Reinforced Can End

The present invention is directed to a method of and apparatus for forming a can end which is highly resistant to internal pressure when seamed to a product-containing can.

Typical of one conventional method of manufacturing socalled pressure resistant can ends is that disclosed in U.S. Pat. No. 4,109,599 in the name of Freddy R. Schultz issued Aug. 29, 1978 and assigned to Aluminum Company of America. In accordance with one method disclosed in this patent, a sheet metal blank is positioned between a pair of dies which are moved to first shear an edge of the blank after which a punch descends to form the now circular blank about an annular ring into an end shell having a peripheral flange, a frusto-conical wall, a radius and an end panel. The end shell is then removed from the first set of dies and inserted into a second set of dies in which the peripheral flange is curled into a downward peripheral flange suitable for double seaming operations.

The end shell is then placed between another pair of dies which when moved toward each other form the radius into a reinforcing channel or annular groove adjoining the simultaneously formed domed central panel. The so-called reinforcing channel or annular groove increases the pressure resistance of the can end because of the reinforcement created by the increased depth of the annular groove with respect to the central panel and the tight radius of curvature of the latter. This type of reinforcement is said to make it possible to reduce the gauge thickness of a can end about 10 to 20 percent while maintaining pressure resistance capabilities of a conventional can end. However, the patent also acknowledges two dichotomous principles which are at work in the manufacture of a pressure resistant can end of this type, namely, the deepening of the annular groove and the tightening of its radius acts to increase pressure resistance, but the drawing operation has the effect of thinning the metal which acts to decrease pressure resistance.

While the objectives of conventional methods and apparatus are acknowledged herein, it is also important to recognize that such known methods also include other disadvantages, particularly when a blank or end shell must be transferred between a first set of dies to a second set of dies which virtually necessarily create alignment and/or tolerance problems, not to mention the simple fact that the transfer itself adds time to an overall forming operation simply becuase of the time involved in the transfer per se. Furthermore, it is not uncommon to lacquer the blanks prior to any forming operation, and forming in different dies and/or transferring between dies increases the tendency of the lacquer or enamel to crack or otherwise expose the metal to the eventual product packaged within a can to which the end has been seamed. The latter can result in undesired product deterioration.

Another disadvantage of forming a pressure resistant can end in a series of different dies between which the blank must be transferred is simply the inability to maintain acceptable tolerances, particularly relative to overall concentricity, flange height and hook length. These three factors collectively establish to a large measure the eventual uniformity of successful double seaming which, once again, can be critical to product shelf life and/or longevity.

In keeping with the foregoing, it is a primary object of this invention to provide a novel method of and apparatus for forming a reinforced pressure resistant can end within a single set of dies and in the absence of any type of transfer or movement of the metallic blank once a forming operation has begun by utilizing the single set of dies to selectively localize an increased thickness of metal at a juncture at an outer frustoconical peripheral wall and a reinforcing countersink radius of the can end, while at the same time localizing a thinner flexible wall portion between a panel radius and a circular central panel of the can end to thereby provide increased reinforcement in the absence of metal exposure, flexibility to transfer or absorb forces, and optimum tolerance including flange height, hook length and concentricity.

A further object of this invention is to provide a novel apparatus and method as latter defined including a draw punch and a reform pad carried by a first support movable relative to an indent ring and a lift ring carried by a second support, means for fluidically, pneumatically and/or spring clamping a central panel of a metallic blank between the reform pad and the indent ring, the draw punch being part of first force exerting means for exerting first forces against a peripheral edge portion of the blank in a first direction to deform the peripheral edge portion out of the plane of the central panel and shape the blank into a generally flanged cup-shaped configuration defined by the central panel, a radius, a frusto-conical wall and an annular flange, and the lift ring defining part of second force exerting means for exerting second forces greater than the first forces against the flange in a second direction opposite the first direction while the center panel is still gripped between the reform pad and the indent ring to deform a part of the metal of the radius in the absence of constraint out of the plane of the central panel and to a side thereof opposite the annular flange to thereby form the reinforcing countersink radius of localized increased thickness as set forth in the previous object.

Still another object of this invention is to provide a novel apparatus as set forth immediately above wherein at least one of the reform pad and the draw punch form an annular chamber into which is formed the radius part during the operation of the second force exerting means to form the reinforcing countersink radius.

A further object of this invention is to provide a novel apparatus as aforesaid wherein the draw punch includes an inner frusto-conical surface in generally opposed relationship to an annular angled surface of the reform pad between the peripheral surface and a terminal end face of the latter which individually or collectively form an annular chamber into which is formed the radius part during the operation of the second force exerting means to form the reinforcing countersink radius.

A further object of this invention is to provide a novel apparatus as heretofore described wherein the indent ring includes a peripheral surface and an axial end face, and means in the form of an annular outwardly opening groove between the peripheral surface and the terminal end face of the indent ring for effecting unrestrained stretching of the material forming the first-mentioned radius during the movement of the draw punch in the first direction.

Another object of this invention is to provide a novel apparatus as aforesaid including respective convex and concave terminal end faces of the draw punch and lift ring for guiding metal therethrough during the movement of the draw punch in the first direction.

Still another object of this invention is to provide a novel apparatus as heretofore described wherein the force exerting means for moving the reform pad and the draw punch is a source of fluidic pressure, and the force of the latter is utilized during movement of the draw punch in the first direction to load a mechanical spring which in turn applies the force in the second direction through the lift ring upon return movement of the draw punch opposite its first direction of travel.

With the above and other objects in view that will hereinafter appear, the nature of the invention will be more clearly understood by reference to the following detailed description, the appended claims and the several views illustrated in the accompanying drawings.

FIG. 1 is a generally axial sectional view with some parts shown in elevation of a press including a punch and die, and illustrates as part of the punch a fluidically (preferably pneumatically) operated reform pad, and as part of the die an indent ring and a mechanically operated lift ring with the tooling shown at the completion of the first or forming operation in which a blank is formed to a generally cup-like configuration defined by a circular center panel, a radius, a frusto-conical wall and an annular flange.

FIG. 2 is an enlarged fragmentary schematic crosssectional view of the draw punch, reform pad, indent ring and lift ring of FIG. 1, and illustrates the latter in association with the planar metallic blank just prior to the blank being cut between a cutting punch and a cut edge of the die.

FIG. 3 is an enlarged fragmentary schematic cross-sectional view of the tooling of FIG. 2, and illustrates a further sequence in the operation of the punch during which the blank is cut between the cutting punch and the die cut edge.

FIG. 4 is an enlarged fragmentary cross-sectional view of the tooling of FIG. 3, and illustrates a generally convex axial end face of the draw punch applying downwardly directed forces to a peripheral edge portion of the blank.

FIG. 5 is an enlarged fragmentary schematic cross-sectional view of the tooling of FIG. 4, and illustrates the position at which a central portion of the metallic blank is clamped between axial end faces of the reform pad and the indent ring.

FIG. 6 is an enlarged fragmentary schematic cross-sectional view of the tooling of FIG. 5, and illustrates the simultaneous downward movement of the draw punch and the lift ring at which time a peripheral edge of the metallic blank is guided between respective convex and concave opposing surfaces of the draw punch and lift ring.

FIG. 7 is an enlarged fragmentary schematic crosssectional view of the tooling of FIG. 6, and illustrates the draw punch at the bottom of its stroke and a portion of the metallic blank bridging an annular outwardly opening groove of the indent ring.

FIG. 8 is an enlarged fragmentary schematic cross-sectional view of the tooling of FIG. 7, and illustrates two phantom outlines and a single solid outline position of the can end during upward movement of the draw punch and lift ring at which time the flange is gripped between the lift ring and the draw punch and the previously formed radius of the can end is progressively formed into a reinforcing countersink radius.

FIG. 9 is an enlarged fragmentary schematic cross-sectional view of the tooling of FIG. 8, and illustrates the position of the tooling at which the reinforcing countersink radius has been fully formed.

FIG. 10 is an enlarged fragmentary schematic cross-sectional view of the tooling of FIG. 9, and illustrates in solid outline the release of the gripping forces by the retraction of the reform pad and in phantom outline the position of the lift ring prior to final ejection of the fully formed can end.

FIG. 11 is an enlarged fragmentary schematic cross-sectional view of the tooling of FIG. 10, and illustrates the punch and die fully opened and the lift ring at a position permitting ejection of the completed can end.

FIG. 12 is a fragmentary cross-sectional view of a reinforced pressure resistant can end constructed in accordance with this invention, and illustrates in conjunction with a graph a variety of different wall thicknesses thereof pertinent to the present invention.

FIG. 13 is an enlarged fragmentary schematic cross-sectional view of a modified form of tooling of the invention at the same position as that illustrated in FIG. 7, and illustrates a modification of the reform pad in which a peripheral surface and a terminal end face are bridged through a radius, a cylindrical surface and an angled surface.

FIG. 14 is an enlarged fragmentary schematic cross-sectional view of the tooling of FIG. 13, and illustrates the manner in which the radius formed by the tooling of FIG. 13 is reformed by the upward movement of the lift ring and draw punch into an annular area set off in part by the reform pad and angled and cylindrical surfaces.

FIG. 15 is a generally fragmentary axial sectional view of another press including another punch and die, and illustrates the tooling thereof in a position forming the configuration of the can end or shell of FIG. 18.

FIG. 16 is an enlarged fragmentary schematic cross-sectional view of a draw punch, reform pad, indent ring and lift ring of FIG. 15, and illustrates the latter in association with a metallic blank which has been cut between a cutting punch and a cut edge of the die.

FIG. 17 is an enlarged fragmentary cross-sectional view of the tooling of FIG. 16, and illustrates a further sequence in the operation of the punch during which the blank is formed into a shallow cup.

FIG. 18 is an enlarged fragmentary schematic cross-sectional view of the tooling of FIG. 17, and illustrates the tooling at the bottom of its stroke after the shallow cup of FIG. 7 has been reformed to an oppositely opening flanged cup.

FIG. 19 is an enlarged fragmentary schematic cross-sectional view of the tooling of FIG. 18, and illustrates the position of the tooling at which a reinforcing countersink radius has been fully formed.

The invention will be best understood by first referring to FIG. 1 of the drawings which illustrates a portion of a conventional multi-die double action press which is generally designated by the reference numeral 10. The press 10 includes a punch 11 and a die or bolster block assembly 12. The bolster block assembly 12 is a stationary portion of the frame (not shown) of the press 10 while the punch 11 is reciprocated in a conventional manner, as by eccentrics or cams between a fully closed or bottom dead center position (FIG. 1) and a fully opened position (FIG. 11).

The die or bolster block assembly 12 includes a generally cylindrical upwardly opening recess 13 housing a draw die base 14 which is secured to the assembly 12 by a plurality of hex screws 15 received in a plurality of counter-bored bores 16 and threaded in threaded bores 17 of the assembly 12. There are six such bores 16 and hex screws 15 equally spaced about the draw die base 14 and six similarly spaced threaded bores 17 formed in the assembly 12 for securely attaching the draw die base 14 to the assembly 12 within the recess 13. A bottom wall (unnumbered) of the draw die base includes an axial bore 18 in which is reciprocally moved an upper portion 20 of a knock-out lift ring rod 21.

The bottom wall (unnumbered) of the draw die base 14 also includes four counterbores 22 of which only one is illustrated in FIG. 1, and a hex screw 23 is received in each counterbore 22 and is threaded in a threaded bore 24 of an indent ring 25 seated within a shallow upwardly opening circular recess 29 of the draw die base 14. The indent ring 25 and a reform pad or draw punch gripper pad 35 of the punch 11, which will be described more fully hereinafter, cooperate to collectively define therebetween means for gripping a central panel CP (FIG. 2) of a metallic uniplanar blank B having at outer peripheral edge or peripheral edge portion PE. Essentially, the central portion or center panel CP of the blank B is gripped between a relatively flat terminal circular end face 26 of the indent ring 25 and a similar flat circular terminal end face 36 of the reform pad 35 (FIG. 2).

The indent ring 25 additionally includes a generally cylindrical or peripheral outer surface 27 and the surfaces 26, 27 are bridged by means 40 (FIG. 2) for creating unrestrained tensioning of the blank B during the formation of a somewhat angulated radius R (FIG. 7) defined by a pair of shoulders or radius portions Rb and Rc spanned by an annular generally flat angled wall portion Rt (FIG. 7). The tensioning means 40 includes a pair of annular shoulders 41, 42 between which is an outwardly opening annular groove 43. The radii of the shoulders 41, 42 are respectively 0.030" and 0.065", while the radius of the annular groove 43 is 0.010". The distance of the axis for the radius of the shoulder 42 from the axial terminal end face 26 of the indent ring 25 is 0.015" and the distance of the axis of the radius 41 from the axis of the indent ring 25 is approximately 0.976"-0.977".

A lower portion (unnumbered) of the indent ring 25 is traversed by a diametric slot 28 which transforms a lower end portion of the indent ring 25 into a pair of legs 30, 31. The diametric slot 28 accommodates reciprocal movement of a hub 61 forming part of a diametric spider (not shown) of a lift ring 60 which will be described more fully hereinafter. However, each of the legs 30, 31 of the indent ring 25 includes a vertical slot 32, 33, respectively, functioning as a vertical limit for reciprocal motion of the lift ring 60.

The draw die base 14 also includes six equally circumferentially spaced bores 34 and six equally circumferentially spaced blind bores 45. Each of the bores 34 receives a reduced end portion 46 of a lift pin 47 while each of the blind bores 45 houses a compression spring 48.

The compression springs 48 bear against the undersurface (unnumbered) of a conventional draw die 70 which cooperates in a conventional manner with a cutting punch 75 of the punch 11 and a cut edge or annular blanking die 76 carried by a die holder or die assembly 78 secured in a conventional manner to the bolster block assembly 12 by a plurality of hex socket screws and nuts 81. Upon the descent of the cutting punch 75, which will be described more fully hereinafter, upon conventional downward motion imparted to the punch 11, the cooperative interaction of the draw die 70, the cutting punch 75 and the cut edge 76 results in the peripheral edge PE of the blank B being blanked or trimmed to a circular configuration as defined by a cut edge CE with, of course, waste material W being eventually discarded during normal operations of the press 10.

The lift ring 60 includes an outer peripheral cylindrical surface 61 and an inner peripheral cylindrical surface 62 which has a groove (unnumbered). The lift ring or annular forming member 60 includes a terminal peripheral end face 64 (FIG. 2) bridging the peripheral surfaces 61 and 62. The terminal peripheral end face 64 includes a shallow upwardly opening convex recess 65, and inboard annular axial face or surface 66 and an outboard annular axial face or surface 67. The surface 66 is radially longer than and slightly above (0.030") the surface 67. The collective surface 65 through 67 provide guidance to inward metal flow of the peripheral edge portion PE of the blank B during the downward or forming stroke of the operation and a clamping or gripping action during the upward or reforming stroke, as will be described more fully hereinafter. Downward movement is imparted to the lift ring or annular forming member 60 by the descent of the cutting punch 75. During such downward movement, the lift pins 47 are also moved downwardly moving a lift pin disc 91 out of contact with a bumper retainer plate 92 and further compressing a previously preloaded spring 93 to load the spring 93 to approximately 2,000 lbs. force. The same downward movement of the lift pins 47 and the lift pin disc 91 is transferred to a lift pin spacer 94 which compresses a compression spring 95. The springs 93, 95 operate in a conventional manner, but the same will be described more completely hereinafter.

The bumper retaining plate 92 is secured to the bolster block assembly 12 by a plurality of hex socket screws 96 received in counterbores 97 of the bumper retainer plate 92 and threaded in threaded bores 98 of the bolster block assembly 12. The bolster block assembly 12 also includes a threaded bore 101 into which is threaded an enlarged threaded portion 102 of a lift ring knock-out bumper pad 103 having an axial bore 104 within which reciprocates the knock-out lift ring rod 21.

The punch 11 includes a conventional blank punch slide assembly 110 which has mounted thereto a conventional cutting punch holder 111 by means of a blank ram attachment 112 (only one illustraated) and an associated set screw 113. The cutting punch 75 is secured in a conventional manner, including a cutting punch holder clamping nut 114, to a lower end portion of the cutting punch holder 111.

An inner piston or draw punch rod 120 is mounted for reciprocal movement within the cutting punch holder 111 and includes a bore 121, a counterbore 122 and an internally threaded end portion 123. The internally threaded end portion 123 is threaded to a threaded portion 82 of a stem 83 of a draw punch 80. The draw punch 80 includes an axial bore 84 and a counterbore 85 defined by a peripheral skirt or annular forming member 86 of the draw punch 80. The counter bore 85 is defined in part by an inner cylindrical peripheral surface 87 which is in intimate sliding contact with a like outer peripheral cylindrical surface 37 of the reform pad 35. The cylindrical surface 37 and the axial end face 36 of the reform pad 35 are bridged by means 38 in the form of an angled annular surface setting-off an obtuse angle of approximately 120.degree. with the terminal end face 36. A like obtuse angle is set-off between the peripheral surface 37 and the angled annular surface 38. The means 38 functions to prevent a coating C, such as lacquer or enamel, from cracking or being wiped off and, thus, prevents metal exposure of the eventually formed inner surface of the blank B during the forming and reforming operation. The same means 38 or angled annular surface 38 cooperatively functions with a frusto-conical surface 88 of the draw punch 80 to define therewith and therebetween means for forming an annular downwardly opening and diverging chamber 130 into which the formed radius R (FIG. 7) can be freely reformed without guidance or restraint (see FIGS. 8 and 9) during the upward stroke or movement of the lift ring or annular forming member 60 to eventually form an annular reinforcing countersink radius Rr, again as will be described more fully hereinafter.

The frusto-conical surface 88 merges with a pair of convex radii 136, 137 bridged by a generally flat annular surface 138. The curvature of the radii/surfaces 136 through 138 corresponds to the curvature of the surface 65 of the groove 64 which together therewith provides added guidance to the inward metal flow during the downward or forming stroke when the blank B is formed to its final formed (though not reformed) configuration (FIG. 7).

A hex screw 140 is threaded into a threaded bore (unnumbered) of a draw punch shaft or piston 141 having a blind bore 142, a plurality of seals 143 and a peripheral flange 144 which can bottom against an annular axial end face 145 of the draw punch stem 83. The counterbore or chamber 122 is connected through the port 121 to a supply of fluidic pressure, such as a nitrogen cylinder and an associated regulator assembly or an air amplifier with appropriate valving and controls, which is simply designated by the headed arrow P1. The inner piston or draw punch rod 120 is likewise urged downwardly by fluidic pressure suitably regulated from the same or a different source as the pressure source P1, and the pressure applied to the draw punch rod is generally designated by the reference character P2 associated with the arrow in FIG. 1, although pressures P1, P2 can be equal. The pressure P1 can be, for example, as low as 600 psi and at 1000 psi, the pressure on the piston 141 is approximately 1060 psi. The pressure is preferably higher, particularly the pressure P2 exerted in a downward direction upon the draw punch rod 120 because the latter pressure is transferred during the downward or forming stroke from the rod 120 through the draw punch 80, the lift ring 60 and the lift pins 47 to unseat the lift pin disc 91 and the lift pin saver 94 and, therefore, load the springs 93, 95 which upon the reform, return or upward stroke of the rod 120 provide the mechanical force to lift the rods 47 and the lift ring 60 upwardly to reform the blank B from the position shown in FIG. 7 to that shown in FIG. 9 under a second force greater than the first pressure or force P2.

The operation of the press 10 will now be described with particular reference to FIGS. 2 through 11 of the drawings and, of course, it will be assumed that the blank punch slide assembly 110 of the punch 11 has been retracted upwardly to its open position (FIG. 11) with the blank B positioned as shown in FIG. 2, but, of course, being supported upon the flat annular face 66 of the lift ring 60. The means for providing the pressures P1 and/or P2 have been activated and, therefore, the flange 144 of the draw punch piston 141 is bottomed against the annular face 145 (FIG. 1) of the stem 83 of the draw punch 80. This positions the axial terminal face 36 of the reform pad 35 slightly above the flat annular surface 138 of the draw punch 80 (FIG. 2). Upper end faces (unnumbered) of the lift pin disc 91 and the lift pin spacer 94 are in abutment with an undersurface (unnumbered) of the bumper retainer plate 92 (FIG. 1).

Conventional eccentric or cam means lower the cutting punch holder 111 which causes the cutting punch 75 to contact (FIG. 2) the peripheral edge portion PE of the blank B and then sever the same (FIG. 3) forming the cut edge CE. At this position (FIG. 3), the peripheral edge portion PE of the blank B is lightly gripped between the cutting punch 75 and the opposing draw die 70 which slightly compresses the springs 48.

The pressure P2 acting downwardly upon the rod 120 continues to move the draw punch 80 in a downward direction causing initial deformation of the peripheral edge PE of the blank B (FIG. 4) without, at this time, the center panel CP being clamped between the faces 26, 36 of the respective indent ring and reform pad 25, 35. The peripheral edge PE is, however, progressively withdrawn inwardly from between the cutting punch 75 and the draw die 70 (compare FIG. 3 and FIG. 4).

The continued downward fluidic pressure P2 upon the rod 120 progressively moves the draw punch 80 downwardly (FIG. 5) until a point is reached at which the surface 36 of the reform pad 35 contacts the center panel CP of the blank B and clamps the same in conjunction with the opposing surface 26 of the indent ring 25. Thus, from this point (FIG. 5) forward during the continuation of the first or forming operation, the central panel CP remains clamped between the reform pad 35 and the indent ring 25.

Eventually, the downward descent of the draw punch 80 reaches a position at which the force P2 is not only transferred to form the peripheral edge PE of the blank B, but also to act indirectly therethrough to force the lift ring 60 downwardly (FIG. 6). During this action, the groove 64 and the surfaces 136 through 138 function to guide the inward metal flow as the blank B is progressively formed toward the eventual angulated radius R (FIG. 7). From the position of the lift ring 60 shown in FIG. 6 to that shown in FIG. 7, the downward movement of the draw punch 80 not only forces the lift ring 60 downwardly but this force or pressure P2 is transferred from the lift ring 60 through the lift pins 47 (FIG. 1) to the lift pin disc 91 and from the latter to the lift pin disc 94, thus loading both springs 93 and 95 to obtain upon the return or reform stroke of the press 10 a mechanical force approximating 2000 lbs. Thus, in addition to loading the springs 93, 95, the draw punch 80 also forms the final configuration of the flange 160 (see FIG. 12) but also forms the angulated radius R (FIG. 7) by stretching or tensioning the central portion Rt between the radius Rb and Rc. As will appear more fully hereinafter, the tensioning in the area Rt is believed to provide the marked increase in flexibility of an annular wall portion 152 of a completely formed can end 150 (FIG. 12) while the work hardening of the radius portion Rb coupled with its eventual reforming into the reinforced countersink radius Rr (FIG. 9) results in a "kink" or an increased thickness portion beyond "nominal", thickness at a portion of a countersink radius 155 between the lines of demarcation L6 and L7 of FIG. 12. Thus, from the position generally shown in FIG. 2 to that shown in FIG. 7, the draw punch 80 moved forcefully downwardly by the pressure P2 is effective for exerting forces sufficient to transform the peripheral edge portion PE of the blank B to the configuration of the formed, though not reformed, blank B of FIG. 7.

The reform or return stroke is initiated without any change in position of the blank punch slide assembly 110 and the cutting punch holder 111 and without in anyway reducing the clamping action against the center panel CP of the blank B between the gripping means 25, 35, i.e., the indent ring 25 and the reform pad 35. As the spring or springs 93, 95 urge the lift pins 47 upwardly against regulated decrease in the pressure P1 and/or P2 (FIG. 8), a flange 160 of the can end 150 is clamped or gripped between the surfaces 36 through 138 of the draw punch 80 and the surface 65 of the lift ring 60 with a progressive upward movement causing the angulated radius R (FIG. 7) to be deformed progressively out of the plane of the center panel CP of the blank B, as is shown in an initial stage in solid lines in FIG. 8. By comparing FIGS. 7 and 8 it can be seen that the radius portion Rc of FIG. 7 is generally reversed progressively from the position shown in FIG. 7 to that which it eventually reaches in FIG. 9 while at the same time the radius portion Rt is deformed progressively and without restraint, guidance or confinement into the annular channel or chamber 130 until the reinforcing countersink radius (Rr of FIG. 7 or 155 of FIG. 12) is fully formed. However, during the movement of the lift ring 60 and the draw punch 80 as aforesaid between the position shown in FIGS. 8 and 9, the earlier tension portion Rt of the radius R tends to deform or bend more readily as opposed to the work hardened portion Rb which characteristically creates a relatively tight radius Rr and the reinforced thickened "kink" between the lines of demarcation L6, L7 (FIG. 12).

Upon completion of the return or reforming stroke (FIG. 9), the pressure P1 on the draw punch shaft 141 (FIG. 1) is released or lessened and unclamping of the blank B occurs as the lift ring 60 continues its upward spring biased return under the mechanical force of the springs 93 and/or 95 until the phantom outline position of FIG. 10 is reached by the lift ring 60. Thereafter, the cutting punch holder 111 is mechanically retracted to the final position shown in FIG. 11 at which point the can end can be conventionally ejected.

Reference is now made to FIG. 12 of the drawings which best illustrates the resultant reinforced pressure resistant can end generally designated by the reference numeral 150.

The can end 150 includes a generally circular center panel or panel portion 151, a flexible annular wall portion 152, a panel radius 153, a frusto-conical peripherally inner wall 154, an annular exteriorly upwardly opening reinforcing countersink radius or channel 155, a frusto-conical peripherally outer wall 156, a radius 157, an annular end wall 158 and a peripheral edge 159 with the latter three portions collectively defining a flange 160 which is utilized in a conventional manner to double seam the can end 150 to the can body.

A graph G has been associated with the can end 150 of FIG. 12 to graphically illustrate the variation in cross-sectional wall thickness of the can end 150 from the central panel 151 to the frusto-conical peripherally outer wall 156. The graph G depicts the percentage of change in gauge or thickness along the ordinate and the abscissa depicts the change in gauge using the countersink radius 155 as the "0" point. The end is a 206 diameter "Carson" shell.

The gauge or cross-sectional wall thickness of the circular central panel 151 of the can end 150 is generally designated by the reference character Tn and on the graph G, this "nominal" thickness is represented by the horizontal dash line at "100". A line L1 represents the point of demarcation between the circular central panel 151 and the flexible annular wall portion 152, although it must be recognized that the position of the line L1 is not exact but is amply adequate to understand the present invention and the variations in the gauge or wall thicknesses throughout the can end 150, as will be come clear hereinafter. A line 11 has been used to reference the line of demarcation L1 with a point P1 on the graph G to indicate that to the right of the point P1, the "nominal" or unformed thickness of the center panel 151 corresponds to the "nominal" thickness of the blank B prior to initiating the forming operation. A line of demarcation L2 indicates the outboard extent of the flexible annular wall portion 152 and the line 12 therefrom to the point P2 indicates on the graph G a progressive thinning of the cross-sectional thickness of the flexible annular wall portion 152 from point P1 to point P2.

Another line of demarcation L3 sets off with the line L2 the extent of the panel radius 153 with a center line of the panel radius 153 being designated by the line C3. A line 13 connects the line L3 with a point P3 on the graph G, while another line 14 connects the line C3 with a point P4 of the graph G. The configuration of the curve passing between the points P2 and P3 indicates the wall thickness or gauge of the panel radius 153 essentially decreases from the line L2 and then increases at the area of the line C3 (Point P4) after which the crosssectional thickness again abruptly decreases and increases toward the point P3 and the line L3. The increased thickness generally in the area of the point P4 as compared to the progressive thinning of the annular wall portion 152 between the points P1 and P2 renders the annular wall portion 152 somewhat more flexible than both the center panel 151 and the panel radius 153 thereby permitting the annular wall portion 152 to flex under abuse, excess internal pressure, or the like, without failure.

Another line of demarcation L5 sets-off the frusto-conical peripherally inner wall 154 with the line L3. A line 15 from the line of demarcation L5 to a point P5 establishes the progressive decrease in wall thickness or gauge of the frusto-conical peripherally inner wall 154 from a point just beyond point P3 toward, but not quite to, to point P5.

The reinforcing countersink radius 155 is set-off between the line of demarcation L5 and another line of demarcation L6 between the two of which is a line C4 representing the radius of the countersink 155 and a line C5 indicating the bottom of the countersink 155. Another line of demarcation L7 is illustrated radially inward of the line of demarcation L6. Lines 16 and 17 connect the respective lines L6, L7 with points P6 and P7, respectively, of the graph G. Similarly, lines 18 and 19 connect the lines C4, C5, respectively, with points P8 and P9, respectively, of the graph G. The significance of the latter described structure is the significant increase from the "nominal" thickness between the points P6 and P7 which results in a thickening, compression, or bulging of the material between the lines of demarcation L6 and L7 and slightly radially outwardly beyond the line L6. The material in this area is visibly "kinked" exteriorly, and the exteriorly surface (unnumbered) of the portion of the countersink radius 155 and the frusto-conical wall 156 generally between the lines of demarcation L6 and L7 bulges outwardly beyond an outer surface 161 of the frusto-conical wall 156 which, of course, from the graph G is seen to progressively thin beyond point P6. The portion of the countersink radius between the lines of demarcation L6 and L7 corresponds generally to the radius Rf (FIG. 7) which is believed to be slightly work hardened during the initial forming operation, and this attendant loss of flexibility permits not only the unrestrained reforming (FIGS. 8 and 9) of the radius R to the configuration of the radius Rr in FIG. 9, but also the accumulation of metal in this same area (between the lines L6 and L7). The increased thickness in the countersink radius 155 at generally the radially outboard portion Rf (FIG. 12) of the can end 150 results in desired end reinforcement whereas the progressively thinner annular wall portion 152 results in desired end flexibility.

The can end 150 of FIG. 12 is, of course, constructed in the absence of metal exposure, as was heretofore noted, and the coating C remains essentially homogeneous and uninterrupted on the inner surface (unnumbered) of the can end. This is, of course, achieved with flange height (F), flange length (Lf) and concentricity (D) (FIG. 12) well within design tolerances.

Variations in the present method and apparatus will become apparent to those skilled in the art and such are considered to be within the scope of this disclosure including various modifications in or reversal of the various elements heretofore described. As an example, reference is made to FIGS. 13 and 14 which have been provided with like though primed reference numerals to identify structure identical to that illustrated respectively in FIGS. 7 and 9. In this case, the reform pad 35' has been modified by altering the overall configuration of adjoining surfaces 170 through 172 bridging the surfaces 36' and 37'. The surface 170 is of an angular configuration, similar to the surface 38 of the reform pad 35. However, the surface 172 is radially outboard of the corresponding radius 41' of the indent ring 25' and as a result the annular downwardly opening chamber 130' abruptly narrows at the cylindrical surface 171'. Thus, upon the return stroke or reform stroke upwardly of the lift ring 60', the radius R'r is "tighter", as is most readily apparent by simply comparing the radius Rr of FIGS. 9 through 10 with the radius R'r of FIG. 14. This results in a more rigid reinforcement of the countersink radius 155' than that provided by the reinforcing radius 155.

It is also readily apparent and within the scope of the present invention to essentially reverse or flip-flop the position of the reform pad 35 and draw punch 80 relative to the indent ring 25 and lift ring 60. In other words, it is clearly within the scope of this invention to have the indent ring 25 and lift ring 60 carried by the draw punch rod 120 and the reform pad 35 and draw punch 80 carried by the die or bolster block assembly 12.

A modification as aforesaid is illustrated in FIG. 15 of the drawing in which a press or tool assembly 210 is illustrated and comprises a punch or upper tool 211 and a die or lower tool 212. The upper tool 211 includes a cutting punch or sleeve 275, a holding ring or lift ring 260 within the cutting punch or sleeve 275 and a first draw punch 225. The components 225, 260 and 275 of the tool assembly 210 will be seen to correspond to the like components 25, 60 and 75 of the press 10. The lower tool 212 includes a blanking die or cutting ring 276, a first draw die 280 surrounded by an annular ring 220 in alignment with the cutting sleeve 275 and a second or "redraw" punch or reform pad 235 within the first draw die 280. The elements 235 and 280 correspond to the elements 35 and 80 of the press 10.

The upper tool 211 is mounted in a top plate 262 of a pillar die set comprising at the top plate 262 a plurality of conventional guide pillars (not shown) and a bottom plate 252 which can reciprocate relative to the top plate 252 and during such movement is guided by the latter-noted pillars. The tool or die assembly 210 of FIG. 15 is mounted in a "C" framed power press on a press plate 265 so that the top plate 262 is urged to reciprocate by the press ram (not shown) and the bottom plate 252 remains stationary on the press plate 265.

In use, a sheet of metal is placed between the upper tool 211 and the lower tool 212 and the tools are closed by movement of the press ram acting on the top plate 262 so that the cutting sleeve 275 cooperates with the cutting ring 276 to cut out a circular blank B" (FIG. 16) with the waste material being designated by the reference character W". As in the case of the blank B of FIGS. 2 through 11 of the drawings, the blank B" includes a center panel CP" and a peripheral edge PE".

After the cut out of the circular blank B", continual downward travel of the press ram urges the top plate 262 of the die assembly to push the sleeve 275 downwardly and through the peripheral edge PE" of the blank B" also pushes the annular ring 220 downwardly toward the position shown in FIG. 17. During the motion of the sleeve 275 and the annular ring 220 from the position shown in FIG. 16 to the position shown in FIG. 17, the peripheral edge PE' is formed over a convex surface 238 of the first draw die 280 with the sleeve 275 and the annular ring 220 functioning as a sprung blank holder from between which the peripheral edge PE" is eventually withdrawn into the sandwiched relationship between the sleeve 275 and the die 280 to shape the peripheral edge PE" into a shallow downwardly opening shallow shell SS (FIG. 17) defined by a substantial cylindrical wall CW and the central panel CP". The downward motion of the first drawing operation compresses a spring (not shown but corresponding to the spring 93 of FIG. 1) through push rods 240 (FIG. 15) so that the blank holding or clamping pressure between the sleeve 275 and the annular ring 220 is controlled as metal is drawn over the face 238 of the draw die 280 to form the inverted shallow shell or cup SS of FIG. 17. The continued drawing moves the punch 225 and the second punch 235 downwardly toward the position shown in FIG. 18 in which the blank B" corresponds generally to the blank B of FIG. 7, except, of course, the now cup-shaped blanks B, B" open in opposite directions (downwardly in FIG. 7 and upwardly in FIG. 18). The central panel CP" is, of course, clamped between the punch 225 and the punch 235 during the movement thereof from the position shown in FIG. 17 to the position shown in FIG. 18, and during this downward movement the peripheral edge PE" is drawn over the convex edge 238 of the die 280, as earlier noted. It is after this formation of the peripheral edge PE" toward the end of the stroke shown in FIG. 18 that the holding ring 260 moves downwardly and now clamps the now formed cover hook or flange 260' (FIG. 18) between the surfaces 238, 265 of the respective tooling elements 280, 260. The holding ring 260 is residentally urged to act against the flange 260' on the surface 238 of the die 280 by springs 239 (FIG. 15) and rods 241 in the upper tool 211 as the punch or indent ring 225 begins to retract upon the return motion of the press ram.

The return motion of the press ram permits the punch 280 to cooperate with the redraw punch 235 of the lower tool 212 which is urged by a compression spring (not shown but acting through a cross head and a plurality of rods 250) to progressively reform or deflect the center panel CP" from the position shown in FIG. 18 to that FIG. 19. The latter movement progressively generates the reinforced countersink raduis or anti peaking radius 255 by a folding action essentially identical to that heretofore described relative to FIGS. 8 and 9 of the drawings. Thus, the eventually formed end or shell 250 corresponds in structure and function identically to that heretofore described relative to the end or shell 150 (FIGS. 11 and 12).

A detailed construction of the various push rods and springs under the press plate 265 are readily understood by those skilled in the art who will also appreciate that springs such as those operating the rods 240, 250 could be replaced by other resilient devices, such as a gas cushion or hydraulic cylinders as forming operations may dictate. If preferred, a power press having a second powered action may be used.

Variations are also well within the scope of the invention as heretofore described relative to FIGS. 15 through 19 of the drawings, and one such variation is apparent from FIG. 18 to which attention is now directed. If during the first downward movement of the draw punch 225, the motion were continued beyond the position shown in FIG. 18 the frusto-conical surface 256 would merge with a cylindrical wall portion (not shown) before merging with the unnumbered radius of the blank B". When such a can end is reformed, the cylindrical portion is pulled radially inward but any spring back of the fold of the radius or anti peaking bead 255 can be used to compensate for relaxing the curve of the anti peak bead.

In both the modification just described and that specifically described relative to the press 10, while it is highly desirable to use fluidic pressure (P1 and/or P2), it is also considered within the scope of this invention to selectively operate the draw punch rod 120 and the draw punch piston 141 through separate cams or eccentrics such that the springs 93 and/or 95 can be loaded during the forming stroke under mechanical as opposed to fluidic pressure. The reform pad 35 may also be biased downwardly by a mechanical spring rather than the fluidic/pneumatic pressure P1.

Although in a preferred embodiment of the invention as has been specifically illustrated and described herein, it is to be understood that minor variations may be made in the apparatus and the method without departing from the spirit and scope of the invention, as defined in the appended claims.