension 25 and continues outwardly from the case In. An anti-friction bearing 21 in the carrier 2| and an anti-friction bearing 28 in the inner part of the extension 25 support the shaft 26 for free rotation. The bearing 21 has shouldered engagement in the carrier 2| and is retained by a ring 29 secured to the carrier 2| by screws 30. A nut 3| is threaded on the shaft 26 at one side of the bearing 21 and a rib or annular flange 32 is provided on the shaft at the other side of the bearing 21 so that the shaft 26 is held against endwise movement. A nut 33 is provided on the inner extremity of the shaft 26 at one side of the bearing 28 and a bushing or spacer 34 is provided on the shaft at the other side of the bearing 26 and these elements may assist in holding the shaft against endwise movement.

A worm 35 is fixed or keyed on the shaft 26 at the end of the spacer 34 and meshes with a worm wheel 36 keyed to the crank shaft I911. The under side of the hub extension 25 is open to pass or admit the worm wheel 36. The worm gearing operatively connects the clutch shaft 26 with the crank shaft |9a.

The power means or drive means further includes a pulley 31 rotatably supported on the projecting portion of the clutch shaft 26 at the exterior of the case I0. A belt 38 operates over the pulley 31 and a pulley 39 fixed on the shaft of the motor M so that the pulley 31 is driven by the motor.

The pulley 31 may be proportioned 75 to serve as a fly wheel and has a long hub 40 which surrounds the projecting portion of the shaft 26 in spaced relation thereto. An antifriction bearing 4| rotatably supports the inner portion of the pulley 31 on the clutch shaft 26. The bearing 4| has shouldered engagement in the pulley 31 and has its inner end engaged against the flange 32. An anti-friction bearing 42 is mounted on a reduced outer end portion of the clutch shaft 26 and rotatably carries the outer part of the pulley hub 40. The inner side of the bearing 42 engages against a shoulder on the shaft 26 and a nut 43 is provided on the end of the shaft to retain the bearing 42 and to assist in preventing endwise movement of the pulley 31. A cap 44 may cover the nut 43. It i preferred to provide a sealing means or sealing assembly 45 on the above mentioned ring 29 to seal between the ring and the hub of the pulley 31 to retain lubricant within the clutch assembly and to prevent the entrance of dirt into the assembly.

The clutch of the drive means includes a sleeve 46 freely slidable on the shaft 26 and located between the nut 3| and the worm 35. An external annular groove 41 is provided in the sleeve 46. Fork means is provided for shifting the sleeve 46 back and forth and includes a shaft or pin 48 turnably carried by spaced lugs 49 on the upper side of the hub extension 25, see Fig. '7. A fork 50 is pivotally supported by the pin 48 between the lugs 49 and projects dcwnwardly through an opening 5| in the upper wall of the extension 25. A yoke 52 is located between the arms of the fork and is pivotally secured thereto by pins 53. The yoke 52 engages in the groove 41 of the sleeve 46.

Manual means is provided for effecting longitudinal shifting of the sleeve 46. A clutch handle or lever 54 is mounted on a side of the case [0 at a conveniently accessible point near the upper end of the case, see Fig. 1. A suitable mechanical linkage 55 operatively connects the lever 54 with the fork 50. It will be seen how manual operation of the lever '54 will result in axial shifting of the sleeve 46 back and forth along the clutch shaft 26.

The clutch means further includes an assembly of friction discs 56 arranged within the outer portion of the pulley hub 49 and an operative connection between the shiftable sleeve 46 and the disc assembly for controlling or operating the latter. The discs 56 are disposed within a tubular shell 51 fixed in the pulley hub 40 and are engaged between spaced collars 58 secured on the shaft 26. Alternate discs 56 are keyed or fixed to the shaft 26 and the intervening discs 56 are keyed or fixed to the shell 51. The discs 56 are adapted to freely pass one another without engagement or appreciable friction when the clutch is released.

The means for operating or controlling the clutch disc assembly 56 includes a sleeve 59 freely surrounding the shaft 26 within the pulley hub 46. An inner sleeve 60 is spaced within the sleeve 59 and is secured to the shaft 26 by a pin 6| or other means. The inner sleeve 60 carries one or more pivoted dogs 62 which are operable to compress the clutch disc assembly 56 to provide for the transmission of rotation between the pulley 31 and the clutch shaft 26. The dogs 62 act against the inner collar or ring 58. Outward movement of the outer sleeve 59 serves to actuate the dogs 62 to provide the clutching engagement at the discs 56. Pins 63 project inwardly from the outer sleeve 59 and are adapted to have camming engagement with the dogs 52 to pivot or actuate the dogs when the sleeve 59 is shifted outwardly.

An operative connection is provided between the fork operated sleeve 46 and the dog actuating sleeve 59. The clutch shaft 26 is bored from its inner end to have a longitudinal opening 64. A shift pin 65 is shiftable longitudinally in the opening 54. The shift pin 65 serves to transmit movement from the sleeve 46 to the sleeve 59. A longitudinal slot 65 is provided in the shaft 26 to communicate with its opening 64 and a pin 61 is engaged in or secured to the sleeve 46 and engages with or is connected to the shift pin 65 to connect the yoke and shift pin. A longitudinal slot 68 is provided in the clutch shaft 26 at a point spaced outwardly from the bearing 41 and a pin 69 is secured to or carried by the outer shaft sleeve 59 and operates in the slot 68. In practice the pin 69 may pass completely through the slot 68 and through an opening in the shift pin 65. The pins 61 and 69 have sufficient Iongitudinal movement in their respective slots 56 and 58 to provide for movement of the sleeve 59 between the position where the clutch is released and the position where the clutch disc assembly 56 is engaged to transmit rotation from the pulley 31 to the clutch shaft 25.

It is preferred to incorporate a brake means in the clutched drive so that the mechanism may be quickly stopped when the clutch is disengaged. U J

This means may include a tubular brake ring secured within the hub .23 and having shouldered engagement in the hub. The brake ring 10 has a tapered internal surface. The sleeve 46, which surrounds the clutch shaft 26 and which is operated by the fork and yoke assembly, carries a tapered or frusto-conical brake part II which is engageable in the ring 10 to brake movement of the machine parts.

It will be seen that when the clutch handle or lever 54 is moved in one direction the sleeve 46 moves outwardly so that the shift pin 65 and outer sleeve 59 likewise move outwardly and upon outward movement of the sleeve 59 the pins 63 actuate the dogs 62 to engage the disc assembly 56 for the transmission of rotation from the pulley 31 to the shaft and thus drive the crank shaft l9. Upon movement of the clutch lever 54 in the other direction the sleeve 46, the shift pin 65 and the sleeve 59 are moved inwardly to release the disc assembly 56 and thus disengage the clutch and the brake part II is brought into cooperation with the brake ring 19 to stop movement of the machine parts. It is to be understood that a suitable switch means is provided I for the control of the motor M.

The feed means l2 operates to intermittently advance or feed a web of paper or other material to the mechanism l3 which cuts the cup blanks therefrom and then forms the blanks into the completed cups. The feed means I 2 embodies several important features. For example, it embodies means for supporting or employing a large-capacity supply roll I2 of waxed paper, or the like, and automatically intermittently withdraws a predetermined length of paper from this supply and delivers it to the cutting and forming mechanism 13 in timed relation thereto. The feed means [2 is readily regulable to advance any desired amount or length of the paper or material to provide for the making of cups throughout a very wide range of cup sizes. This adjustment, together with appropriate changes in the dies of the mechanism 13, adapts the single machine for the manufacture of a wide range of containers 01 cups. The feed means I2 operates in timed synchronism with the mechanism I3 and is positive and eflicient in its feeding of the paper as the supply roll reduces in diameter until completely exhausted.

The feed means I2 includes a structure for supporting a supply of the material or paper of which the cups are to be formed. This structure may include a support or bracket l3 mounted on the front of the case if! and carrying a pair of forwardly projecting rigid arms 16. A horizontal shaft '55 extends between and is supported by the outer portions of the arms 14. The shaft 15 serves to carry the supply roll 12 of paper.

The roll 12 comprises a single continuous web or length of waxed paper or other material of which the cups are to be formed. As illustrated, the shaft 75 is adapted to carry a large supply roll 32. Adjustable spools '16 are provided on the shaft 15 to center and support the roll 12, Fig. 3. It is to be understood that the roll 12 is readily replaced when exhausted. The supply roll 12 is positioned so that the web or strip S of the paper passes from the upper portion of the roll toward the front of the case I0.

Idler means is provided to prevent the development of slack in the strip S as it passes from the roll 12 to the feed means proper of the machine. A pair of levers or arms Ti is pivotally supported on the end portions of the shaft 15 and projects rearwardly toward the case It A shaft 18 extends between the end portions of the arms 11 and supports a freely rotatable roll 19. This roll 19 is in the nature of an idler or tensioning roll. The paper strip S passes down under the roll 19 and continues back up to the feed means proper of the machine. It is preferred to spring load the arms Tl so that a proper tension is maintained on the strip S and so that the paper will not buckle or develop excessive slack. In the construction illustrated leaf springs 86 are secured to the bracket arms 14 and bear downwardly on the arms 1'! so that the idler roll 3'9 is constantly urged downward.

The feed means I2 further includes a pair of spaced feed rolls 8! and 82 for advancing the strip S across the top of the machine, see Figs. 9 and 18. Mounting means or brackets 83 and 64 are provided on the front and the rear walls respectively of the case it adjacent the top of the case to carry the feed rolls 8! and 82 and the associated parts. The feed rolls 8! and 82 are carried by horizontal shafts which are rotatably supported by suitable bearings 85 on the brackets 8-3. It is preferred to face or cover the feed rolls 8| and 82 with rubber or friction material to assure the positive advance of the paper strip S. In accordance with the invention the feed rolls 8| and 82 are connected for simultaneous intermittent rotation. A sprocket 86 is provided on an end of each feed roll 8| and 82 and an endless chain 81 operates over the two sprockets 86. The chain 8? is operated or driven by the power means by a drive to be described below. A roll 88 is located above the forward feed roll 8i to cooperate with the paper strip S to maintain the strip in frictional cooperation with the feed roll so that the strip is positively advanced. The roll 85 is carried by a shaft 89 which is eccentric with respect to its end portions 9% see Fig. 18. These end portions are turnably mounted in suitable bearings 95 on the forward bracket 83 and a lever or handle 92 is fixed to one end of the shaft 89 so that the shaft may be manually turned. The operator may move the roll 88 into and out of cooperation with the strip S by merely shifting or operating the handle 92. When the handle 92 is moved in one direction the roll 88 is lowered to press against the strip S and thus maintain the strip in engagement with the forward feed roll 8I to be advanced by the same. When the handle 92 is turned in the other direction the roll 88 is raised from the strip S and the strip is no longer driven or advanced by the roll 8!. Thus, the movably supported roll 88 forms a convenient means for initiating and stopping the advancement of the paper strip S as required during operation of the machine. A roll 93, similar to the roll 88, is provided above the rear feed roll 82. The shaft of the roll 93 is carried by suitable bearings 94 on the rear bracket 84. The roll 93 has its axis spaced forwardly from the axis of the rear feed roll 92 so that it is par ticularly effective in maintaining the paper strip S in engagement with the face of the roll 82. It is preferred to face or cover the rolls 88 and 93 with rubber or friction material. The rear driving roll or feed roll 82 advances or ejects the scrap paper remaining after the cup blanks have been cut from the strip S by the mechanism The machine preferably includes means for aiding in removing or withdrawing the paper strip S from the supply roll I2. cludes a pair of arms 95 pivotally supported by a pin 96 secured to the forward bracket 83. The arms 95 project forwardly and downwardly to pass above the center of the supply roll i2 and are preferably curved upwardly so that they do not interfere with the supply roll. A horizontal pin or shaft 91 is carried by the outer ends of the arms 95 and a roll 98 is freely rotatable on the shaft 91. The roll 98 is adapted to engage or bear downwardly against the periphery of the supply roll 72 and is faced with rubber or friction material to have driving engagement with the outermost convolution of the roll. The drive for the roll 98 comprises a flat rubber belt 99 operated over the above described roll 88 and the roll 98. There may be a single centrally disposed belt 99 engaged in annular grooves in the rolls 88 and 98. The belt 99 passes over an idler pulley I on the pin 96 and engages over a second idler I0! spaced forwardly from the pulley I00. The rubber belt 99 is extensible and contractible to compensate for changes in the angular position of the arms 95 as the diameter of the supply roll 12 grows less during operation of the machine. It will be seen that the forward feed roll 8! drives the adjustable roll 88 and that the belt 99 operatively connects the roll 98 with the roll 88 so that the roll 98 is effectively driven. The rotating roll 98 assists in rotating the feed roll I2 and in advancing the paper strip from the surface of the supply roll.

The drive for the feed means I2 is characterized by its adjustability whereby the material strip S may be advanced any selected or required distance during each phase of operation. The drive for the feed means includes a walking beam I02 having one end supported by a pivot pin I03 fixed on a wall of the case I9, see Fig. 13. The walking beam I02 is arranged within the lower portion of the case l0 and is spaced above the crank shaft I9. The walking beam I02 extends in a direction transverse of the crank shaft I9. bearing I05 engaged on the intermediate crank I06 of the crank shaft I9 and has its other end This means in- A connecting rod I94 has a connected with the walking beam I02 by a pin I07. During each revolution of the crank shaft if! the walking beam I02 swings or pivots up and down. A pair of flexible elements or driving chains is connected with the walking beam I02 and extends to a compound sprocket I09 positioned below and adjacent the feed chain 8'1.

It is a feature of the construction that the connection of the chains I08 with the walking beam I 02 is adjustable along the beam to vary the stroke or movement of the feed chain 81 and, therefore, vary the extent of advancement of the strip S. A longitudinal slot II 0 of substantial length is provided in the upper portion of the Walking beam I02. A block III is shiftable along the slot and carries a yoke II2 which projects above the beam. The engagement of the block III in the slot IIO holds the block against turning. A pin II3 passes through openings in the yoke H2 and carries an equalizing bar H4. The lower ends of the spaced chains I08 are anchored to the opposite end portions of the equalizing bar H4.

Accurate and conveniently operable means is provided for adjusting the block II I along the slot H0 to shift the point of connection of the chains I08 with the beam I02, moving this point of connection toward or away from the axis of the walking beam I 02 as required to regulate the stroke or advancement of the strip S. This adjusting means includes a screw H5 extending longitudinally through the slot H0 and having screw threaded engagement in an opening in the block I I I. The screw H5 is engaged in an opening I IS in the walking beam I02 to be held against longitudinal movement and has a head I I! on its outer end exposed at the end of the beam I02 for ready engagement by a wrench or the like. A look nut H8 is threaded on the screw H5 to normally lock or hold the screw against rotation. The screw head H1 and the nut II8 are located to be readily engageable by a wrench or similar tool inserted through an opening in the rear wall of the case I0. It will be seen that upon loosening the nut II8 the screw II5 may be rotated to shift the block II'I toward or away from the pivotal axis of the walking beam I02 to shorten or lengthen the stroke or movement imparted to the chains I08.

The compound sprocket I09, which is best illustrated in Fig. 8 of the drawings, is a clutched sprocket for producing movement of the chain 81 when turned by downward movement of the chains I08 but which imparts no motion to the chain 81 during the return stroke of the walking beam I02 and its chains I08. The sprocket I09 comprises two bolted together sections II9 provided at their outer ends with sprocket teeth I20. The chains I08 are trained over the series of teeth I and are anchored or fixed to the sprocket II9 as at I2I in Fig. 18. The sprocket sections II9 are tubular having a central longitudinal opening I22 which receives a horizontal shaft I23 with substantial clearance. The sprocket I09 is supported on the shaft I23 by antifriction bearings I24 so that it may have free rotation on the shaft. A central internal annular groove I25 is provided in the sprocket sections H9 and a ring I26 is fixed in the groove. The ring I28 has a series of annular internal pitched faces I21, each terminating in an abrupt shoulder I28. A collar I29 is keyed to the shaft I23 within the sprocket I09 and has an annular enlargement or flange I 30 which extends into the above mentioned groove I25. The flange I30 is provided with a finished cylindrical concentric peripheral surface.

A ball or roller member I3I rides on each pitched surface I2'I of the ring I26 and the members are cooperable with the periphery of the flange I30. Springs I32 are engaged between the shoulders I28 and the members l3I to yieldingly urge the members to ride down the faces I27 into cooperation with the peripheral surface of the flange I30. When the sprocket I09 is turned in a clockwise direction, as indicated by the arrow in Fig. 18, the members I3I are caused to ride inwardly on the surfaces I21 and thus almost immediately bind between the surfaces I21 and the periphery of the flange I39 to transmit rotation from the sprocket I09 to the shaft I23. When the sprocket I09 is given retrograde movement the members I3I ride back or out on the surfaces I2? and the sprocket I09 is free to turn without producing rotation of the shaft I23. The shaft I23 extends outwardly beyond both ends of the clutched sprocket I09 and is rotatably supported at one end by an anti-friction bearing I33 carried by a flange or bracket I34 of the case I9. A spacer I35 is provided on the shaft I23 between the bearing I33 and the adjacent bearing I24. The collar I29 within the sprocket I09 serves to space the two bearings I24 and the bearings have shouldered cooperation with the sprocket I99. A nut I35 is threaded on the shaft I23 and clamps against the outermost bearing I24. It will be seen that the structure just described serves to hold the clutched sprocket I09 against axial movement along the shaft I 23.

The shaft 123- of the clutched sprocket I09 carries a sprocket I31 for driving the chain 9?. The sprocket I3! is keyed on the end portion of the shaft 23 which projects beyond the bearing I33. A screw I38 is threaded in the end portion of the shaft I23 and clamps a washer I39 against the hub of the sprocket I31 to hold the sprocket in against the bearing I33, which in turn bears inwardly against the spacer I35. A lubricant passage M9 leads inwardly through the shaft I23 from the outer end of the screw I38 to carry lubricant to the interior of the collar D29 which has a lubricant channel I4I leading to the bearings I24.

Ihe drive sprocket I31 keyed to the clutch shaft 523 is spaced below and forwardly of the rear feed roll 82 and an idler sprocket I 42 1s spaced below the feed r011 sprocket 35 to direct the chain Bl over the drive sprocket I31. The idler sprocket I42 has an eccentric shaft I43 carried by suitable bearings I44 on the rear case bracket 84 and the eccentric shaft may be adjusted or turned so that the idler sprocket E42 takes up any slack that may develop in the chain 9?. It will be seen that upon the downward stroke of the walking beam I02 that the chains E58 cause rotation of the sprocket I99 and this rotation is transmitted to the drive sprocket I3! through the clutch members I3! and the shaft I23 so that the chain 81 is moved a given distance to advance a pre-determined length or portion of the paper strip S to the cutting and cup formmg mechanism I3.

Means is provided to turn back or return the clutched sprocket I09 during the upward strokes of the walking beam I92. This means is preferably a spring means associated with the clutched sprocket I 09. In the preferred construction illustrated the spring return for the sprocket I09 includes an anchor block I45 secured in an opening I45 of a flange or bracket I-47 in the case Ill. The block I45 is tubular to receive the projecting end portion of the shaft I23 and the block I45 may be of suificient length to partially telescope over the nut I36. A cup or flange I50 may be provided on the adjacent end of the sprocket I99 to telescope over the end portion of the anchor block I45 with substantial clearance. A coiled torsional spring I48 SLHIOLlIldS the anchor block I95 and has an out-turned end portion engaged in a slot 549 in the flange I50 and has its other end portion anchored in an opening I'5I in the anchor block I45. When the sprocket I09 is turned during the downward stroke of the walking beam 502 the spring I48 is subjected to torque or increased torque and energy is stored up in the spring. When the walking beam I02 begins its upward stroke the spring I48turns the sprocket 599 back so that the chains I08 are rewound on the sprocket. The spring I48 operates to completely restore the sprocket I09 during each upward stroke of the walking beam I02 to prepare the sprocket for the next active stroke. During the return movement of the sprocket I09, that is, during the upward stroke of the walking beam I02 the clutch members i3I ride outward on the surface I2! or at least do not Wedge between the surfaces I21 and the periphery of the flange I39 and the sprocket I09 is turned back without producing rotation of the shaft I23. Accordingly, the drive chain 81 of the paper feed means remains stationary during the return strokes or upward strokes of the walking beam I02. It is to be observed that the feed means I2 described in detail above is entirely automatic and p ra e t adva e the p per s rip a given distance, that is to supply a given amount of paper to the mechanism I2, during each revolution of the chank shaft I9.

The mechanism I3 receives the strip S as it is advanced by the feed means I2 and cuts a disc 40 shaped cup blank from each strip portion thus I advanced and then performs a number of operations on the blank to shape the same into a complete strong, self-sustaining container or cup having a beaded or rolled rim. The mechanism I3 performs the several operations during the time period required for the advancement of each portion of the strip S, that is, during each complete up and down cycle of the walking beam I 02 and the mechanism I3 may be operated rapidly to form a large number of completed cups per minute. The blank cutting and forming mechanism I3 comprises a number of forming dies and punches assembled and operated in concentric relation relative to a single axis so that all of the cup blank cutting and cup forming operations occur while the cup remains on a single axis. In the preferred structure illustrated the cup .0 moves but a short distance along a vertical axis without turning or rotating and is at the l pper 0 part or side of the case I0 at all times so that it cannot be soiled by the lubricant of the drive means, etc.

The mechanism I3 includes a supporting plate I52 mounted on the upper wall of the case i0 65 to extend across an opening I53 therein. Ahorizontal passage or guide channel I54 passes below this plate 552. The channel I 54 extends from the forward feed roll BI and serves to guide or direct the strip S to the mechanism 13 and to guide 7 the scrap from the mechanism. The first Operation performed by the mechanism I3 in the manufacture of a given cup 0 is the cutting of the cup blank and I will proceed with a description of the blank cutting means, best illustrated in Fig. 4.

The blank cutting means includes a fixed rin of the stationary channel structure I59. ring I64 is substantiall compressed during the .upward movement of the blank cutting sleeve I56 I55 and a movable ring or sleeve I56 cooperable one with the other to shear off the paper and thus form a disc shaped blank. The stationary ring 155 is secured to the under side of the fixed plate cutting ring or sleeve I56 is secured in the upper portion of a vertically movable cross head NH.

The cross head I6I has a flanged or thickened lower portion provided with a central opening I62. An upstanding central hub or collar I63 is bolted or otherwise fixed to the thickened lower portion of the cross head I6I and the blank cutting sleeve I56 is secured in the collar I63 to project beyond its upper end. The cutting sleeve I56 has a flat upper end and the sleeve is proportioned to accurately or closely fit within the stationary ring I55. between a position where its upper end is spaced below the channel I54 and the position where its The sleeve I56 is movable upper portion is received Within the ring I55, serving to cut the cup blank during this movement and operating to support the cup blank within the ring I55 when in its uppermost position. An annular member or ring I64 of rubber or other resilient material engages around the .projecting upper portion of the movable blank cutting sleeve I56 and is engaged between the upper end of the collar I63 and the lower side The and serves to clear the sleeve I56 and return the same to its lower position.

The cross head I6I carrying the cutting sleeve I56 is operated by the power shaft or crank shaft IS. The means for operating the cross head I6I includes ears or lugs I65 projecting from opposite ends of the cross head I6I and pairs of operating rods I66 secured to the lugs I65 and projecting .downwardly therefrom, see Fig. 14. Bull gears I61 are keyed or fixed to end portions of the shaft I9 which project beyond the bearings 20 and the inner sides of the bull gears IIi'I carry, what I will term, outer cams I68. Each of the cams I68 has a lift or raised part I69 on its active peripheral face, see Fig. 15. A roller I19 is rotatably secured to the lower ends of each pair of rods I66 being carried by pins or shafts I1I fixed in the cross bars I12 which connect the lower ends of the adjacent rods I66. The rollers I19 cooperate with the cams I68. During each revolution of the crank shaft I9 the raised cam parts I69 cooperate with the rollers I19 to move the cross head I6I upwardly to actuate the cutting sleeve I56. Asillustrated in Fig. 15, the raised cam parts I69 are relatively short and the cutter sleeve I56 remains in its actuated or raised position only a relative short time and then returns to its idle or lower position when the rollers I19 leave forming die I 14, see Fig. 4. The lower die or punch I13 is movable vartically within the above described cutting sleeve I56, while the upper die I14 is stationary, being mounted in the plate I52. The lower die or punch I13 is a tubular member or ring having a central vertical opening I15 and the punch is shaped and proportioned to ride up and down within the sleeve I56 to be guided thereby. The upper die I14 is likewise a tubular or ring-like part having a central opening I16 which registers with an opening I11 in the plate I52. The upper die I14 is fixed to the under side of the plate I52 and may be secured in a central recess in the plate by the screws I 51 which serve to attach the cutting ring I55 to the plate, as described above. The die I14 nests within the upper portion of the cutting ring I55 and has a flange I18 provided with openings which pass or receive the screws I51, see Fig. 4.

The under side of the die I14 is dished, having a frusto-conical concave surface pitched upwardly and inwardly from the cutting ring I55 to the opening I16. A plurality of radial grooves I19 is provided in the dished-under surface of the die I14. The grooves I19 are equally circumferentially spaced and are identical in size and shape. The radial grooves I19 preferably have flat downwardly convergent side walls and flat bottom or upper walls which are pitched upwardly and inwardly toward the common vertical axis of the mechanism I3. The upper side of the lower flute forming die or punch I19 is formed to mate with or nest in the die I14 to press or form the flutes in the blank of the cup. The upper side of the punch I13 is fr-usto-conical sloping upwardly and inwardly .from its periphery to the central opening I15. A plurality of circumferentially spaced ribs I89 is provided on the upper side of the flute forming punch I13. The ribs I39 are identical in size and shape and are equally spaced one from the other. The grooves I 19 and the ribs I89 are related so that the ribs I89 are adapted to enter the grooves to form the flutes in the paper blank. It will be seen that when the lower die or punch I13 is pressed upwardly within the stationary die I14 the grooves I19 and ribs I90 cooperate to form the flutes in the cup blank and the cooperation of the die and punch gives the blank its initial dished shape. It should be noted that the grooves I19 and ribs I99 diminish in depth as the extend inwardly and that they terminate some distance from the common vertical axis of the mechanism I3 leaving a plain or unfluted central portion in the blank.

The means for carrying and operating the flute forming punch I13 includes a cross head I8I disposed below the cross head I6I of the blank cutting means, see Fig. 4. The cross head IBI is flanged or reenforced and has a central vertical opening which receives a tubular upstanding column I82. A nut I83 may be threaded on the lower portion of the column I82 to clamp against the under side of the cross head I8I' to secure the column to the head. The column I62 extends upwardly and is received within the tubular cross head I6I. A flange I84 on the upper end of the column I82 is slidably received within the collar I63. Screws I85 removably secure the die or punch I 13 to the upper side of the flange I84. The flange I84 and the punch I13 are eifectively guided for vertical movement by the collar I63 and the cutting sleeve I56.

Cam means associated with the crank shaft I9 is provided to operate the cross head I8I of the flute forming punch I13. Pairs of spaced adjacent push rods or operating rods I are fixed to lugs or enlargements on the ends of the cross head I8I, see Fig. 14. The rods I86 extend downwardly to adjacent the bull gears I61 and the low or ends of the adjacent rods I80 are connected by heads or tie members I07, see Fig. 15. An annular cam I00 is fixed to the inner side of each bull gear I01 within the outer cam I08. Each cam I00 has an outwardly projecting continuous cam track or cam ridge I00 and the tie members I81 on the rods I80 carry means for cooperating with these cam ridges. In practice, each tie member I87 carries an upper roller I90 for cooperating with the outer surface of the cam ridge I80 and carries a lower roller I9I for cooperating with the inner surface of the cam ridge I89. The rollers I00 and I0! are rotatably supported on shafts or pins I02 and I93, respectively, on the members I 31. The cams I38 hare. identical shapes and settings and are formed to cause rather sudden or rapid upward and downward movements of the flute forming punch I73. The cooperation of the external surface of the cam ridges I80 with the rollers I50 produces the upward or active movement of the flute forming punch H3 and the engagement of the inner surfaces of the ridges I80 with the inner rollers I9I produces the return or downward stroke of the punch. It will be seen that during each revolution of the crank shaft I0 the flute forming punch I'IS is positively operated up and down so that the fiutes are formed in the cup blank and the blank is given a dished configuration.

When the flutes have been formed in the blank by the punch I'I3 and die I'M, as just described, the mechanism I3 operates to compress the flutes of the cup blank and to give the blank its final cup shape, the collapsing or compressing of the flutes permitting or providing for the forming of the cup C to the required shape and also giving the wall of the cup substantially rigidity. The mechanism It includes a pair of cooperating die elements for giving the cup blank its cup shape. The lower die element is in the nature of a punch I 04 and the upper die element is a socket-like die I95 facing downwardly to receive the punch I90, 'see Fig. 4. In accordance with the invention the punch I 00 and the die I95 are in coaxial telescopic relation with the other cup forming elements of the mechanism I3.

The cup forming die I94 is an elongate tubular member adapted to move up through the openings I16 and III with considerable clearance to enter or cooperate with the downwardly moving die I05 which is disposed above the plate I52. The punch I90 has a cylindrical lower portion and its upper portion is shaped to give the wall of the finished cup C the desired configuration. In the preferred construction the upper portion of the punch I04 is round in cross section and its external surface I90 gradually slopes upwardly and inwardly. This external active surface I95 of the punch I04 is smooth and regular to engage within the cup C without marring or distorting the paper of the cup. As best illustrated in Figs. 16 and 17, an annular upwardly facing shoulder I01 occurs on the exterior of the punch I94 where the sloping surface I90 mates or joins the cylindrical surface on the lower portion of the punch I00. The shoulder I0? is preferably fiat and occupies a plane normal to the longitudinal axis of the punch I04. The upperend of the punch I04 is flat and normal to its longitudinal axis except for 14 a raised annular ridge I08 occurring at its periphcry.

The cup forming punch I94 is carried by a vertically movable rod or column 200 through the medium of a spring loaded slack connection. The column 200 has its lower portion received in a central opening 20I in a cross head 202 which is located below the cross head IN. A flange 203 on the column 200 engages against the upper side of the cross head 202 and a nut 204 is threaded on the column 200 to engage against the under side of the cross head 202 and thus secure the column to the cross head. The column 200 passes upwardly through the column I02 with ample clearance and is provided with a central longitudinal opening 205 which extends through it from its upper end to its lower end. The upper end portion of the column 200 is reduced in external diameter. A stem 206 is slidable in the upper portion of the column opening 205 and the stem is provided With a central longitudinal opening 201. The cup forming punch I94 is removably attached to the upper end of the slidable stem 20% to move therewith. A screw 208 is entered in the upper end of the punch I94 and its head has shouldered engagement within the punch. The screw 200 extends beyond the lower end of the punch I54 and is threaded in the opening 20? of the stem 205. The screw 208 has shouldered cooperation with the upper portion of the stem 205 at 200. Means is provided for limiting the movement of the stem 205 and punch I94 relative to the column 200. This means may include a pin 2I0 carried in a transverse opening in the stem 200, The pin 2I0 projects from opposite sides of the stem 206 and extends-into diametrically opposite longitudinal slots 2II in the wall of the column 200.

The punch I04 is spring held or spring loaded, being urged upwardly so that it is spaced some distance above the upper end of the column 200 when in its idle or unactuated condition. The means for yieldingly urging the punch I94 upwardly comprises a coiled spring 2I2 arranged within the opening 205 of the column 200. The spring 205 is held under compression between the lower end of the punch carrying stem 205 and the upper end of a plug 2I3 threaded in the lower end of the column 200. The spring 2I2 is normally under compression to hold the punch I04 where its lower end is spaced above the upper end of the column 200 but the spring is yieldable and is subject to further compression when the punch I94 is engaged in the die I95, as will be later described.

The cup forming punch I94 is operated by the shaft I9 through the medium of crank pins and connecting rods. A crank pin 2M projects from the outer side of each bull gear I61, see Fig, 14. The pins 2i4 are turnably engaged in openings 2I5 in the lower ends of connecting rods ZIG. The ends of the cross head 202 are provided with outwardly projecting studs or pins 2I'I. These pins 2I'I are turnably received in openings H8 in the upper ends of the connecting rods 2I0. It will be seen how the crank means just described produces upward and downward movement of the cup forming punch I94 during each revolution of the crank shaft. In practice, the parts may be related so that the punch I04 is moving upwardly during the upward actuation of the flute forming punch I13 and the upper end of the punch I94 may be in a plane at the upper end of the grooved active face of the die I14 when the flute forming operation is completed.

Immediately thereafter the flute forming punch I13 moves downwardly to free the cup blank and the punch I94 continues upwardly to push the cup blank upwardly from the die I". In this connection it is to be observed that the inner corners or faces of the flute forming die I14 may be rounded or bevelled off so that the cup blank is not injured or distorted when the punch I94 draws it upwardly out of the die I14.

The cup forming die I95 is removably carried by a cross head 2I9 disposed above the case I9 and spaced above the plate I52. A carrier 229 is bolted or otherwise secured to the under side of the cross head 2I9 and projects downwardly toward the plate I 52. The carrier 229 has a socket 22I (Fig. in its lower side whose longitudinal axis is concentric with the common axis of the several elements of the mechanism I3. An open.- ing 222 of reduced diameter continues upwardly through the carrier 229 from the socket 22 I. The cup forming die I95 is centrally and vertically disposed within the socket 22L The die I95 is a tubular member received in the socket 22I with ample clearance and the upper end of the die I95 has an inturned head or flange 223 presenting an end of increased area which bears on the end wall of the socket. The exterior of the die I95 is cylindrical and of uniform diameter throughout.

The interior of the die I95 has an active cup shaping surface 224 corresponding in configuration to the surface I96. The surface 224 slopes downwardly and outwardly to the lower end 225 of the die I95. The lower end 225 of the die I95 is flat and lies in a horizontal plane. The end surface 225 is adapted to be directly opposite the shoulder I91 of the punch I94 to form a step or shoulder 226 on the cup C, see Figs. 16 and 1'7. The cup shaping surface 224 of the die I95 has substantially the same inclination as the cup shaping surface I96 of the punch I94 and when the die and punch are cooperating the wall of the cup C is given its final flaring configuration by these cooperating surfaces. Further, it will be observed that the cooperating active surfaces of the punch I94 and die I95 compress the fluted wall of the cup blank and the flutes are converted into pleats or folds of double thickness, thus materially increasing the strength and stability of the cup. The die I95 may be secured in the carrier 220 by a bushing 22'! which extends through the opening 222 of the carrier 229. The bushing 22'! extends downwardly into the die I95 and has a flange 229 on its lower end which bears upwardly against the flange 223 of the die I95 to clamp the die upwardly against the upper wall of the socket 22I. The bushing 22! projects upwardly beyond the upper end of the carrier 229 and an elongated cap 229a is threaded on the projecting portion of the bushing and clamps against the upper end of the carrier 229 to secure the bushing in the carrier.

The cup forming die I95 moves downwardly as the cup forming punch I94 moves upwardly, in other words, the two cup forming elements move toward one another to form the cup C. The means for actuating the cup forming die I95 includes connecting rods 239 engaged on and operated by intermediate cranks 23I of the crank shaft I9, see Fig. 14. The connecting rods 239 extend upwardly and outwardly from their cranks 23I and are pivotally connected with a travelling horizontally disposed bar 232. The bar 232 is provided at its under side with pairs of downwardly projecting ears 233. Horizontal pins 234 are carried in openings in the ears 233 and are turnably received in openings in the upper ends of the connecting rods 239 to connect the rods with the travelling bars 232. Rods 235 are attached to the end portions of the travelling bar 232 by screws 236 and extend upwardly to the cross head 2I9. As illustrated in Fig. 14 of the drawings the rods 235 may slidably pass through openings 23'! provided the thickened end portions of the cross head 292. This assists in guiding and steadying the rods 235. The rods 235 are further guided by bushings 238 secured in openings 239 in the upper wall of the case I9. The upper ends of the spaced vertical rods 235 carry the cross head 2I9. It will be seen that the cross head 2| 9 carrying the die I moves up and down through a complete cycle during each revolution of the crank shaft I9. The cranks or eccentric elements of the drive are so related that the upper cup forming die I95 moves downwardly as the cup forming punch I94 moves upwardly. These movements continue until the punch I94 bottoms in the die I95 to bring about the full compression of the flutes and to give the blank its permanent cup shape.

The mechanism I3 further embodies novel means for forming a bead B on the rim of the cup C. This means is associated with the cup forming elements just described and is driven by the same operating or driving means to form and complete the bead immediately following the shaping of the cup C. The bead forming means includes a sleeve 249 engaged around the die I95. The sleeve 249 is slidable or movable in the annulus existing between the exterior of the die I95 and the wall of the socket 22I. The length of the sleeve 249 is such that the lower end of the sleeve is slightly below the lower end of the die I95 when the sleeve has its upper end bearing against the upper wall of the socket 22I. The sleeve 249 is movable vertically but friction means is provided to resist such movement. A recess MI is formed in the side wall of the socket 22I at the lower end of the carrier 229. The outer wall of the recess 24I converges or slopes upwardly and inwardly. Suitable friction material 242, such as fiber or the like, is tightly packed in the recess 2 to offer substantial resistance to movement of the sleeve 249. An annular follower 243 is engaged against the lower end of the friction material 242. A gland or nut 244 is threaded on the lower end of the carrier 229 to force the follower 243 upwardly against the friction material 242. When the nut 244 is threaded upwardly the friction material 242 is tightly compressed against the sleeve 249. The friction material 242 serves to hold the sleeve 249 against vertical movement until the sleeve is subjected to a positive moving force. The importance and function of this friction holding means will be described below.

At the time when the die I95 and the punch I94 are moving together to shape the cup C the sleeve 249 is in a position where it projects a substantial distance below the lower end of the die I 95. The friction material 242 holds the sleeve in this position and the sleeve moves downwardly with the carrier 220 without movement relative to the die I95. As best illustrated in Fig. 16 of the drawings, the internal diameter of the sleeve 249 is slightly greater than the external diameter of the cylindrical surface 245 of the punch I9 1. The clearance between the internal and external surfaces, respectively, of the sleeve 249 and punch I94 is just sufficient to receive the paper thickness of the cup blank.

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