SCHOLEY IAN (GB)
RIBEIRO LEONARDO (BR)
PRATURLON SYLVAN (US)
US3702559A | 1972-11-14 | |||
US3696657A | 1972-10-10 | |||
US5617755A | 1997-04-08 | |||
US5335532A | 1994-08-09 | |||
US3165203A | 1965-01-12 |
What is Claimed is: 1. A ram drive assembly for a can bodymaker including a mounting assembly and a number of forming assemblies supported thereon, each forming assembly including: a stationary assembly and a moving assembly, the stationary assembly including a die 5 pack and a domer, the moving assembly including a ram assembly and a cam follower assembly, the die pack defining an elongated forming passage having a proximal end and a distal end, the domer disposed adjacent the distal end of the forming passage, the ram assembly including an elongated ram body having a proximal end and a distal end, the cam follower assembly coupled to the proximal end of the ram body, the ram body 10 structured to reciprocate through the forming passage of the die pack between a retracted, first position, wherein the distal end of the ram body is spaced from the die pack, and, an extended, second position wherein the distal end of the ram body is adjacent the domer, the ram drive assembly comprising: a cam having a body with a number of cooperative cam surfaces structured to 15 operatively engage the cam follower assembly of each forming assembly; and a motor having a rotating output shaft operatively coupled to said cam body and structured to rotate said cam body. 2. The ram drive assembly of claim 1, wherein: 20 the number of cooperative cam surfaces define a plurality of drive portions including a forward stroke portion and a rearward stroke portion; and at least one of the forward stroke portion or the rearward stroke portion has a substantially constant velocity cam profile. 25 3. The ram drive assembly of claim 2, wherein: the number of cooperative cam surfaces define a number of dwell portions; each dwell portion has a no velocity cam profile; and at least one dwell portion is disposed between at least one forward stroke portion and one rearward stroke portion. 30 4. The ram drive assembly of claim 3, wherein: the number of cooperative cam surfaces define a number of acceleration portions; each acceleration portion having an acceleration profile; and each acceleration portion is disposed between one drive portion of the plurality of drive portions and one dwell portion of the number of dwell portions. 5. The ram drive assembly of claim 1, wherein the cam body is one of a disk 5 cam or a barrel cam. 6. The ram drive assembly of claim 1, wherein the cam body is a dynamic cam body. 10 7. The ram drive assembly of claim 1, wherein the cam body is a steady state cam body. 8. The ram drive assembly of claim 1, wherein the cam is structured to generate a smooth ironing action in the ram body. 15 9. The ram drive assembly of claim 1, wherein the cam is structured to be a direct operative coupling element. 10. A can bodymaker comprising: 20 a mounting assembly including a body with an upper, first surface; a ram drive assembly comprising: a cam having a body with a number of cooperative cam surfaces, and a motor having a rotating output shaft operatively coupled to said cam body and structured to rotate said cam body; and 25 a forming system including a number of forming assemblies positioned on the mounting assembly, each forming assembly comprising: a stationary assembly including: a die pack defining an elongated forming passage having a proximal end and a distal end, and 30 a domer disposed adjacent the distal end of the forming passage, and a moving assembly including: a ram assembly including an elongated ram body having a proximal end and a distal end, and a cam follower assembly coupled to the proximal end of the ram body, 5 wherein each cam follower assembly of each forming assembly cooperatively engages the number of cooperative cam surfaces of the body of the cam, and wherein for each forming assembly, the ram body is reciprocated through the forming passage of the die pack by the cam follower assembly between a retracted, first position, wherein the distal end of the ram body is spaced from the die pack, and, an 10 extended, second position wherein the distal end of the ram body is adjacent the domer. 11. The can bodymaker of claim 10, wherein: the number of cooperative cam surfaces define a plurality of drive portions including a forward stroke portion and a rearward stroke portion; and 15 at least one of the forward stroke portion or the rearward stroke portion has a substantially constant velocity cam profile. 12. The can bodymaker of claim 11, wherein: the number of cooperative cam surfaces define a number of dwell portions; 20 each dwell portion has a no velocity cam profile; and at least one dwell portion is disposed between at least one forward stroke portion and one rearward stroke portion. 13. The can bodymaker of claim 12 wherein: 25 the number of cooperative cam surfaces define a number of acceleration portions; each acceleration portion having an acceleration profile; and each acceleration portion is disposed between one drive portion of the plurality of drive portions and one dwell portion of the number of dwell portions. 30 14. The can bodymaker of claim 10 wherein said cam body is one of a disk cam or a barrel cam. 15. The can bodymaker of claim 10 wherein said cam body is a dynamic cam body. 16. The can bodymaker of claim 10 wherein said cam body is a steady state cam 5 body. 17. The can bodymaker of claim 10 wherein said cam is structured to generate a smooth ironing action in said ram body. 10 18. The can bodymaker of claim 10 wherein said cam is a direct operative coupling element. 19. The can bodymaker of claim 10 wherein said ram drive assembly does not include either of a crank or a swing arm. 15 20. The can bodymaker of claim 10 wherein: the forming system is structured to form standard beverage can bodies; each said ram body has a stroke length; and the stroke length of each ram is one of a reduced stroke length, a very reduced stroke20 length, or an exceedingly reduced stroke length. 25 |
Moving on to the die pack 56, the die pack 56 includes a number, and typically a plurality, of dies (none numbered). Each die includes a generally toroid body (none shown) having a central opening sized to iron and otherwise form the cup/blank into a can body (not shown). That is, as is well known, the die pack 56 is structured to reform/form a cup/blank disposed on a punch 124/ram body 122 into a can body (discussed below). As such, the dies of the die pack 56 define a forming passage 100 having an upstream, proximal end 102 (or “mouth” 102) and a downstream, distal end 104.
The redraw assembly 200 is disposed at the proximal end 102 of the forming passage 100. Further, and as is known, the die pack 56 includes, or is disposed adjacent or immediately adjacent, a stripper assembly 106 structured to strip, remove, a can body from the ram body 122 during the return stroke, as described below. That is, the stripper assembly 106 is disposed at the distal end of the forming passage 100.
In an exemplary embodiment, the die pack 56 further includes a cup (or blank) feed assembly 108. In an exemplary embodiment, the cup feed assembly 108 includes a servomotor and a rotary support (neither numbered). Cups, or blanks, are disposed on the cup feed assembly rotary support. The cup feed assembly servo-motor is structured to, and does, rotate the cup feed assembly rotary 7 support so that a cup (or blank) is positioned at the proximal end 102 of the forming passage 100 of the die pack 56 prior to the ram body 122 moving through the die pack 56, as discussed below 7 .
The dorner 58 includes a mounting assembly 110 and a domer body 112, The mounting assembly 110 is structured to be coupled to the domer support 70. The mounting assembly 110 is further structured to adjustably support the domer body 112. The domer body 112 includes a domed surface 114 having a vertex 116. The domed surface 114/vertex 116 is disposed facing, and generally aligned with, the forming passage 100 of the die pack 56, as is known.
Referring to Figures 4-6, the moving assembly 44 of the forming assembly 16 includes a ram assembly 120 and a cam follower assembly 150. The ram assembly 120 includes an elongated body 122 (hereinafter, and as used herein, “ram body” 122) and a punch 124 (hereinafter, and as used herein, “punch” 124). The ram body 122 has a proximal, or first, end 126, a medial portion 125 and a distal, or second, end 128. As is known, the punch 124 is coupled, directly coupled, or fixed to the ram body distal end 128. As is known, the distal end 128 has a smaller cross-sectional area relative to the proximal end 126 and the medial portion 125. In an exemplary embodiment, the punch 124 has a 5 cross-sectional area that is substantially similar to the proximal end 126 and the medial portion 125. Thus, there is a generally, or a substantially, smooth transition between the punch 124 and the ram body 122. The cam follower assembly 150 is disposed at, and coupled to, the proximal end 126 of the ram body 122. Further, in an exemplary embodiment, the ram body 122 is generally hollow. That 10 is, the ram body 122 defines a cavity 130. The distal end 128 of the ram body 122 includes a passage 129 that is in fluid communication with the cavity 130. Further, if a punch 124 is used, the punch 124 also includes an axially extending passage 127. That is, the passage 129 of the ram body 122 (and, if included, the punch passage 127) extends from the axial surface of the distal end 128 of the ram body 122 to the cavity 130. The cavity 130 is 15 selectively in fluid communication with a pressure assembly (discussed below). The pressure assembly is structured to, and does, generate a positive and/or a negative fluid pressure. As is known, the cavity 130 of the ram body 122 is selectively in fluid communication with a negative fluid pressure when the ram body 122 is moving forward (i.e., away from the ram drive assembly 300). In this configuration, a negative fluid 20 pressure biases the cup/blank toward the ram body 122 and/or punch 124. When the ram body 122 is moving backward (i.e., toward the ram drive assembly 300), a positive pressure helps to remove the now formed can body from the ram body 122 /punch 124. As the ram body 122 is one of the longer elements of the forming assembly 16, as used herein, the longitudinal axis L of the ram body 122 is also the longitudinal axis of the forming assembly 25 16. Referring to Figures 4, 5 and 7A-7D, the cam follower assembly 150 of the moving assembly 44 of a forming assembly 16 includes a slider 152 and a number of cam follower members 154 (two are shown in the example). In an exemplary embodiment, the slider 152 includes a slider body 160, a lower frame portion 162 extending downward from the 30 slider body 160, and an upper frame portion 164 extending upward from the slider body 160. In the example illustrated, slider body 160 is disposed generally parallel to the plane of the first surface 22 of the mounting assembly body 18, i.e., generally horizontally as shown. The lower frame portion 162 of the slider body 160 includes a first member 162A extending downward generally from at or near a first edge 160A of slider body 16, a second member 162B extending downward generally from at or near a second edge 160B of slider body 160 opposite the first edge 160A, and a third member 162C extending between the 5 first and second members 162A and 162B and spaced a distance below slider body 160. In the example shown in Figure 7D, the third member 162C extends generally horizontally, parallel to the slider body 160, between first and second members 162A and 162B. Each of the first, second, and third members 162A-162C may be formed integrally as portions of a single unitary member, such as shown in the example of Figure 7D, or alternatively may 10 be formed as separately and then coupled together via any suitable method (e.g., bolts, welding, etc.). The upper frame portion 164 of the slider body 160 includes a first member 164A extending upward generally from at or near the first edge 160A of slider body 160, a second member 164B extending upward generally from at or near the second edge 160B of slider15 body 160, and a third member 164C extending between the first and second members 164A and 164B and spaced a distance above slider body 160. Each of the first, second, and third members 164A-164C may be formed integrally as portions of a single unitary member, such as shown in the example of Figure 7D, or alternatively may be formed as separately and then coupled together via any suitable method (e.g., bolts, welding, etc.). 20 Continuing to refer to Figures 7A and 7D, the cam follower assembly 150 further includes a cam follower bearing assembly 165 having a number of hydrostatic/hydrodynamic bearing pads 166 which are positioned and structured to engage with corresponding, cooperatively positioned, bearing members 167 provided as part(s) of stationary assembly 42. Each bearing member 167 includes a bearing surface 168 upon25 which each bearing pad 166 is positioned and structured to slide. A hydrostatic/hydrodynamic bearing assembly is discussed in detail in U.S. Patent No. 10,137,490 and the disclosure of the hydrostatic/hydrodynamic bearing assembly therein is incorporated herein by reference. Each bearing pad 166 includes a recessed bearing pocket 169 (two of which, 169A and 169C, are numbered in Figure 7D) that is structured to 30 generally house a pressurized supply of oil or other suitable bearing fluid (not shown) provided therein (as discussed further below). Prior art drive assemblies, such as drive assembly 2 previously discussed in regard to Figure 1 exert vertical forces on ram bodies, such as ram body 7B, that must be addressed/managed by bearings that generally completely surround the ram body. Such vertical forces can result in ram “droop” However, unlike such prior art arrangements, arrangements utilizing a cam drive such as described herein are generally only subjected to moderate lateral forces and are not subjected to any meaningful vertical forces. Hence, the 5 cam follower bearing assembly 165 is of unique design as compared to known arrangements. In the example illustrated in Figures 7A-7D, the cam follower bearing assembly 165 includes three generally planar hydrostatic/hydrodynamic bearing pads 166: a first bearing pad 166A coupled, directly coupled, or fixed to an outward facing face of first member 164A; a second bearing pad 166B coupled, directly coupled, or fixed to an 10 outward facing face of second member 164B (i.e., facing in the opposite direction from first bearing pad 166A); and a third bearing pad 166C coupled, directly coupled, or fixed to an upward facing face of third member 164C. In such example, the cam follower bearing assembly 165 also includes three bearing members 167A, 167B and 167C, respectively having bearing surfaces 168A, 168B and 168C. More particularly, the first bearing member 15 167A is fixedly coupled to the stationary assembly base 50 of the forming assembly 16 such that the bearing surface 168A thereof is positioned outward, above, and parallel to the longitudinal axis L of the ram body 122 of the forming assembly 16, and generally perpendicular to the stationary assembly base 50. The second bearing member 167B is fixedly coupled to the stationary assembly base 50 of the forming assembly 16 such that 20 the bearing surface 168B thereof is positioned outward, above, and parallel to the longitudinal axis L of the ram body 122 of the forming assembly 16; generally perpendicular to the stationary assembly base 50, and facing the bearing surface 168A of the first bearing member 167A. The third bearing member 167C is fixedly coupled to the stationary assembly base 50 of the forming assembly 16 such that the bearing surface 168C 25 thereof is positioned directly above and parallel to the longitudinal axis L of the ram body 122 of the forming assembly 16, generally parallel to the stationary assembly base 50, and perpendicular to each of the bearing surfaces 168A and 168B of the first bearing member 167A and the second bearing member 167B. Accordingly, as can be readily appreciated from the sectional view of Figure 7C, the three bearing members 167A-167C are positioned 30 so as to form a downward opening channel (with the bearing surfaces 168A-168C facing inward) that is disposed about the upper frame portion 164 of the slider body 160 and the outward facing bearings pads 166A-166C thereof. In one exemplary embodiment in accordance with the disclosed concept, each of the bearing surfaces 168A-168C are ground to a 4-8 micron surface finish and parallelism and squareness within 0.0002”. As previously discussed, the ram body 122 is generally hollow and defines the cavity 130 therein that is selectively in fluid communication with a pressure assembly. 5 Such communication between a pressure assembly (not shown) and cavity 130 of ram body 122 is provided via a flexible conduit or hose 170 that extends between a lower rotary seal 170A that is coupled to mounting assembly body 18 or any other suitable fixed location for connection to the aforementioned pressure assembly, and an upper rotary seal 170B that is coupled to the lower frame portion 162 of the slider body 160. The upper rotary seal 170B 10 is in fluid communication with the cavity 130 of the ram body via any suitable conduit arrangement provided as a part of cam follower assembly 150. A shock absorber arrangement 171 is provided about hose 170 to minimize hose whipping resulting from the reciprocating movement of cam follower assembly 150. As also previously discussed, each bearing pad 166 includes a recessed bearing 15 pocket 169 that is structured to generally house a pressurized supply of oil or other suitable bearing fluid (not shown) provided therein. Such supply of oil or other suitable bearing fluid is provided in a similar manner as the conductive pressure arrangement just described. In other words, the supply of oil or other suitable bearing fluid is provided to a second upper rotary seal 172B (see Figures 7B and 7C) that is coupled to the lower frame portion 162 of 20 the slider body 160. The supply is provided via a hose coupled to a second lower rotary seal (neither of which are shown) positioned similarly to hose and lower rotary seal 170 and 170A (and shock absorber arrangement 171) that is coupled to a suitable source of the supply (also not shown). The supply of oil or other suitable bearing fluid is communicated from the second upper rotary seal 172B to the recessed bearing pocket 169 of each of the 25 number of bearing pads 166A, 166B, 166C via any suitable conduit arrangement provided as a part of cam follower assembly 150 connected to an inlet 173 (see Figure 7D) provided in each bearing pocket 169. In one exemplary embodiment in accordance with the disclosed concept, an oil flow is injected into a manifold (not numbered) at a pressure of approximately 1000 psi. From the aforementioned manifold the oil flow is fed to each 30 bearing pad 166A, 166B, 166C. The oil flow is controlled by leejets (i.e., calibrated orifices). It is to be appreciated that such arrangement of bearing pads 166A, 166B, 166C, corresponding bearing surfaces 168A, 168B, 168C, and oil flow results in an oil film between the corresponding bearing pads 166A, 166B, 166C and bearing surfaces 168A, 168B, 168C that prevents any metal to metal contact and thus provides for smooth sliding of cam follower assembly 150 along bearing members 167A, 167B, 167C and thus smooth translations relative to the stationary assembly base 50 of the forming assembly 16. Referring now to Figure 5, the slider body 160 includes a number of passages (not 5 collectively numbered) defined therethrough. The passages include a number of cam follower mounting passages, two shown 174 and 175. If there are two cam follower mounting passages 174, 175, the cam follower mounting passages 174, 175 are disposed generally along a line that, when the forming assembly 16 is coupled to the mounting assembly 14, is generally a radial line extending outward from the passage 20 of the 10 mounting assembly body 18 and aligned above the longitudinal axis L of the ram body 122 of forming assembly 16. Another passage defined through slider body 160 is an alignment pin passage 178 positioned generally adjacent the end of slider body 160 opposite ram body 122. The cam follower members 154 are structured to be, and are, operatively engaged 15 by the cam 330 of the ram drive assembly 300. Stated alternately, the cam 330 is structured to be, and is, operatively coupled to the cam follower members 154 of the moving assembly 44 of each forming assembly 16 and is, therefore, operatively coupled to each ram assembly 120 and/or forming assembly 16. In one embodiment, not shown, the cam follower members 154 are rigid bearings. 20 In the embodiment shown in Figures 2-6 and 7A-7D, the cam follower members 154 are roller bearings 180 (hereinafter, and as used herein, the “cam follower roller bearings” 180). As shown, and in an exemplary embodiment, each cam follower roller bearing includes an axle 184 and a wheel 186 (see Figure 5). Further, and in an exemplary embodiment, one of the cam follower roller bearings 180 includes an eccentric bushing 187. The eccentric 25 bushing 187 includes a hollow tubular body 188 that is structured to fit within cam follower mounting passage 175 (or alternatively passage 174). The tubular body 188 has a generally cylindrical outer surface 190 having a first center (not numbered), and, a generally cylindrical outer surface 192 having a second center (not numbered). The first and second centers noted in the prior sentence are not aligned. That is, the first and second centers30 noted above are offset from each other. In this configuration, the eccentric bushing 187 includes a portion with a maximum thickness, hereinafter the “thicker” side 188’ of the eccentric bushing 187, and, a portion with a minimum thickness, hereinafter the “thinner” side 188’’ of the eccentric bushing 187. Further, the eccentric bushing 187 includes an orientation tab 194 that extends generally radially from the outer surface 190 of the tubular body 188. In this configuration, the eccentric bushing 187 is structured to, and does, move the associated roller bearing wheel 186 between a spaced, first position and a close, second position, as discussed below. 5 Thus, as used herein, a “forming assembly” 16 includes at least a die pack 56, a domer 58, and a ram body 122. Further, a “forming assembly” 16 selectively includes additional elements such as, but not limited to, a ram guide assembly 52 and a redraw assembly 200. A forming assembly 16 is assembled as follows. The ram guide assembly 52, the 10 redraw assembly 200, and the die pack 56 are coupled, directly coupled, or fixed to the base planar member 60, i.e., the stationary assembly base 50. The domer 58 is coupled, directly coupled, or fixed to the domer support 70, i.e., which, as previously discussed, is coupled to, or formed as a unitary portion of, the stationary assembly base 50. Generally, the ram guide assembly 52 is disposed closest to the passage 20 of the mounting assembly body 18. 15 The redraw assembly 200 is disposed adjacent the ram guide assembly 52. The die pack 56 is disposed adjacent the ram guide assembly 52 with the cup feed assembly 108 disposed between the redraw assembly 200 and the die pack 56. Further, as noted above, the stripper assembly 106 is disposed at the distal end 104 of the forming passage 100 of the die pack 56. Finally, the domer 58 is spaced from the die pack 56 and/or stripper assembly 106. 20 That is, the domer 58 (or stripper assembly 106) is spaced from the die pack 56 by a distance that is at least the length of a can body and, as shown, a distance that is greater than at least the length of a can body. In one embodiment, and in the configuration described above, the stationary assembly 42 of the forming assembly 16 is complete. The moving assembly 44 of the forming assembly 16 is assembled as follows. The 25 proximal end 126 of the ram body 122 is coupled, directly coupled, or fixed to the slider 152 of the cam follower assembly 150. As shown, and in an exemplary embodiment, the proximal end 126 of the ram body 122 is coupled to the lower frame portion 162 of the slider body 160. The punch 124 is disposed over and coupled, directly coupled, or fixed to the distal end 128 of the ram body 122. In this configuration, the longitudinal axis L of the 30 ram body 122 is generally, or substantially, aligned with the longitudinal axis of the passage 81, the redraw assembly 200, and the forming passage 100 of the die pack 56. Further, the longitudinal axis L of the ram body 122 is generally, or substantially, aligned with the vertex 116 of the domed surface 114 of the domer body 112. That is, if the longitudinal axis L of the ram body 122 were extended, it would pass through, or be immediately adjacent the vertex 116 of the domed surface 114 of the domer body 112. In this configuration, and in one embodiment, the forming assembly 16 is complete. Further, as noted above, the forming assembly 16 is a “unified” assembly. Further, it is 5 understood that as the forming assembly 16 is assembled, the various elements are positioned to be in proper alignment, as is known in the art. That is, for example, the ram body 122 is adjusted/repositioned until the longitudinal axis L of the ram body 122 is generally, or substantially, aligned with the longitudinal axis of the passage 81 of the housing 80 of the ram guide assembly 52 and the longitudinal axis of the forming passage 10 100 of the die pack 56. As the forming assembly 16 is a “unified” assembly, the elements thereof remain aligned with each other. That is, when the forming assembly 16 is removed from the mounting assembly 14, the elements thereof are not separated. As such, the elements of the forming assembly 16 do not have to be adjusted so as to be in alignment each time the forming assembly 16 is installed. A forming assembly 16 that maintains the 15 alignment of the elements, i.e., wherein the elements of the stationary assembly 42 and the moving assembly 44 are not separated, during an installation is, as used herein, an “aligned” unified forming assembly 16. A unified forming assembly 16 or an aligned unified forming assembly 16 solves the problem(s) noted above. As shown in Figures 2-3, the ram drive assembly 300 of bodymaker 10 is structured 20 to, and does, move the moving assembly 44 of the forming assembly 16, i.e., the ram assembly 120 or the ram body 122, between a retracted (i.e., toward the ram drive assembly 300), first position, wherein the ram body 122 is not disposed in the forming passage 100 and the distal end 128 of the ram body 122 is spaced from an associated die pack 56, and, an extended (i.e., away from the ram drive assembly 300), second position wherein the ram 25 body 122 is disposed in the forming passage 100 and the distal end 128 of the ram body 122 is adjacent an associated domer 58. The ram drive assembly 300, as detailed below, does not include either a crank, a swing arm, and/or pivoting connecting rods. This solves the problem(s) noted above. Referring to Figure 3, the ram drive assembly 300 includes a motor 310 and a cam 30 330 that is rotated around a prime axis of rotation 330 by the motor 310. The motor 310 includes a rotating output shaft 312. In an exemplary embodiment, the motor 310 is disposed below the mounting assembly body 18 within the enclosed space 30 defined by housing 28. As shown, a primary axle 314 is generally disposed within the hollow mounting assembly enclosed space 30 and rotatable about prime axis 333. The motor output shaft 312 is operatively coupled to the primary axle 314, e.g., by a gear box 315. As such, the primary axle 314 is also identified herein as a part of the motor 310. The primary axle 314 includes an elongated axle body 316 having an upper, first end 318 and a lower, 5 second end (not numbered) coupled to the gear box 315. The lower second end of axle body 316 may be selectively coupled to the gear box 315 via a suitable clutch arrangement that provides for axle body 316 to be selectively engaged or disengaged from the gear box 315, and thus motor 310. The first end 318 of the axle body 316 extends through the passage 20 of the mounting assembly body 18. The first end 318 of the axle body 316 is 10 structured to be, and is, coupled to the cam body 332. A brake arrangement 319 (e.g., a disk brake or other suitable arrangement) is positioned along primary axle 314 for selectively bringing rotation about prime axis 333 of primary axle 314 and cam body 332 to a controlled and timely stop. The cam 330 of the ram drive assembly 300 includes a body 332 defining, or having, 15 a number of cooperative cam surfaces 334, 336, (two shown) and identified herein as the inner, first cam surface 334 and the outer, second cam surface 336. The cam 330/cam body 332 is structured to, and does, impart a reciprocal motion to each forming assembly 16 and, in an exemplary embodiment, to each moving assembly 44 and/or ram assembly 120. Further it is noted that, as discussed below, the cam 330 moves while each forming 20 assembly 16 is mounted on the mounting assembly 14. That is, the cam 330 is dynamic and each forming assembly 16 is statically mounted. Thus, the cam body 332 is a “dynamic cam body”. This solves the problems noted above. Alternatively, the cam body 332 could be fixed or held in a steady state with each forming assembly 16 moving thereabout. In such arrangement, cam body 332 would be a “steady state cam body”. 25 Further, in an exemplary embodiment, the cam 330/cam body 332 is structured to, and does, generate a “smooth ironing action” in the distal end 128 of the ram body 122/punch 124 as the ram body 122/punch 124 moves through the die pack 56. As used herein, a “smooth ironing action” means that the construct that supports the cup, which is typically the distal end 128 of the ram body 122 or punch 124, is not being accelerated or 30 decelerated as the construct that supports the cup passes through the die pack 56. In an exemplary embodiment, the cam body 332 includes cooperative cam surfaces 334, 336, discussed below, having a substantially constant velocity cam profile, discussed below. The cam surfaces 334, 336 with a constant velocity cam profile cause the distal end 128 of the ram body 122 or punch 124 to move at a substantially constant velocity, i.e., no acceleration or deceleration, as the distal end 128 of the ram body 122 or punch 124 pass through the die pack 56. Thus, such a cam 330/cam body 332 is structured to, and does, generate a “smooth ironing action.” This solves the problem(s) noted above. 5 Further, in an exemplary embodiment, the components (i.e., the ram assembly 120 and cam follower assembly 150) of the moving assembly 44 of the forming assembly 16 are of low mass. Use of such a low mass moving assembly 44 with a cam 330 having dwell portions (and thus zero acceleration and, consequently, zero inertial forces and deformations) at the travel extremes results in zero or essentially zero deformations in 10 moving assembly 44 and components thereof at virtually any operating speed. Hence, once the position of ram assembly 120 is adjusted for optimum doming position, such positioning will not change with the production speed. This solves the problem(s) above. Further, in an exemplary embodiment, the cam 330/cam body 332 is structured to be, and is, a “direct operative coupling element.” As used herein, a “direct operative 15 coupling element” means an element that is structured to be directly coupled to both the construct that generates motion and the ram assembly of a bodymaker. In the embodiment above, the construct that generates motion is the motor 310. To be “directly coupled” to a construct that generates motion, as used herein, means that an element is directly coupled to a motor output shaft or a mounting on a motor output shaft. As used herein, a “mounting” 20 for a motor output shaft is a construct that rotates with the motor output shaft and which has a body that is disposed substantially symmetrically about the motor output shaft. That is, for example, the crank of a prior art bodymaker is, typically, “directly coupled” to a motor output shaft; the crank, however, does not have a body that is disposed substantially symmetrically about the motor output shaft; thus, as used herein, a crank is not a 25 “mounting.” Further, as used herein, the “ram assembly” means the elements that move with, and substantially parallel to, a ram body path of travel. That is, for example, in the prior art arrangement such as shown in Figure 1, both the carriage 7A and the second connecting rod 6B both move with the ram body 7B, but the second connecting rod 6B does not move with, and substantially parallel to, the ram body 7B path of travel. Thus, the 30 second connecting rod 6B, and similar elements, are not part of the “ram assembly.” Thus, as described above, the prior art multi-element linkage, i.e., crank 4/swing arm 5/first connecting rod 6A/second connecting rod 6B, does not, and cannot, be a “direct operative coupling element.” That is, such a linkage is not a single element and such a linkage is not directly coupled” to a motor output shaft. Thus, the cam 330/cam body 332 that is structured to be, and is, a “direct operative coupling element” solves the problem(s) noted above. In one embodiment, the cam body 332 is a generally solid, unitary, planar with an 5 axially extending hub 337 (Figure 3) and a ridge 338 extending about the cam body 332 axis of rotation (i.e., prime axis 333). In another embodiment such as shown in Figure 13, the cam body 332’ is a two-part assembly, an outer ring 332A’ disposed about an inner section 332B’. Outer ring 332A’ and inner section 332B’ may be formed from different materials and one or both of outer ring 332A’ and 332B’ may have one or more apertures 10 or open sections defined therein or thereby to lighten such sections and thus reduce the moment of inertia of such cam 330’. Referring again to Figure 3, the cam body hub 337 defines a coupling passage 339. In an exemplary embodiment, the coupling passage 339 is tapered and narrows from bottom to top (e.g., see Figure 3). In an exemplary embodiment, the first end 318 of the axle body15 316 is structured to be, and is, coupled to the cam body 332 at the coupling passage 339. As shown, the cam body ridge 338, in an exemplary embodiment, extends about the perimeter of the cam body 332. As shown in Figure 2, when viewed from above, the ridge 338 of the cam body 332 is not substantially circular, as discussed in detail below; that is, the ridge 338 does not have a substantially consistent radius R relative to the axis of rotation 20 (i.e., prime axis 333) of the cam body 332, but instead is varied in a predetermined manner to create desired movement of the moving assembly 44. The overall variation in the radius R (i.e., the difference between the minimum and maximum value of the radius R, which is equal to the stroke of the ram assembly 120) is dependent on the height of the can body being produced. In an exemplary embodiment, a stroke of 22” is used to manufacture cans 25 up to 6.5” tall/long. As used herein, a generally planar cam body 332 having a ridge 338 extending about the perimeter of the cam body 332 is a “disk cam.” In this embodiment, the ridge 338 includes the inner, first cam surface 334 and the outer, second cam surface 336. Further, in an exemplary embodiment, the radial width W (Figure 5) of the cam body ridge 338 is generally, or substantially, consistent. That is, the distance between the first 30 cam surface 334 and the second cam surface 336 is generally, or substantially, consistent. Further, in an exemplary embodiment, the cam body 332 includes a number of alignment passages 344 disposed adjacent the cam body ridge 338, the purpose of which is discussed below. In another example embodiment, such as shown in Figures 10 and 11, a bodymaker 10B utilizing a “barrel” cam 330B is shown. The bodymaker 10B is of a similar arrangement as the bodymaker 10 previously discussed in conjunction with Figures 2-6 except the bodymaker 10B only includes two forming assemblies 16 and includes a ram 5 drive assembly 300B that includes/utilizes the “barrel” cam 330B instead of a disk cam. Hereinafter, and in relation to the barrel cam 330B, reference numbers similar to the embodiment shown in Figures 2-6 will be used, but the reference numbers will include the letter “B.” In this embodiment, the cam body 332B is generally cylindrical and includes a groove (not shown) or a ridge (as shown) 338B disposed thereabout on a cylindrical surface 10 (not numbered) of the cam body 332B. The ridge 338B extends generally axially while also forming a loop about the cylindrical cam body 332B. In this configuration, the cam body 332B, i.e., the ridge 338B thereon, defines a generally axial first cam surface 334B and a generally axial second cam surface 336B. It is understood that, where the ridge 338B reverses direction, the ridge 338B extends generally circumferentially around the cam body 15 332B rather than axially along the cam body 332B. In this embodiment, the opposing sides of the ridge 338B are the cooperative cam surfaces 334B, 336B. It is noted that a ram drive assembly 300 including, or consisting of, these elements does not include pivotal couplings. This solves the problem(s) stated above. In either of such example arrangements, the cooperative cam surfaces 334, 336 or20 334B, 336B are structured to, and do, operatively engage each cam follower assembly 150. In the embodiment shown in Figures 2-6, the cam follower assembly 150 includes two cam follower members 154, i.e., roller bearings 180, also identified herein as first cam follower member 156 and second cam follower member 158. The first cam follower member 156 is disposed adjacent the first cam surface 334. That is, the wheel 186 of the first cam 25 follower member 156 is disposed adjacent to the first cam surface 334. The second cam follower member 158 is disposed adjacent the second cam surface 336. That is, the wheel 186 of the second cam follower member 158 is disposed adjacent to the second cam surface 336. Thus, in such embodiment, the first and second cam follower members 156, 158 “sandwich” the cam body ridge 338. That is, the first and second cam follower members 30 156, 158 are disposed on opposite sides of the cam body ridge 338. In an exemplary embodiment with a barrel cam having a groove instead of a ridge 334B, there is a single cam follower member which is structured to be, and is, disposed in the groove. Further, as shown in Figures 10 and 11, in an exemplary embodiment, the bodymaker 10B has a barrel cam 330B that includes two separate barrel cams 330B’, 330B’’ that are coupled, directly coupled, or fixed to the output shaft 312B of a motor 310B. It is understood that, in an exemplary embodiment, each barrel cam 330B’, 330B’’ 5 is structured to be, and is, operatively coupled to a respective forming assembly 16, such as previously discussed in regard to Figures 2-6. Thus, in an embodiment with a single barrel cam 330B and two forming assemblies 16, such as shown in Figures 10 and 11, the bodymaker 10B produces two can bodies per cycle. Although only two forming assemblies 16 are shown in Figures 10 and 11 being used in conjunction with barrel cam 330B, it is to 10 be appreciated that more than two forming assemblies may be employed without varying from the scope of the present concepts. For example, additional forming assemblies 16 may be provided with the respective cam follower assemblies 150 thereof positioned to engage the 338B at generally any point around the barrel cam 330B (i.e., in addition to, or instead of only at the top as shown in Figures 10 and 11). As an example, when viewed 15 generally along the prime axis of rotation 333B of barrel cam 330B, an arrangement utilizing twelve forming assemblies 150 spaced equally about the circumference of the barrel cam 330B would generally resemble the positioning of the twelve hour indicators on the face of a traditional clock. As described above, each forming assembly 16 is coupled, directly coupled, or fixed 20 to the mounting assembly 14. Thus, each forming assembly 16 is disposed at a fixed location adjacent the cam body 332. Further, relative to each forming assembly 16, the cam body ridge 338 moves radially outwardly and radially inwardly as the cam body 332 rotates. It is understood that as the radius of the cam body ridge 338 decreases, the first cam surface 340 operatively engages a first cam follower member 156. Conversely, when 25 as the radius of the cam body ridge 338 increases, the second cam surface 342 operatively engages a second cam follower member 158. It is understood that as one cam surface 340, 342 operatively engages a cam follower member 156, 158, the other cam surface 340, 342 does not operatively engage a cam follower member 156, 158. That is, only one cam surface 340, 342 operatively engages a cam follower member 156, 158 at a time. 30 As the cam follower assembly 150 is coupled, directly coupled, or fixed to the forming assembly moving assembly ram assembly 120, the cam 330 is structured to, and does, pull the ram body 122 radially inwardly as the first cam surface 334 operatively engages a first cam follower member 156. Conversely, the cam 330 is structured to, and does, push the ram body 122 radially outwardly as the second cam surface 336 operatively engages a second cam follower member 158. That is, as used herein, a cam surface/cam profile is a cam surface that “operatively engages” a cam follower, or constructs coupled to a cam follower, when the cam follower moves relative to the cam surface/cam profile 5 and/or when the cam surface/cam profile moves relative to the cam follower. As shown in Figure 12, the cooperative cam surfaces 334, 336, i.e., first cam surface 334 and second cam surface 336, are divided into “portions.” That is, the cam surfaces 334, 336 include, or define, a number of drive portions 350, 352 (two shown). As used herein, a “drive” portion of a cam surface means that the cam surface is structured to move 10 another element or assembly. In an exemplary embodiment, the cam surface drive portions 350, 352 include a forward or forming stroke portion 350 and a rearward or return stroke portion 352. That is, as used herein, a “forward stroke” portion 350 is an alternate name for a drive portion that causes a cam follower 150 (as well as constructs coupled to the cam follower 150 such as, but not limited to, the ram body 122) to move toward an associated 15 domer 58. Further, as used herein, a “rearward stroke” portion 352 is an alternate name for a drive portion that causes a cam follower 150 (or constructs coupled to the cam follower 150 such as, but not limited to, the ram body 122) to move away from an associated domer 58. As described above, the operative engagement of the second cam surface 336 with 20 the second cam follower member 158 causes the moving assembly 44 of the forming assembly 16, including the ram body 122, to move radially outwardly. Thus, a portion of the second cam surface 336 wherein the radius is “increasing” as the cam body 332 moves is a cooperative cam surface forward stroke portion 350. Conversely, the operative engagement of the first cam surface 334 with the first cam follower member 156 causes the 25 moving assembly 44 of the forming assembly 16, including the ram body 122, to move radially inwardly. Thus, a portion of the first cam surface 340 wherein the radius is “decreasing” as the cam body 332 moves is a cooperative cam surface rearward stroke portion 352. As noted above, only one of first cam surface 334 or second cam surface 336 operatively engages a cam follower member 156, 158 at a time. As used herein, however, 30 the opposed cam surfaces 334, 336 are identified by the same portion name. That is, the portion of the first cam surface 334 opposed to the second cam surface forward stroke portion 350 is also identified as the “forward stroke portion 350” even though the first cam surface 334 does not operatively engage the first cam follower member 156 at the forward stroke portion 350. Stated alternately, and further to the definition above, i.e., as used herein, a “forward stroke portion” 350 of associated first cam surface 334 and second cam surface 336, means a portion of the cooperative cam surfaces 334, 336 wherein at least one of the cooperative cam surfaces 334, 336 operatively engages, directly or indirectly, a ram 5 body 122 and causes that ram body 122 to move toward an associated domer 58. Conversely, and further to the definition above, i.e., as used herein, a “rearward stroke portion” 352 of associated cooperative first cam surface 334 and second cam surface 336 means a portion of the cooperative cam surfaces 334, 336 wherein at least one of the cooperative cam surfaces 334, 336 operatively engages, directly or indirectly, a ram body 10 122 and causes that ram body 122 to move away from an associated domer 58. Further, it is understood that as the cam body 332 rotates, the cooperative cam surface drive portions 350, 352 operatively engage a cam follower member 156, 158. Thus, each cooperative cam surface drive portion 350, 352 (or alternatively the cam body cooperative cam surface forward stroke portion 350 and the cam body cooperative cam 15 surface rearward stroke portion 352) has a beginning/upstream, first end 350U, 352U and an ending/downstream, second end 350D, 352D. That is, as the cam body 332 rotates, the cooperative cam surface drive portion first end 350U, 352U initially operatively engages a cam follower member 156, 158. As the cam body 332 rotates further, the cooperative cam surface drive portion second end 350D, 352D passes by a cam follower member 156, 158. 20 When this occurs, the cam follower member 156, 158 is no longer disposed at that cooperative cam surface drive portion 350, 352. The nomenclature of [reference number]U and [reference number]D shall be used herein with each cam surface portion to identify the upstream, first end and downstream, second end of the named portion. For example, as discussed below, the cooperative cam 25 surfaces 334, 336 also include, or define, a first dwell portion 360’. Thus, the upstream/first end of the first dwell portion 360’ is identified as “first dwell portion first end 360’U.” It is noted that the pitch (radial change relative to circumferential change) of the cam body ridge 338, and therefore the cooperative first cam surface 334 and second cam surface 336, determines whether the cam follower member 156, 158, and therefore the ram 30 body 122, moves at a generally, or substantially, constant velocity, is accelerating/decelerating (and/or the rate of acceleration/deceleration), or is substantially stationary. That is, as a simplified example (exemplary elements not shown), it is assumed that a ram must move forward (toward a domer) three inches. Further, it is assumed that the cam body cooperative cam surface forward stroke portion extends over an arc of ninety degrees (90°). For this exemplary configuration, the radius of the cooperative cam surfaces and more specifically the second cam surface, increases three inches over the ninety degrees (90°) of the cam body cooperative cam surface forward stroke portion. That is, the 5 movement of the ram body is proportional to the radius of the cooperative cam surfaces. Thus, when the radius of the cooperative cam surfaces increases an inch, the ram moves forward an inch. Further, as noted and in an exemplary embodiment, the cooperative cam surface drive portion 350 (or alternatively the cam body cooperative cam surface forward stroke 10 portion 350) have a substantially constant velocity cam profile, i.e., a shape structured to impart a substantially constant velocity to the element/assembly that is operatively engaged by the cam surface. In the example above (exemplary elements not shown), wherein the radius of the cooperative cam surfaces and more specifically the second cam surface, increases three inches over the ninety degrees (90°), an increase in the radius of one inch 15 every 30° would produce a substantially constant velocity in the ram. A cam body ridge 338, and therefore the cooperative first cam surface 334 and second cam surface 336, which operatively engages a cam follower (or constructs coupled to the cam follower such as, but not limited to, the ram body 122) and which has a pitch that is structured to, and does, produce a substantially constant velocity in the cam follower 20 (or constructs coupled thereto) has, as used herein, a “substantially constant velocity cam profile.” In an exemplary embodiment, at least one of, or both, the cooperative cam surface forward stroke portion 350 and the cooperative cam surface rearward stroke portion 352 have a substantially constant velocity cam profile. Further, in an exemplary embodiment, the cooperative cam surface forward stroke portion 350 extends over an arc of about one 25 hundred eighty three and one half degrees (183.5°) and the cooperative cam surface rearward stroke portion 352 extends over an arc of about one hundred and forty three degrees (143.0°). In an exemplary embodiment, the cooperative cam surfaces 334, 336 also include, or define, a number of dwell portions 360’, 360’’ (two shown) and identified herein as the30 first dwell portion 360’ and the second dwell portion 360’’. As used herein, a “dwell portion” 360’, 360’’ of the associated cooperative first cam surface 334 and second cam surface 336, means a portion of the cooperative cam surfaces 334, 336 wherein neither of the cooperative cam surfaces 334, 336 operatively engages a cam follower (or constructs coupled to the cam follower such as, but not limited to, the ram body 122). Thus, the ram body 122 is generally stationary and does not move toward or away from an associated domer 58. In an exemplary embodiment, and at a cooperative cam surface dwell portion 360’, 360’’, the radius of the cam body ridge 338, and therefore the cooperative first cam 5 surface 334 and second cam surface 336, does not substantially increase or decrease. Thus, the cam body ridge 338, and therefore the cooperative first cam surface 334 and second cam surface 336, do not operatively engage a cam follower member 154 (or constructs coupled to the cam follower member 154 such as, but not limited to, the ram body 122). As used herein, a cam surface that does not operatively engage a cam follower member 154 10 has a “no velocity cam profile.” That is, a “no velocity cam profile” means that cooperative cam surfaces 334, 336 do not cause a cam follower (or constructs coupled to the cam follower such as, but not limited to, the ram body 122) to move toward or away from an associated domer 58. Thus, the cooperative cam surface dwell portions 360’, 360’’ have a “no velocity cam profile.” However, to maintain consistent terminology, hereinafter the 15 first dwell portion 360’ and the second dwell portion 360’’ will be said to “engage” or “operatively engage” the moving assembly 44 of a forming assembly 16 (or elements thereof such as, but not limited to, the cam follower members 154). It is understood that while the terms “engage” or “operatively engage” are used, the first dwell portion 360’ and the second dwell portion 360’’ do not actually cause the moving assembly 44 (or elements 20 thereof such as, but not limited to, the cam follower members 154) to move. That is, with respect to the first dwell portion 360’ and the second dwell portion 360’’ only, and as used herein, the terms “engage” and “operatively engage” do not have the meanings set forth above and instead mean that the first dwell portion 360’ and the second dwell portion 360’’ are directly coupled to the cam follower assembly 150. 25 In an exemplary embodiment, no cooperative cam surface dwell portion 360’, 360’’ extends over an arc greater than thirty degrees (30°). As used herein, the existence of cooperative cam surface dwell portions 360’, 360’’ extending over an arc no greater than thirty degrees does not mean that the cam body ridge 338 has a generally, or substantially, consistent radius relative to the cam body 332 axis of rotation. That is, so long as the30 cooperative cam surface dwell portions 360’, 360’’ extend over an arc no greater than thirty degrees, the cam body ridge 338 does not have a generally, or substantially, consistent radius relative to the cam body 332 axis of rotation. In an exemplary embodiment, at least one cam body cooperative cam surface dwell portion 360’, 360’’ is disposed between at least one of the cam body cooperative cam surface forward stroke portion 350 and the cam body cooperative cam surface rearward stroke portion 352, or, the cam body cooperative cam surface rearward stroke portion 352 5 and the cam body cooperative cam surface forward stroke portion 350. In another exemplary embodiment, each cooperative cam surface dwell portion 360’, 360’’ is disposed between cam body cooperative cam surface drive portions 350, 352. That is, there is a cooperative cam surface first dwell portion 360’ disposed between the forward stroke portion second end 350D and the rearward stroke portion first end 352U, and, a cooperative 10 cam surface second dwell portion 360’’ disposed between the rearward stroke portion second end 352D and the forward stroke portion first end 350U. In an exemplary embodiment, the cooperative cam surface first dwell portion 360’ extends over an arc of about three and one half degrees (3.5°) and the cooperative cam surface second dwell portion 360’’ extends over an arc of about thirty degrees (30°). 15 In an exemplary embodiment, the cooperative cam surfaces 334, 336 also include, or define, a number of portions 370, 372 (two shown), hereinafter identified as the acceleration portion 370 and the deceleration portion 372. The acceleration portion 370 and the deceleration portion 372 each have an “acceleration profile.” As used herein, an “acceleration profile” means that the cam body ridge 338, and therefore the cooperative 20 first cam surface 334 and second cam surface 336, operatively engages a cam follower (or constructs coupled to the cam follower such as, but not limited to, the ram body 122) and produce a changing velocity in a ram body 122. That is, an “acceleration profile” means that the cam body ridge 338, and therefore the cooperative first cam surface 334 and second cam surface 336 has/have a pitch that is structured to, and does, produce a changing velocity 25 in a cam follower (or constructs coupled to the cam follower such as, but not limited to, the ram body 122) when the cam surface operatively engages the cam follower. Thus, the surface portions 370, 372 either cause a ram body 122 to increase or decrease its velocity. That is, deceleration of a ram body’s 122 velocity is, stated alternately, acceleration in a direction opposite the velocity of the ram body 122. 30 In an exemplary embodiment such as illustrated in Figure 12, the cooperative cam surface acceleration portion 370 and deceleration portion 372 are disposed between the cooperative cam surface drive portions 350, 352 and the cooperative cam surface dwell portions 360’, 360’’. That is, starting at the end of dwell portion 360’’ associated with the ram body 122 being in the first position (i.e., furthest from the domer 58), and moving sequentially about the cam surfaces 334, 336, the portions are in this order: the acceleration portion 370 (which causes an acceleration of the ram body 122 toward the domer 58), a constant speed portion 350, the deceleration portion 372 (which causes a deceleration to no 5 velocity), the first dwell portion 360’, the varying speed portion 352 which is of varying speed, and the second dwell portion 360’’. The acceleration portion 370, the constant speed portion 350, and the deceleration portion 372 make up the forming stroke, whereas the varying speed portion 352 makes up the return stroke. In an exemplary embodiment such as shown in Figure 12, the acceleration portion 370 extends over an arc of about thirty three 10 degrees (33°) and the deceleration portion 372 extends over an arc of about thirty three and one half degrees (33.5°). Thus, as shown in Figure 12, and in an exemplary embodiment, the cooperative first cam surface 334 and second cam surface 336, are divided into the following portions which extend sequentially over the identified arcs. 15 For a cam 330 such as described above, Figure 12A shows the position or displacement of a punch 124 relative to the first position and relative to the cam 330, as described above, as the cam 330 rotates. Figure 12B shows the velocity of a ram assembly 120/punch 124 as the cam 330 rotates. Figure 12C shows the acceleration (or deceleration) 20 of a ram assembly 120/punch 124 as the cam 330 rotates. When a forming assembly 16 is coupled, directly coupled, or fixed to the mounting assembly 14, the cam body ridge 338 is disposed between the first cam follower member 156 and the second cam follower member 158. That is, as noted above, the wheel 186 of the first cam follower member 156 is disposed adjacent to the first cam surface 334, and, 25 the wheel 186 of the second cam follower member 158 is disposed adjacent to the second cam surface 336. Thus, when the cam 330, i.e., cam body 332, rotates, and when the radius of the cam body ridge 338 is “decreasing” as described above, the first cam surface 334 operatively engages the first cam follower member 156. Conversely, when the cam 330, i.e., cam body 332, rotates, and when the radius of the cam body ridge 338 is “increasing” as described above, the second cam surface 336 operatively engages the second cam follower member 158. 5 The operative engagement of the first and second cam follower members 156, 158 by the cooperative cam surfaces 334, 336 cause the cam follower assembly 150 and the elements coupled thereto, i.e., the ram assembly 120, to move. That is, the operative engagement of the first and second cam follower members 156, 158 by the cooperative cam surfaces 334, 336 cause the moving assembly 44 of the forming assembly 16 to move. 10 Thus, the motion of the moving assembly 44 of a forming assembly 16 sequentially occurs as follows. Initially, the moving assembly 44 is in the first position. When the first and second cam follower members 156, 158 are at the second dwell portion 360’’, the moving assembly 44 (including the ram body 122 and the punch 124) does/do not move. As the moving elements of the moving assembly 44 do not suddenly, or instantly, reverse 15 directions, the moving assembly 44 does not substantially vibrate. This solves the problem(s) noted above. That is, the second cooperative cam surface dwell portion 360’’ solves the problem(s) noted above. Further, at this time, a cup is moved into position at the mouth of the die pack 56. As the cam 330, i.e., cam body 332, rotates, the first cooperative cam surface20 acceleration portion 370 engages the first and second cam follower members 156, 158 which causes the moving assembly 44 (including the ram body 122 and the punch 124) to accelerate and move toward the associated domer 58. As the cam 330, i.e., cam body 332, continues to rotate, the cooperative cam surface forward stroke portion 350 engages the first and second cam follower members 156, 158 which causes the moving assembly 44 25 (including the ram body 122 and the punch 124) to move toward the associated domer 58 at a substantially constant velocity. This solves the problem(s) noted above. That is, the cooperative cam surface forward stroke portion 350 solves the problem(s) noted above. As the cam 330, i.e., cam body 332, continues to rotate, the deceleration portion 372 engages the first and second cam follower members 156, 158 which causes the moving 30 assembly 44 (including the ram body 122 and the punch 124) to decelerate, i.e., accelerate in a direction opposite the velocity, to no velocity. As the cam 330, i.e., cam body 332, continues to rotate, the first cooperative cam surface dwell portion 360’ engages the first and second cam follower members 156, 158 which causes the moving assembly 44 (including the ram body 122 and the punch 124) to be maintained in the second position. That is, as the moving elements of the moving assembly 44 do not suddenly, or instantly, reverse directions, the moving assembly 44 does not substantially vibrate. The lack of motion/acceleration when the moving assembly 44 is in the second position solves the 5 problem(s) noted above. That is, the first cooperative cam surface dwell portion 360’ solves the problem(s) noted above. Moreover, because the moving assembly 44 dwells in the second position (and in the first position, as discussed below) prior to reversing the direction of the motion, the moving assembly 44 is not subject to “whiplash.” This, in turn, means that the elements of 10 the moving assembly 44 are not subject to elongation as described above. Stated alternately, and as used herein, a ram drive assembly 300 that is structured to, and does, avoid “whiplash” in any element operatively engaged thereby is a “steady state” drive assembly. Similarly, a cam 330, or a cam body 332, that is structured to, and does, avoid “whiplash” in any element that is operatively engaged by the cam 330, or a cam body 332, 15 is a “steady state” cam 330, or cam body 332. This solves the problem(s) noted above. As the cam 330, i.e., cam body 332, continues to rotate, the cooperative cam surface rearward stroke portion 352 engages the first and second cam follower members 156, 158 which causes the moving assembly 44 (including the ram body 122 and the punch 124) to move with a motion generally low in acceleration, pressure angle, and vibrations. This 20 solves the problem(s) noted above. That is, the cooperative cam surface rearward stroke portion 352 solves the problem(s) noted above. As the cam 330, i.e., cam body 332, continues to rotate, the second cooperative cam surface dwell portion 360’’ again engages the first and second cam follower members 156, 158 as the cycle begins again. It is understood that each time the cam body 322 rotates 36025 degrees, i.e., and as used herein, one “cycle” of the bodymaker 10, a forming assembly 16 makes a can body. As noted above in conjunction with Figure 5, one cam follower mounting passage 175 includes an eccentric bushing 187 with the orientation tab 194. The eccentric bushing 187 is structured to, and does, allow the cam follower assembly 150 to move between two30 configurations. That is, when the eccentric bushing 187 is disposed so that the thinner side 188’’ is disposed closer to the mounting assembly body passage 20, the distance between the cam follower members 154 is at a maximum. This is the first configuration of the cam follower assembly 150. In this configuration, the distance between the cam follower members 154 is greater than the radial width W of the cam body ridge 338. Thus, as described below, the forming assembly 16 is able to be moved in a direction generally normal to the plane of the cam body 332 without contacting the cam body ridge 338. That is, when the cam body 332 is disposed so that the plane of the cam body 332 is generally 5 horizontal, and when the cam follower assembly 150 is in the first configuration, the forming assembly 16 is able to be lifted, or lowered (e.g., via a suitable overhead lift mechanism), relative to the cam body 332 without the cam follower assembly 150 contacting, or substantially contacting, the cam body ridge 338. It is understood that when the forming assembly moving assembly cam follower assembly 150 is in the first 10 configuration, the cam follower roller bearing eccentric bushing orientation tab 194 is fixed via any suitable arrangement (e.g., a radial recess). Thus, the eccentric bushing 187 is not able to rotate within the mounting passage 175. Conversely, when the eccentric bushing 187 is disposed so that the thicker side 188’’ is disposed closer to the mounting assembly body passage 20 (such as shown in 15 Figure 5), the distance between the cam follower members 154 is at a minimum. This is the second configuration of the forming assembly moving assembly cam follower assembly 150. In this configuration, the distance between the cam follower members 154 is generally, or substantially, the same as the radial width W of the cam body ridge 338. This is the operational configuration of the cam follower assembly 150. In this configuration, 20 any radial change in the position of the cam body ridge 338, i.e., the associated cooperative cam surfaces 334, 336, or, first cam surface 340 and second cam surface 342, causes the cooperative cam surfaces 334, 336 to operatively engage the cam follower assembly 150. In this configuration, the bodymaker 10 solves the problem(s) stated above. That is, for example, the ram drive assembly 300 is a “direct” ram drive assembly 300, as that 25 term is defined above. That is, the ram drive assembly 300 is structured to, and does, convert a rotational motion (from the motor output shaft 312) to a reciprocal motion (of the ram body 122) without a pivoting construct such as, but not limited to, a swing arm. This solves the problem(s) noted above. It is further noted that a bodymaker 10 as described above with a disk cam 330 has 30 a configuration unlike known bodymakers. As noted above, each ram body 122 has a longitudinal axis L. Further, the cam body 332 axis of rotation is a “prime axis of rotation” for the bodymaker ram drive assembly 300, as that term is defined above. Thus, the cam body 332 axis of rotation is also identified herein as the “ram drive assembly prime axis of rotation 333.” As described above, each ram body longitudinal axis L extends generally radially relative to the ram drive assembly prime axis of rotation 333 (e.g., see Figure 2). That is, the ram body longitudinal axes L are generally disposed in a plane and are radially offset about the ram drive assembly prime axis of rotation 333. In an exemplary embodiment, the forming assemblies 16 are generally evenly disposed about the ram drive assembly prime axis of rotation 333. That is, for “N” number of forming assemblies 16, the forming assemblies 16 are disposed about 360°/N degrees apart. In an exemplary embodiment, there are two or more forming assemblies 16 disposed about the ram drive assembly prime axis of rotation 333. That is, in an exemplar) '’ embodiment, the number of forming assemblies 16 includes between two and ten forming assemblies 16. Further, in an exemplary embodiment, the number of forming assemblies 16 includes one of two forming assemblies 16, four forming assemblies 16, six forming assemblies 16, eight forming assemblies 16 or ten forming assemblies 16.
Further, in an exemplary embodiment, when there is an even number of forming assemblies 16, each forming assembly 16 may be disposed generally in opposition to another forming assembly 16 across the ram drive assembly prime axis of rotation 333 (i.e., positioned generally 180° about the prime axis 333). However, it is to be appreciated that the drive arrangements as described herein allow' for the forming assemblies 16 to be positioned in other configurations that are not in opposition to each other across the ram drive assembly prime axis of rotation 333 (i.e., positioned other than 180° with respect to each other). For example, in one exemplary embodiment, a bodymaker 10 includes only two forming assemblies 16 positioned only 45° apart about the prime axis 333, In another example, a bodymaker 10 includes only two forming assemblies 16 positioned only 36° apart about the prime axis 333, Further, it is to be appreciated that the angular spacing between adjacent forming assemblies 16 of a bodymaker 10 may differ among pairs of forming assemblies 16 within the bodymaker 10. As an example, without limitation, a bodymaker 10 having three forming assemblies 16 may have two of the forming assemblies 16 positioned 90° apart about the prime axis 333, with the third forming assembly spaced 135° about the prime axis 333 relative to each of the other two forming assemblies 16. In any of these configurations, the ram drive assembly 300 is a “single source/[X} -output ram drive assembly,” as that term is defined above. That is, for example, if the forming system 12 includes three forming assemblies 16, the ram drive assembly 300 is a single source/3 - output ram drive assembly. Thus, for a forming system 12 including one of four, five, six, seven, eight, nine or ten forming assemblies 16, the ram drive assembly 300 is a single source/4-output ram drive assembly, a single source/5-output ram drive assembly, a single source/6-output ram drive assembly, a single source/7-output ram drive assembly, a single source/8-output ram drive assembly, a single source/9-output ram drive assembly, a single 5 source/10-output ram drive assembly, respectively. An embodiment with eight forming assemblies 16 is shown in Figure 13. In an exemplary embodiment, the forming system 12 includes four forming assemblies 16. As shown in Figure 2, the four forming assemblies 16 are disposed about, or substantially, ninety degrees apart about the prime axis 333 of the ram drive assembly 10 300. Further, in this configuration, the forming assemblies 16 are “asymmetrical forming assemblies.” That is, in this configuration, the forming elements do not move substantially in opposition to each other. In an embodiment such as shown in Figure 11 wherein the bodymaker is a barrel cam 330B, the axis of rotation of the cam body 332B defines a prime axis of rotation 333B. 15 In this embodiment, however, the longitudinal axis L of each ram body 122 extends generally parallel to the prime axis of rotation 333B of the barrel cam 330B. Another aspect of the motion of the ram assembly 120, i.e., the ram body 122, caused by operative engagement by a cam 330 of a ram drive assembly 300 as described above is that no two ram bodies are in the same “medial position” at one time. That is, for20 example, no two ram bodies 122 are disposed with the punch 124 entering the die pack 56 associated therewith at the same time. It is noted, however, that two ram bodies 122 are, in certain configurations, disposed with the punch 124 in die pack 56 associated therewith at the same time. That is, for example, the forming system 12 with the cam 330 in a specific orientation may have one ram body 122 with the punch 124 at the upstream end of the die 25 pack 56 associated therewith while another ram body 122 has the punch 124 disposed at the downstream end of the die pack 56 associated therewith. When the forming assemblies 16 are “asymmetrical forming assemblies,” the power needed, i.e., the size/power of the motor 310 is reduced because no ram assemblies 120 are disposed at the same time in a location that generates the maximum resistance. This solves the problem(s) noted above. 30 Further, the bodymaker 10, i.e., the ram drive assembly 300, as described above is structured to, and selectively does, operate with less than the full set of forming assemblies. That is, the bodymaker 10 as described above has a number of forming assemblies 16. Whatever the maximum number of forming assemblies 16 associated with a specific bodymaker 10 is, as used herein, a “full set” of forming assemblies 16. For example, in an embodiment wherein the maximum number of forming assemblies 16 is four, the “full set” of forming assemblies 16 means four forming assemblies 16. Unlike prior art bodymakers which needed to balance the loads created by the 5 forming assemblies 16, the present bodymaker 10 is structured to, and, when required, does, operate with less than a “full set” of forming assemblies 16. For example, in an embodiment wherein the “full set” of forming assemblies 16 means four forming assemblies 16, the bodymaker 10, i.e., the ram drive assembly 300, is structured to, and does, operate with three, two, or one forming assemblies 16. This solves the problem(s) 10 noted above. Stated alternately, the bodymaker 10 is structured to, and when required does, operate with fewer than all forming assemblies operatively coupled to the drive assembly. That is, unlike a prior art bodymaker having two forming assemblies coupled to a crank, the use of a cam 330 eliminates the need for the drive assembly to be balanced. Thus, for 15 example, if one of four forming assemblies 16 needs repaired, the defective forming assembly 16 is disengaged from the drive assembly 300 and then the remaining three forming assemblies 16 are put back into operation. As used herein, a bodymaker drive assembly 300 that is structured to operate with less than all forming assemblies 16 engaged thereby is a “limited load” drive assembly 300. Use of a limited load drive assembly 300 20 solves the problem(s) noted above. In an exemplary embodiment, such as shown in Figures 3, 4 and 6, the mounting assembly 14 further includes a number of forming assembly positioning assemblies 400. There is one positioning assembly 400 associated with each forming assembly 16. When the mounting assembly body 18 is disposed in a generally horizontal plane, each25 positioning assembly 400 is substantially disposed below the mounting assembly body 18. Each forming assembly positioning assembly 400 is structured to, and does, move (and in this configuration lift/lower) a forming assembly 16. That is, each forming assembly positioning assembly 400 is structured to, and does, move a forming assembly 16 among a first (non-operational) position, such as shown in Figure 6, wherein the forming assembly 30 16 is spaced from an associated mounting assembly planar body upper surface recess 34 (i.e., is above an associated mounting assembly planar body upper surface recess 34), and a second (operational) position such as shown in Figure 4, wherein the forming assembly 16 is disposed within an associated mounting assembly planar body upper surface recess 34. In the illustrated exemplary embodiment, each positioning assembly 400 includes a fluid pressure source 402 and a number of actuators 404 coupled thereto via fluid conduits 5 406. The fluid pressure source 402 may be any suitable source of pneumatic or hydraulic pressure (e.g., without limitation an air compressor, an hydraulic pump, a supply line from a remote pressure source, etc.). Each actuator may be a suitable pneumatic or hydraulic actuator coupled to the corresponding suitable pressure source via flexible or rigid conduits 406. Control of movement of each actuator 404 may be provided via any suitable control 10 arrangement (not numbered). Alternatively, each positioning assembly may utilize electric actuators powered by a suitable source of electrical power and controlled by a suitable controller. Additionally, each positioning assembly 400 may include one or more suitable locking mechanisms (not numbered, e.g., mechanical and/or electromagnetic arrangements) for securing each forming assembly 16 to mounting assembly 14. 15 It is to be understood that, when a forming assembly 16 is being moved between the first and second positions, and when the forming assembly 16 is in the first (non- operational) position, the cam follower assembly 150 is in the first (widely spaced) configuration previously discussed. Further, when the forming assembly 16 is in the second (operational) position, the cam follower assembly 150 is in the second (closely spaced)20 configuration previously discussed. When the mounting assembly planar body upper surface recesses 34 are “machined” recesses 34, each forming assembly 16 is automatically positioned as the forming assembly 16 is moved into the machined mounting assembly planar body upper surface recess 34. Alternatively, after a forming assembly 16 is disposed in a mounting 25 assembly planar body upper surface recess 34, a user brings the forming assembly 16 into the proper alignment by passing guide pins 39 through the associated guide pin passages 36, 68. Further, a guide pin 39 is temporarily disposed in the alignment pin passage 178 of the slider 152 of the cam follower assembly 150 and the alignment passage 344 of the cam 330. Use of the guide pins 39 brings each forming assembly 16 into proper alignment with 30 the cam 330. It is again noted that each forming assembly 16 is, in an exemplary embodiment, an aligned, unitary forming assembly 16; thus, the elements with each forming assembly 16 do not require further alignment. This solves the problem(s) noted above. In one embodiment, the bodymaker 10 includes a single forming assembly 16. In another embodiment, the bodymaker 10 includes a plurality of forming assemblies 16. In another embodiment, the bodymaker 10 includes an even number of forming assemblies 16. Thus, in an exemplary embodiment, the number of forming assemblies includes one of 5 a single forming assembly 16, two forming assemblies 16, four forming assemblies 16, six forming assemblies 16, eight forming assemblies 16 or ten forming assemblies 16. Further, and as described above, with forming assemblies 16 disposed about the cam body 332 axis of rotation, the longitudinal axes of the forming assemblies 16 extend generally, or substantially, radially relative to the cam 320 axis of rotation. 10 Further, in a configuration disclosed above wherein the bodymaker 10 includes more than two forming assemblies 16, the bodymaker 10 produces more than two can bodies per cycle. This solves the problem(s) noted above. That is, for example, in an embodiment with four forming assemblies 16, the bodymaker 10 produces four can bodies per cycle. Moreover, with a cam 330 rotating at 320 r.p.m., the bodymaker 10 with four 15 forming assemblies 16, or alternately, the forming system 12 with four forming assemblies 16, produces one of a large number of can bodies per minute, a very large number of can bodies per minute, or an exceedingly large number of can bodies per minute. As used herein, a “large” number of can bodies per minute means more than 1,280 can bodies per minute. As used herein, a “very large” number of can bodies per minute means more than 20 1,440 can bodies per minute. As used herein, an “exceedingly large” number of can bodies per minute means more than 1,600 can bodies per minute. A bodymaker 10 that produces any of a large number of can bodies per minute, a very large number of can bodies per minute, or an exceedingly large number of can bodies per minute solves the problem(s) noted above. 25 Further, the can bodymaker 10 as described above occupies a “reduced” floor space as compared to conventional bodymakers. As used herein, the term “floor space” includes the space bound by the perimeter of the elements extending from the bodymaker. For example, Figure 13 shows an overhead view of a layout of a bodymaker 10’ in accordance with an exemplary embodiment of the disclosed concept having eight forming assemblies 30 16 and related machinery (e.g., trimmers). Such layout occupies/requires a floor space having dimensions of about D1’ x D2’. In such example both D1’ and D2’ are 366 inches. Hence, the overall floor space occupied/required by such layout is 133,956 in 2 or about 930 ft 2 . In comparison, Figure 14 shows a layout of eight prior art bodymakers 1 (i.e., the number of prior art bodymakers 1 needed to achieve the same or similar output as bodymaker 10’ of Figure 13) and related machinery. Such layout occupies/requires a floor space having dimensions of about D1 x D2. In such example D1 is 885.5 inches and D2 is 432 inches. Hence, the overall floor space occupied/required by such layout is 382,536 in 2 5 or about 2,656 ft 2 , almost three times the floor space as the bodymaker 10’ in accordance with the disclosed concept. As a bodymaker in accordance with the disclosed concept provides for similar output while requiring a lesser or “reduced” floor space such bodymaker occupies a “reduced” floor space as compared to conventional bodymakers. In addition to saving floor space, it is to be appreciated that bodymakers in 10 accordance with the disclosed concept require less energy to produce an equivalent amount of can bodies as compared to conventional arrangements. As an example, a conventional single head bodymaker requires a 75 HP motor. A recently released two head unit also requires 75 HP, and a four head unit requires 300 HP. In stark contrast, a four head (i.e., four forming assembly 16) bodymaker in accordance with the disclosed concept requires 15 only a single 30 HP hp motor. Hence for the same can body output, a bodymaker in accordance with the disclosed concept provides significant energy savings. Further, conventional bodymakers require flywheels of considerable mass to supply the energy needed to form a can due to their forming/drive arrangement(s). In contrast, bodymakers in accordance with the disclosed concept do not require such flywheels because of the low 20 mass of the forming assembly as well as the profile available due to the use of the disk cam (i.e., zero acceleration portions at the end of the strokes and, consequently, zero inertia forces and deformations). While specific embodiments of the invention have been described in detail, it will be appreciated by those skilled in the art that various modifications and alternatives to those 25 details could be developed in light of the overall teachings of the disclosure. Accordingly, the particular arrangements disclosed are meant to be illustrative only and not limiting as to the scope of invention which is to be given the full breadth of the claims appended and any and all equivalents thereof.
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