US2352095A - Metalworking machine - Google Patents

Description

June 20, 1944. C C, GROTNES 2,352,095

METAL WORKING MACHINE Filed June 5, 1939 8 Sheets-Sheet 1 mm, r/ C @ro/hes June 20, 1944. c. c. GROTNES METAL WORKING MACHINE Filed June 5, 1959 8 Sheets-Shea?I 2 Cro/nes Z W Y@ u y y@ y -I .0. -mM Il ---2.-. im-- Il i -q -J4 4 3 3 o 9J m ,WW I@ M 4 2 o 6 ix l 7 L W. \|l/ 5 nrw mw 0 x l xd 2 Q 2 III J o 2 ..\}-m. O/NQ 9 L K 4 O :O dw j 5 3 5 Q June 20, 1944- c. c. GROTNES METAL WORKING MACHINE 8 Sheeis-Sheet 3 Filed June 5, 1939 June 20, 1944. Q Q @R01-NES 2,352,095

METAL WORKING MACHINE lll' lI I.

NVENTQJ ('flTTo ways June 20, 1944. C;l C, @R01-NES 2,352,095

METAL WORKING MACHINE Filed June 5, 1939 e sheets-Sheet 5 IM x."

[HIllIH June 20, 1944. 1;;t Q @R01-NES 2,352,095

METAL WORKING MACHINE Filed June 5, 1959 8 Sheets-Sheet 6 June 20, 1944. c. c. GROTNES METAL WORKING MACHINE 8 sheets-sheet 7 Filed-June 5, 1939 8 Sheets-Sheet 8 C. C. GROTNES METAL WORKING MACHINE Filed June 5, 1959 `lune 20, 1944.

Patented Jane 2o, 1944 UNITED STATES PATENT OFFICE METALWORKING MACHINE Carl C. Grotnes, Park Ridge, Ill. Application June 5, 1939, Serial No. 277,371

6 Claims.

The invention relates to metal working machines generally, and more particularly to an improved machine for operating on cylindrical sheet metal shells to shape them for use as parts of containers such as pails, drums, barrels or the like.

In the manufacture of containers of the above general character, the body is initially formed from a sheet metal blank rolled to constitute a generally cylindrical sheet metal shell. Usually four forming operations are performed on the shell, two on each end thereof, to shape it for assembly with other parts of the container. These operations commonly include the rolling of a bead on the upper end of the shell and the formation of an annular rib around the shell adjacent the bead for the purpose of rounding and stiffening the shell. Another operation consists of drawing inthe metal at the lower end of the shell to form a neck of reduced diameter and finally to form a fiange on the lower edge of the shell for the reception of the bottom element of the container. It has been the usual practice heretofore to perform the above operations as separate and distinct steps and on separate, independent machines. This not only requires a large investment in forming machines but it also necessitates considerable manual handling of the work which slows up production and materially increases the unit cost per container.

With the above in view, the primary object of the present invention is to provide a unitary machine structure capable of performing all of the above operations as parts of one complete integrated manufacturing process without manual handling of the work piece between operations.

More particularly, it is one object of the invention to provide an improved metal working machine adapted to receive a continuous succession of cylindrical metal shells, to automatically perform a plurality of shaping operations on both ends of each shell, and to discharge the completely formed shells in a continuous stream, thereby effecting a material reduction in the amount of manual labor required and in the unit cost per shell.

Another object is to provide an improved metal working machine adapted to perform a series of shaping operations on opposite ends of a cylindrical metal shell and embodying novel means for turning the shell end-for-end between operations.

Another object is to provide improved means for feeding thefshells to the forming units of the metal working machine, for accurately positioning the shells for engagement with the dies of the units, and for removing the shells after the units have completed their forming operations.

Still another object is to provide an improved metal working machine embodying a plurality of forming units, turning mechanism, feed mechanism, and novel means for coordinating and controlling the operation of the units and the mechanisms.

Other objects and advantages of the invention will become apparent from the following detailed description of the preferred `embodiment illustrated in the accompanying drawings, in which:

Figure 1 is aside elevational view of a metal working machine embodying the features of the invention.

Fig. 2 is -a vertical sectional view of one of the forming units of the machine taken substantially along the line 2--2 of Fig. 1.

Fig. 3 is a vertical sectional view of another of the forming units of the machine taken along the line 3 3 of Fig. 1.

Figs. 4 and 5 are fragmentary bottom views of the die assembly of the second forming unit, the rst mentioned figure showing the dies opened and the latter showing the dies closed.

Fig. 6 is a fragmentary vertical sectional view showing details of the forming dies illustrated in Figs. 4 and 5.

Fig. '7 is a sectional view taken along the line 1 1 of Fig. 6.

Fig. 8 is a side view of the turnover mechanism showing the driving instrumentalities.

Fig. 9 is a view showing the driving instrumentalities in normal position.

Fig. 10 is a sectional view taken along the line l-IU of Fig. 8.

Fig. 11 is a plan View of the turnover mechanism.

Figs. 12' and 13 are detail views of the gripping device forming a part of the turnover mechanism.

Fig. 14 is a. plan view of the feed mechanism showing its relationship to the forming units.

Fig. 15 is a fragmentary perspective view of a portion of the feed mechanism.

Fig. 16 is a diagrammatic view showing the relationship of the various elements of the feed mechanism.

Fig. 17 is an end view of one of the gripping devices constituting a portion of the feed mechanism.

For the purpose of illustration, the invention has been shown in the drawings as a unitary machine structure .for rolling a bead 2| (Figs. 1 and 16) and expanding a stiffening rib 22 at one end of a cylindrical sheet metal shell 23 and for drawing in the other end of the shell to form a neck 24 of reduced diameter and for forming a circumferential flange 25 thereon. It is to be understood, however, that the invention is not limited to the performance of these particular operations, and the appended claims are intended to cover all modifications, adaptations, and alternative constructions falling within the spirit and scope of the invention.

General The machine selected to illustrate the invention is arranged to perform the several forming operations above referred to at two different operating stations designated respectively as station No. 1 and station No. 2 in the diagrammatic layout shown in Fig. 16. At each of these stations there is installed a forming unit equipped with suitable cooperating die sets for shaping one end of the shell, the latter being turned through an angle of 180 between operations. It will be undestood, of course, that the forming units may be equipped with dies for shaping the shells to any desired contour.

The two operating stations No. l and No. 2 are separated in the present instance by an intermediate or work turning station No. 3 and are preceded and followed respectively by loading and unloading stations No. 4 and No. 5. The cylindrical shells 23, constituting the work pieces to be operated on, are placed on a horizontal platform 28 at the loading station and are fed along this platform intermittently by means of a power actuated feed mechanism operating in timed relation with the operations of the forming units. This mechanism advances the work pieces in succession from the loading station No. 4 to the first operating station No. 1, then to the turning station No. 3, to the second operating station No. 2, and finally to the unloading station No. 5. At each operating station the work piece is brought to rest and accurately positioned for engagement by the forming dies of the unit at that station. By coordinating the feed mechanism with the operating units, the work pieces are caused to remain stationary or dwell at the operating units while the dies operate thereon. During the interval that the forming units are executing their respective operations, the work piece at station No. 3 is turned through an angle of 180 by a turnover mechanism installed at that station so that the work piece will be positioned correctly for presentation to the second forming unit.

The forming units, turnover mechanism, and feed mechanism are all assembled as elements of a unitary machine structure and are supported on an elongated horizontal base 21. The units and mechanisms are mechanically interconnected and, in the present instance, are driven by a common motor M (Fig. 2) so that their respective functions are invariably executed in the proper timed relation. Operation of the machine is continuous. a succession of work pieces being fed in at one end and discharged in finished condition at the other end. Thus, only two very simple manual operations are required in the production of container shells, namely, the placing of the plain shells on the platform at the loading station No. 4 and the removal of the finished shells at the unloading station No. 5. These manual operations may be dispensed with and the work performed automatically, if desired.

The first ,forming unit The forming unit at operating station No. l. which may be of any suitable type, is -herein shown as comprising a machine structure generally similar to that disclosed in my copending application, Serial No. 204,402, led April 25, 1938. Briefly described, the unit comprises a rigid, generally rectangular metal frame 3l (Figs. 1 and 2) supported above the platform 23 by four hollow columns 32 which rest on a bed plate 33 bolted or otherwise rigidly secured to the top of the base. One or more removable spacers 34 may be interposed between the tops of the columns -and the frame to adjust the distance of the. latter with respect to the base and thus adapt the machine for operating on work pieces of different lengths. The frame and associated parts are rigidly held together and secured to the base by tie rods 35 which extend through the frame and the hollow columns and have their lower ends projecting through the bed plate and the top of the base. Nuts 36. threaded onto the ends of the rod, clamp the parts together and provide means whereby the effective lengths of the tie rods can be varied as required by the number of spacers 34 in use.

Slidably supported for movement vertically in the frame 3| is a die head 4I which carries on its lower end a circular beading die 42 and an expansible rib forming die 43, both of well known construction. To support the work to be operated on by the dies there is provided a generally circular work support or table 44 mounted on the upper end of a vertical standard 45 threaded into a stepped bushing 43 which is seated in a stepped socket in the bed 33. In use, the table is adjusted with its top abutting the underside of the platform 23 to support the same as the die 42 engages the work piece in the bead forming operation. The work pieces are shifted along the platform and positioned above the table in their progression through the machine under control of the feed mechanism.

The feed mechanism not only delivers the work pieces to the forming unit, but positions them accurately in axial alinernent with the dies 42 and 43. After the work piece is so positioned, the head 4| is moved downwardly and the die 42 engages its upper end and rolls back the edge to form the bead 2|. The extent 0f this downward movement is determined by the position of stop nuts 4|* (Fig. l) threaded on the ends of rods 42* secured to the head and projecting through vertically disposed apertures in the frame structure. The nuts are adapted to engage suitable resilient stops 43 upon completion of the bead forming operation.

In the course of the movement of the head to form the bead 2| the die 43 is inserted within the shell and is then expanded to form the stiff ening rib 22. 'I'he die is then contracted and the head 4i withdrawn to its initial position to permit the removal of the partially finished work piece and the presentation of a new work piece by the feed mechanism.

The reciprocation of the head 4I and the actuation of the die 43 above referred to is effected -by a common power actuated driving mechanism so arranged that the various operating steps take place in succession and in proper timed relation. This mechanism as herein shown includes a single throw crank shaft 41 (Figs. 1 and 2) journaled on the upper end of the frame 3l. Rotation of the crank shaft is effected through the medium of a pair of spur gears 43 keyed thereto and meshing with pinions 49 fast on a countershaft 50 journaled in the frame 3| and extend' ing parallel to the crank shaft. The countershaft is driven by a gear meshing with a pinion -52 on a shaft 53 which, in the present instance, constitutes the main drive shaft of the machine and which also serves to drive the second forming unit as will appear presently. The main shaft is continuously driven by the motor M through the medium of a gear 54 and pinion 55 on the motor shaft. The motor is herein shown as mounted on a bracket 56 projecting rearwardly from the frame 3|.

The crank shaft 41 is operatively connected with the head and the die 43 by a pitman 51 having a draw lbar 58 pivotally secured thereto and.

projecting axially through the head and the die. A generally cone-shaped member 59 fast on the end of the draw bar acts in the downward movement of the crank arm to expand the die 43 in the well known manner. In the upward movement of the bar, the member engages the lower end of the head and raises the same to its normal retracted position. The head tends to follow'the downward movement of the member 59 by reason of its weight until it engages the upper end of the work piece. Further movement of the head to cause the die 42 to roll the bead on the work piece is effected by a pair of cams 60 rigid with the gears 48 which cooperate with suitable cam follower rollers 8| carried on the head. Thus, in each revolution of the crank shaft the head is advanced to roll the bead on the work piece and thereafter the die 49 is expanded to form the stiiening rib therein. The die is then contracted and it, together with the head and bead forming die, is returned to initial position in readiness for the next operating cycle.

The second ,forming unit The forming unit at the No. 2 operating station is located adjacent the end of the base opposite the first forming unit and in line with said first unit as shown in Fig. l. Like the unit above described, the second forming unit includes a generally rectangular frame 3| supported above the platform by hollowd columns 82' resting on a bed 33 rigidly secured to the top of the base 21. Removable spacers 34' are interposed between the tops of the supporting columns and the frame for adjusting the height of the unit as required by work pieces of different lengths. Tie rods extending through the columns hold the parts together in the unitary structure in the same manner as the tie rods 35.

The second forming unit is also equipped with a work table 44' similar to the work table 44 and adjustably supported by a post threaded into a bushing 48' carried on the bed 33'. In this instance, however, the table is provided with a supplemental top 1| which is supported on the table proper by means of a series of coiled compression springs 12 which permit a limited yielding movement of the top. This construction is employed to prevent damage to the dies or the work piece in the event that a slightly oversize work piece is presented to the machine. The table is set with the supplemental top in the same plane as the platform 25 so that the work pieces may slide onto and off of the table.

In the exemplary machine the second forming unit is required to form the reduced neck 24 and the flange 25 on the end of the shell opposite the bead 2|. The unit is, accordingly, equipped with a die assembly including a pair of opposed vseries of blocks.

annular die sets Il and 14 (Figs. 3, 4, 5 and 6) and with die actuating mechanism suitable for this purpose. While the die assembly may be of any suitable construction, I have shown a structure embodying a number Vof novel and advantageous features which are particularly adapted for operation at high speed and which insure true roundness oi' the shell and clean and accurate shaping of the neck and flange without folds or wrinkles.

Referring to Figs. 4, 5 and 6, the die set 19, which, in this instance, constitutes the inner or expanding set of the pair, comprises a series of die blocks 15 arranged in a circle and carrying on their outer ends removable forming dies 16 shaped to define the contour to which the shell is to be drawn. The die blocks 15 are slidably supported for radial movement in a frame comprising an upper plate 11 carried on the lower end of a vertically reciprocable head 18 and an annular lower plate 19 secured to the upper plate by bolts I9. As shown in Figs. 4 and 5 the bolts are disposed between adjacent die blocks, the edges of the latter being notched as at 8| to accommodate the blots and to permit a limited movement of the blocks. Keys 82 engaging in complementary slots in the bottom plate 19 and in the respective die blocks guide the latter for true radial movement.

The die blocks of the inner die set 19 are normally held in an inner or contracted position by an annular coil spring 83 (Fig. 6) encircling the Outward movement of the blocks to expanded position is effected by means of an actuator 84 carried on a draw bar 85 which is slidably supported in a centrally located bushing 85 (Fig. 3) in the head. 'I'he lower end of the actuator is formed with an inclined cam surface 81 adapted to coact with an oppositely inclined cam surface 88 formed on the inner end of each die block and effective to shift the die blocks outwardly in the initial movement of the actuator from retracted position. The upper end of the actuator is of generally cylindrical form.

- thus presenting vertical wall 89 engageable with a vertical wall 90 on each ofthe die blocks to hold the same in fully expanded position while the actuator completes its full stroke.

The outer die set 14, as herein shown, comprises a series of blocks 9| arranged in a circle concentric with the inner die set 13. These blocks are likewise supported for radial movement in this instance between the plate 11 and an an.

nular bottom plate 92 secured thereto by bolts 93. The die blocks may be keyed to the latter plate as by key bars 94 (Figs. 6 and 7) to insure true radial movement. Each die block carries on its inner end a removable forming die 95 generally complementary to the die 15 and adapted to cooperate therewith in forming the neck and flange on the work piece.

The die blocks 9| are normally held in an expanded position by individual springs 95, each connected at one end to a pin 91 on the associated block and at the other end to the bottom plate 92. When the die blocks 9| are fully retracted, that is, when the die set is expanded, as shown in Fig. 4, they, with the inner set of die blocks 15. define an annular space 98 for the reception of the end of the shell to be operated on. Stops 99, carried on the inner set of die blocks and projecting outwardly therefrom into the space 98, define the limit position of the shell in the die and thus insure formation of the neck and flange at the proper location.

The die sets are brought into operative association with the work piece by a downward movement of the head 18 whereupon the inner die set is expanded in the manner above explained to center the work piece and to give it the desired accurately shaped form. The die set is preferably adjusted so that the shell is placed under slight tension so that the outer die set 14 on contracting is enabled to draw in the metal of the shell to form the neck 24 and to shape the flange 25 therein without folds or wrinkles such as are commonly produced when a nonexpansive inner die or mandrel is employed.

Contraction of the outer die set 14 is effected in the present instance by means of a series of cams IDI, each coacting with an inclined cam surface |02 formed in the outer ends of the die blocks These cams may be formed integrally with or rigidly secured to the inner surface of a ring |03 which encircles the die set, the ring in this instance constituting the lower end of a sleeve memberv |04 which encircles the head 18 and which is slidably supported for vertical movement on suitable ways |05 formed in the machine frame 3|'. The head 18 is loosely fitted in the cam sleeve and is guided in its movement relative'thereto by guide bars |08 (Fig. 3) extending longitudinally of the head and engaging in vertical slots in the inner wall of the sleeve.

I-n the operation of the unit, the head 18, die actuator 84, and cam sleeve |04 are advanced together until the die sets are positioned over the end of the shell to be operated on'. Movement of the head is interrupted at the proper point by suitable adjustable stops herein shown as rods |01 (Fig. 3) threaded into the upper end of the head and projecting through apertures in the machine frame. Nuts |08 threaded onto the projecting ends of the rods are in position to engage the machine frame or suitable resilient stops similar to the stops 43, as the head approaches its limit position. While the head remains stationary, the die actuator 84 and cam sleeve |04 continue their advance to actuate the inner and outer die sets. The cam surface 81 of the actuator is spaced somewhat below the cams |0| of the sleeve member so that the inner die set 13 is expanded to center and tension the work piece. The outer die set is then contracted to form the neck and flange therein. After the forming operation is completed, the actuator and sleeve are retracted, the die assemblies opening up tq release the work piece and the head is withdrawn to its initial position by engagement of the actuator therewith.

The advancing and withdrawal movements of the die actuators and head are imparted thereto by power driven means including a shaft |09 (Fig. 3) journaled in suitable bearings ||0 on the upper end of the frame 3|. The shaft is arranged to be rotated cyclically through the medium of a pair of gears (Fig. 1) keyed thereto which mesh with pinions ||2 (Fig. 3) fast on a countershaft ||3 journaled on the frame. The countershaft in turn is driven from the main drive shaft 53 by means of a gear ||4 and pinion ||5.

For advancing the head 18, the shaft |09 is equipped with a pair of cams ||6 (Fig. 1) which coact with roller cam followers ||1 (Fig. 3) on the head. An eccentrically disposed shaft section A ||8 extending between the two cams ||6 constitutes a crank arm for operating the die actuator 84 and to this end is operatively connected with the draw bar 05 by means of a pitman ||9. Finally eccentrica |20 on the outer-ends of the shaft |09 are connected by eccentric straps |2| and rigid links |22 with studs |23 rigid with the cam sleeve |04 and projecting laterally therefrom. These eccentrics thus serve to reciprocate the sleeve in the manner and for the purpose above explained.

The turnover mechanism The turnover mechanism referred to hereinbefore is preferably located at the turning station No. 3 between the two forming units and its function is to turn the work pieces end-for-end so that the second unit may operate on the end opposite to that shaped by the first unit. This mechanism is preferably power driven and its operation is synchronized with the operation of the forming units and the feed mechanism so as to make possible the continuous operation of the machine.

Referring to Figs. l, 8 and 11, the turnover mechanism in its preferred form comprises a box-like, generally rectangular metal work supporting members or frame |25 consisting of flat metal end plates |26 rigidly connected on opposite sides by side plates |21. The other two sides of the frame are open so that the work pieces can be loaded therein and removed therefrom by movement longitudinally of the platform 26.

As herein shown, the frame |25 is supported for rotation about a transverse horizontal axis by trunnions in the form of shafts |28 (Fig. 11) secured at their inner ends in supporting members |29 rigidly secured to the side plates |21 and projecting laterally therefrom. These shafts are journaled in bearings |30 adjustably supported on upright standards |3| bolted or otherwise rigidly secured to the machine base. The bearings are adapted to be raised or lowered by means of adjusting screws |32 to position the frame at the proper height for receiving the work pieces in their travel along the platform 25.

In order to hold the work piece in place in the turning operation, the frame |25 is equipped l with gripping devices which grip the sides of the same as the frame starts its turning movement and releases the work piece upon completion of the operation. In the particular embodiment illustrated, two gripping devices are provided, one on each side of the frame as shown in Figs. 11, l2 and 13. Each gripping device comprises a pair of clamping jaws herein shown as generally rectangular plates |35 having their adjacent end portions bifurcated as at |38 to straddle the l supporting member |29, the end portions of one plate overlapping those of the other as shown in Fig. 12. Pivot pins |31 extending through the overlapping portions of the plates and into the member |29 support the `jaws for pivotal movement about an axis substantially perpendicular to the axis of rotation of the turning frame.

Formed on the free end of each of the plates |35 adjacent the upper and lower edges thereof are a pair of inwardly projecting lugs or work engaging elements |38 having their ends suitably shaped for snug engagement of the sides of a work piece. Tension springs |39 connecting between the clamping jaws normally tend to draw the jaws together to force the elements into engagement with the work piece in the frame. When so engaged the elements hold the work pieces securely in place regardless of the position of the frame.

In order to enable the work pieces to be inserted in and removed from the frame, means assaoes is provided for opening the clamping jaws when the frame is in an upright position. This means as herein shown comprises a pair of stationary cam plates |40 carried on the bearing members |30 on opposite sides of the frame. Each cam plate is formed with a pair of oppositely facing inclined cam surfaces |4| adapted to coact with rearwardly projecting lugs |42 formed on the respective jaw plates |35. In the illustrative embodiment, the cam .surfaces |4| are positioned to be engaged by the lugs |42 for opening the gripping Jaws as the frame rotates into upright position as shown in Figs. 1, 9 and 11. As the frame rotates out of the upright position to turn a work piece, the cams release the clamping jaws for movement by their actuating springs lls'into the work clamping position shown in Fig. 13.

While any suitable means may be employed for rotating the turning frame |25 to turn the work pieces, it is preferred to utilize for this purpose a novel power driven mechanism operating in coordination with the forming units and the feed mechanism. The rotating mechanism as herein shown includes a friction clutch compris'- ing a constantly rotating driving member |45 (Figs. 8, and 11) and a cooperating driven member |46. The driving member, herein shown as a circular plate having an integrally forming hub |41, is loosely mounted on a shaft |48 journaled on the machine base below the turning frame. The driven member |46 comprises a steel disk keyed to the outer end of the shaft |46 and having secured to its inner face a generally conical friction element |46a of wood or other suitable material adapted to t into a correspondingly shaped depression in the face of the driving member |45 to establish a friction driving connection between the members.

In the present instance, the driving member |45 of the clutch is arranged to be driven by the motor M through suitable gearing including a bevel gear |49 (Fig. 1) keyed to the countershaft 50 of the first forming unit. This gear meshes with a bevel gear |50 fast on the upper end of a vertical shaft |5| journaled in suitable brackets |52 carried on the frame 3|. A bevel pinion |53 (Figs. 8 and 1l) fast on the lower end of the vertical shaft drives a bevel gear |54 keyed to a horizontalshaft |55 journaled on the base 26 in parallel relation to the shaft |48. A gear |56 on this shaft meshes with gear teeth cut in the periphery of the clutch driving member |45 to drive the same.

The driven clutch member |46 is adapted upon rotation to rotate the turning frame |25. To this end, the member is provided with an eccentrically located crank pin |51 (Figs. 8, 9 and 11) connected by a rigid link |58 with a stud |59 fast on one end of a crank arm |60 keyed to the trunnion shaft |26. As herein shown the link |56 is constructed in two sections connected by a turn buckle |6| to permit adjustment of the length of the link when the position of the bearing |30 is changed. To avoid any possibility of the driving member stalling on dead center, an adjustable auxiliary link |62 similar to the main driving link is arranged parallel thereto. The auxiliary link as shown herein is connected between a crank arm |63 keyed to the eccentric pin |51 and a crank arm |64 keyed to the stud |59. The two links are disposed in different vertical planes as shown in Figs. 10 and 11 to enable them to execute their respective movements without interfering.

The driven member |46 of the clutch is nor-'- mally held stationary in a position such as to maintain the turning frame upright as shown in Figs. 1 and 9. This is accomplished by means of a latch |65(Fig. 8) adapted to coact with either of two diametrically spaced latch lugs |66 During certain portions of the machine cycle and while the rotation of the member |46 is blocked by the latch, the driving clutch member |45/is moved out of engagement therewith by a cam |66 on the inner face of the gear |56. The cam engages a cam follower |69 (Fig. 10) on one end of a clutch shifting member |10 pivoted intermediate its ends as at |1|. The other end of the lever is operatively connected with the driving member of the clutch by a pin |12 engaging in a circumferential slot |13 in the hub |41 of the member.

In order ,to coordinate the operation of the turnover mechanism with the operations of the other elements of the machine, the cam |68 is shaped to reengage the clutch and suitable means is provided for withdrawing the latch |65 at a definite predetermined point in the ma chine cycle. The means for withdrawing the latch as herein shown comprises a. lug |14 (Fig. 8) on the outer face of the gear |56 having an inclined cam surface |15 adapted, in the rotation of the gear, to engage a pin |16 on the latch and swing the same out of engagement with the latch lug |66. The clutch members are engaged substantially at this instant bythe action of the cam |68, and the driven member |46 accordingly -rotates with the driving member.

In the present instance, the lug |14 is shaped so as to hold the latch in withdrawn position for an interval suicient to allow the latch lug |66 to pass, the latch then being released and returned by gravity to a position in which it is effectivel to engage the opposite latch lug |66 and thereby stop the driven clutch member upon completion of one-half of a revolution. As indicated above, this interruption takes place as the turning frame |25 moves into its upright position. The frame is thus maintained in this position until the gear |56 completes a full revolution, marking the end of a machine cycle. While the frame is upright, the feed mechanism operates to remove the work piece from the frame and to deposit a new work piece therein to be turned. Since the feed mechanism as well as the turning mechanism is actuated by com mon driving means. the various operations always take place in proper sequence and in proper timed relation. i

Feed mechanism important functions in this connection. First, it

feeds a continuous succession of work pieces to the umts and turnover mechanism. Secondly, it positions the work pieces accurately with respect to the forming dies of the units, thereby eifectually avoiding any possibility of damage to the machine or work. The feed mechanism is entirely automatic in operation, and as herein shown is driven by the main driving motor M and is mechanically interlockedv with the other elements of the machine so that its various operating steps are always properly timed with reference to the operation of the other elements of the machine organization.

The feed mechanism in its preferred form comprises a slide assembly consisting of a.A series of generally rectangular slides, four in the present instance, designated respectively by the reference characters |8I, |82, |83 and I (Figs. 14, and 16). These slides are rigidly connected together in spaced relation by rigid rods |88 to form a unitary structure adapted to operate with a reciprocatory or shuttle action. To this end, the various slides are dovetailed to a slideway |86 extending longitudinally of the machine base 21 immediately below the platform 28.

Functionally, the slide assembly may be considered as comprising four serially related sections with oneA of the slides included in each section. The first of these sections is concerned with the transfer of work pieces from the loadlng station No. 4 to the first operating station No. 1, the second section with the transfer of work pieces from the flrst operating station to the turning station No. 3, the third section with the transfer of the work pieces from the turning station to the second station No. 2, and the fourth section with the transfer of the' work pieces from the second operating station to the l unloading station No. 5. Such transfer is effected by intermittently sliding the work pieces along the platform 28 with suitable rest intervals or dwells betweensteps to enable the forming units and turning mechanism to perform their respective functions.

To impart the necessary movements to the work pieces, the entire slide assembly is adapted to be reciprocated in timed relation to the operations of the other elements of the machine. The means for effecting this reciprocation, as herein shown, comprises a disk |81 (Figs. 1, 2 and 11) fast on the cross shaft |55 which drives the turnover mechanism as above described. An eccentric pin |88 adjustably secured r in a T-slot in the face of the disk operates through the medium of a rigid link |89 to oscillate a lever |90 which is pivoted at its lower end on a bracket |9| carried on the end of the base 21. The other end of the lever is connected by a link |92 with a lug |93 (Figs. 15, 16 and 17) depending from the first slide |8| of the assembly.

As herein shown, a lost motion connection is provided between the link |89 and the lever |98 to afford a measure of adjustment for properly timing the movements of the slide. This connection, as herein shown, comprises a generally rectangular block |94 pivoted intermediate the ends of the lever and having an aperture for the reception of the link. Nuts |98 threaded to the link on opposite sides of the member complete the connection. With this arrangement, each revolution of the disk |81 is effective to move the slide assembly forwardly, that is, to the right as viewed in Figs. 1 and 12, and then to return it to its normal position. The amplitude of this movement may be readily adjusted by shifting the pin |88 in its slot. The timing, of course, is automatically coordinated with the other elements of the machine by reason of the common mechanical drive. In operation, the parts are so adjusted that the slide assembly advances while the dies of the respective forming units are withdrawn from engagement with the work. While the die's are operating on the work, the slide assembly executes its return movement to condition it for the next operating cycle.

The slide assembly is equipped with suitable means for advancing all of the work pieces including those in the forming units and the turning frame as well as those on the platform 28. The work pieces are allowed to rest while the slide assembly returns to its initial position so that inthe next advance each pice will be moved forward a further step until the progression through the machine is completed. The advancing means. includes various devices for engaging the work pieces, these devices differing somewhat in construction and mode of op-V eration according to the particular function to be performed. For convenience, the devices will be described in the order in which they act upon any one work piece in its passage through the machine.

Considering first the means for moving the.

either by means of suitable counterweightsy formed thereon or by a tension spring |98' and are rocked into operative position periodically by an actuating mechanism common to all of the devices of the slide assembly.

The pawls |98 and |98' when rocked to operative position project their tips through a slot extending longitudinally of the platform 28 for engagement with the work pieces resting on the platform. The pawls are spaced apart so that the foremost one is effective in one machine cycle to move the work piece from the loading station No. 4 tg a first rest position while the other -pawl operates in the next cycle to advance the work piece from the first rest position to a second rest position. In a third operating cycle the gripping arms |91 grasp the work piece and carry it from the second rest position to the operating station No. 1 and accurately position thel same on the work support of the forming unit at that station.

The gripping arms |91 are mounted on opposite sides of the slide Ill and, while they are arranged to follow the movements of the slide, they are preferably supported independently thereof for pivotal movement transversely of the platform 28 between active and inactive positions. As herein shown, each of the arms is formed with an integral hub |99 apertured for the reception of a square bar 200. These bars are disposed on opposite sides of the slide assembly and extend parallel thereto for substantially the entire length of the machine base. They constitute a part of the actuating mechanism for operating the pawls |98 and |98' above described.

The gripping arms are constrained to follow the reciprocating movements of the slide by a cross member secured to the slide and having arcuate end pieces engaging in circumferential grooves in the hubs |99. The arms are thus free to rock with the bars 200 which, in the present instance, are rotatably supported on the base 26 at a plurality of spaced points by stationary bearing brackets 202, the bars being turned to cylindrical form at such points. Each arm is equipped at its upper end with a Work engaging member 203 having an arcuate face conforming generally to the shape of the work piece. When the arms are rocked toward each other into active position, the members 203 engage and grip the work piece to carry it along with the slide. Due to the arcuate shape of these members, the work is accurately located on the table of the first forming unit. When the arms are rocked back to inactive position, the work piece is freed so that it is not carried back on the return movement of the slide assembly.

Coincident with the rocking of the gripping arms to active position, the pawls |96 and |96' are rocked about their pivots for engagement with the work pieces at the loading station and the adjacent rest position. For this purpose, the hubs |99 are formed inwardly with projecting fingers 204 adapted to engage one arm of a pivoted bell crank 205 having its other arm connected by a link 209 with the pawl |96. Actuation of the bell crank serves to rock the pawls |96 and |96'. Inthis way the pawls are rendered effective to engage the work pieces and pull them along the platform 26 in the forward movement of the slide assembly.

The operation of the bars 200 to condition the pawls and the gripping arms for operation is effected in the present instance by means of a cam 201 (Figs. 10, 15 and 16) fast on the inter'- mittently rotated shaft |49 which drives the turnover mechanism. The cam is arranged to cooperate with a follower in the form of a roller 209 carried on the lower end of a slide bar 209 dovetailed in a vertical slideway on the base 21. A cross bar 2I0 fast on the upper end of the slide bar is connected at each end by links 2|| with inwardly projecting arms 2|2 pinned to the respective bars 200. The cam 201 is shaped to release the slide bar to the action of a tension spring 2|3 as the slide assembly begins its forward movement so that the bars 200 are rocked in a direction to condition the pawls and the gripping arms for operation. Upon the return movement of the slide assembly the cam raises the slide bar 209 and thus rocks the bars back to their normal position. The gripping arms are accordingly opened and the pawls |96 and |99' are retracted below the platform so that the work pieces previously advanced are left in their advanced position.

The second section of the slide assembly which functions to remove the work pieces from the first forming unit and to transfer them to the turnover mechanism, includes the slide |92 which, like the slide |9 I, is equipped with various devices for cooperating with the work pieces. These devices include a pair of oppositely facing gripping arms, each comprising two upright standards 2|5 (Figs. 14, 15 and 16) having a common hub 2|6 slidable on the square bar 200 in the same manner as the hubs |99. The hubs 2|6 are anchored to the slide |92 for reciprocation therewith by a cross member having arcuate ends 2|1 engaging in circumferential grooves in the respective hubs.

Welded or otherwise rigidly secured to the upper ends of each pair of standards 2|5 is an elongated metal strip 2|9 having a projecting end portion bent. to conform generally Ito the shape of the work piece. These strips constitue work engaging devices adapted to grasp the Work piece when the gripping arms are closed together. The work piece is accordingly withdrawn from the first forming unit and moved along the platform 26 in theforward movement of the slide assembly. As the slide starts its return movement, the gripping arms are opened to release the work piece at a rest position preceding the turning station No. 3. In the next machine cycle, the work piece is picked up by n pawl 2|9 and shifted along the platform into the turning frame |25.

The pawl 2|9 is similar to the paw] |96' in construction and mode of operation. In the present instance, however, it is pivoted on the right end of the slide |92 in a position such that it may be projected through the platform 29 in the rear of the work piece to push the work piece into the turning frame |25 in the advance of the slide. As shown in Fig. 14, the pawl 2|9 is adapted to be rocked from an inactive to an active position by inwardly projecting fingers 220 on the hubs 2|6 which engage an integrally formed tail'piece 22| on the pawl as an incident to the movement of the gripping arms to active position.l

The next or third section of the slide ^ssem bly is equipped with devices for removing the work piece from the turning frame and for delivering it to the second unit. For this purpose, the slide |83 is provided at its left end with an extension 225 on which is pivoted a pawl 226 similar to the pawl |99. The pawl is normally held in an inactive position by a spring 221 (Fig. 16) and is adapted to be rocked to an active position at the same time the other pawls are operated by rocking of the bars 200 of the actu` ating mechanism. These bars impart their movement to a pair of members 229 which constitute the hubs of a pair of gripping arms 229 similar to the gripping arms |91 hereinbefore described. Each member 229 has an inwardly projecting finger 230 (Figs. 14 and 16) engageable with one arm of a bell crank 23| whose other arm is connected by a link 232 with the pawl 226. When the pawl is rocked by actuation of the bell crank, its free end is projected through a slot in the end wall |26 of the turning frame so that, in the advance of the slide, the pawl is effective to pull the work piece along onto the platform 26. The pawl is then restored to inactive position by its associated spring and the work piece remains stationary at a rest position while the slide executes its return movement.

In the next machine cycle the gripping arms 229 engage the work piece in the rest position at which it was left by the pawl 226 and carry it ahead one step to the second forming unit. Foi this purpose the gripping arms are provided at their upper ends with gripping members in the form of arcuately bent strips 233 (Fig. 14) adapted to snugly fit the work piece. The members thus serve to position the work piece accurately on the Work table of the second forming unit.

The strips 233 serve the additional purpose of discharging the completed Work piece from the second forming unit in the succeeding operating cycle. For this purpose, the right end of each bar is formed with an extension 234 with its end portion bent outwardly to form an abutment 235 for engaging the sides of a work piece. The abutments thus serve to push the work piece alongthe platform toward the unloading station No. in the advancing movement of the slide assembly.

Finally, the work piece at the last rest position is transferred to the unloading station by mechanism associated with the fourth section of the slide assembly. For this purpose, a pawl 23|, similar to the pawls |36' and 223, is pivoted on an extension of the slide |34 for engagement with the work piece in the rest position preceding the unloading station. The pawl 23B isnormally held in a retracted position by a spring 231 and is adapted to be rocked to activeposition at the proper point of the machine cycle by means of a link 233 connecting it with one arm of a bell crank 239 pivoted on the slide |34. The other arm of the bell crank is engaged by inwardly projecting fingers 240 on a pair of sleeve members 2li mounted on the rods 20D of the actuating mechanism in the same manner as the hubs of the gripping arms previously described. These members are reciprocable with the slide and, when rocked by the operation of the rods 200 project the tip of the pawl 236 above the plane of the platform 26. The'pawl accordingly engages the work piece on the platform and carries it to the unloading station in the next forward movement of the slide assembly.

It will be seen from the foregoing that the feed mechanism operates automatically to feed the work pieces intermittently from the loading station to the first forming unit, the turnover mechanism, the second forming unit in succession, and finally delivers the completed work piece at the unloading station. The operation of this mechanism is accurately timed so that each f eed step is executed in the portion of the machine cycle in which the forming dies of the units are inactive and in which the turning frame is in an upright position with its gripping jaws open. In this way, the work pieces progress through the machine in a continuous succession, entering as plain cylindrical shells and leaving as completely formed container parts so that a high rate of production can lbe maintained. Moreover, no manual handling of the work pieces is negessary, thus reducing the unit cost per piece to a minimum.

I claim as my invention:

l. In a machine for operating onsheet metal shells. in combination, a pair of cyclically operable formino.r units for shaping opposite ends of the shells, intermittently operating feed mechanism for transferring the shells step by step from one unit to the other. and a work turning mechanism interposed between the units for turning theshells to position them for presentation to said other unit by the feed mechanism, said turning mechanism comprising, a frame open at opposite sides for the passage of the shells in their transfer between the units, means included in said feed mechanism for depositing a shell in said frame in one operating cycle and for removing the shell therefrom in the succeeding operating cycle, means supporting said frame for rotation about a horizontal axis, power actuated means including a friction clutch for rotating said frame, a latch acting to hold the frame against rotation, and means for momentarily withdrawing said latch in timed relation to the operation of said feed mechanism to release the frame for `rotation between each operating cycle of the feed mechanism. said latch acting to stop the vframe assaoas.

upon completion of a half revolution with the shell therein positioned for presentation to the second forming unit.

2. In a machine for operating on sheet metal shells, in combination, a pair of cyclically operable forming umts for shaping opposite ends of the shells intermittently operating feed mechanism for transferring the shells step by step from one unit to the other, and a work turning mechanism interposed between the units for turning the shells to position them for presentation to said other unit by the feed mechanism, said turning mechanism comprising, a frame open at opposite sides for the passage oi' the shells in their transfer between the units, means included in said feed mechanism for depositing a shell in said frame in one operating cycle and for removing the shell therefrom in the succeeding operating cycle, means supporting said frame for rotation about a horizontal axis, power actuated means including a friction clutch for rotating said frame to turn the work piece therein, means operating in synchronism with the feed mechanism for engaging and .disengaging said clutch, a latch for accurately determining the stopping positions of the frame, and means for momentarily withdrawing said latch in timed relation to the operation of said clutch engaging and disengaging means.

3. In a machine for operating on sheet metal shells, in combination, a pair of cyclically operable forming units for shaping opposite ends of the shells, intermittently operating feed mechanism for transferring the shells step by step from one unit to the other, and a work turning mechanism interposed between the units for turning the shells to position them for presentation to said other unit by the feed mechanism, said turning mechanism comprising, a frame open at opposite sides for the passage of the shells in their transfer between the units, means included in said feed mechanism for depositing a shell in said frame in one operating cycle and for removing the shell therefrom in the succeeding operating cycle, means supporting said frame for rotation about a horizontal axis, means for rotating the frame through a half revolution between successive operating cycles of the feed mechanism to turn the shell deposited therein for presentation to the second forming unit, clamping means on said frame including a plurality of sets of clamping jaws adapted to be closed to grip the shell and hold it in place in the frame, and cam means coacting with said jaws in the rotation of the frame for opening and closing the jaws.

4. In a machine for operating on sheet metal shells, in combination, a pair of cyclically operable forming units for shaping opposite ends of the shells, intermittently operating feed mechanism for transferring the shells step by step from one unit to the other, and a work turning mechanism interposed between the units for turning the shells to position them for presentation to the second unit by the feed mechanism, said turning mechanism comprising, a frame open at opposite sides for the passage of the shells in their transfer between the units, means included in said feed mechanism for depositing a shell in said frame in one operating cycle and for removing the shell therefrom in the succeeding operating cycle, means supporting said frame for rotation about a horizontal axis, means for rotating the frame through a half revolution between successive operating cycles of the feed mechanism to turn the shell deposited therein for presentation to the second forming unit, clamping means on said frame including a plurality oi' sets of clamping Jaws adapted when closed to grip the shell and hold it in place in the frame, springs tending to close said jaws, and stationary cams coacting with said jaws to open the same when the frame is rotated to an upright pomtion to free the shell for discharge from the frame and to condition the frame for the reception of another shell.

5. The combination with a pair of forming umts for shaping the ends of sheet metal shells and feed mechanism for transferring the shells from one unit to the other, of mechanism for inverting the shells in their transfer comprising. a frame supported for rotation about a horizontal axis, said frame including spaced end members adapted alternately to receive and support a shell when the frame is in an upright position, clamping members disposed on opposite sides of said frame and rotatable therewith, and actuating means operative to shift said members to a withdrawn position when the tionofthe'frametoshitttheclampingmembers into engagement with the shell and thereby old the same in the frame during such rota- 6. The combination with a pair of forming units for shaping the ends of sheet metal shells and feed mechanism for transferring the shells from one unit to the other, of mechanism for inverting the shells in their transfer comprising. a frame supported for rotation about a.

horizontal axis. saidframe including spaced end members adapted alternately to receive and support a shell when the frame is in an upright position. clamping members disposed on opposite sides of said frame, and actuating means including spring means and cams operative in the rotation of the frame to shift the clamping members into and out of clamping engagement with the shell positioned in said frame, said cams being formed so as to retract the members when the frame is in an upright position and to release the members to theaction of said spring means whereby the members are caused to exert a clamping action when the frame is turned frame is in said upright position and thereby 25 from said upright position,

permit the loading of a shell in said frame, said actuating means being operative in the rota-1 cant. c. cmo'rru.l

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