US2453200A - Double seamer - Google Patents

Description

Nov. 9, 1948. E. v. CRANE El AL 2,453,200

' DOUBLE sEAuER r Filed Dec. 10, 1943 13 Sheets-Sheet 1 mm 0R5. EDWARD v.- cRANEe/KARL KUHN. v

Nov. 9, 1948. E. V. CRANE ET AL 2,453,200

DOUBLE SEAMER Filed Dec. 10, 194:s 1:5 Sheets-Sheet 2 EDWARD I v. CRANE {PI/KARL KUHN.

INVENI'ORS.

Now 9 1948. V a. CRANE El AL I 2,453,200

DOUBLE SEAIIER -Fi1ed Dec. 10, 1943 v 1s Sheets-Sheet 4 Nov. 9', 1948. 'E,v, CRANE H M 2,453,200

I DOUBLE SEAMER Filed Dec. 10, 1943 13 Sheets-Sheet '7 INVENTORS. .EDWARDV. cRAuEemARL KUHN Nov. 9, 1948. E. V. CRANE ET AL DOUBLE SEAMER Filed Dec. 1 0, i943 l3 SheetsShe t 8 2 T H 5 uj. 1 8091 WK. M M 1 mm 6 A K. m a F. m k 7 m fi |H u w L m WM, 7. n m 3 i m w m 9 NOV. 9, 1948. v. CRANE ET AL 2,453,200

DOUBLE SEAMER 1 Filed De'c. 10, 1943 15 Shets-Sheet 9 IVE 0R5. :owmo v. CRANEE/KA L UHN.

' Nov. 9, 1948.

' DOUBLE SEAMER 13 Sheets-Sheet 11 Filed Dec. 10, 194:;

m: (Nu kla Zu LEW RE EHO INVENTORS.

Nov. 9,1948; E; v. CRANE ET AL- 5 3 Q DOUBLE SEAMER l3 Sheets-Sheet l2 Fiied Dec. 10, 1943 y INVENTORS. EDWARD v. CRANEGIKARL. KUHN Nov. 9, 1948. E. v. CRANE ET AL DOUBLE SEAMER 13 Sheets-Sheet 13 Filed Dec. 10, 1943 'IIIIIIIIIIIIIIIIII'" I INVENTORS suwmo v. CRANEFIKARL KUHN Patented Nov. 9, 1948 DOUBLE SEAMER Edward V. Crane and Karl Kuhn, Brooklyn, N. Y., assignors to E. W. Bliss Company, Brooklyn,

N. Y., a corporation of Delaware Application December 10, 1943, Serial No. 513,710 2 Claims. (Cl. 11s '24) This invention relates, as indicated, to double seamers, that is to say, machines for double seaming ends to can bodies.

A primary object of the invention is to provide a machine of the character described in which the number of revolving parts 'which must be started and stopped incidental to each cycle of operation of the machine is reduced to a minimum. Stated somewhat differently, the revolving mass whichmust be arrested as each can is seamed is reduced as far as possible. To accomplish this, the seaming parts are in constant motion, permitting the seaming head to function in a manner analogous to that of a flywheel, thereby relieving the load on the motor and the clutch, the clutch being called upon only to operate in connecting the intermediate drive of the seaming mechanism for each can to be operated upon.

Another object of the invention is to provide in a machine of the character described an increased rigidity, due to the provision of tubular seaming arms which afford suitable bearing and pivoting of seaming roll levers within the arms and a toggle action which is utilized to apply a seaming pressure.

A further object of the invention is the provision in a machine of the character described of an enclosed master cycle shaft for rotating the seaming head as well as means for reducing the cam load by reason of pair balancing.

A still further object of the invention is to provide in a machine of the character described, a vertical shaft motor which drives the main shaft of the machine by means of a single belt reach, instead of by the conventional twisted belt drive.

A still further object of the invention is to provide a double seamer which is of a neat, attractive design.

To the accomplishment of the foregoing and related ends, said invention, then, consists of the means hereinafter fully described and particularly pointed out in the claims; the annexed drawings and the following description setting forth in detail certain mechanism embodying the invention, such disclosed means constituting,

however, but one of various means in which the.

principle of the invention may be used.

In said annexed drawings: Fig. 1 is a front elevation of the double seamer selected to illustrate an embodiment of our indouble seamer, with a portion removed to more clearly expose some of the operatin mechanism;

Fig. 5 is a view, partly in section, and partly in .elevation, taken approximately on the line 5-5 of Fig. 4;

Fig. 6 is'a cross-sectional view, taken approximately on the line 6-6 of Fig. 4;

Fig. 6A is a cross-sectional view, on an enlarged scale, of a portion of Fig. 6;

Fig. 6B is a cross-sectional view, through a portion of the seaming head, taken at right angles to the view in Fig.,6A;

Fig. 6C is a perspective view, showing linkage employed in actuating the seaming rolls;

Fig. '7 is a cross-sectional view, taken approximately on the line I-'! of Fig. 4; v

Fig. 8 is a view, partly in plan, and partly in section, taken approximately on the line 8-8 of Fig. 3;

Fig. 9 is a cross-sectional view, taken approximately on the line 9--9 of Fig. 8;

Fig. 10 is a plan view, illustrating in a more or less diagrammatic manner, the location of the seaming rolls and other elements carried by the seaming head;

fig. 11 is a plan view of the seamer cam;

Fig. 12 is a transverse cross-sectional view of the seamer cam, taken on the line l2l2 of Fig. 11;

Fig. 13 is a view illustrating the development of the seamer cam;

Fig. 14 is a view, illustrating the timing of the various operations of the seamer;

Fig. 15 is a view showing the profile of one of the first operation rolls of the seamer;

Fig. 16 is a view showing the profile of one of the second operation roll of the seamer;

Fig. 1'7 is a view illustrating the first step in the operation of double seaming a can end to a can body; I

Fig. 18 is a view illustrating the second step in the operation of doubleseaming a can end to a can body;

Fig. 19 is a View illustrating thethird step in the operation of double seaming a can end to a can body;

Fig. 20 is a view illustrating the retracted position of the seaming rolls after the double seam ing operation is completed;

Fig. 21 is a view of a chuck such as used for double seaming round cans;

Fig. 22 is -a view, illustrating diagrammatically the location of the various cams of the double seamer relatively to each other;

Fig. 23 is a plan view of the seaming head Fig. 24 is a view, partly in elevation, and partly v in section, taken approximately on the line base portion 2 and a pad 3 at its upper end, which provides a support for a housing 4, within which the seaming head and other mechanism to be described are enclosed. I

The housing 4 is open at the front, and this opening is adapted to be closed by means of a cover 5, which is hingedly secured, as at 6, to the housing. Mounted on the housing t is a top housing I, for the intermediate drive of the seamer, which will be presently described.

Rigidly secured to the upper wall of the housing 6,.is a seaming head support 8 (Fig. 6) about which an annular head gear 9 is adapted to be rotated. The gear 9 has a hub IE to which a seaming head I! iskeyed.

The support 8 has a lower portion |2 of reduced diameter, and to which is secured, as by bolts 3, a, bearing plate id. The bearing plate M by its outer edge portion engages a second bearing plate having a flange |6 which forms a support for the seaming head H, the seaming head bein thus confined against vertica1 movement by the gear 9 and the plate l5.

To facilitate rotation of the seaming head, a roller thrust bearing I1 is interposed between the bearing plates M and I5.

The seaming head I"! is provided with four radially extending hollow arms l8, which are spaced circumferentially 90 degrees apart, each arm having a vertical bore i9, within which is disposed the upright hub of a tubular seaming arm 2|, the hub 20 being locked to the arm |'8 by means of a collar 20a. The seaming arm has pivotally connected thereto, as at 22, a seaming roll lever 23 having a depending portion 24 upon which is journalled a seaming roll 25.

The lever 23 is adapted to be rocked in a horizontal plane about its piovtal axis 22, and for this purpose it has connected thereto, as at 26, a connecting link 21 which extends through the arm 2| and is connected at its outerend to an adjustably mounted bell crank 28. The crank 28 is mounted on the arm 2|, as at 29, for rocking movement in a vertical plane. Extending through a hole 30 in the crank 28, and in threaded engagement therewith, is an adjusting screw 3| having a knurled knob 32 secured to its outer end, and provided at its inner end with a cup 22 which bears against the ball head 34 of a stem 35.

The stem 35 is slidab ly mounted in a fork 36,

which is disposed within the hub 20 of the seaming arm, and is vertically reciprocable in the latter, the stem bein secured against displacement from' the fork by a nut 31 secured to the upper end of the stem. A preloaded coil spring 38 is mounted on the stem 35, being interposed 4 between the fork 38 and a washer 38 resting on the head 34 of the stem.

It will be apparent from the foregoing description that downward movement of the fork 38 will be communicated through the spring 38, stem 35, screw 3|, crank 28, and link 2Tto the lever 23, so as to rock the lever and move the seaming roll 25 thereof to an operative position. Adjustmentof this movement may be effected by adjustment of the screw 3|, which changes the effective point of connection of the stem 35 to the crank 28. The spring 38 is effective to absorb shocks occasioned by irregularities encountered during th seaming action of the roll 25.

For the purpose of effecting a return of the roll 25 to its retracted or inoperative position, a tension spring is provided, which is connected at one end to the arm 2|, and at its other end to a groove pin 4 which extends from the lever 23. A stop or plug 4|a, which is interposed between the screw 20a and the fork 35 operates to limit the return movement of the roll.

Threadedly secured to the lower bearing plate H is a pin 42 having an axial bore 43 extending therethrough which is in alignment with an axial bore M in the support 8. The threaded pin 42 has a portion which projects through the lower face of the plate It and has secured thereto a chuck 45 having an axial bore 46 (Fig. 21) in alignment with the bores 43 and 44. Secured to the lower end of this chuck is chuck plate 41 against the lower face of which the end of the can which is to be double-seamed is clamped by means which will be presently described.

The seaming rollers 25 are adapted to be simultaneously moved into operative engagement with the work to be double-seamed, and for this purpose, mechanism is employed, which will now be described.

Such mechanism comprises a spider 48, which is mounted upon a bearing 49 which, in turn, is mounted on the support 8, the spider being retained against endwise displacement from the bearing 49 by means of a lock nut 5|, which is threadedly secured to the lower end of the hearing. The spider is provided with radially-extending ears arranged in pairs, the cars in each pair being diametrically-opposed to each other. One pair of these ears, designated 52, is shown in Figs. 6 and 6A, and'the other pair, spaced degrees from the cars 52 circumferentially of the spider, and designated 52a, is shown in Fig. 6B. The ears 52 have journalled therein pins 53 having flat portions 53a, to which are secured toggle links 55, arranged in pairs, each pair of toggle links being secured at its outer ends to a pin 56, which is mounted in a bell-crank 57, The ears 52a have journalled therein pins 53' having flat portions 53b, to which are secured toggle links 55a, arranged in pairs, each pair of such links being secured at its outer ends to a pin 56, which is mounted in a bell-crank 51. The pins 53'- are mounted in the ears 52a at a somewhat higher elevation than the pins are mounted in the ears 52. Moreover, the links 55a are somewhat longer than the links 55, that is to say, the distances between the axes of the pins 53' and the pins 56 to which the links 55a are connected, are greater than the distances from the pins 53 and the pins 56 to which the links 55 are connected. The linkage embodying the links 55a operates the first operation rolls, as hereinafter described, while the linkage embodying the links 55 operates the second operation or finishing rolls.

Each bell crank 51 is pivotally connected, as by shaft 88, to an arm I8 of the seaming head II, and the outer arm of each bell crank is connected,

' as by pins 59, to one of the ball stem forks 88,

which havebeen previously referred to. The walls of the cylindrical hub portions 28' of the seaming arms 2| are slotted to allow the rocking movement of the bell cranks 51, when vertical movement is imparted to the spider 48 in order to rock the rollers 28 to their operative position.

This vertical movement of the spider 48 is effected in the following manner: Secured to the upper flange of the bearing 48 arefour push rods 58a, which are spaced apart 90 degrees circumferentially of the bearing and extend upwardly through openings 88a in the support 8, the push rods having a slide fit in the support so as to be freely movable up and down in the support.

(These push rods also extend through the upper wall of the housing 4, and are provided at their upper ends with threaded stems 88, whereby the push rods are connected, as by means of nuts 8| to a yoke 62.

Yoke 62 is pivotally connected to links 88, which are pivoted at their upper ends to the inwardly extending arm 64 of a rocker lever 85. Lever 85 is pivotally supported, as at 68, on a support 81, which is rigidly secured to the upper wall of the housing 4. The other arm 68 of the lever 85 is pivotally connected to a pair of links 88, the opposite ends of which are connected to a slide 18, whichis mounted for reciprocal sliding movement on the upper wall of the housing 4, the slide being confined during such movement between guides orribs 1|, which are secured to such wall.

Reciprocal movement of the slide 18 is effected by means of a cam 13,'hereinafter referred to as the seamer cam, and having a cam groove 14 in its lower face. The slide 18 has a bearing pin 15 mounted in one end thereof, which supports a cam roller 16, a needle bearing. 11 being interposed between the pin and roller. The roller 18 rides in the cam groove 14, as the cam 18 is rotated.

The cam 13 is secured, as by screws 18, to the main gear 19 of the seamer, and the gear 19, in turn, has secured thereto, as by screws 88, a clutch operating cam 8|, having a recess 82 in its upper edge. The gear 19 is secured, as by a key 83, to the upper end of a cam shaft 84, being retained against axial displacement from said shaft by a dog point set screw 85.

86, which is loosely mounted on a clutch shaft 81,

the latter being journalled in and supported by a bearing 81a. The clutch shaft has keyed to the lower end thereof a gear 88, hereinafter referred to as the head gear driver, and which is in driving engagement with the head gear 9 of the seamer. It may be noted at this point that the clutch shaft is in continuous rotation, so that the seaming head, acting as a flywheel, re lieves the motor. The clutch, as hereinafter described, being operated only when a can is brought into position, also relieves the motor from constant work,

The clutch shaft 81 is provided adjacent its upper end with a clutch, preferably of the single multi-disc dry type, and consisting of a drive cup 89, which is keyed on the hub sleeve of gear 88, and a member 98, which is keyed to, but slidable longitudinally of the' clutch shaft. The clutch member 98 is adapted to be moved when the clutch is to be energized, and for this purpose, the member 98 is engaged by the yoke of a lever 9|, which is keyed to a rock shaft 94, extending -to the ears I88 of the brake straps.

transversely of the seamer and to the top hous -ing 1 thereof. The shaft 84 is suitably journalled in brackets or ears 85 depending from the upper wall of this housing. The lever 8| is provided at its opposite end with a cam roller 86 which is normally urged into engagement with the upper surface of the clutch operating cam 8|, as by means of a coil spring 91 which is interposed between a laterally-disposed seat 88 on the lever and a set screw 88 secured to the upper wall of the top 1.

The shaft 84 projects beyond one of the side walls of the top 1 and has keyed thereto adjacent such projecting end a brake lever I88, to

one end of which is secured a rod I'8I, whose lower end is pivotally secured to one end of a .treadle I82, which is mounted to rock about a shaft I88 extending from the pedestal I adjacent the base portion 2 thereof.

A brake is also provided consisting of a pair of substantially semi-circular lined brake straps I84, which are pivotally connected at one end, as by a pin I85, and are normally urged into braking contact with the drive cup 89 of the clutch by means of a coil spring I88. The spring I88 is mounted on a rod I81, which extends through ears I88 onthe straps I84, the spring being interposed between one of these ears and a washer I89 mounted near one end of the rod The rod is secured against displacement from the ears I88 by means of a nut I I8 secured to its other end. The spring thus acts to normally force the brake straps I84 against the drumportion of the drive cup 89 of the clutch.

For the purpose of releasing. the brake at the time the seamer is placed in operation, a lever II I is provided having a boss I I2 whichis mounted upon an eccentric bushing II3 (Fig. 7) which is secured to the base of the housing 1. This lever III has one arm II4 thereof pivotally connected to a pin II5, which pivotally joins a pair of links '6 and I I1, which are connected The other arm II8 of the lever III has a swivel connection with a rod II 9, which is pivotally connected to an arm I28 which extends from the brake lever I88. When the rod II9 is moved to the left, as viewed in Fig. 4, the point of connection of the links I I8 and I I1 is moved downwardly, as viewed in Fig. 4, thereby releasing the brake, and at the same time, the clutch is energized. The eccentric bushing I I3 serves to insure the straight line movement of the point of connection of thelinks IIS and H1.

Means are also provided for supporting the can to be double-seamed in a. position to be acted upon by the seaming rolls, such means being actuated by the treadle I82. Such means are best shownin Figs. 8 and 9 and comprise a. bracket l2| which is mounted on the pedestal I. This bracket is provided with a tubular portion I2Ia having a. bore I22a, in the end of which a sleeve in turn, is secured a top I21, shown, in this intance, as a round top.

Extending through the sleeve I22 is a spindle I28 having a lock nut I29 secured to its upper end and bearing against a shoulder I38 of the sleeve. The spindle extends also through a sleeve I3I, which extends into the lower end of the bore I 2|, and is retained by a lock nut I32, which having a forked end I in which a pin MI is,

secured. The pin I4l has an aperture I42 there in through which the upper end of a rod I43 extends, the rod being secured to the pin by a set screw I44.

The rod I43 is adiustably secured at its lower end to a sleeve I45 having a forked lower end I46, which is pivotally connected to the treadie I02 at a point at the opposite side of the shaft I03 from that to which the rod MI is secured.

The lever I31 has revolubly mounted upon a stud I460. secured to its rear .end, a cam roller I41.

The bracket I2I is provided with a tubular por:- tion I48 having a bore I49 therein in which a cam member I50 is secured as by a collar I5I, the cam member, although secured by said collar, being free to rotate within said tubular portion I48. The member I50 has a flange portion I52, the face I53 of which forms a cam surface adapted, at times, to engage the cam roller I". The member I50 is keyed to the lower end of the cam shaft 84.

Mounted onthe bracket I2I about the tubular portion I2Ia of the latter, is a circular disc-like member I54 having spaced concentric flanges I55 and I56 forming an annular trough into which the overflow from cans being seamed may enter. The flange I56 is provided at diametric points 'with horizontally extending flanges or ledges I51 and I58, the ledge I51 having mounted thereon an inlet can table I59 and the ledge I58 having mounted thereon an outlet can table I60. Secured to the table I59 adjacent its rear edge is a can guide I8I, which may be adjusted forwardly or rearwardly, in accordance with the size or diameter of the cam to be seamed.

In order to eliminate any-tendency of the can, after being seamed, to stick to the lower surface of the chuckplate 41, means are provided for knocking the can, at the conclusion of the seaming operation, from said plate. Such means comprises a knockout rod I62, which extends through the axial bores 43, 44 and 46, and has a thrust collar I63 secured to its upper end, as by a cotter pin I64. The lower end of the knockout rod I62 is normally disposed substantially flush with the lowerend of the bore 46, and is maintained in such position by means of a compression coil spring I which is interposed between the collar I63 anda seat I65a formed at the bottom of a recess I66 within the support 8.

The knockout means further includes a knockout screw I61, which is adjustably secured to the yoke 62, and is disposed so that its lower end is immediately above and in spaced relation to the upper end of the rod I62.

The seamer is adapted to be driven by a motor I68 which is mounted laterally of the top housing 1, and drives the clutch shaft 81 through the intermediary of a pulley and belt drive I69.

The aforesaid description is primarily that of a double seamer which has been set up to double seam round cans, and the following description will accordingly be directed more speciflcally to the seaming of such cans, reference being had also to Figs. 10 to 20 inclusive, which are intended to diagrammatically illustrate the cycle of opera tions incident to the double seaming of a single can. In, connection with such operation, the operations of the seamer, as a whole, will be described.

1 In commencing the operations, the operator will place, the can body B, with a top T mounted thereon in a position to be connected to such body, on the table I59 and against the guide I5I thereof, it being understood that this table is in its lowermost position. He then pushes the can body along the guide I6I and onto the top I21 01' the base plate I26, the canbeing approximately centeredon this top.

: Having thus located the can, the operator will depress the treadie I02, and thereby, through the intermediary of the sleeve I45, rod I43, lever I38, and spindle I28, elevate the can so as to bring the top T thereof into engagement with. the

chuck plate 41, thereby clamping the can between the top I21 and the plate 41. Incident 'to this operation, spring I33 is compressed to a certain degree, so that the clamping engagement is of a. yielding character, permitting movement of the can in a direction transverse to its axis, so as to permit it to be centered on the top I21 in a manher to be presently described.

' The depression of the treadie I02 also results in an elevation of the rod IOI, thereby causing the brake to-be released, and the clutch to be energized. This results in the various moving elements of the seamer being set into operation. More specifically, the main gear 19 will be rotated, the headgear driver 88 being already in rotation. As'the seaming head II is rotated by the head gear driver 88, guide plates 92, which are secured to the inner ends of the seaming arms 21 (see Fig. 10), engage the can body, and serve to center the latter and to maintain it against dis-' placement during the seamin operations. The rotation of the gear 19 causes simultaneous rotation of the cam 13 and the clutch operating cam III. As the latter begins to rbtate, the cam roller 96, which has been elevated fromthe recess 82 of the cam against the tension of the spring 91, comes into contact with'the upper edge of the cam, and is maintained by said spring against such edge during a complete revolution of the cam, that is, until the roller is again moved into said recess by the spring. The seamer therefore remains in ol ution of the cam 8|,

This corresponds to a complete revolution of the cam 13, which revolution may be described as covering one complete cycle of operations of the seamer. During such revolution of the cam 13, the seaming rolls 25 will be caused to move in and out of the arms 2|, in a manner which will be apparent from the timing diagram of Fig. 14. It may be stated that at this pointone pair of diametrically opposite rollers 25 .are used for the first seaming operation, while the other pair of diametrically opposite rollers are used for the second seaming operation. The first and second operation rollers, as shown in Figs. 15 and 16, respectively, have somewhat different profiles or contours. The'movement of the secondoperationrollers relatively to the arms 2i, moreover,jis difierent from that of the first operation rollers, since it is necessary that the second operation 'rollers .do not come into contact with the Work to be seamed until the first operation rollers have operation for one complete rev-- revolution of the cam shaft 84 and thereby maintains the lever I31 in can elevating position. This enables the operator to remove his foot from the treadle I02 immediately after the seamer is placed in operation.

Referring to Fig. 14, it will be noted that during the first 18' movement of the cam 13, the movement of the cam roller 16 in the groove 14 of said cam is such that the pair of first operation rolls 25 approach the flange F of the can top .T, the position of such rolls at the beginning of this movement being indicated by the dotted lines in Fig. 17 and the position thereof at the conclusion of the movement being indicated by the solid lines.

As the cam 13 rotates another 96 degrees, the first operation rolls are moved further inwardly, producing a curling and bending of'the flanges of the body and cover ofthe can, as shown in Fig. 18, the rolls being maintained in this position during another 27 degree movement of the cam 13, the maintenance of the rolls in such position being referred to in the diagrams as the dwell.

In further explanation of the above movements, it may be stated that the movements of the rolls are effected by movement of the spider 4B downwardly, as viewed in Fig 6B of the drawings. This downward movement of the spider 48 first causes the bell-cranks 51 to move about their shafts 58 in such a direction as to cause downward movement of the forks 35, until the lines A--A connecting the axes of the pins 53' and pins 56 are disposed at right angles to the axis of the spider. This position of the parts constitutes the dwell, the relationship between the spider 48, links 55a, bell-cranks 51, pins 53' and 56 and shafts 58 being, in effect, a toggle or knuckle-joint relation. Continued downward movement of the spider 48 results in a reversal of the direction of rotation of the bell-cranks 51 about the shafts 58, causing the axes of the pins 56 to move toward the spider, elevating the forks 36 and withdrawing the first operation rolls from the work.

Prior to the point at which such continued downward movement of the spider 48 causes a reverse rotating of the bell cranks 51, the second operation or finishing rolls approach the work, and at the completion of the seaming work of the first operation rolls, shown in Fig; 18, the second operation rolls reach the position shown in dotted lines in this figure. This movement of the second operation rolls is effected by the linkage shown in Fig. 6A of the drawings.

During the next 21 degree movement of the cam 13, the second operation rolls complete the double seaming operation, as shown in Fig. 19, the first operation rolls having, in the meantime, been retracted to a slight extent, to the position shown in dotted lines in such figure.

During the next 51 degree movement of the cam 13, the second operation rolls remain in contact with the double seamed edge, this period being known as the dwell of the second operation '10 rolls. The first operation rolls, during this period, remain in their retracted position.

Durin the dwell" of the second operation rolls, the relation between the axis of the pins 53 I and 56 (Fig. 6A) is such that a straight line connecting these axes is at right angles to the axis of thespider.

During the next 2'7 degree movement of the cam 13, both the first and second operation rolls are retracted to the position shown in Fig. 20, so as to clear the seamed edge of the can. As the cam 13 completes a single revolution, the first and second operation rolls return to their initial position. The retraction of the second operation rolls is effected by the continued downward movement of the spider 48, which causes the bell cranks 51, as shown in Fig. 6A, to be rocked in a reverse direction, as already described in connection with Fig. 6B.

It may be mentioned at this point that the timing, as determined by the seaming cam 13, only varies as the flange length or the gauge of the metal varies in the cans to be seamed, with minor variations due to can sizes.

As soon as the first and second operation rolls have cleared the can seam, as described above, the cam I53 releases the roller I 41, permitting the spring, I33 to pull the spindle I28 downwardly, and carrying the top I21 downwardly to its initial or loading position. At the same time, the seamed can is stripped from the chuck plate 41, due to the action of the screw I61, which comes into engagement with the upper end of the rod I62 andmomentarily forces the later downwardly so as to cause it to project from the lower end of the bore 46, thereby stripping the can from said chuck. plate.

The can which has thus been stripped from the chuck plate 41 follows the top I 21 downwardly, and when such top has reached its lowermost po-- sition, the operator may push the can onto the outlet can table I60, whence it slides into a suitable receptacle.

The toggle or knuckle-joint relation which has been described, together with the lost-motion provision of the first-operation roll linkage, is of considerable importance in connection with the present invention, since they permit the elimination of three cams, one to operate the first-operation rolls, one to operate the finishing rolls, and a third for operating the knockout rod. In addition, ,a great mechanical advantage is obtained by For the purpose of double seaming larger cans,

which may be square, rectangular, oblong or round, the double seamer which has been described is modified in the manner shown in Figs. 23, 24 and 25 of the drawings.

Referring to these figures, it will be noted that in order to cause the seaming arms 2| to follow the general contour of the can, during the seaming operations, such arms are so mounted in the arms I8 of the seaming head II' as to be revoluble in a horizontal plane. This requires that In this.

. ll the hub portions 2| of the seaming arms'be free to rotate in the arms I8, a condition which is attained by unscrewing the screw 200, so as to provide a clearance c, as shown in Fig. 25, between the flange of this screw and the upper end of the arm' I 8'. g

In order to cause the seaming arms 2I' to follow the contour of the can, a cam I80 is secured to the pin 42', and a chuck 45' is secured, as by screws IBI, to the lower face of this cam, this chuck having, of course, the contour of the rectangular can which is to be double seamed. The cam I80 has a cam groove I82 therein, which is of the same contour as the can to be double seamed,

' and the seaming arm 2I' has mounted therein a pin I83, which carries a cam roller I84, which rides in the groove I82, thereby causing the seaming arm to follow the contour of .the can to be seamed.

The mechanism for moving the seaming rolls 2( l relatively to the seaming arms is essentially the same as that described in connection with the double seaming of small cans, but in this case, it will be noted that the linkage between the ears- 52' of the spider 48' and the bell crank levers 01',

is somewhat different, due to the larger dimensions of the larger cans. Such linkage comprises links 00' which are are pivotally connected-to the ears 02', to idler supporting levers I90, pivotally supported on the seaming head II' as at' I8I and to links I02. The links I02 are pivotally connected to the bell cranks 51'.

Itis to be understood that while the seaming head shown in Fig. 6 has been described with reference to the seaming of round cans, and the head shown in Fig. 24 has been described more particularly with reference to the seaming of cans having a rectangular contour, that the head in Fig. 6 can be readily adapted for the seaming of cansother than round and the head in Fig. 40

24 can be easily adapted for the seaming of round cans.

In order to adapt the head of Fig. 6 for the seaming of cans other than round, it is only necessary to free the hub portions 20 of the seaming arms 2I by unscrewing the collars 20a,

provide a cam similar to the cam I80 of Fig. 24, a chuck similar to the chuck 45' and a cam roller similar to the cam roller I 84. In order to adapt the head of Fig. 24 for the seaming of round cans,.it is only necessary to eliminate the contour cam I80 and cam roller I84 and lock the hub portions of the seaming arms 2I' by means of the collars 20a.

If it be assumed that the heads in Figs. 6 and 24 have been set up to operate on round cans of sizes and flange widths well within the normal dimensional rangeof each head, a schedule of operational modifications may be setup in the following manner.

1. If it be desired to operate on a can of a round shape, but slightly larger, having the same width of seam flange, the only change to be made in either of the heads shown in Figs. 6 and 24 is to change the chuck size.

2. If it be desired to operate on a can of round shape of substantially the same size but with a wider seaming flange or stifier blank metal, the only changes necessary in the seaming heads of Figs. 6 and 24 are to slightly modify the profile of the cam shown in Fig. 11 of the drawings and to adjust the screw I85 and slide I86 of each respective linkage to produce long 'periods of ironi2 but for a can of larger size, an additional change of a chuck is required.

4. If it be desired to seam a square can of approximately the same size and same width of seaming flange, the seaming heads of Figs. 6 and 24 are changed by providing a contour cam similar to cam I80, loosening the screw 20a, connecting the seamer roll supporting arm to the contour cam through the medium of the roller I82 and pin I83, and providing a chuck of the con-.

tour of the can being seamed.

It may be noted that in each instance, the modification eflected are identical, the fundamental distinction between the seeming head of Fig. 24 and Fig. 6 being one of dimension and not of kind.

Referring to Figs. 26 and 27, it will be seen that in order to permit an increased travel -of the seaming rolls, as when seaming wide end flanges, provision is made forvarying the pivotal point of connection of the links or levers I92 to the bell crank levers 51'. This is accomplished by means of screws I85, adjustment of which causes slides I86 to which the links I92 are pivoted to move upwardly or downwardly along the inner faces of the levers 51'. This adjustment is also adaptable for use with that form of construction shown in Fig. 6.

If desired, the main drive shaft of the machine may be utilized to drive the feed mechanism (not shown) for the can bodies and tops. the construction of the machine readily. adapting such shaft for these functions.

Other modes of applying the principle ofour tions extending transversely to said hub portions,

lever pivotally mounted in said transverse arm portions, seaming rolls journalled in said levers, and means for transmitting a rocking movement to said levers, said means including bell crank levers having arms extending into said hub portions; forked elements mounted for reciprocal movement in said hub portions, stems slidably mounted in said forks, levers pivotally mounted on said second-named arms and movable by said stems, and links interconnecting said last-named I levers with the levers in which said seaming rolls are joumalled.

2. A machine of the character described, a revolvable seaming head; an arm having a tubularv hub portion at one end thereof and being attached to said head at the hub portion; a seaming roll carrying mechanism mounted on said arm; and means for actuating said mechanism comprising, a bell crank lever pivotally mounted on said arm'adjacent to the hub portion thereof, a second bell crank lever pivotally mounted on said head and having an arm thereof extending into alignment with the opening through said hub portion, an operative connection between said arm of said second bell crank lever and the first mentioned bell crank lever comprising a compression spring located within said hub, whereby movement of said second bell crank is transmitted to the first mentioned bell crank through said spring and means for rocking said Number Name Date second bell crank lever, 1,348,892 Pierson Aug, 10, 1920 EDWARD V. CRANE. 1,431,749 Newman Oct. 10, 1922 KARL KUHN. 1,494,661 Brenzinger May 20, 1924 5 1,639,515 Lange Aug. 16, 1927 REFERENCES CITED 1,639,552 Brenzlnger Aug. 16, 1927 The following references are of record in the 11647587 coyle 1, 1927 file of t t: 1,941, 2 Cameron Jan. 2, 934 2,130,518 Bach Sept. 20, 1938 UNITED STATES PATENTS 10 2,163,894 Bissell June 27, 1939 v N m Date 2,216,082 Kronquest Sept. 24, 1940 figggo m t 22 13 9 ,297, 3 Silverman Sept. 29, 1942 ,84 Rogers ADI- 19, 1904 FOREIGN PATENTS 905,801 Diecks Dec. 1, 1908 923,687 Nelson June 1, 1909 15 Number Country Date r 9 3 Qsflin Aug 3 1910 415,126 Germany m 1929 1,108,898 Garrett Sept, 1, 1914

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