US3288095A

US3288095A - Modified crank drive for feed bar drive and wing drive

Info

Publication number: US3288095A
Application number: US313384A
Authority: US
Inventors: James A Ballo
Original assignee: Carnation Co
Current assignee: Carnation Co
Priority date: 1963-10-02
Filing date: 1963-10-02
Publication date: 1966-11-29
Anticipated expiration: 1983-11-29
Also published as: BE653892A; NL6410091A; GB1075546A

Description

Nov. 29, 1966 J. A. BALLO 3,288,095

MODIFIED CRANK DRIVE FOR FEED BAR DRIVE AND WING DRIVE Filed Oct. 2, 1963 4 Sheets-Sheet 1 BLANK. MAGAYJ NE.

JAME$ A. BALLO INVENTOR. F70. Z

ATTORNEY.

Nov. 29, 1966 J. A. BALLO 3,288,095

MODIFIED CRANK DRIVE FOR FEED BAR DRIVE AND WING DRIVE Filed Oct. 2, 1963 4 Sheets-Sheet 2 JAMES A. BALLO INVENTOR.

- v BY ATTORNEY.

Nov. 29, 1966 J. A. BALLO 3,288,095

MODIFIED CRANK DRIVE FOR FEED BAR DRIVE AND WING DRIVE Filed Oct. 2, 1963 4 Sheets-Sheet 5 VENTOR. JA M55 5 4 Z10 BY I A 7'7'0rG/VEV Nov. 29, 1966 J. A. BALLO 3,288,095

MODIFIED CRANK DRIVE FOR FEED BAR DRIVE AND WING DRIVE Filed Oct. 2, 1963 4 Sheets-Sheet 4 INVENTOR, x/A/l/E A. 54110 Delaware Filed Get. 2, 1963, Ser. No. 313,384 10 Claims. (Cl. 113-113) This invention relates to an improvement in the power train of the feed mechanism and wing drive of high speed machinery such as can body makers. In particular, the invention concerns the incorporation of dwell motion into the feed bar mechanism of a can body maker to reduce the velocity of the feed bar at the time of impact against the work piece. Further, the invention concerns the wing drive of a can body maker and the use of dwell motion in the wing drive to reduce the impact of the wings against the can blank.

In can body making machinery, tin blanks are moved from station to station by a reciprocating feed bar mechanism. The feed bar is equipped with dogs which project above the elevation of the work table to engage a tin blank and move it to the next station. As the feed bar begins its backward stroke, the dogs retract and pass under the immediately succeeding tin blank, while an operation such as notching or crimping is being performed on the blank. With the forward stroke of the feed bar, the dogs again extend to engage the blank. The reciprocating motion of the feed bar thus moves the tin from station to station and eventually on to a horn where it is formed into a cylinder.

Each time the tin blank is moved to a successive station, the dogs strike it when they engage the tin blank. A primary limitation upon the speed of a can body maker is the velocity of the feed bar mechanism. If the feed bar reciprocates' at extremely high velocity the impact of the dogs against the tin blank crimps and distorts the edge of the tin blank. In addition to the velocity of the feed bar, crimping of tin blanks is a function of the weight and thickness of the tin blank, the size of the can and the length of the feed ba-r stroke. But generally, the limiting variable, with respect to any given size can, is the velocity of the feed bar at the time of impact against the tin blank. Crimping renders the blanks useless and often jams the machine. Thus, when making cans four inches or larger, it is current practice in the can industry to operate a can machine below about 400 cycles per minute to avoid crimping tin when the dogs of the feed bar strike the tin blank.

It is an object of this invention to provide a high speed can body maker capable of operating at 50% or more increase in the feed bar velocity without crimping tin blanks. In particular, it is an object to provide a can body maker which can operate at 600 cycles per minute or more utilizing cans of four inches or larger. A further object is to eliminate crimping and bending of can body blanks by reducing the impact of the dogs against the blank.

Another object of the invention is to accomplish the increase in can production through a mechanism which is adaptable for use in existing can body making equipment. Still another object of the invention is a dependable, durable, high speed feed trains for use in machines such as can body makers.

When a can blank reaches the horn of the can body machine, it has been flexed, knurled, notched and crimped. On the horn, the blank is formed into a cylinder and closed. Wings form the blank into a cylinder by closing the blank around the circular horn. The horn is expanded to positively interlock the folds at the overlapping States Patent Patented Nov. 29, 1966 edges of the blank, and the can is closed by the impact of a hammer on the interlocking edges.

Forming the body of a can around the horn must be done precisely or the body will not form a true cylinder. In the prior art, the impact of the wings against a tin blank often bent the blank or caused it to move out of position on the horn. A bent blank does not form a true cylinder, which makes it difficult or impossible to solder the can ends to form a seal. A blank which is moved out of position on the horn forms an imperfect cylinder or a cylinder having angular ends. These cylinders are rejected since they cannot be properly soldered.

To avoid the forming problems caused by the impact of the wings against the can blank, the prior art incorporated into can machines a pre-forming operation. In pre-forming the can blank is gradually formed into a partial cylinder before it is placed on the horn under the wings. In this manner, the distance the wings must move the blank to interlock the folded edges is reduced and the probability that the blank will be bent or moved out of position is also reduced.

An advantage of the present invention, when utilized in the wing drive of a can body maker, is that it reduces the impact of the wings on the can blank and eliminated the need for pre-forming.

Another advantage of the invention is that it permits the wing drive to be operated at higher speed.

It is a further object of this invention to provide a wing drive mechanism which reduces the impact of the wings on the can blank and does not bend the can blank or move it out of alinement on the horn.

The foregoing objects are accomplished through the invention:

(1) By incorporating into the feed bar drive mechanism means for causing the feed bar to dwell before the dogs contact the work piece and to thereby reduce the velocity of the feed bar at the time it engages the work piece.

(2) By incorporating into the wing drive means for causing the wings to dwell prior to contacting the can blank. In a preferred embodiment of the invention, the dwell is induced by a modified hypocycloidal crank drive.

With reference to the feed bar mechanism, the invention embodies a work table where a work piece is moved through successive operations by the action of a reciprocating or oscillating feed means, which is driven through a link mechanism by a modified crank drive. Into the crank drive is incorporated means for producing a dwell motion of the feed means at a time in the cycle prior to the time when the feed means engages the work piece.

The feed mechanism is of the type which moves a work piece through a series of operations in space relation, and is driven by a power train. The power train comprises a link means for connecting the feed mechanism of a machine and a modified crank drive. The link mechanism transmits the power supplied by the crank drive and converts the rotary motion of the crank into reciprocating motion of the feed mechanism. The essence of the invention is the dwell motion of crank drive which is timed to cause the feed bar to hold behind the work piece for a period and then move into the work piece at a linear velocity lower than that normally produced by any given cycle speed at the point of impact in the cycle.

The wing mechanism comprises three basic parts: wings or jaws which open and close around a horn to form a work piece into a cylinder, link means which transmit power to the wings, and drive means which operate through the link means to cause the wings to open and close around the horn. Preferably, the drive means is a modified hypocyloidal crank drive designed to impart to the wings a dwell motion which results in the wings striking a Work piece at a velocity lower than that normally produced by a given cycle speed at the point of impact in the cycle.

The hypocycloidal drive, of the preferred embodiments involves the concurrent motion :of two shafts. One shaft is a driven shaft, the other is drivingly connected to the first. The drive shaft rotates about its axis; the second shaft revolve with respect to the drive shaft, and the second shaft concurrently rotates about an axis removed from its own axis. The revolution of the drive shaft and the rotation of the second shaft are timed so that, with respect to the link means, their motions will, at a period in the major cycle of the crank, work to off-set each other and cause the feed means or wings to dwell.

The members of the modified crank drive are the drive shaft, drivingly connected crank shaft and means for causing the crank shaft to rotate about an axis, remote from its own, concurrently with the revolution of the drive shaft. More specifically, the modified crank drive is composed of a drive shaft and a crank shaft disposed at a distance from the drive shaft and connected to revolve with the drive shaft. The crank shaft comprises two'sections, a gear and a crank shaft pin, i.e. a revolving minor crank. The pin is afiixed to the gear and positioned eccentrically with respect to the axis of the gear to produce the minor crank motion. A second stationary gear is positioned to intermesh with the crank shaft gear, thereby producing rotation of the crank shaft pin as the drive gear revolves.

There are six figures illustrating the invention and its utilization.

FIGURE 1 is a side elevation of a limited portion of a can body maker. This figure illustrates the relationship between the modified crank drive, link means and the feed means.

FIGURE 2 is a detailed partial section of the modified crank drive; it is intended to illustrate the construction of the preferred embodiment.

FIGURES 3 and 4 are sections through the modified crank construction of FIGURE 2. These figures specifically illustrate the motion of the modified crank drive.

FIGURE 5 is a front elevation of the wing drive mechanism showing their relative relationship.

FIGURE 6 is a partial cross section through a second embodiment of the modified hypocycloidal crank drive.

With reference to the feed bar mechanism, and specifically referring to FIGURE 1 of the invention, the tin blank magazine 11 is recessed to one side of the work table 12. Tin blanks are supplied to the work table 12 through a series of flexer rolls, which are not shown. Disposed under the work table 12 is the feed bar 13 which is supported laterally on rolls 16. The feed bar 13 has a series of dogs 14 affixed along the length of the feed bar. When the feed bar 13 moves forward, in the di motion of A to B, the dogs 14 project above the level of the work table 12 and are held in that position by springs 17. When the feed bar moves backward, in the direction B to A, the dogs 14 retract below the level of the work table 12 and pass under a tin blank which rests on the Work table 12.

The drive link 18 is affixed to the feed bar 13. Drive rod 21 is rotatably atached .to drive link 18 and to the arm 23, by the pin 22. Arm 23 is composed of upper and lower members which may form an integral arm or be separate parts keyed to the pin 24. Arm 23 rotates about the fixed pin 24, which is mounted on the frame 25. A universal joint 27 connects the lower end of the arm 23 and the crank arm 26. A crank drive, which will be described in greater detail hereafter, supplies a rotational motion which is transmitted to the arm 23 by the crank arm 26. The arm 23 converts the rotational motion of the crank into a reciprocating motion, which is transmit ted through the rod 21 and link 18 to the feed bar 13. The elements described in the foregoing paragraph may generally be described as the link means. Their function is to convert the rotational motion of the crank drive into reciprocating motion, and to transmit the motion of the crank drive to the feed bar 12.

FIGURE 2 illustrates in detail the preferred modified epicyclic crank drive utilized to produce the dwell motion in the feed' bar mechanism. The stationary crank housing 31 is pinned to the frame 32 by the pin 33. The frame 32 encases the drive shaft 34. The drive shaft 34 rotates the crank mechanism. '

Bearings

36 and 37 support the drive shaft 34. The static-nary housing 31 and the rotating hub 38 are provided with an oil seal 39. Gear 41 is pinned to the stationary housing 31 by

pins

42 and 43. The gear 41 doe not rotate with shaft 34. The shaft 34 passes through an opening in gear 41 and is separated from it. The hub 38, collar 47, planetary pinion gear 46 and crank shaft 48 rotate with shaft 34. The collar 47 and hub 38 are keyed to the shaft 34 by the key 49 and gear 46 and crank 48 are housed in the collar 47.

Planetary pinion gear 46 meshes with stationary gear 41. The planetary gear 46 is aifixed to the crank shaft 48, which is supported by

bearings

51 and 52. The crank arm 26 is rotatably connected to the crank shaft 48 and rotates on bearing 53. Retaining ring 54 holds the crank arm 26 on the crank shaft 48.

The crank shaft 48 revolves about the shaft 34 and at the same time rotates within

bearings

51 and 52. The revolution of shaft 48 is produced directly from shaft 34 through the collar 47 and hub 38 which house the crank shaft 48 and are keyed to the shaft 34. The concurrent rotation of crank shaft 48 is induced through intermeshing gears 41 and 46. The planetary gear 46 is rigidly mounted upon the shaft 48 and the intermeshing of

gears

41 and 46 causes the shaft 48 to rotate as the planetary gear 46 orbits the stationary gear 41.

FIGURE 3 is a vertical section through the shaft 34, stationary gear 41 and planetary pinion gear 46. FIG- URE 3 illustrates in detail the revolving of the planetary gear 46 about the stationary gear 41 and the rotation of shaft 48 and planetary gear 46 around their axis. The stationary gear 41 is pinned to the housing 31 at 42, 43, 44 and 45. The shaft 34 rotates within stationary gear 41. The collar 47 and crank shaft 48 are keyed to the shaft 34 by key 49. Thus, the rotation of shaft 34 causes the crank shaft 48 and the planetary gear 46 to revolve or orbit about the stationary gear 41 in a clockwise direction. As the planetary gear orbits the stationary gear 41 the action of the intermeshing gears causes the planetary gear 46 and shaft 48 to rotate clockwise about its axis. I

The shaft 48 is composed of two sections having uncommon axis. It could also be formed by crank pin 483 being directly eccentrically attached to the gear 46. The entire shaft 48 rotates clockwise Within the

bearings

51 and 52. That portion represented by 48A rotates concentrically, and the eccentric pin, represented by 48B, rotates eccentrically.

The motion of shaft 48 and its construction may also be understood by reference to FIGURE 4, which is a vertical section view through the shaft 48B of FIGURE 2. The shaft 34 is fixed to the hub 38 and collar 47 by the key 49, and all rotate clockwise. As the shaft 34 rotates, the shaft 48 rotates on its axis driven by the intermeshing gears 41 and 46. The portion of the shaft designated 48A thus revolves or orbits in a concentric circle about the shaft 34 while it rotates or spins upon its axis. The eccentric crankshaft pin 48B is similarly revolved about the shaft 34; but, it does not follow a concentric circle. The offset of the axis of shaft 48A with respect to the axis of crank shaft pin 488 causes crank shaft pin 48B to rotate eccentrically, i.e. about a remote axis.

The dual motion of crank shaft pin 48B causes the periodic dwell of the feed bar 13. The motion of the major cycle of the crank pin 48B, i.e. revolution of crank pin 48B about shaft 34, and the rotational motion of crank pin 48B about the axis of 48A combine to hold the arm 23 in a substantially stable position for a period of the major cycle of the crank. During the time the arm 23 is stable and not oscillating about the pin 24, it is apparent that the feed bar 13 will dwell.

It is important that a period of dwell in the cycle of the feed bar 13 be timed to occur prior to the point of impact between the dogs 14 of the feed bar 13 and the tin blank so as to decrease the velocity of the feed bar at the time of impact. The dwell period may be followed by rapid acceleration of the feed bar 13, but this will not increase the velocity of the feed bar 13 at the time it contacts the tin blank. The critical factor is that the dwell period be arranged to reduce the velocity of the feed bar at the time it engages the tin blank, thereby reducing the impact and preventing crimping and distortion of the tin blank.

Upon reading the foregoing description of the modified epicyclic crank drive and its utilization to decrease the velocity of the feed bar dogs at the time of impact against the tin plate, the precise manner of causing the dwell to occur at the proper time in the crank cycle will be apparent to those of skill in the art. However, as a guide, it is pointed out that the length of offset between the axis of the shaft 48A and the eccentric crank pin 48B is dependent upon the radius of revolution of shaft 48A, the vertical displacement of the feed bar 13 from the crank pin 43B, and the gear ratio between the stationary gear 41 and the planetary pinion gear 46. These specific dimensions will vary with the machine. The period of dwell in the preferred embodiment is 30. The dwell period is set to terminate when the dogs are about .085 inch behind the tin blank. The exact gear ratio and displacement of the crank pin 48B from the axis of the shaft 48A, for any machine and any arrangement of the crank drive and link means can be calculated using velocity vectors and techniques known in the art.

As pointed out above, commercial can body makers, using a reciprocating feed bar, and the line associated with the body maker are currently designed to operate optimumly at about 400 cycles per minute, and generally at a lower rate for cans four inches or more in height. A body maker, using a feed bar drive of the same design as the preferred embodiment described above (which included high speed antifriction bearings and similar modifications to prevent breakdown at higher speeds) will operate at 600 cycles per minute or more without crimping or distorting the tin plate from the impact of the feed bar dogs.

After the feed bar picks up the tin blank it accelerates rapidly due to the dwell period. The rapid acceleration and deceleration of the feed bar while carrying the can blank may cause the tin to fly i.e. lose contact with the feed bar dogs. This problem can be overcome through the use of positive stops at the stations, hold-downs, and other techniques known in the art for positively positioning the tin plate at the station.

Referring to FIGURE 5, which illustrates the general operation of the wing mechanism, the wings 61 and 62 are pivotally mounted on the pin 63 and concealed pin 64. The horn 66 of the can body maker fits within the arc of the wings 61 and 62. The

lever arms

67 and 68 form a part of the link means transmitting power to the wings 61 and 62. Lever arm 67 is pivotally mounted upon pin 69, and lever arm 68 is pivotally mounted upon pin 71. The lever arm 67 actuates the wing 61 through the connecting member 72, and the lever arm 68 actuates the wing 62 through the connecting member 73. The wings are supported in a stationary position by attaching member 74 to an overhead support (not shown).

Crank rod 76 is attached to lever arm 67 by the bolt 77. Slot 78 permits the attached end of the crank rod 76 to be moved laterally along the lever arm 67 so as to vary the are described by the pivotally mounted lever arm 67. The other crank rod 79 is similarly attached to the lever arm 68 by the bolt 81, and the lever arm 68 is provided with a slot 82 to permit the attached end of the crank rod 76 to be moved laterally.

The crank

rods

76 and 79 are actuated by the modified hypocycloidal crank drive. Separate crank drives may be provided for each rod, or the power from one crank drive may be transmitted to both drive rods 76 and 77 through suitable link work means. The operation of the wing drive mechanism will be described with reference to the right wing 61 and its power train. It should be understood that the left wing 62 operates in exactly the same manner and in unison with the right wing 61. As shown in FIGURE 5, the crank pin 83A is near the bottom of its cycle, and the wing 61, which is actuated by the rotation of crank pin 83A, is in a closed position. As the crank pin 83A travels 180 to the top of its cycle, the lever arm 67 pivots upon the pin 69 and thereby opens the wing 61. While the wings 61 and 62 are in an open position, above the horns 66, a can blank is moved onto the horn 66 under the wings 61 and 62. The blank is held in position by the stop 70. The wings 61 and 62 then close around the horn 66 and the horn expands, forming the flat can blank into a cylinder. The folded, overlapping edges of the can blank are interlocked at the bottom of the horn and a hammer (not shown), strikes the folded edges to form a seam. Wings 61 and 62 release the cylinder and the horn 66 contracts to release the cylinder so that another can blank may be moved under the wings to be formed into a cylinder.

As explained early in the application, in the prior art, to allow time for the can blank to be inserted under the wings, and for other operations to be performed, the wings were raised a substantial distance above the elevation of the can blank. The impact of the wings against the can blank often bend the can or moved its position on the horn. In the present invention, a dwell motion is incorporated into the crank drives and 85. The dwell motion causes the wing 61 and 62 to raise just above the elevation of the top of the horn 66, and hold so that the can blank may be inserted under the wings. The wings 61 and 62 then close around the can blank and the Wings strike the can blank at a velocity lower than that normally produced by a given cycle speed at that point in the cycle, thereby reducing the impact of the wings against the can blank.

FIGURE 6 illustrates the preferred embodiment of the modified epicyclic crank drive used to produce dwell in the cycle of the wings. The stationary crank housing 84 is attached to the frame 86 of the can body maker by the

screws

87 and 88. The frame 86 houses the drive shaft 89, and the drive shaft 89 is supported by bearing 91. The stationary housing 84 is provided with gear teeth 92.

Mounted upon the crank shaft 89 are rotating hub 94, planetary gear collar 96 and planetary crank 83. The collar 96 and the hub 94 are keyed to the shaft 89 by the key 97 so that all three rotate with the shaft 89. An oil seal 100 is provided between the rotating collar 94 and the stationary housing 84. Planetary crank 83 is provided with gear 98, which is positioned to mesh with stationary gear 92 as the drive shaft 89 rotates. The planetary crank 83 is supported within the collar 96 by bearings 99 and 101.

As the planetary crank 83 revolves about the shaft 89, it concurrently rotates within bearings 96 and 101 in response to the action of intermeshing gears 98 and 92. The crank 83 is composed of two sections having uncommon axes. The crank pin 83B is positioned eccentrically upon the shaft 83A. Thus, as the shaft 83A concurrently revolves about shaft 89 and rotates about its axis the crank pin 83B prescribes a second minor crank motion. The concurrent motions of the major and minor crank cycles combine to produce a dwell motion at predetermined periods during the major crank cycle. This dwell motion is, of course, imparted to the wings 61 and 7 62 through the link means connecting the crank drive and the wings. In general, it will be appreciated that the embodiment illustrated in FIGURE 6 operates upon the same principles enumerated for the embodiment illustrated in FIGURE 2, except that FIGURE 6 utilizes an internal gear means 92.

From the foregoing it will be appreciated that the dwell motion of the crank pin 333 results in periodic dwell in the major cycle of the crank pin 833. It is important that the period of dwell imparted to the wings 61 and 62 by the crank drive 35 be timed so that the wings hold just above the elevation of the can blank, so as to decrease the velocity of the wings at the time they contact the can blank.

As in the case of the feed bar mechanism, the period of dwell, the amount of off set in the eccentric and the gear ratio of the crank drive for the wings will vary with the machine. These factors can be calculated by those skilled in the art for any type machine into which the modified epicyclic crank drive is incorporated. In the preferred embodiment of the wing drive mechanism, the period of dwell is 90. It is not essential tthat the dwell be absolute; the wings may flutter during the period of dwell, so long as they do not touch the can blank. The preferred distance between the wings and the can blank at the termination of the dwell period is about .187 inch.

It will be appreciated that no attempt has been made herein to describe the complete can body maker. The complete machine consists of successive stations for flexing, knurling, notching, crimping, forming, closing and soldering the can body. Its operation is well known in the art, and the relationship of the feed bar drive and wing drive to the whole machine is apparent from the described embodiments. The various operations of the can machine are generally run off one or more main drive shafts which run the length of the body maker. In the particular model utilized to illustrate the present invention there are three drive shafts (two of thes are not shown) and the power to actuate the crank drive of the feed bar mechanism is taken off the right shaft (herein shaft 34). This embodiment specifically illustrates the relationship between the feed bar, work table and the modified crank drive used to produce the dwell in the feed bar. This invention is not limited to a machine employing three shafts; the power take off for the crank drive and the position of the crank, link work means and feed bar can be arranged to suit the particular machine.

The preferred modified epicy-clic crank drive is particularly advantageous in that it may be incorporated into existing crank drive fee-d bar mechanisms and wing drive mechanisms of can body makers without extensive modification. Thus, at relatively little expense the output of the machine is increased by 50% or more.

The invention has been described with reference to a tin can body maker, but it is applicable to other machinery employing a reciprocating feed bar or wing drive mechanism of the general type described. Neither is the applicability of the invention limited to machines for making tin cans; other sheet metal and sheet material may -be used.

While the invention has been described with reference to a particularly preferred embodiment, it should be understood that these are only illustrative and not intended to limit the scope of the invention. Accordingly it is intended that variations and modifications which fall within appended claims be included.

Having described the invention, what is claimed is:

1. A feed mechanism for advancing a sheet metal work piece through a series of operations along a work table which comprises: reciprocating feed means for striking said work piece; a link means, said link means being capable of converting rotational motion into reciprocating motion and transmitting said reciprocating motion to said feed means; a modified crank drive comprising: a

8 drive shaft; a revolving, rotating crank shaft, said crank shaft defined by a crank gear and a crank shaft pin positioned eccentrically to the axis of said crank gear; a stationary gear positioned to mesh with said crank gear; means for drivingly interconnecting said drive shaft and said crank whereby the revolution of said drive shaft causes relative orbital movement of said crank gear with respect to said drive shaft and causes concurrent rotation of said crank shaft pin about the axis of the crank shaft gear so that the link means connecting said crank pin and said feed means imparts a dwell to said feed means prior to the time the feed means strikes the work piece.

2. An apparatus comprising: a reciprocating feed means positioned to strike a sheet metal work piece resting on a work table and advance the work piece through a series of operations; a link means for transmitting rotational motion into reciprocating motion; a modified crank drive comprising: a drive shaft, a crank shaft d-rivingly connected to said drive shaft, said crank shaft defined by a pinion gear and crank shaft pin, said crank shaft pin being positioned eccentrically on said pinion gear and having an axis parallel to the axis of said pinion gear; a stationary gear positioned to mesh with the pinion gear as the drive shaft revolves the crank in relative orbital movement whereby the crank shaft pin is caused to concurrently rotate about the axis of the pinion gear; link means connecting said feed means and said crank drive so as to convert the rotational motion of said crank into reciprocating motion and transmit said reciprocating motion to the feed means.

3. In a machine for forming can bodies from sheet metal blanks by moving said blanks through a series of operations, the improvement in the reciprocating feed means for advancing said blanks which comprises: a modified crank means for driving said reciprocating feed means which comprises: a first shaft; a second shaft, said second shaft trained to move in an orbit concentric from an axis remote from the axis of said second shaft; an external planetary gear keyed to a fixed ring gear whereby the revolution of said first shaft causes relative orbital movement of said second shaft concentrically with respect to said given axis and concurrent revolution of said second shaft in timed orbital movement with said second shaft with reference to said given axis.

4. In a machine for forming can bodies from sheet metal blanks by advancing said blanks through a series of operations, the improvement in the reciprocating feed means for advancing said blanks along a work table which comprises: a modified crank means for driving said reciprocating feed means which comprises: a drive shaft; a planetary crank comprising a first member and a secand member having an axis uncommon to said first memher, said first member trained to rotate concentrically about said second member; means for drivingly interconnecting said drive shaft and said planetary crank whereby the revolution of said drive shaft causes relative orbital movement of said crank shaft with respect to said drive shaft and causes concentric rotation of said first member about said second member in timed orbital movement to impart to said feed means at a time just prior to the feed means striking the blank.

5. In a machine for forming can bodies from sheet metal blanks by advancing said blanks through a series of operations along a work table, the improvement in the reciprocating feed means for advancing said blanks which comprises: a modified crank means for driving said reciprocating feed means which comprises: a drive shaft; a revolving, rotating crank shaft, said crank shaft defined by a crank gear and a crank shaft pin positioned eccentrically to the axis of said crank gear, said pin having an axis parallel tothe axis of said crank gear; a stationary gear positioned to mesh externally with said crank gear; means for driviingly interconnecting said drive shaft and said crank whereby the revolution of said drive shaft causes relative orbital movement of said crank gear with respect to said drive shaft and concurrent rotation of said crank shaft pin about the axis of the crank gear in timed orbital movement to impart to said feed means a dwell at a time just prior to the feed means striking the blank.

6. In a power train for driving a feed means constrained to reciprocate in a linear path, the improvement which comprises: a first crank; 21 second crank mounted on the throw of said first crank; means interconnecting the throw of said second crank with said feed means, said connecting means being capable of converting the rotational motion of said second crank into reciprocating motion of said feed means; means for driving said first crank; means for driving said second crank in timed relation to the revolution of said first crank whereby the throw of said second crank is caused to move in predetermined relation with respect to the throw of said first crank, whereby a dwell is effected in the movement of said feed means at a time just prior to the reciprocating feed means striking a Work piece.

7. In a power train for driving a reciprocating feed means of a can body maker, the improvement which comprises: a modified crank drive; a link means, said link means arranged to connect said modified crank drive and said feed means so as to cause said feed means to reciprocate in response to the revolution of the crank drive; said modified crank drive further defined by, a first crank, a second crank mounted on the throw of said first crank, an external planetary gear keyed to a ring gear to concurrently rotate in timed orbital movement with the revolution of said first crank so that the concurrent motion of said cranks impart a dwell to the reciprocating feed means at a predetermined time during its cycle.

8. In a machine for forming can bodies from sheet metal blanks the improvement in the power train of the wing drive mechanism which comprises: a modified crank means for driving said Wings which comprises: a drive shaft; a planetary crank comprising a first member and a second member having an axis uncommon to said first member, said first member trained to rotate concentrically about said second member; means for drivingly interconnecting said drive shaft and said planetary crank whereby the revolution of said drive shaft causes relative orbital movement of said crank shaft with respect to said drive shaft and causes concentric rotation of said first member about said second member in timed orbital movement to impart to said wing means a dwell during a period in the cycle just prior to the wing means contact-ing the sheet metal blank.

9. In a power train for driving the Wing mechanism of a can bodymaker, the improvement which comprises: a modified crank drive; a link means, said link means arranged to connect said modified crank drive and said wing means so as to cause said wing means to open and close in response to the revolution of the crank drive; said modified crank drive further defined by, a first crank, a second crank mounted on the throw of said first crank, means for causing said second crank to concurrently rotate in timed orbital movement With the revolution of said first crank so that the concurrent motion of said cranks impart a dwell to the wing means at a predetermined time during its cycle.

10. A modified crank drive means for imparting a dwell motion to the feed bar mechanism and wing drive mechanism of a can body maker at a time just prior to v the wing mechanism contacting a can body, which crank drive means comprises: a first shaft; a second shaft, said second shaft being trained to move in an orbit concentric from an axis remote from the axis of said second shaft; means for drivingly interconnecting said first shaft with said second shaft whereby the revolution of said first shaft causes relative orbital movement of said first shaft concentrically with respect to said given axis and concurrent revolution of said second shaft and timed orbital movement of said second shaft with reference to said given axis.

References Cited by the Examiner UNITED STATES PATENTS 1,736,935 11/1929 Navarre 113-113 2,360,762 10/1944 Conrad 74-52 2,614,520 10/1952 Allen 7452 2,676,799 4/ 1954 Fletcher 7452 3,060,880 10/1962 Laxo 113115 3,100,470 8/1963 Wolfe 113113 CHARLES W. LANHAM, Primary Examiner.

RICHARD J. HERBST, Examiner.

Claims

1. A FEED MECHANISM FOR ADVANCING A SHEET METAL WORK PIECE THROUGH A SERIES OF OPERATIONS ALONG A WORK TABLE WHICH COMPRISES: RECIPROCATING FEED MEANS FOR STRIKING SAID WORK PIECE; A LINK MEANS, SAID LINK MEANS BEING CAPABLE OF CONVERTING ROTATIONAL MOTION INTO RECIPROCATING MOTION AND TRANSMITTING SAID RECIPROCATING MOTION TO SAID FEED MEANS; A MODIFIED CRANK DRIVE COMPRISING: A DRIVE SHAFT; A REVOLVING, ROTATING CRANK SHAFT, SAID CRANK SHAFT DEFINED BY A CRANK GEAR AND A CRANK SHAFT PIN POSITIONED ECCENTRICALLY TO THE AXIS OF SAID CRANK GEAR; A STATIONARY GEAR POSITIONED TO MESH WITH SAID CRANK GEAR; MEANS FOR DRIVINGLY INTERCONNECTING SAID DRIVE SHAFT AND SAID CRANK WHEREBY THE REVOLUTION OF SAID DRIVE SHAFT CAUSES RELATIVE ORBITAL MOVEMENT OF SAID CRANK GEAR WITH RESPECT TO SAID DRIVE SHAFT AND CAUSES CONCURRENT ROTATION OF SAID CRANK SHAFT PIN ABOUT THE AXIS OF THE CRANK SHAFT GEAR TO THAT THE LINK MEANS CONNECTING SAID CRANK PIN AND SAID FEED MEANS IMPARTS A DWELL TO SAID FEED MEASN PRIOR TO THE TIME THE FEED MEANS STRIKES THE WORK PIECE.