US20220241839A1 - Cam driven multi-output bodymaker - Google Patents
Cam driven multi-output bodymaker Download PDFInfo
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- US20220241839A1 US20220241839A1 US17/726,874 US202217726874A US2022241839A1 US 20220241839 A1 US20220241839 A1 US 20220241839A1 US 202217726874 A US202217726874 A US 202217726874A US 2022241839 A1 US2022241839 A1 US 2022241839A1
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- assembly
- ram
- forming
- cam
- bodymaker
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D51/00—Making hollow objects
- B21D51/16—Making hollow objects characterised by the use of the objects
- B21D51/26—Making hollow objects characterised by the use of the objects cans or tins; Closing same in a permanent manner
- B21D51/2692—Manipulating, e.g. feeding and positioning devices; Control systems
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D51/00—Making hollow objects
- B21D51/16—Making hollow objects characterised by the use of the objects
- B21D51/26—Making hollow objects characterised by the use of the objects cans or tins; Closing same in a permanent manner
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
- B21D22/20—Deep-drawing
- B21D22/28—Deep-drawing of cylindrical articles using consecutive dies
Abstract
A can bodymaker includes a mounting assembly and a forming system. The forming system includes a plurality of forming assemblies, each forming assembly coupled to the mounting assembly, each forming assembly including a ram assembly with an elongated ram body, and a ram drive assembly operatively coupled to each forming assembly. The ram drive assembly is a direct ram drive assembly.
Description
- This application is a continuation of, and claims priority under 35 U.S.C. § 120 from, U.S. patent application Ser. No. 16/885,494, filed May 28, 2020, entitled “CAM DRIVEN MULTI-OUTPUT BODYMAKER”, the contents of which are incorporated herein by reference.
- The disclosed and claimed concept relates to a can bodymaker and, more specifically, to a can bodymaker including multiple forming assemblies that have a centralized ram drive assembly.
- Generally, an aluminum can begins as a disk of aluminum, also known as a “blank,” that is punched from a sheet or coil of aluminum. That is, the sheet is fed into a press where a “blank” disk is cut from the sheet by an outer slide/ram motion. An inner slide/ram then pushes the “blank” through a draw process to create a cup. The cup has a bottom and a depending sidewall. The cup is fed into a bodymaker which further performs a redraw and ironing operation that forms the cup into a can body. That is, the bodymaker includes a punch disposed on an elongated, reciprocating ram assembly. The cup is positioned in front of the punch which then moves the cup through a die pack wherein the radius of the cup is reduced and the depending sidewall is elongated and thinned.
- More specifically, the cup is disposed at the mouth of a die pack having multiple dies defining passages. The cup is held in place by a redraw sleeve, which is part of a redraw assembly. As the punch/ram engages the cup, the cup is moved through a passage in a redraw die. The cup is then moved through a number of ironing dies. That is, the ironing dies are disposed behind, and axially aligned with, the redraw die. At the end of the die pack opposite the ram is a domer. The domer is a die structured to form a concave dome in the bottom of the cup/can body.
- Generally, and as shown in
FIG. 1 , abodymaker 1 includes a drive assembly 2 and a forming assembly 3. The drive assembly 2 includes a motor (not shown) that is operatively coupled to a rotating crank 4 having a flywheel (not numbered) coupled thereto of considerable mass for storing kinetic energy for metal forming such that the motor does not have to supply variable energy. The crank 4 is further coupled to a pivotingswing arm 5 by a first connecting rod 6A. Theswing arm 5 is coupled, via a second connecting rod 6B, to a ram assembly 7. That is, the forming assembly 3 includes the ram assembly 7, a die pack 8 and a domer 9. The ram assembly 7 includes acarriage 7A and an elongated ram (or ram body) 7B and, in some embodiments, a punch 7C disposed at the distal end of the ram body 7B from the second connecting rod 6B. The die pack 8 includes a number of ironing dies (not numbered) which define a forming passage (not numbered). The ram body 7B/punch 7C is structured to, and does, reciprocate through the die pack 8. That is, the ram body 7B/punch 7C moves between a first position, wherein the ram body 7B/punch 7C is withdrawn from the die pack 8 (i.e., shifted to the right inFIG. 1 ), and a second position, wherein the ram body 7B/punch 7C extends through the die pack 8 to a position adjacent the domer 9 (i.e., shifted to the left inFIG. 1 ). As is known, a cup feeder, not numbered, positions a cup at the mouth, or upstream end, of the die pack 8 when the ram body 7B is in the first position. Thus, as the ram body 7B moves toward the second position, the ram body 7B/punch 7C moves the cup through the die pack 8 where it is formed into a can body. The use of a crank, a swing arm, and/or pivoting connecting rods in a bodymaker drive assembly is a problem. That is, there are many disadvantages associated with a crank/swing arm drive assembly in a bodymaker as discussed below. - For example, in this configuration, the circular motion of the crank 4 is converted into a reciprocal motion in the ram body 7B and punch 7C. The crank 4 rotates at speeds of about 320 r.p.m. to 400 r.p.m. and the ram body 7B/punch 7C reciprocates once during each cycle. A can body is formed during each cycle; thus, the
bodymaker 1 makes about 320 to 400 cans per minute. That is, for each cycle of the drive assembly 2, i.e., each time the crank 4 rotates three hundred and sixty degrees (360°), thebodymaker 1 makes one can body. Alternatively, in an embodiment wherein the crank 4 drives two ram bodies 7B, thebodymaker 1 makes two can bodies during each cycle. As it is desirable to produce as many can bodies per minute as possible, the number of can bodies made per cycle is a problem. That is, it is desirable to have a bodymaker operating with a higher, or greater, output. - Operating at a higher speed, however, is difficult due to the limitations and characteristics of the elements of the bodymaker. For example, the ram and punch are made of metal, typically steel, and have a considerable mass. The drive assembly must be structured to move the mass of the ram and punch and to resist the forces generated by the moving ram and punch. Thus, as discussed above, the drive assembly is also, typically, made of metal/steel and, as such, also has a considerable mass. Further, the elements of the drive assembly are substantially rigid and coupled to each other at rotational and pivotal couplings. At this speed, and in this configuration, there are a number of detrimental effects on elements of the bodymaker drive assembly 2. That is, this configuration includes rigid, elongated elements (which include the
swing arm 5, connecting rods 6A, 6B and ram body 7B) which are operatively engaged by a rotating element (i.e., the crank 4 and flywheel). As the rotational motion of the crank 4 is converted into the reciprocating motion of the ram body 7B, the rigid elements move and are either accelerating or decelerating (except for the instant wherein acceleration becomes deceleration). That is, the drive assembly and certain forming assembly elements are, essentially, either accelerating or decelerating and are, essentially, never moving at a constant velocity. This type of motion, i.e., not moving at a constant velocity, causes the distal end of the ram body, including the punch, to vibrate. This is a problem. - Further, a bodymaker in a drive assembly configured as described above, i.e., a crank operatively coupled to a swing arm that is further operatively coupled to a ram assembly, all of the elements are, essentially, in constant motion. That is, with the exception of the instant when the ram assembly reverses direction, the elements operatively coupled to the drive assembly are in constant motion. A bodymaker in this configuration has problems.
- For example, the motion of the elongated elements of the drive assembly and/or the ram assembly is suddenly, or instantly, reversed from a forward motion to a rearward motion. This rapid change in the direction of the motion is, as used herein, “whiplash.” At the forward end of the ram body 7B stroke, this effect causes an undesirable vibration in the ram body 7B which is transferred to the die pack 8. At the rearward end of the ram body 7B stroke, the rapid change in direction causes an undesirable vibration just before the punch 7C engages a cup. Further, at these speeds and with such rapid changes in the motion, the momentum of the various elements and the interaction between elements cause the elongated elements of the drive assembly to deform/elongate. This elongation, in turn, causes the position of the ram assembly 7 relative to the die pack 8 and domer 9 to change. More specifically, the distal end of the ram/punch will, essentially, be positioned beyond the domer. This condition is identified herein as “overstroke.” That is, as used herein, the “overstroke” of the ram/punch means that when the ram is in the second position, the elongation of the ram (and/or other elements) position the distal end of the ram/punch further than is necessary to form the dome in the cup; i.e., the distal end of the ram/punch is positioned too close to the domer, which can damage the ram/punch, domer, and/or result in improperly formed can bodies. To prevent such overstroke and damage resulting therefrom, the positioning of forming arrangements of such prior art arrangements are typically adjusted for the maximum production speed, and thus positioned for the maximum deformations and not properly positioned for operation at lower speeds (and thus lower deformations). Accordingly, in order to avoid potential damage and/or improperly formed can bodies at less than maximum production speeds the flywheels of such arrangements have to be engaged to the forming ram motion mechanisms in no more than two strokes without making cans at speeds no less than 80% of the maximum speed required. Such engagement is rather abrupt and requires a strong clutch. These are problems.
- It is noted that certain forming devices used in the process of making cans and/or can bodies, utilize a cam in the drive assembly. For example, “necker” machines, i.e., machines structured to form necks in can bodies, often utilize a fixed cam disk and rotating forming assemblies. That is, the cam disk is fixed to a housing or other mounting and a plurality of forming assemblies move about the cam. As the forming assemblies move, the forming assemblies engage the cam and the cam drives dies and other forming elements within the forming assemblies. Thus, the cam is static and the forming assemblies are dynamically mounted. That is, the entire forming assembly moves while the internal elements of the forming assemblies move relative to each other. Generally, the mounting assemblies for the forming assemblies are complex and are subject to wear and tear. This is a problem. That is, having a static cam and dynamically mounted forming assemblies is a problem.
- Further, the drive assembly linkage of
FIG. 1 as described above includes at least three rotational couplings that undergo a pivoting motion (connecting rod 6A/swing arm 5,swing arm 5/connecting rod 6B and connecting rod 6B/carriage 7A). These rotational couplings are hereinafter, and as used herein, identified as “pivotal” couplings. When maintenance is required, or when the drive assembly and the forming assembly are being swapped with another drive assembly and forming assembly to form can bodies with different characteristics, technicians must perform multiple decoupling/coupling operations at each rotational/pivotal coupling. The replacement of elements joined by pivotal couplings is a time consuming process. For example, while the drive assembly elements are being replaced, the bodymaker is not operational. As such, a drive assembly 2 that includes pivotal couplings is a problem. - Stated alternately, the drive assembly 2 drive device, i.e., the construct that generates motion (which is the motor in the embodiment described above) is operatively coupled to the ram assembly 7 via a multi-element linkage, i.e., crank 4/
swing arm 5/first connecting rod 6A/second connecting rod 6B. Such a multi-element linkage cannot act as a “direct operative coupling element” between the motor and the ram assembly. This is a problem because as the number of elements increase, the cost, the weight of the drive assembly, and the energy required to operate the drive assembly increase. - Further, when the separate elements of the forming assembly are being installed, the elements must be carefully aligned with each other. For example, the ram must be aligned with the forming passage through the die pack and with the domer. As there are multiple elements in the forming assembly that are completely separate from each other, this process takes a considerable amount of time during which the bodymaker is not operational. This is a problem. That is, a forming assembly wherein the moving elements are not maintained in alignment with the stationary elements of the forming assembly is a problem.
- It is understood that, as the speed of the drive assembly increases, these problems are intensified. Thus, there is a limit as to how many can bodies a bodymaker having such a drive assembly is able to form. One adaptation that allows for additional can bodies to be formed includes a second forming assembly. The second forming assembly includes a ram assembly that moves in opposition to the first forming assembly ram assembly. That is, generally, the crank is operatively coupled to two separate rams. When the first ram assembly is in the first position, the second ram assembly is in the second position, and, when the first ram assembly is in the second position, the second ram assembly is in the first position. Thus, the rams are generally moving in opposition to each other. This configuration effectively doubles the output of the bodymaker. The problem with this configuration is that when one ram assembly needs to be replaced or repaired, both ram assemblies are non-operational. That is, due to balance and similar issues, it is not possible to operate the bodymaker with less than all forming assemblies/ram assemblies coupled to the drive assembly. This is a problem.
- Further, in such a bodymaker with two rams generally moving in opposition to each other, certain actions occur simultaneously, or near simultaneously, such as the reversal in the direction the ram is moving. Thus, both rams experience “whiplash” at the same time. This is a problem because such simultaneous actions generate an undesirable vibration and, moreover, this vibration is more intense than in a bodymaker with a single ram. That is, it is not desirable to have vibration generating actions occur at the same time to different ram bodies. This is a problem.
- Further, when the elements of the drive assembly and/or ram assembly are in constant motion, the length of the ram stroke, i.e., the distance between the first and second positions, must be larger. That is, as described above, prior to being formed in the die pack, a cup must be positioned in front of the ram/punch at the die pack. Generally a cup feeder, or similar device, is structured to start moving a cup into position, i.e., at the mouth of the die pack, as soon as the ram has withdrawn from the die pack. As the ram is in constant motion, the ram must be moving the entire time the cup is being positioned. That is, the ram cannot stop once it is retracted from the die pack. Thus, the ram stroke length must have a sufficient length so that there is enough time for a cup to be placed at the mouth of the die pack prior to the ram moving forward to engage the cup and move the cup through the die pack. Thus, the stroke length is a problem.
- For a 12 ounce standard beverage can body, the ram assembly travels over a distance of nineteen inches to twenty-four inches or sometimes more. That is, for example, the distal end of the ram body 7B moves a distance of nineteen inches to twenty-four inches or more as the ram body 7B moves from the retracted, first position to the extended, second position; the distance the ram moves is, as used herein, the “stroke length.” The longer the stroke length, the larger/longer the elements of the drive assembly must be. Larger/longer elements require more energy to move. This is a problem. Smaller/shorter elements are desirable. That is, smaller/shorter elements generate a shorter stroke length and have a reduced weight. Elements that have a reduced weight require less energy to operate. Thus, a bodymaker with a shorter stroke length is desirable and would solve these problems.
- There is, therefore, a need for a bodymaker drive assembly that does not include either a crank, a swing arm, and/or pivoting connecting rods. There is a further need for a bodymaker that is structured to produce 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. There is a further need for a bodymaker drive assembly wherein the drive assembly imparts a motion to the forming assembly wherein at least some of the motion is at a constant velocity. There is a further need for a bodymaker drive assembly that does not create a sudden, or instant, change in the direction of the movable forming assembly elements, i.e., a bodymaker drive assembly that is structured to cause the movable forming assembly elements to dwell prior to changing directions. There is a further need for a bodymaker drive assembly that does not include pivotal couplings. There is a further need for a bodymaker with a unified forming assembly. There is a further need for a bodymaker having a plurality of forming assemblies wherein, if less than all of the forming assemblies are engaged, the bodymaker is still operational. There is a further need for a bodymaker drive assembly having a reduced stroke length.
- Another manner of increasing the output of the bodymaker is to include multiple rams that are driven by a single drive assembly. That is, certain bodymakers include multiple drive assemblies wherein each drive assembly is associated with an independent ram. These are, essentially, independent bodymakers that have separate drive assemblies linked together. This is done so that the timing of the coupled bodymakers can be controlled. Bodymakers in this configuration do not include multiple rams that are driven by a single drive assembly. Other bodymakers, however, have a single drive assembly that is structured to, and does, drive multiple rams.
- For example, U.S. Pat. No. 9,162,274 discloses a double-action bodymaker having a single motor that is coupled to a crank having offset journals which are further coupled to two separate rams. The two rams move in opposition, and in opposite directions, relative to each other. More specifically, when compared to the bodymaker described above, the double-action bodymaker includes a single motor, a single crank (with two journals), two swing levers and two rams. The rams extend in generally opposite directions and move in opposition to each other. That is, when one ram is in the first position, the second ram is in the second position. Moreover, a bodymaker in this configuration includes two pivoting elements, i.e., the swing levers.
- As an alternate example, U.S. Pat. No. 10,343,208 discloses a vertical bodymaker having a single motor that is coupled, via a single crank with offset journals, to two separate ram assemblies. The rams move in opposition, but in the same direction, relative to each other. More specifically, when compared to the bodymaker described above, the vertical bodymaker includes a single motor, a single crank (with two journals), two connecting rods and two ram assemblies. U.S. Pat. No. 10,343,208 notes that the bodymaker, in an embodiment that is not shown, includes more than two ram assemblies. In this configuration there would be, for example, two synchronized ram assemblies moving toward the second position at the same time, and two synchronized ram assemblies moving toward the first position at the same time. That is, the pairs of ram assemblies move in opposition to each other.
- As another alternate example, U.S. Pat. No. 7,882,721 discloses a bodymaker having a single motor coupled to a gearbox having a crank arm that is operatively coupled to two ram assemblies. In this configuration, the two rams move in opposition, and in opposite directions, relative to each other.
- The swing levers in U.S. Pat. No. 9,162,274 and the connecting rods in U.S. Pat. No. 10,343,208 are substantially similar to the “
swing arm 5” ofFIG. 1 , described above. That is, the combination of the crank and the “swing arm 5,” and/or the similar elements noted above, are the constructs that convert the rotational motion of the motor output shaft to a reciprocal motion in the rams. It is understood that guides and other constructs control, or limit, the path over which the ram travels, but the crank/swing arms (or similar constructs) are the elements that convert the rotational motion of the motor output shaft to a reciprocal motion in the rams. Similarly, the gearbox of U.S. Pat. No. 7,882,721 converts the rotational motion of the motor output shaft to a reciprocal motion in the rams. Such configurations are a problem in that the motor must drive multiple elements so as to convert the rotational motion of the motor output shaft to a reciprocal motion in the ram. That is, the crank/swing arms/gearbox elements are heavy; thus the motor must be more robust, i.e., able to drive heavy elements. Such motors are expensive. Further, the crank/swing arms/gearbox are prone to wear and tear. Thus, a bodymaker with multiple swing arms or a gearbox is more expensive to maintain. These are problems with the prior art. - Further, in such bodymakers, the drive assembly is structured, i.e., balanced, to operate the ram assemblies at the same time. That is, for example, if one of the two ram assemblies is not in operation, the bodymaker cannot be used with one ram assembly as the loads/reactive loads are unbalanced which causes the drive assembly to become inoperable.
- Further, while it is desirable to increase the output of a bodymaker, it is not desirable to increase the floor space required by the bodymaker. That is, for example, a single Standun Bodymaker (manufactured by Stolle Machinery Company, LLC) arrangement, such as generally shown in
FIG. 1 , occupies about 333 square feet. Ostensibly, one could provide a single housing for two such bodymakers and assert that the output has doubled. But it is understood that the floor space required by such a bodymaker would be about double the floor space required by one such bodymaker. This is a problem. That is, increasing the output of a bodymaker while limiting the floor space required by one such bodymaker is a problem. - There is, therefore, a need for a bodymaker with a direct ram drive assembly, i.e., a ram drive assembly that does not include a swing arm or a gearbox. There is a further need for a bodymaker with a ram drive assembly structured to operate wherein no two ram bodies are in the same medial position at one time and/or wherein the forming assemblies are asymmetrical forming assemblies. There is a further need for a bodymaker with a ram drive assembly structured to operate with less than a full set of forming assemblies. That is, there is a further need for a bodymaker with a limited load ram drive. There is a further need for a bodymaker structured to produce 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. There is a further need for such a bodymaker to occupy a reduced floor space. There is a further need for such a bodymaker to have a single source/multiple output ram drive assembly. The bodymaker as described below and variations thereof solve the stated problems.
- These needs, and others, are met by at least one embodiment of the disclosed concept that provides a can bodymaker comprising: a mounting assembly; a forming system including: a plurality of forming assemblies, each forming assembly coupled to the mounting assembly, each forming assembly including a ram assembly with an elongated ram body, and a ram drive assembly operatively coupled to each forming assembly, wherein the ram drive assembly is a direct ram drive assembly.
- Each ram body may have a longitudinal axis; the ram drive assembly may include a prime axis of rotation; and the longitudinal axis of each ram body may extend generally radially outward from the prime axis of rotation of the ram drive assembly.
- The longitudinal axis of each ram body may extend generally perpendicular to the prime axis of rotation of the ram drive assembly.
- The ram drive assembly may include one of a disk cam or a barrel cam; and the disk cam or the barrel cam may be operatively coupled to each forming assembly.
- The plurality of forming assemblies may be between two and ten forming assemblies.
- The ram drive assembly may include a prime axis of rotation, and the plurality of forming assemblies may comprise two forming assemblies positioned relative to each other about the prime axis of rotation of the ram drive assembly at an angle other than 180°.
- The ram drive assembly may include a prime axis of rotation, and the plurality of forming assemblies may comprise two forming assemblies positioned relative to each other about the prime axis of rotation of the ram drive assembly at an angle of 180°.
- The ram drive assembly may include a disk cam structured to rotate about a prime axis of rotation; and the plurality of forming assemblies may include four forming assemblies, each disposed about ninety degrees apart about said ram drive assembly prime axis of rotation.
- The ram drive assembly may be structured to move each ram body between a retracted, first position and an extended, second position as well as a number of medial positions between the first positon and the second position; and no two ram bodies may be in the same medial position at one time.
- The ram drive assembly may be structured to move each ram body between a retracted, first position and an extended, second position as well as a number of medial positions between the first positon and the second position; and no two ram bodies may be in the same medial position at one time.
- The forming assemblies may be asymmetrical forming assemblies.
- Each forming assembly may include a full set of forming assemblies; and the ram drive assembly may be structured to operate with less than the full set of forming assemblies.
- The ram drive assembly may be a limited load drive assembly.
- Each forming assembly may include a stationary assembly and a moving assembly; and the stationary assembly of each forming assembly may be a unified assembly.
- The forming system may be structured to produce 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.
- The ram drive assembly may be one of: a single source/3-output ram drive assembly, 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, or a single source/10-output ram drive assembly.
- The ram drive assembly may include a barrel cam structured to rotate about a prime axis of rotation; and each ram body may have a longitudinal axis extending generally parallel to the prime axis of rotation of the ram drive assembly.
- The ram drive assembly may include a prime axis of rotation, the plurality of forming assemblies may comprise at least three forming assemblies, and the angular spacing about the prime axis of rotation between an adjacent two of the at least three forming assemblies may be different than the angular spacing between another adjacent two of the at least three forming assemblies.
- A full understanding of the disclosed concept can be gained from the following description of the preferred embodiments when read in conjunction with the accompanying drawings in which:
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FIG. 1 is a schematic side elevation view of a prior art bodymaker. -
FIG. 2 is a schematic top view of a bodymaker with four forming assemblies driven by a disk cam in accordance with one example embodiment of the disclosed concept. -
FIG. 3 is a schematic partially-sectional side elevation view of the bodymaker ofFIG. 2 taken along the line identified inFIG. 2 . -
FIG. 4 is a schematic detail cross-sectional side elevation view of a forming assembly of the bodymaker ofFIGS. 2 and 3 , as indicated inFIG. 3 , shown in an operational engaged position with the disk cam. -
FIG. 5 is a schematic detail cross-sectional side elevation view of a cam follower of the bodymaker ofFIGS. 2-4 as indicated inFIG. 4 . -
FIG. 6 is a schematic detail cross-sectional side elevation view of another forming assembly of the bodymaker ofFIGS. 2 and 3 , as indicated inFIG. 3 , shown in a non-operational disengaged position from the disk cam. -
FIG. 7A is a schematic top view of a ram guide assembly in accordance with one example embodiment of the disclosed concept shown with a portion removed to show details below.FIG. 7B is a schematic cross-sectional side elevation view of the ram guide assembly ofFIG. 7A as indicated inFIG. 7A .FIG. 7C is a schematic cross-sectional elevation view of the ram guide assembly ofFIGS. 7A and 7B as indicated inFIG. 7A .FIG. 7D is a schematic perspective view of a portion of the cam follower of the ram guide assembly ofFIGS. 7A-7C . -
FIG. 8A is a schematic top view of a redraw assembly in accordance with one example embodiment of the disclosed concept.FIG. 8B is a schematic sectional view of the redraw assembly ofFIG. 8A as indicated inFIG. 8A .FIG. 8C is a schematic sectional view of the redraw assembly ofFIGS. 8A and 8B as indicated inFIG. 8B . -
FIG. 9A is a schematic top view of a redraw assembly in accordance with one example embodiment of the disclosed concept.FIG. 9B is a schematic sectional view of the redraw assembly ofFIG. 9A as indicated inFIG. 9A .FIG. 9C is a schematic sectional view of the redraw assembly ofFIGS. 9A and 9B as indicated inFIG. 9B . -
FIG. 10 is a schematic top view of a bodymaker with two forming assemblies driven by a barrel cam in accordance with one example embodiment of the disclosed concept. -
FIG. 11 is a schematic partially-sectional side elevation view of the bodymaker ofFIG. 10 taken along the line indicated inFIG. 10 . -
FIG. 12 is a schematic top view of a cam in accordance with one example embodiment of the disclosed concept.FIG. 12A is a graph showing the displacement of a punch during a stroke associated with the cam ofFIG. 12 .FIG. 12B is a graph showing the velocity of a punch during a stroke associated with the cam ofFIG. 12 . -
FIG. 12C is a graph showing the acceleration of a punch during a stroke associated with the cam ofFIG. 12 . -
FIG. 13 is a schematic top view of a bodymaker with eight forming assemblies and related machinery in accordance with one example embodiment of the disclosed concept. -
FIG. 14 is a schematic top view of eight prior art bodymakers and related machinery arranged in a known manner and required spacing. - It will be appreciated that the specific elements and embodiments illustrated in the figures herein and described in the following specification are simply exemplary embodiments of the disclosed concept, which are provided as non-limiting examples solely for the purpose of illustration. Therefore, specific dimensions, orientations, assembly, number of components used, embodiment configurations and other physical characteristics related to the embodiments disclosed herein are not to be considered limiting on the scope of the disclosed concept.
- Directional phrases used herein, such as, for example, clockwise, counterclockwise, left, right, top, bottom, upwards, downwards and derivatives thereof, relate to the orientation of the elements shown in the drawings and are not limiting upon the claims unless expressly recited therein.
- As used herein, the singular form of “a,” “an,” and “the” include plural references unless the context clearly dictates otherwise.
- As used herein, “movably coupled” means that two elements are coupled in a manner such that at least some movement of one or both of the elements with respect to the other element is permitted without uncoupling the elements. For example, a door is “movably coupled” to a door frame by one or more hinges.
- As used herein, “selectively coupled” means that two or more elements are coupled in a manner which may be readily undone without causing damage to either of such elements. For example, two elements that are bolted or screwed together are “selectively coupled”, while two elements that are glued or welded together are not “selectively coupled” as used herein.
- As used herein, “structured to [verb]” means that the identified element or assembly has a structure that is shaped, sized, disposed, coupled and/or configured to perform the identified verb. For example, a member that is “structured to move” is movably coupled to another element and includes elements that cause the member to move or the member is otherwise configured to move in response to other elements or assemblies. As such, as used herein, “structured to [verb]” recites structure and not function. Further, as used herein, “structured to [verb]” means that the identified element or assembly is intended to, and is designed to, perform the identified verb. Thus, an element that is merely capable of performing the identified verb but which is not intended to, and is not designed to, perform the identified verb is not “structured to [verb].”
- As used herein, in a term such as, but not limited to, “[X] structured to [verb] [Y],” the “[Y]” is not a recited element. Rather, “[Y]” further defines the structure of “[X].” That is, assume in the following two examples “[X]” is “a mounting” and the [verb] is “support.” In a first example, the full term is “a mounting structured to support a flying bird.” That is, in this example, “[Y]” is “a flying bird.” It is known that flying birds, as opposed to swimming birds or walking birds, typically grasp a branch for support. Thus, for a mounting, i.e., “[X],” to be “structured” to support a bird, the mounting is shaped and sized to be something a bird is able to grasp similar to a branch. This does not mean, however, that the bird is a recited element. In a second example, “[Y]” is a house; that is the second exemplary term is “a mounting structured to support a house.” In this example, the mounting is structured as a foundation as it is well known that houses are supported by foundations. As before, the house is not a recited element, but rather defines the shape, size, and configuration of the mounting, i.e., the shape, size, and configuration of “[X]” in the term “[X] structured to [verb] [Y].”
- As used herein, “associated” means that the elements are part of the same assembly and/or operate together, or, act upon/with each other in some manner. For example, an automobile has four tires and four hubcaps. While all the elements are coupled as part of the automobile, it is understood that each hubcap is “associated” with a specific tire.
- As used herein, a “coupling assembly” includes two or more couplings or coupling components. The components of a coupling or coupling assembly are generally not part of the same element or other component. As such, the components of a “coupling assembly” may not be described at the same time in the following description.
- Further, as used herein, a “cooperative coupling” or a “cooperative coupling assembly” includes two or more couplings or coupling components. The components of a cooperative coupling assembly are generally not part of the same element or other component. As such, the components of a “cooperative coupling assembly” may not be described at the same time in the following description. “Cooperative coupling assemblies” include, but are not limited to, (1) a combination of a nut, a bolt and passages in other elements through which the bolt extends, (2) a screw/rivet and passages in other elements through which the screw/rivet extend, and (3) tongue-and-groove assemblies.
- As used herein, a “unilateral coupling” or a “unilateral coupling assembly” means a construct that is structured to be coupled to another element or assembly wherein the other element or assembly is not structured to be coupled to the “unilateral coupling.” “Unilateral coupling assemblies” include, but are not limited to clamps, tension members (e.g., a rope), and adhesive constructs. Further, it is understood that the nature of such constructs as a “unilateral coupling assembly” depend upon the other element to which the coupling assembly is coupled. That is, for example, reins on a horse are a “unilateral coupling” when coupled to a tree because the tree is not a construct that is structured to be coupled to the reins. Conversely, reins on a horse are a “cooperative coupling” when coupled to a hitching post because a hitching post is a construct that is structured to be coupled to the reins.
- As used herein, a “coupling” or “coupling component(s)” is one or more component(s) of a “coupling assembly,” i.e., either a “cooperative coupling” or a “unilateral coupling.” That is, a cooperative coupling assembly includes at least two components that are structured to be coupled together. It is understood that the components of a cooperative coupling assembly are compatible with each other. For example, in a cooperative coupling assembly, if one coupling component is a snap socket, the other cooperative coupling component is a snap plug, or, if one cooperative coupling component is a bolt, then the other cooperative coupling component is a nut (as well as an opening through which the bolt extends) or threaded bore. In a “unilateral coupling,” the “coupling” or “coupling component” is the construct that is structured to be coupled to another construct. For example, given a rope with a loop formed thereon, the loop in the rope is the “coupling” or “coupling component.”
- As used herein, a “fastener” is a separate component structured to couple two or more elements. Thus, for example, a bolt is a “fastener” but a tongue-and-groove coupling is not a “fastener.” That is, the tongue-and-groove elements are part of the elements being coupled and are not a separate component.
- As used herein, the statement that two or more parts or components are “coupled” shall mean that the parts are joined or operate together either directly or indirectly, i.e., through one or more intermediate parts or components, so long as a link occurs. As used herein, “directly coupled” means that two elements are directly in contact with each other. As used herein, “fixedly coupled” or “fixed” means that two components are coupled so as to move as one while maintaining a constant orientation relative to each other. Accordingly, when two elements are coupled, all portions of those elements are coupled. A description, however, of a specific portion of a first element being coupled to a second element, e.g., an axle first end being coupled to a first wheel, means that the specific portion of the first element is disposed closer to the second element than the other portions thereof. Further, an object resting on another object held in place only by gravity is not “coupled” to the lower object unless the upper object is otherwise maintained substantially in place. That is, for example, a book on a table is not coupled thereto, but a book glued to a table is coupled thereto.
- As used herein, the phrase “removably coupled” or “temporarily coupled” means that one component is coupled with another component in an essentially temporary manner. That is, the two components are coupled in such a way that the joining or separation of the components is easy and would not damage the components. For example, two components secured to each other with a limited number of readily accessible fasteners, i.e., fasteners that are not difficult to access, are “removably coupled” whereas two components that are welded together or joined by difficult to access fasteners are not “removably coupled.” A “difficult to access fastener” is one that requires the removal of one or more other components prior to accessing the fastener wherein the “other component” is not an access device such as, but not limited to, a door.
- As used herein, “temporarily disposed” means that a first element(s) or assembly (ies) is(are) resting on a second element(s) or assembly(ies) in a manner that allows the first element/assembly to be moved without having to decouple or otherwise manipulate the first element. For example, a book simply resting on a table, i.e., the book is not glued or fastened to the table, is “temporarily disposed” on the table.
- As used herein, “operatively coupled” means that a number of elements or assemblies, each of which is movable between a first position and a second position, or a first configuration and a second configuration, are coupled so that as the first element moves from one position/configuration to the other, the second element moves between positions/configurations as well. It is noted that a first element may be “operatively coupled” to another without the opposite being true. With regard to electronic devices, a first electronic device is “operatively coupled” to a second electronic device when the first electronic device is structured to, and does, send a signal or current to the second electronic device causing the second electronic device to actuate or otherwise become powered or active.
- As used herein, the statement that two or more parts or components “engage” one another means that the elements exert a force or bias against one another either directly or through one or more intermediate elements or components. Further, as used herein with regard to moving parts, a moving part may “engage” another element during the motion from one position to another and/or may “engage” another element once in the described position. Thus, it is understood that the statements, “when element A moves to element A first position, element A engages element B,” and “when element A is in element A first position, element A engages element B” are equivalent statements and mean that element A either engages element B while moving to element A first position and/or element A engages element B while in element A first position.
- As used herein, “operatively engage” means “engage and move.” That is, “operatively engage” when used in relation to a first component that is structured to move a movable or rotatable second component means that the first component applies a force sufficient to cause the second component to move. For example, a screwdriver may be placed into contact with a screw. When no force is applied to the screwdriver, the screwdriver is merely “temporarily coupled” to the screw. If an axial force is applied to the screwdriver, the screwdriver is pressed against the screw and “engages” the screw. However, when a rotational force is applied to the screwdriver, the screwdriver “operatively engages” the screw and causes the screw to rotate. Further, with electronic components, “operatively engage” means that one component controls another component by a control signal or current.
- As used herein, in the phrase “[x] moves between its first position and second position,” or, “[y] is structured to move [x] between its first position and second position,” “[x]” is the name of an element or assembly. Further, when [x] is an element or assembly that moves between a number of positions, the pronoun “its” means “[x],” i.e., the named element or assembly that precedes the pronoun “its.”
- As used herein, “correspond” indicates that two structural components are sized and shaped to be similar to each other and may be coupled with a minimum amount of friction. Thus, an opening which “corresponds” to a member is sized slightly larger than the member so that the member may pass through the opening with a minimum amount of friction. This definition is modified if the two components are to fit “snugly” together. In that situation, the difference between the size of the components is even smaller whereby the amount of friction increases. If the element defining the opening and/or the component inserted into the opening is made from a deformable or compressible material, the opening may even be slightly smaller than the component being inserted into the opening. With regard to surfaces, shapes, and lines, two, or more, “corresponding” surfaces, shapes, or lines have generally the same size, shape, and contours. With regard to elements/assemblies that are movable or configurable, “corresponding” means that when elements/assemblies are related and that as one element/assembly is moved/reconfigured, then the other element/assembly is also moved/reconfigured in a predetermined manner. For example, a lever including a central fulcrum and elongated board, i.e., a “see-saw” or “teeter-totter,” the board has a first end and a second end. When the board first end is in a raised position, the board second end is in a lowered position. When the board first end is moved to a lowered position, the board second end moves to a “corresponding” raised position. Alternately, a cam shaft in an engine has a first lobe operatively coupled to a first piston. When the first lobe moves to its upward position, the first piston moves to a “corresponding” upper position, and, when the first lobe moves to a lower position, the first piston, moves to a “corresponding” lower position.
- As used herein, a “path of travel” or “path,” when used in association with an element that moves, includes the space an element moves through when in motion. As such, any element that moves inherently has a “path of travel” or “path.” Further, a “path of travel” or “path” relates to a motion of one identifiable construct as a whole relative to another object. For example, assuming a perfectly smooth road, a rotating wheel (an identifiable construct) on an automobile generally does not move relative to the body (another object) of the automobile. That is, the wheel, as a whole, does not change its position relative to, for example, the adjacent fender. Thus, a rotating wheel does not have a “path of travel” or “path” relative to the body of the automobile. Conversely, the air inlet valve on that wheel (an identifiable construct) does have a “path of travel” or “path” relative to the body of the automobile. That is, while the wheel rotates and is in motion, the air inlet valve, as a whole, moves relative to the body of the automobile.
- As used herein, a “planar body” or “planar member” is a generally thin element including opposed, wide, generally parallel surfaces, i.e., the planar surfaces of the planar member, as well as a thinner edge surface extending between the wide parallel surfaces. That is, as used herein, it is inherent that a “planar” element has two opposed planar surfaces with an edge surface extending therebetween. The perimeter, and therefore the edge surface, may include generally straight portions, e.g., as on a rectangular planar member such as on a credit card, or be curved, as on a disk such as on a coin, or have any other shape.
- As used herein, the word “unitary” means a component that is created as a single piece or unit. That is, a component that includes pieces that are created separately and then coupled together as a unit is not a “unitary” component or body.
- As used herein, “unified” means that all the elements of an assembly are disposed in a single location and/or within a single housing, frame or similar construct.
- As used herein, the term “number” shall mean one or an integer greater than one (i.e., a plurality). That is, for example, the phrase “a number of elements” means one element or a plurality of elements. It is specifically noted that the term “a ‘number’ of [X]” includes a single [X].
- As used herein, a “radial side/surface” for a circular or cylindrical body is a side/surface that extends about, or encircles, the center thereof or a height line passing through the center thereof. As used herein, an “axial side/surface” for a circular or cylindrical body is a side that extends in a plane extending generally perpendicular to a height line passing through the center. That is, generally, for a cylindrical soup can, the “radial side/surface” is the generally circular sidewall and the “axial side(s)/surface(s)” are the top and bottom of the soup can. Further, as used herein, “radially extending” means extending in a radial direction or along a radial line. That is, for example, a “radially extending” line extends from the center of the circle or cylinder toward the radial side/surface. Further, as used herein, “axially extending” means extending in the axial direction or along an axial line. That is, for example, an “axially extending” line extends from the bottom of a cylinder toward the top of the cylinder and substantially parallel to, or along, a central longitudinal axis of the cylinder.
- As used herein, a “tension member” is a construct that has a maximum length when exposed to tension, but is otherwise substantially flexible, such as, but not limited to, a chain or a cable.
- As used herein, “generally curvilinear” includes elements having multiple curved portions, combinations of curved portions and planar portions, and a plurality of linear/planar portions or segments disposed at angles relative to each other thereby forming a curve.
- As used herein, an “elongated” element inherently includes a longitudinal axis and/or longitudinal line extending in the direction of the elongation.
- As used herein, “about” in a phrase such as “disposed about [an element, point or axis]” or “extend about [an element, point or axis]” or “[X] degrees about an [an element, point or axis],” means encircle, extend around, or measured around. When used in reference to a measurement or in a similar manner, “about” means “approximately,” i.e., in an approximate range relevant to the measurement as would be understood by one of ordinary skill in the art.
- As used herein, “generally” means “in a general manner” relevant to the term being modified as would be understood by one of ordinary skill in the art.
- As used herein, “substantially” means “by a large amount or degree” relevant to the term being modified as would be understood by one of ordinary skill in the art.
- As used herein, “at” means on and/or near relevant to the term being modified as would be understood by one of ordinary skill in the art.
- As used herein, a “standard beverage can” or “standard beverage can body” means a generally cylindrical, aluminum can body for a twelve ounce beverage such as, but not limited to, soda or beer. A “standard beverage can” includes, but is not limited to, a “202 beverage can” and cans having a similar shape. See, http://www.cancentral.com/beverage-cans/standards.
- As used herein, a “dynamic” element is an element that moves during the formation of a can body. Conversely, a “static” element is an element that does not move during the formation of a can body.
- As used herein, “cooperative” cam surfaces mean two cam surfaces that extend generally parallel to each other and which are structured to be, and/or are, operatively coupled to the same element or assembly. For example, the inner radial surface and the outer radial surface on a generally toroid cam body wherein the two surfaces impart a motion to the same element or assembly are “cooperative” cam surfaces. That is, the inner radial surface and the outer radial surface extend generally parallel to each other. It is understood that the “cooperative” cam surfaces do not necessarily operatively engage the other element or assembly at the same time. That is, when the “cooperative” cam surfaces are defined by a ridge, the “cooperative” cam surfaces do not operatively engage the other element or assembly at the same time. Conversely, when the “cooperative” cam surfaces are defined by a groove, the “cooperative” cam surfaces selectively, operatively engage the other element or assembly at the same time. That is, when the “cooperative” cam surfaces are defined by a groove, the “cooperative” cam surfaces, or portions thereof, are structured to both operatively engage the other element or assembly at the same time, or, are structured to individually operatively engage the other element or assembly at a given time.
- As used herein, a “direct” [ram] drive assembly means a drive assembly for a ram assembly wherein a rotational motion is converted to a reciprocal motion without a pivoting construct such as, but not limited to, a swing arm. Further, a “direct” [ram] drive assembly means a drive assembly for a ram assembly wherein a rotational motion is converted to a reciprocal motion without a gear box structured to convert rotational motion to a reciprocal motion. That is, to be a “direct” drive assembly, the moving elements of the drive assembly either rotate with, or otherwise correspond to the rotation of, a motor output shaft, or, move generally linearly with the ram assembly. As used herein, to “rotate with, or otherwise correspond to the rotation of, a motor output shaft” does not include a reciprocal pivoting motion that corresponds to the rotation of a motor output shaft. As used herein, to “move generally linearly with the ram assembly” means that an element moves over a path that is generally parallel to, or aligned with, the path of the ram assembly. As used herein, a pivoting construct such as, but not limited to, a swing arm cannot “move generally linearly with the ram assembly.”
- As used herein, a “single source/[X]-output ram drive assembly” means that the drive assembly includes a single motor, or similar construct that generates motion, that is operatively coupled to [X] forming assemblies where “[X]” is an integer greater than one. Further, a “single motor” means a single construct or assembly that generates motion and which is the only such construct that is operatively coupled to the forming assemblies. That is, as a counter example, a bodymaker with a drive assembly having two motors disposed in an enclosure wherein each motor is coupled to a ram may be described as having a single “drive assembly” (as the motors are disposed in an enclosure), but the drive assembly is not a “single source/[X]-output ram drive assembly” because neither motor is the “single construct or assembly that generates motion and which is the only such construct that is operatively coupled to the forming assemblies.” Stated alternately, merely coupling multiple motors to a housing or similar construct does not convert the multiple motors into a “single source/[X]-output ram drive assembly.”
- As used herein, a “prime axis of rotation” for a bodymaker ram drive assembly means an axis of rotation of a rotating ram drive assembly element wherein that element is operatively coupled to a plurality of ram assemblies/ram bodies. It is noted that in a bodymaker drive assembly with a crank operatively coupled to two swing arms, and each swing arm coupled to separate connecting rods, and each connecting rod coupled to a separate ram assembly/ram body, the couplings between the connecting rod and a ram assembly/ram body is not a “prime axis of rotation” as the connecting rod is operatively coupled to a single ram assembly/ram body. Further, a “prime axis of rotation” means that the rotating element rotates rather than pivots. That is, for example, a bodymaker crank may have a “prime axis of rotation” but a bodymaker pivoting swing arm can never have a “prime axis of rotation.”
- As noted above, a ram body moves between a retracted, first position and an extended, second position. Further, a ram body moves over a path with a number of medial positions between the first position and the second position. Thus, as used herein, a ram assembly or a ram body in a “medial position” means that the ram assembly or a ram body is disposed at a position between the first position and the second position. Further, a ram assembly or a ram body in a “medial position” means that the ram assembly or the ram body is moving toward either the first position or the second position. The direction the ram assembly or the ram body is moving is, when needed, indicated by the terms “forward” or “rearward.” That is, when the ram body is moving toward the second position and is in a medial position, the ram body is, as used herein, in a “forward” medial position. The term “forward” indicates the direction associated with the ram assembly or a ram body in a medial position. Conversely, when the ram assembly or the ram body is moving toward the first position and is in a medial position, the ram assembly or the ram body is, as used herein, in a “rearward” medial position. That is, the term “rearward” indicates the direction associated with the ram assembly or the ram body in a medial position. As noted, the terms “forward” and “rearward” are used when needed for clarity. Thus, as used herein, the statement that, “no two ram bodies are in the same medial position at one time” includes a configuration wherein two different ram assemblies/ram bodies are at the midpoint between the first and second positions, but wherein the two different ram assemblies/ram bodies are moving in different directions.
- Further, it is understood that, and as used herein, when the ram body is exactly at the first or second position, the ram body is not moving forward or rearward; thus, a ram body at the first or second position does not have an associated direction. Further, a medial “position” is selectively identified by “[X]%” wherein the percentage means the portion of the path between the two end positions. That is, for example, a ram body at the “forward 25%” position means that the ram body is moving toward the second position and has traveled 25%, i.e., one quarter, of the distance between the first and second positon. As a further example, a ram body at the “rearward 50%” position means that the ram body is moving toward the first position and has traveled 50%, i.e., one half, of the distance between the first and second positon. Further, a ram assembly that is in a “forward” medial position is, depending upon the position of the blank/cup, in a “forming” position. That is, as used herein, the “forming” position occurs when the blank/cup is moving through the bodymaker die pack.
- Referring now to
FIGS. 2-6 , a can bodymaker 10 in accordance with one example embodiment of the disclosed concept is shown. Thebodymaker 10 includes a formingsystem 12 and a mountingassembly 14. The formingsystem 12 includes a number of forming assemblies 16 (four are shown in the example ofFIGS. 2-6 , labeled 16A-16D) and aram drive assembly 300. In one exemplary embodiment, thebodymaker 10 and/or each formingassembly 16 is structured to, and does, form standard beverage can bodies. The mountingassembly 14 is structured to, and does, support the number of formingassemblies 16. The mountingassembly 14 is further structured to, and does, rotatably support acam 330, discussed below, of theram drive assembly 300. In one exemplary embodiment, the mountingassembly 14 includes a generally planar mountingassembly body 18. - Referring to
FIG. 3 , the mountingassembly body 18 is oriented to be generally horizontal and includes an upper,first surface 22 and a lower,second surface 24 opposite thefirst surface 30. Further, and for abodymaker 10 including four formingassemblies assembly body 18 is generally square. It is understood that the shape of the mountingassembly body 18 may be varied so long as the mountingassembly body 18 is structured to support the number of formingassemblies 16. In an exemplary embodiment, the mountingassembly body 18 defines a generally centrally disposedpassage 20 that extends between the first andsecond surfaces assembly body 18. - Continuing to refer to
FIG. 3 , in the exemplary embodiment shown, the mountingassembly 14 further includes a number of depending element(s) 26 disposed at the perimeter of the mountingassembly body 18. If there is a single mountingassembly depending element 26 extending about the perimeter of the mountingassembly body 18, the single mountingassembly depending element 26 forms ahousing 28 defining anenclosed space 30 under the mountingassembly body 18. If there are a plurality of relatively thin, spaced separate mountingassembly depending elements 26, the separate mountingassembly depending elements 26 are identified herein as “legs,” similar to table legs. The mounting assembly depending element(s) 26 are structured to, and do, support the mountingassembly body 18 and elements disposed thereon. - Further, in an example embodiment, the
first surface 22 of the mountingassembly body 18 defines a number of recesses 34 (FIGS. 4 and 6 ), eachrecess 34 being for a corresponding formingassembly 16. In an exemplary embodiment, eachrecess 34 is a “machined”recess 34. As used herein, a “machined” recess means a recess having contours structured to specifically position a formingassembly 16 on the mountingassembly body 18, and thus specifically position the formingassembly 16 relative to theram drive assembly 300 and thecam 330. As used herein, “specifically position” means to position a formingassembly 16 relative to theram drive assembly 300 and thecam 330 in a manner wherein further positioning of the formingassembly 16, and/or elements thereof, relative to theram drive assembly 300 is not required. That is, while typically not mentioned in references/patents, it is well known that the position of elements of a formingassembly 16 are adjusted following installation so as to ensure proper alignment of the elements. Thus, unless the lack of adjustment of the forming assembly 16 (or elements thereof) relative to the ram drive assembly 300 (or elements thereof) is specifically mentioned in a reference/patent, then the reference/patent does not disclose a configuration wherein the formingassembly 16, and/or elements thereof, are “specifically position[ed].” That is, unless the lack of adjustment of the formingassembly 16, and/or elements thereof, is specifically mentioned in a reference/patent, then the reference/patent does not disclose a “machined” recess, as used herein. - Further, in another exemplary embodiment, each
recess 34 includes a number, and as shown a plurality, ofguide pin passages 36 defined in, and extending through the mountingassembly body 18. Eachguide pin passage 36 has a cross-sectional area structured to accommodate aguide bushing 37. Eachguide bushing 37 includes atoroid body 38. Eachguide bushing 37 is disposed in acorresponding passage 36. Eachguide bushing 37 is structured to allow aguide pin 39 to be passed therethrough. - The forming
assemblies 16 are substantially similar and as such only one is described in detail herein. As previously mentioned, it is noted that the different formingassemblies 16 shown in the Figures are identified by additional letters. Thus, when there are four formingassemblies 16, such as shown in the example ofFIG. 2 , the separate formingassemblies 16 are identified as formingassemblies assemblies assembly 16 is described as having adie pack 56, the first formingassembly 16A has adie pack 56A and the second forming assembly 16B has adie pack 56B, and so forth. - Referring now to
FIGS. 3 and 4 , a formingassembly 16 includes astationary assembly 42 and a movingassembly 44. In one example embodiment, not shown, thestationary assembly 42 is coupled, directly coupled, or fixed to thefirst surface 22 of the mountingassembly body 18, and the movingassembly 44 is movably coupled to thefirst surface 22 of the mountingassembly body 18 via thestationary assembly 42. In the embodiment shown, and as described below, thestationary assembly 42 and the movingassembly 44 are a “unified” assembly that is structured to be, and is, temporarily coupled to the mountingassembly body 18. That is, the elements of thestationary assembly 42 and the movingassembly 44 are coupled, directly coupled, or fixed to each other. Further, thestationary assembly 42 and the movingassembly 44 are structured to be, and are, temporarily coupled to astationary assembly base 50, as discussed below. In this configuration, the formingassembly 16 is a unified assembly. - As shown in the example embodiment of
FIG. 4 , thestationary assembly 42 of the formingassembly 16 includes thestationary assembly base 50, aram guide assembly 52, a redrawassembly 200, adie pack 56 and adomer 58. Thebase 50 includes a generallyplanar member 60 with a number of upwardly depending, generally planar supports 62. Theplanar member 60 is structured to, i.e., is machined to, substantially correspond to therecess 34 defined in thefirst surface 22 of the mountingassembly body 18. Theplanar member 60 has aproximal end 64 and adistal end 66. When the formingassembly 16 is operatively coupled to theram drive assembly 300, theproximal end 64 of theplanar member 60 is the end closer to thecam 330 of theram drive assembly 300 and thedistal end 66 of theplanar member 60 is the end further from thecam 330 of theram drive assembly 300. - In one example embodiment, the
planar member 60 includes a number, and as shown a plurality, ofguide pin passages 68 extending through theplanar member 60 of thebase 50 of thestationary assembly 42. The number ofguide pin passages 68 are disposed in a pattern corresponding to theguide pin passages 36 of therecess 34 of the mountingassembly body 18 previously discussed. Eachguide pin passage 68 has a cross-sectional area structured to accommodate aguide bushing 69. The number ofguide pin passages 36 of therecess 34 and the number ofguide pin passages 68 of theplanar member 60, along with the associatedguide bushings assembly 16 relative to thecam 330. That is, in an embodiment including theguide pin passages planar member 60 is disposed in a machinedrecess 34, eachguide pin passage 36 generally aligns with an associatedguide pin passage 68. Further, when guide pins 39 are passed through the associatedguide pin passages 36, 68 (and the associatedbushings 37, 69), theplanar member 60 is brought into alignment with thecam 330. Although two sets of associatedguide pin passages guide pin passages - The supports 62 of the base 50 include at least a
domer support 70. Thedomer support 70 includes a generally planar body 72 that may be a separate member coupled to theplanar member 60, or may be formed unitarily with theplanar member 60. As shown, the body 72 of thedomer support 70 extends generally laterally relative to a longitudinal axis L of aram body 122, discussed below. The supports 62 of the base 50 further include adie pack support 74 which, as shown, is a frame 76 that is raised above the plane of theplanar member 60 of thebase 50 of the formingassembly 16. Further, thesupports 62 of the base 50 include a ramguide assembly support 78 that is structured to, and does, support theram guide assembly 52 of thestationary assembly 42. As shown, the ramguide assembly support 78 includes a generally planar body 79 that may be a separate member coupled to theplanar member 60, or may be formed unitary with theplanar member 60. The body 79 extends generally parallel to the plane of the body 72 of thedomer support 70. - Continuing to refer to
FIG. 4 , as well as toFIG. 7B , theram guide assembly 52 includes ahousing 80 defining apassage 81. A number ofbearing assemblies 82 such as, but not limited to, hydrostatic/hydrodynamic bearing assemblies 84 (which also define a passage, not numbered) are disposed in thehousing 80. The bearingassemblies 84 are structured to, and do, support theram body 122 as theram body 122 reciprocates, as described below. Theram guide assembly 52 further includes a seal pack assembly 86 (FIG. 4 ) that is structured to, and does, substantially remove the hydrostatic/hydrodynamic bearing fluid from the ram body 122 (discussed below), as is known. - As shown in
FIG. 4 andFIGS. 8A-8C , the redrawassembly 200 includes both stationary elements and moving elements and is included herein with thestationary assembly 42 of the formingassembly 16. In an exemplary embodiment, the redrawassembly 200 includes a hold down piston 202 (shown schematically) and a blank (cup)holder 204. Theblank holder 204 is coupled, directly coupled, or fixed to the hold downpiston 202 and moves therewith. The hold downpiston 202 and theblank holder 204 each include a generallytoroid body ram body 122 to pass therethrough. The redrawassembly 200 also includes a servo-motor 209, or similar construct, that is structured to move the hold downpiston 202, and therefore theblank holder 204, in a generally reciprocal motion. That is, the hold downpiston 202 and theblank holder 204 are structured to move/translate in a linear fashion (e.g., along a translation axis 229) between a first positioning, wherein the hold downpiston 202 and theblank holder 204 are spaced from thedie pack 56, and, a second positioning wherein the hold downpiston 202 andblank holder 204 are disposed immediately adjacent thedie pack 56. As is known, a cup feed assembly 108 (discussed below) or similar construct, positions a cup or blank at the mouth of thedie pack 56. Theblank holder 204 maintains the cup/blank in this position until theram body 122 engages the cup/blank and moves the cup/blank through thedie pack 56. - In an exemplary embodiment, such as illustrated in
FIG. 4 andFIGS. 8A-8C , a servo-motor 209 is coupled to a number ofcam disks cam 330 of theram drive assembly 300, discussed below, is identified as the “cam 330”; while, as used herein, the “cam disk 214” is identified as the “cam disk 214”) and the hold downpiston 202 and theblank holder 204 are coupled to, or biased against (i.e., away from the die pack 56) thecam disk 214 via a number of suitable biasing members 210 (e.g., spring(s) or other suitable arrangement(s)). In the exemplary embodiment shown inFIG. 4 , thecam disk 214 is a generally planar body that is rotatable about a rotation axis 215 (disposed perpendicular to theaforementioned translation axis 229 of the hold downpiston 202 and the blank holder 204) by theservo motor 209. The hold downpiston 202 and theblank holder 204 are biased against theedge surface 211 of thecam disk 214. Theedge surface 211 of thecam disk 214 defines aforward stroke portion 216, aforward dwell portion 218, abackward stroke portion 220 and abackward dwell portion 222. That is, as theforward stroke portion 216 engages the hold downpiston 202, the hold downpiston 202, and therefore theblank holder 204, moves from the first position to the second position (i.e., toward the die pack 56), compressing the number of biasingmembers 210. As theforward dwell portion 218 engages the hold downpiston 202, the hold downpiston 202, and therefore theblank holder 204, are maintained in the second position. As thebackward stroke portion 220 engages the hold downpiston 202, the hold downpiston 202, and therefore theblank holder 204, move from the second position to the first position (i.e., away from the die pack 56) due to the force of the number of biasingmembers 210. As thebackward dwell portion 222 engages the hold downpiston 202, the hold downpiston 202, and therefore theblank holder 204, are maintained in the first position. Thus, the hold downpiston 202, and therefore theblank holder 204 moves between the first and second positions while dwelling at those positions between periods of motion. This allows a cup/blank to be positioned between theblank holder 204 and thedie pack 56 while theblank holder 204 dwells at the first position, and, allows theblank holder 204 to maintain a cup/blank at thedie pack 56 while theblank holder 204 dwells at the second position. In another embodiment, not shown, theram drive assembly 300 includes a linkage that moves the hold downpiston 202 and theblank holder 204 between the first and second positions in a similar manner, i.e., moving with dwell periods in between motion periods, thus eliminating thecam disk 214. -
FIGS. 9A-9C show another exemplary embodiment of a redrawassembly 200′ including a hold downpiston 202 andblank holder 204 similar to redrawassembly 200. The hold downpiston 202 andblank holder 204 are slidably coupled to the die pack support 74 (e.g., via a number of linear bearing pins 226 and cooperating linear bearing bushings 228) such that the hold downpiston 202 andblank holder 204 are readily translatable along atranslation axis 229 disposed perpendicular to therotation axis 215. Redraw assembly 200′ functions similarly to the redrawassembly 200 ofFIG. 4 except the redrawassembly 200′ utilizes acam disk 214′ having agroove 230′ that is engaged by aroller member 232 or other suitable construct that is coupled to the hold downpiston 202. Optionally, redraw assembly 200′ further utilizes asecond cam disk 214″ having agroove 230″ that is likewise engaged by asecond roller member 232′. In operation, one or both ofcam disks 214′ and 214″ are rotated about therotation axis 215 by a servo-motor 212, or similar construct that is directly coupled the servo motor 212 (as shown) or coupled thereto via a belt or other suitable arrangement. As one or both ofcam disks 214′ and 214″ are rotated, thegrooves 230′ and 230″ thereof interact with theroller members piston 202 and theblank holder 204 to translate back and forth along thetranslation axis 229 among a first positioning, wherein the hold downpiston 202 and theblank holder 204 are spaced from thedie pack 56, and a second positioning, wherein the hold downpiston 202 and theblank holder 204 are disposed immediately adjacent thedie pack 56. - Moving on to the
die pack 56, thedie 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, thedie pack 56 is structured to reform/form a cup/blank disposed on apunch 124/ram body 122 into a can body (discussed below). As such, the dies of thedie pack 56 define a formingpassage 100 having an upstream, proximal end 102 (or “mouth” 102) and a downstream,distal end 104. - The redraw
assembly 200 is disposed at theproximal end 102 of the formingpassage 100. Further, and as is known, thedie pack 56 includes, or is disposed adjacent or immediately adjacent, astripper assembly 106 structured to strip, i.e., remove, a can body from theram body 122 during the return stroke, as described below. That is, thestripper assembly 106 is disposed at the distal end of the formingpassage 100. - In an exemplary embodiment, the
die pack 56 further includes a cup (or blank)feed assembly 108. In an exemplary embodiment, thecup feed assembly 108 includes a servo-motor 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 support so that a cup (or blank) is positioned at theproximal end 102 of the formingpassage 100 of thedie pack 56 prior to theram body 122 moving through thedie pack 56, as discussed below. - The
domer 58 includes a mountingassembly 110 and adomer body 112. The mountingassembly 110 is structured to be coupled to thedomer support 70. The mountingassembly 110 is further structured to adjustably support thedomer body 112. Thedomer body 112 includes a domed surface 114 having avertex 116. The domed surface 114/vertex 116 is disposed facing, and generally aligned with, the formingpassage 100 of thedie pack 56, as is known. - Referring to
FIGS. 4-6 , the movingassembly 44 of the formingassembly 16 includes aram assembly 120 and acam follower assembly 150. Theram 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). Theram body 122 has a proximal, or first,end 126, amedial portion 125 and a distal, or second,end 128. As is known, thepunch 124 is coupled, directly coupled, or fixed to the ram bodydistal end 128. As is known, thedistal end 128 has a smaller cross-sectional area relative to theproximal end 126 and themedial portion 125. In an exemplary embodiment, thepunch 124 has a cross-sectional area that is substantially similar to theproximal end 126 and themedial portion 125. Thus, there is a generally, or a substantially, smooth transition between thepunch 124 and theram body 122. Thecam follower assembly 150 is disposed at, and coupled to, theproximal end 126 of theram body 122. - Further, in an exemplary embodiment, the
ram body 122 is generally hollow. That is, theram body 122 defines acavity 130. Thedistal end 128 of theram body 122 includes apassage 129 that is in fluid communication with thecavity 130. Further, if apunch 124 is used, thepunch 124 also includes an axially extending passage 127. That is, thepassage 129 of the ram body 122 (and, if included, the punch passage 127) extends from the axial surface of thedistal end 128 of theram body 122 to thecavity 130. Thecavity 130 is 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, thecavity 130 of theram body 122 is selectively in fluid communication with a negative fluid pressure when theram body 122 is moving forward (i.e., away from the ram drive assembly 300). In this configuration, a negative fluid pressure biases the cup/blank toward theram body 122 and/or punch 124. When theram 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 theram body 122/punch 124. As theram body 122 is one of the longer elements of the formingassembly 16, as used herein, the longitudinal axis L of theram body 122 is also the longitudinal axis of the formingassembly 16. - Referring to
FIGS. 4, 5 and 7A-7D , thecam follower assembly 150 of the movingassembly 44 of a formingassembly 16 includes aslider 152 and a number of cam follower members 154 (two are shown in the example). In an exemplary embodiment, theslider 152 includes aslider body 160, alower frame portion 162 extending downward from theslider body 160, and anupper frame portion 164 extending upward from theslider body 160. In the example illustrated,slider body 160 is disposed generally parallel to the plane of thefirst surface 22 of the mountingassembly body 18, i.e., generally horizontally as shown. - The
lower frame portion 162 of theslider body 160 includes afirst member 162A extending downward generally from at or near afirst edge 160A ofslider body 16, asecond member 162B extending downward generally from at or near a second edge 160B ofslider body 160 opposite thefirst edge 160A, and athird member 162C extending between the first andsecond members slider body 160. In the example shown inFIG. 7D , thethird member 162C extends generally horizontally, parallel to theslider body 160, between first andsecond members third members 162A-162C may be formed integrally as portions of a single unitary member, such as shown in the example ofFIG. 7D , or alternatively may be formed as separately and then coupled together via any suitable method (e.g., bolts, welding, etc.). - The
upper frame portion 164 of theslider body 160 includes afirst member 164A extending upward generally from at or near thefirst edge 160A ofslider body 160, asecond member 164B extending upward generally from at or near the second edge 160B ofslider body 160, and athird member 164C extending between the first andsecond members slider body 160. Each of the first, second, andthird members 164A-164C may be formed integrally as portions of a single unitary member, such as shown in the example ofFIG. 7D , or alternatively may be formed as separately and then coupled together via any suitable method (e.g., bolts, welding, etc.). - Continuing to refer to
FIGS. 7A and 7D , thecam follower assembly 150 further includes a camfollower 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) ofstationary assembly 42. Each bearing member 167 includes abearing surface 168 upon which each bearing pad 166 is positioned and structured to slide. A hydrostatic/hydrodynamic bearing assembly is discussed in detail in U.S. Pat. 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 inFIG. 7D ) that is structured to 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
FIG. 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 camfollower bearing assembly 165 is of unique design as compared to known arrangements. In the example illustrated inFIGS. 7A-7D , the camfollower bearing assembly 165 includes three generally planar hydrostatic/hydrodynamic bearing pads 166: afirst bearing pad 166A coupled, directly coupled, or fixed to an outward facing face offirst member 164A; a second bearing pad 166B coupled, directly coupled, or fixed to an outward facing face ofsecond member 164B (i.e., facing in the opposite direction fromfirst bearing pad 166A); and athird bearing pad 166C coupled, directly coupled, or fixed to an upward facing face ofthird member 164C. In such example, the camfollower bearing assembly 165 also includes three bearingmembers bearing surfaces first bearing member 167A is fixedly coupled to thestationary assembly base 50 of the formingassembly 16 such that the bearingsurface 168A thereof is positioned outward, above, and parallel to the longitudinal axis L of theram body 122 of the formingassembly 16, and generally perpendicular to thestationary assembly base 50. The second bearing member 167B is fixedly coupled to thestationary assembly base 50 of the formingassembly 16 such that the bearing surface 168B thereof is positioned outward, above, and parallel to the longitudinal axis L of theram body 122 of the formingassembly 16; generally perpendicular to thestationary assembly base 50, and facing the bearingsurface 168A of thefirst bearing member 167A. Thethird bearing member 167C is fixedly coupled to thestationary assembly base 50 of the formingassembly 16 such that the bearingsurface 168C thereof is positioned directly above and parallel to the longitudinal axis L of theram body 122 of the formingassembly 16, generally parallel to thestationary assembly base 50, and perpendicular to each of the bearing surfaces 168A and 168B of thefirst bearing member 167A and the second bearing member 167B. Accordingly, as can be readily appreciated from the sectional view ofFIG. 7C , the three bearingmembers 167A-167C are positioned so as to form a downward opening channel (with the bearing surfaces 168A-168C facing inward) that is disposed about theupper frame portion 164 of theslider body 160 and the outwardfacing 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 thecavity 130 therein that is selectively in fluid communication with a pressure assembly. Such communication between a pressure assembly (not shown) andcavity 130 ofram body 122 is provided via a flexible conduit orhose 170 that extends between a lowerrotary seal 170A that is coupled to mountingassembly 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 thelower frame portion 162 of theslider body 160. The upper rotary seal 170B is in fluid communication with thecavity 130 of the ram body via any suitable conduit arrangement provided as a part ofcam follower assembly 150. Ashock absorber arrangement 171 is provided abouthose 170 to minimize hose whipping resulting from the reciprocating movement ofcam follower assembly 150. - As also previously discussed, each bearing pad 166 includes a recessed bearing 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 (seeFIGS. 7B and 7C ) that is coupled to thelower frame portion 162 of theslider 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 lowerrotary seal upper rotary seal 172B to the recessed bearing pocket 169 of each of the number ofbearing pads cam follower assembly 150 connected to an inlet 173 (seeFIG. 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 eachbearing pad pads corresponding bearing pads surfaces cam follower assembly 150 along bearingmembers stationary assembly base 50 of the formingassembly 16. - Referring now to
FIG. 5 , theslider body 160 includes a number of passages (not collectively numbered) defined therethrough. The passages include a number of cam follower mounting passages, two shown 174 and 175. If there are two camfollower mounting passages follower mounting passages assembly 16 is coupled to the mountingassembly 14, is generally a radial line extending outward from thepassage 20 of the mountingassembly body 18 and aligned above the longitudinal axis L of theram body 122 of formingassembly 16. Another passage defined throughslider body 160 is analignment pin passage 178 positioned generally adjacent the end ofslider body 160opposite ram body 122. - The
cam follower members 154 are structured to be, and are, operatively engaged by thecam 330 of theram drive assembly 300. Stated alternately, thecam 330 is structured to be, and is, operatively coupled to thecam follower members 154 of the movingassembly 44 of each formingassembly 16 and is, therefore, operatively coupled to eachram assembly 120 and/or formingassembly 16. - In one embodiment, not shown, the
cam follower members 154 are rigid bearings. In the embodiment shown inFIGS. 2-6 and 7A-7D , thecam 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 anaxle 184 and a wheel 186 (seeFIG. 5 ). Further, and in an exemplary embodiment, one of the camfollower roller bearings 180 includes aneccentric bushing 187. Theeccentric bushing 187 includes a hollowtubular body 188 that is structured to fit within cam follower mounting passage 175 (or alternatively passage 174). Thetubular body 188 has a generally cylindricalouter 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 centers noted above are offset from each other. In this configuration, theeccentric bushing 187 includes a portion with a maximum thickness, hereinafter the “thicker”side 188′ of theeccentric bushing 187, and, a portion with a minimum thickness, hereinafter the “thinner”side 188″ of theeccentric bushing 187. Further, theeccentric bushing 187 includes anorientation tab 194 that extends generally radially from theouter surface 190 of thetubular body 188. In this configuration, theeccentric bushing 187 is structured to, and does, move the associatedroller bearing wheel 186 between a spaced, first position and a close, second position, as discussed below. - Thus, as used herein, a “forming assembly” 16 includes at least a
die pack 56, adomer 58, and aram body 122. Further, a “forming assembly” 16 selectively includes additional elements such as, but not limited to, aram guide assembly 52 and a redrawassembly 200. - A forming
assembly 16 is assembled as follows. Theram guide assembly 52, the redrawassembly 200, and thedie pack 56 are coupled, directly coupled, or fixed to the baseplanar member 60, i.e., thestationary assembly base 50. Thedomer 58 is coupled, directly coupled, or fixed to thedomer support 70, i.e., which, as previously discussed, is coupled to, or formed as a unitary portion of, thestationary assembly base 50. Generally, theram guide assembly 52 is disposed closest to thepassage 20 of the mountingassembly body 18. The redrawassembly 200 is disposed adjacent theram guide assembly 52. Thedie pack 56 is disposed adjacent theram guide assembly 52 with thecup feed assembly 108 disposed between the redrawassembly 200 and thedie pack 56. Further, as noted above, thestripper assembly 106 is disposed at thedistal end 104 of the formingpassage 100 of thedie pack 56. Finally, thedomer 58 is spaced from thedie pack 56 and/orstripper assembly 106. That is, the domer 58 (or stripper assembly 106) is spaced from thedie 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, thestationary assembly 42 of the formingassembly 16 is complete. - The moving
assembly 44 of the formingassembly 16 is assembled as follows. Theproximal end 126 of theram body 122 is coupled, directly coupled, or fixed to theslider 152 of thecam follower assembly 150. As shown, and in an exemplary embodiment, theproximal end 126 of theram body 122 is coupled to thelower frame portion 162 of theslider body 160. Thepunch 124 is disposed over and coupled, directly coupled, or fixed to thedistal end 128 of theram body 122. In this configuration, the longitudinal axis L of theram body 122 is generally, or substantially, aligned with the longitudinal axis of thepassage 81, the redrawassembly 200, and the formingpassage 100 of thedie pack 56. Further, the longitudinal axis L of theram body 122 is generally, or substantially, aligned with thevertex 116 of the domed surface 114 of thedomer body 112. That is, if the longitudinal axis L of theram body 122 were extended, it would pass through, or be immediately adjacent thevertex 116 of the domed surface 114 of thedomer body 112. - In this configuration, and in one embodiment, the forming
assembly 16 is complete. Further, as noted above, the formingassembly 16 is a “unified” assembly. Further, it is understood that as the formingassembly 16 is assembled, the various elements are positioned to be in proper alignment, as is known in the art. That is, for example, theram body 122 is adjusted/repositioned until the longitudinal axis L of theram body 122 is generally, or substantially, aligned with the longitudinal axis of thepassage 81 of thehousing 80 of theram guide assembly 52 and the longitudinal axis of the formingpassage 100 of thedie pack 56. As the formingassembly 16 is a “unified” assembly, the elements thereof remain aligned with each other. That is, when the formingassembly 16 is removed from the mountingassembly 14, the elements thereof are not separated. As such, the elements of the formingassembly 16 do not have to be adjusted so as to be in alignment each time the formingassembly 16 is installed. A formingassembly 16 that maintains the alignment of the elements, i.e., wherein the elements of thestationary assembly 42 and the movingassembly 44 are not separated, during an installation is, as used herein, an “aligned” unified formingassembly 16. A unified formingassembly 16 or an aligned unified formingassembly 16 solves the problem(s) noted above. - As shown in
FIGS. 2-3 , theram drive assembly 300 ofbodymaker 10 is structured to, and does, move the movingassembly 44 of the formingassembly 16, i.e., theram assembly 120 or theram body 122, between a retracted (i.e., toward the ram drive assembly 300), first position, wherein theram body 122 is not disposed in the formingpassage 100 and thedistal end 128 of theram body 122 is spaced from an associateddie pack 56, and, an extended (i.e., away from the ram drive assembly 300), second position wherein theram body 122 is disposed in the formingpassage 100 and thedistal end 128 of theram body 122 is adjacent an associateddomer 58. Theram 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
FIG. 3 , theram drive assembly 300 includes amotor 310 and acam 330 that is rotated around a prime axis ofrotation 330 by themotor 310. Themotor 310 includes arotating output shaft 312. In an exemplary embodiment, themotor 310 is disposed below the mountingassembly body 18 within the enclosedspace 30 defined byhousing 28. As shown, aprimary axle 314 is generally disposed within the hollow mounting assembly enclosedspace 30 and rotatable aboutprime axis 333. Themotor output shaft 312 is operatively coupled to theprimary axle 314, e.g., by agear box 315. As such, theprimary axle 314 is also identified herein as a part of themotor 310. Theprimary axle 314 includes anelongated axle body 316 having an upper,first end 318 and a lower, second end (not numbered) coupled to thegear box 315. The lower second end ofaxle body 316 may be selectively coupled to thegear box 315 via a suitable clutch arrangement that provides foraxle body 316 to be selectively engaged or disengaged from thegear box 315, and thus motor 310. Thefirst end 318 of theaxle body 316 extends through thepassage 20 of the mountingassembly body 18. Thefirst end 318 of theaxle body 316 is structured to be, and is, coupled to thecam body 332. A brake arrangement 319 (e.g., a disk brake or other suitable arrangement) is positioned alongprimary axle 314 for selectively bringing rotation aboutprime axis 333 ofprimary axle 314 andcam body 332 to a controlled and timely stop. - The
cam 330 of theram drive assembly 300 includes abody 332 defining, or having, 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. Thecam 330/cam body 332 is structured to, and does, impart a reciprocal motion to each formingassembly 16 and, in an exemplary embodiment, to each movingassembly 44 and/or ramassembly 120. Further it is noted that, as discussed below, thecam 330 moves while each formingassembly 16 is mounted on the mountingassembly 14. That is, thecam 330 is dynamic and each formingassembly 16 is statically mounted. Thus, thecam body 332 is a “dynamic cam body”. This solves the problems noted above. Alternatively, thecam body 332 could be fixed or held in a steady state with each formingassembly 16 moving thereabout. In such arrangement,cam body 332 would be a “steady state cam body”. - Further, in an exemplary embodiment, the
cam 330/cam body 332 is structured to, and does, generate a “smooth ironing action” in thedistal end 128 of theram body 122/punch 124 as theram body 122/punch 124 moves through thedie pack 56. As used herein, a “smooth ironing action” means that the construct that supports the cup, which is typically thedistal end 128 of theram body 122 or punch 124, is not being accelerated or decelerated as the construct that supports the cup passes through thedie pack 56. In an exemplary embodiment, thecam 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 thedistal end 128 of theram body 122 or punch 124 to move at a substantially constant velocity, i.e., no acceleration or deceleration, as thedistal end 128 of theram body 122 or punch 124 pass through thedie pack 56. Thus, such acam 330/cam body 332 is structured to, and does, generate a “smooth ironing action.” This solves the problem(s) noted above. - Further, in an exemplary embodiment, the components (i.e., the
ram assembly 120 and cam follower assembly 150) of the movingassembly 44 of the formingassembly 16 are of low mass. Use of such a lowmass moving assembly 44 with acam 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 movingassembly 44 and components thereof at virtually any operating speed. Hence, once the position ofram 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 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 themotor 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” 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 “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 inFIG. 1 , both thecarriage 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 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, thecam 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 axially extending hub 337 (FIG. 3 ) and aridge 338 extending about thecam body 332 axis of rotation (i.e., prime axis 333). In another embodiment such as shown inFIG. 13 , thecam body 332′ is a two-part assembly, anouter ring 332A′ disposed about aninner section 332B′.Outer ring 332A′ andinner section 332B′ may be formed from different materials and one or both ofouter ring 332A′ and 332B′ may have one or more apertures or open sections defined therein or thereby to lighten such sections and thus reduce the moment of inertia ofsuch cam 330′. - Referring again to
FIG. 3 , thecam body hub 337 defines acoupling passage 339. In an exemplary embodiment, thecoupling passage 339 is tapered and narrows from bottom to top (e.g., seeFIG. 3 ). In an exemplary embodiment, thefirst end 318 of theaxle body 316 is structured to be, and is, coupled to thecam body 332 at thecoupling passage 339. As shown, thecam body ridge 338, in an exemplary embodiment, extends about the perimeter of thecam body 332. As shown inFIG. 2 , when viewed from above, theridge 338 of thecam body 332 is not substantially circular, as discussed in detail below; that is, theridge 338 does not have a substantially consistent radius R relative to the axis of rotation (i.e., prime axis 333) of thecam body 332, but instead is varied in a predetermined manner to create desired movement of the movingassembly 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 up to 6.5″ tall/long. As used herein, a generallyplanar cam body 332 having aridge 338 extending about the perimeter of thecam body 332 is a “disk cam.” In this embodiment, theridge 338 includes the inner,first cam surface 334 and the outer,second cam surface 336. Further, in an exemplary embodiment, the radial width W (FIG. 5 ) of thecam body ridge 338 is generally, or substantially, consistent. That is, the distance between thefirst cam surface 334 and thesecond cam surface 336 is generally, or substantially, consistent. Further, in an exemplary embodiment, thecam body 332 includes a number ofalignment passages 344 disposed adjacent thecam body ridge 338, the purpose of which is discussed below. - In another example embodiment, such as shown in
FIGS. 10 and 11 , abodymaker 10B utilizing a “barrel”cam 330B is shown. Thebodymaker 10B is of a similar arrangement as thebodymaker 10 previously discussed in conjunction withFIGS. 2-6 except thebodymaker 10B only includes two formingassemblies 16 and includes aram drive assembly 300B that includes/utilizes the “barrel”cam 330B instead of a disk cam. Hereinafter, and in relation to thebarrel cam 330B, reference numbers similar to the embodiment shown inFIGS. 2-6 will be used, but the reference numbers will include the letter “B.” In this embodiment, thecam body 332B is generally cylindrical and includes a groove (not shown) or a ridge (as shown) 338B disposed thereabout on a cylindrical surface (not numbered) of thecam body 332B. Theridge 338B extends generally axially while also forming a loop about thecylindrical cam body 332B. In this configuration, thecam body 332B, i.e., theridge 338B thereon, defines a generally axialfirst cam surface 334B and a generally axial second cam surface 336B. It is understood that, where theridge 338B reverses direction, theridge 338B extends generally circumferentially around thecam body 332B rather than axially along thecam body 332B. In this embodiment, the opposing sides of theridge 338B are the cooperative cam surfaces 334B, 336B. It is noted that aram 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 or 334B, 336B are structured to, and do, operatively engage each
cam follower assembly 150. In the embodiment shown inFIGS. 2-6 , thecam follower assembly 150 includes twocam follower members 154, i.e.,roller bearings 180, also identified herein as firstcam follower member 156 and secondcam follower member 158. The firstcam follower member 156 is disposed adjacent thefirst cam surface 334. That is, thewheel 186 of the firstcam follower member 156 is disposed adjacent to thefirst cam surface 334. The secondcam follower member 158 is disposed adjacent thesecond cam surface 336. That is, thewheel 186 of the secondcam follower member 158 is disposed adjacent to thesecond cam surface 336. Thus, in such embodiment, the first and secondcam follower members cam body ridge 338. That is, the first and secondcam follower members cam body ridge 338. In an exemplary embodiment with a barrel cam having a groove instead of aridge 334B, there is a single cam follower member which is structured to be, and is, disposed in the groove. - Further, as shown in
FIGS. 10 and 11 , in an exemplary embodiment, thebodymaker 10B has abarrel cam 330B that includes twoseparate barrel cams 330B′, 330B″ that are coupled, directly coupled, or fixed to theoutput shaft 312B of amotor 310B. It is understood that, in an exemplary embodiment, eachbarrel cam 330B′, 330B″ is structured to be, and is, operatively coupled to a respective formingassembly 16, such as previously discussed in regard toFIGS. 2-6 . Thus, in an embodiment with asingle barrel cam 330B and two formingassemblies 16, such as shown inFIGS. 10 and 11 , thebodymaker 10B produces two can bodies per cycle. Although only two formingassemblies 16 are shown inFIGS. 10 and 11 being used in conjunction withbarrel cam 330B, it is to be appreciated that more than two forming assemblies may be employed without varying from the scope of the present concepts. For example, additional formingassemblies 16 may be provided with the respectivecam follower assemblies 150 thereof positioned to engage the 338B at generally any point around thebarrel cam 330B (i.e., in addition to, or instead of only at the top as shown inFIGS. 10 and 11 ). As an example, when viewed generally along the prime axis ofrotation 333B ofbarrel cam 330B, an arrangement utilizing twelve formingassemblies 150 spaced equally about the circumference of thebarrel 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 to the mountingassembly 14. Thus, each formingassembly 16 is disposed at a fixed location adjacent thecam body 332. Further, relative to each formingassembly 16, thecam body ridge 338 moves radially outwardly and radially inwardly as thecam body 332 rotates. It is understood that as the radius of thecam body ridge 338 decreases, thefirst cam surface 340 operatively engages a firstcam follower member 156. Conversely, when as the radius of thecam body ridge 338 increases, the second cam surface 342 operatively engages a secondcam follower member 158. It is understood that as onecam surface 340, 342 operatively engages acam follower member other cam surface 340, 342 does not operatively engage acam follower member cam surface 340, 342 operatively engages acam follower member - As the
cam follower assembly 150 is coupled, directly coupled, or fixed to the forming assembly movingassembly ram assembly 120, thecam 330 is structured to, and does, pull theram body 122 radially inwardly as thefirst cam surface 334 operatively engages a firstcam follower member 156. Conversely, thecam 330 is structured to, and does, push theram body 122 radially outwardly as thesecond cam surface 336 operatively engages a secondcam 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 and/or when the cam surface/cam profile moves relative to the cam follower. - As shown in
FIG. 12 , the cooperative cam surfaces 334, 336, i.e.,first cam surface 334 andsecond cam surface 336, are divided into “portions.” That is, the cam surfaces 334, 336 include, or define, a number ofdrive portions 350, 352 (two shown). As used herein, a “drive” portion of a cam surface means that the cam surface is structured to move another element or assembly. In an exemplary embodiment, the camsurface drive portions stroke portion 350 and a rearward or returnstroke 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 thecam follower 150 such as, but not limited to, the ram body 122) to move toward an associateddomer 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 thecam follower 150 such as, but not limited to, the ram body 122) to move away from an associateddomer 58. - As described above, the operative engagement of the
second cam surface 336 with the secondcam follower member 158 causes the movingassembly 44 of the formingassembly 16, including theram body 122, to move radially outwardly. Thus, a portion of thesecond cam surface 336 wherein the radius is “increasing” as thecam body 332 moves is a cooperative cam surface forwardstroke portion 350. Conversely, the operative engagement of thefirst cam surface 334 with the firstcam follower member 156 causes the movingassembly 44 of the formingassembly 16, including theram body 122, to move radially inwardly. Thus, a portion of thefirst cam surface 340 wherein the radius is “decreasing” as thecam body 332 moves is a cooperative cam surface rearwardstroke portion 352. As noted above, only one offirst cam surface 334 orsecond cam surface 336 operatively engages acam follower member first cam surface 334 opposed to the second cam surface forwardstroke portion 350 is also identified as the “forward stroke portion 350” even though thefirst cam surface 334 does not operatively engage the firstcam follower member 156 at theforward stroke portion 350. Stated alternately, and further to the definition above, i.e., as used herein, a “forward stroke portion” 350 of associatedfirst cam surface 334 andsecond 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, aram body 122 and causes that rambody 122 to move toward an associateddomer 58. Conversely, and further to the definition above, i.e., as used herein, a “rearward stroke portion” 352 of associated cooperativefirst cam surface 334 andsecond 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, aram body 122 and causes that rambody 122 to move away from an associateddomer 58. - Further, it is understood that as the
cam body 332 rotates, the cooperative camsurface drive portions cam follower member surface drive portion 350, 352 (or alternatively the cam body cooperative cam surface forwardstroke portion 350 and the cam body cooperative cam surface rearward stroke portion 352) has a beginning/upstream,first end 350U, 352U and an ending/downstream, second end 350D, 352D. That is, as thecam body 332 rotates, the cooperative cam surface drive portionfirst end 350U, 352U initially operatively engages acam follower member cam body 332 rotates further, the cooperative cam surface drive portion second end 350D, 352D passes by acam follower member cam follower member surface drive portion - 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 surfaces 334, 336 also include, or define, a
first dwell portion 360′. Thus, the upstream/first end of thefirst dwell portion 360′ is identified as “first dwell portionfirst end 360′U.” - It is noted that the pitch (radial change relative to circumferential change) of the
cam body ridge 338, and therefore the cooperativefirst cam surface 334 andsecond cam surface 336, determines whether thecam follower member ram 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 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 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 every 30° would produce a substantially constant velocity in the ram.
- A
cam body ridge 338, and therefore the cooperativefirst cam surface 334 andsecond 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 (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 forwardstroke portion 350 and the cooperative cam surface rearwardstroke portion 352 have a substantially constant velocity cam profile. Further, in an exemplary embodiment, the cooperative cam surface forwardstroke portion 350 extends over an arc of about one hundred eighty three and one half degrees (183.5°) and the cooperative cam surface rearwardstroke 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 thefirst dwell portion 360′ and thesecond dwell portion 360″. As used herein, a “dwell portion” 360′, 360″ of the associated cooperativefirst cam surface 334 andsecond 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, theram body 122 is generally stationary and does not move toward or away from an associateddomer 58. In an exemplary embodiment, and at a cooperative camsurface dwell portion 360′, 360″, the radius of thecam body ridge 338, and therefore the cooperativefirst cam surface 334 andsecond cam surface 336, does not substantially increase or decrease. Thus, thecam body ridge 338, and therefore the cooperativefirst cam surface 334 andsecond cam surface 336, do not operatively engage a cam follower member 154 (or constructs coupled to thecam follower member 154 such as, but not limited to, the ram body 122). As used herein, a cam surface that does not operatively engage acam follower member 154 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 associateddomer 58. Thus, the cooperative cam surface dwellportions 360′, 360″ have a “no velocity cam profile.” However, to maintain consistent terminology, hereinafter thefirst dwell portion 360′ and thesecond dwell portion 360″ will be said to “engage” or “operatively engage” the movingassembly 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, thefirst dwell portion 360′ and thesecond dwell portion 360″ do not actually cause the moving assembly 44 (or elements thereof such as, but not limited to, the cam follower members 154) to move. That is, with respect to thefirst dwell portion 360′ and thesecond 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 thefirst dwell portion 360′ and thesecond dwell portion 360″ are directly coupled to thecam follower assembly 150. - 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 dwellportions 360′, 360″ extending over an arc no greater than thirty degrees does not mean that thecam body ridge 338 has a generally, or substantially, consistent radius relative to thecam body 332 axis of rotation. That is, so long as the cooperative cam surface dwellportions 360′, 360″ extend over an arc no greater than thirty degrees, thecam body ridge 338 does not have a generally, or substantially, consistent radius relative to thecam 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 forwardstroke portion 350 and the cam body cooperative cam surface rearwardstroke portion 352, or, the cam body cooperative cam surface rearwardstroke portion 352 and the cam body cooperative cam surface forwardstroke portion 350. In another exemplary embodiment, each cooperative camsurface dwell portion 360′, 360″ is disposed between cam body cooperative camsurface drive portions first dwell portion 360′ disposed between the forward stroke portion second end 350D and the rearward stroke portion first end 352U, and, a cooperative cam surfacesecond dwell portion 360″ disposed between the rearward stroke portion second end 352D and the forward stroke portionfirst end 350U. In an exemplary embodiment, the cooperative cam surfacefirst dwell portion 360′ extends over an arc of about three and one half degrees (3.5°) and the cooperative cam surfacesecond dwell portion 360″ extends over an arc of about thirty degrees (30°). - 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 theacceleration portion 370 and thedeceleration portion 372. Theacceleration portion 370 and thedeceleration portion 372 each have an “acceleration profile.” As used herein, an “acceleration profile” means that thecam body ridge 338, and therefore the cooperativefirst cam surface 334 andsecond 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 aram body 122. That is, an “acceleration profile” means that thecam body ridge 338, and therefore the cooperativefirst cam surface 334 andsecond cam surface 336 has/have a pitch that is structured to, and does, produce a changing velocity 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, thesurface portions 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 theram body 122. - In an exemplary embodiment such as illustrated in
FIG. 12 , the cooperative camsurface acceleration portion 370 anddeceleration portion 372 are disposed between the cooperative camsurface drive portions portions 360′, 360″. That is, starting at the end ofdwell portion 360″ associated with theram 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 theram body 122 toward the domer 58), aconstant speed portion 350, the deceleration portion 372 (which causes a deceleration to no velocity), thefirst dwell portion 360′, the varyingspeed portion 352 which is of varying speed, and thesecond dwell portion 360″. Theacceleration portion 370, theconstant speed portion 350, and thedeceleration portion 372 make up the forming stroke, whereas the varyingspeed portion 352 makes up the return stroke. In an exemplary embodiment such as shown inFIG. 12 , theacceleration portion 370 extends over an arc of about thirty three degrees (33°) and thedeceleration portion 372 extends over an arc of about thirty three and one half degrees (33.5°). - Thus, as shown in
FIG. 12 , and in an exemplary embodiment, the cooperativefirst cam surface 334 andsecond cam surface 336, are divided into the following portions which extend sequentially over the identified arcs. -
Acceleration portion 3700° to 33° Constant speed portion 35033° to 150° Deceleration portion 372150° to 183.5° First dwell portion 360' 183.5° to 187° Varying speed portion 352187° to 330° Second dwell portion 360”330° to 360° - For a
cam 330 such as described above,FIG. 12A shows the position or displacement of apunch 124 relative to the first position and relative to thecam 330, as described above, as thecam 330 rotates.FIG. 12B shows the velocity of aram assembly 120/punch 124 as thecam 330 rotates.FIG. 12C shows the acceleration (or deceleration) of aram assembly 120/punch 124 as thecam 330 rotates. - When a forming
assembly 16 is coupled, directly coupled, or fixed to the mountingassembly 14, thecam body ridge 338 is disposed between the firstcam follower member 156 and the secondcam follower member 158. That is, as noted above, thewheel 186 of the firstcam follower member 156 is disposed adjacent to thefirst cam surface 334, and, thewheel 186 of the secondcam follower member 158 is disposed adjacent to thesecond cam surface 336. Thus, when thecam 330, i.e.,cam body 332, rotates, and when the radius of thecam body ridge 338 is “decreasing” as described above, thefirst cam surface 334 operatively engages the firstcam follower member 156. Conversely, when thecam 330, i.e.,cam body 332, rotates, and when the radius of thecam body ridge 338 is “increasing” as described above, thesecond cam surface 336 operatively engages the secondcam follower member 158. - The operative engagement of the first and second
cam follower members cam follower assembly 150 and the elements coupled thereto, i.e., theram assembly 120, to move. That is, the operative engagement of the first and secondcam follower members assembly 44 of the formingassembly 16 to move. - Thus, the motion of the moving
assembly 44 of a formingassembly 16 sequentially occurs as follows. Initially, the movingassembly 44 is in the first position. When the first and secondcam follower members second dwell portion 360″, the moving assembly 44 (including theram body 122 and the punch 124) does/do not move. As the moving elements of the movingassembly 44 do not suddenly, or instantly, reverse directions, the movingassembly 44 does not substantially vibrate. This solves the problem(s) noted above. That is, the second cooperative camsurface dwell portion 360″ solves the problem(s) noted above. Further, at this time, a cup is moved into position at the mouth of thedie pack 56. - As the
cam 330, i.e.,cam body 332, rotates, the first cooperative camsurface acceleration portion 370 engages the first and secondcam follower members ram body 122 and the punch 124) to accelerate and move toward the associateddomer 58. As thecam 330, i.e.,cam body 332, continues to rotate, the cooperative cam surface forwardstroke portion 350 engages the first and secondcam follower members ram body 122 and the punch 124) to move toward the associateddomer 58 at a substantially constant velocity. This solves the problem(s) noted above. That is, the cooperative cam surface forwardstroke portion 350 solves the problem(s) noted above. - As the
cam 330, i.e.,cam body 332, continues to rotate, thedeceleration portion 372 engages the first and secondcam follower members ram body 122 and the punch 124) to decelerate, i.e., accelerate in a direction opposite the velocity, to no velocity. As thecam 330, i.e.,cam body 332, continues to rotate, the first cooperative camsurface dwell portion 360′ engages the first and secondcam follower members ram body 122 and the punch 124) to be maintained in the second position. That is, as the moving elements of the movingassembly 44 do not suddenly, or instantly, reverse directions, the movingassembly 44 does not substantially vibrate. The lack of motion/acceleration when the movingassembly 44 is in the second position solves the problem(s) noted above. That is, the first cooperative camsurface 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 movingassembly 44 is not subject to “whiplash.” This, in turn, means that the elements of the movingassembly 44 are not subject to elongation as described above. Stated alternately, and as used herein, aram drive assembly 300 that is structured to, and does, avoid “whiplash” in any element operatively engaged thereby is a “steady state” drive assembly. Similarly, acam 330, or acam body 332, that is structured to, and does, avoid “whiplash” in any element that is operatively engaged by thecam 330, or acam body 332, is a “steady state”cam 330, orcam 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 rearwardstroke portion 352 engages the first and secondcam follower members ram body 122 and the punch 124) to move with a motion generally low in acceleration, pressure angle, and vibrations. This solves the problem(s) noted above. That is, the cooperative cam surface rearwardstroke portion 352 solves the problem(s) noted above. - As the
cam 330, i.e.,cam body 332, continues to rotate, the second cooperative camsurface dwell portion 360″ again engages the first and secondcam follower members bodymaker 10, a formingassembly 16 makes a can body. - As noted above in conjunction with
FIG. 5 , one camfollower mounting passage 175 includes aneccentric bushing 187 with theorientation tab 194. Theeccentric bushing 187 is structured to, and does, allow thecam follower assembly 150 to move between two configurations. That is, when theeccentric bushing 187 is disposed so that thethinner side 188″ is disposed closer to the mountingassembly body passage 20, the distance between thecam follower members 154 is at a maximum. This is the first configuration of thecam follower assembly 150. In this configuration, the distance between thecam follower members 154 is greater than the radial width W of thecam body ridge 338. Thus, as described below, the formingassembly 16 is able to be moved in a direction generally normal to the plane of thecam body 332 without contacting thecam body ridge 338. That is, when thecam body 332 is disposed so that the plane of thecam body 332 is generally horizontal, and when thecam follower assembly 150 is in the first configuration, the formingassembly 16 is able to be lifted, or lowered (e.g., via a suitable overhead lift mechanism), relative to thecam body 332 without thecam follower assembly 150 contacting, or substantially contacting, thecam body ridge 338. It is understood that when the forming assembly moving assemblycam follower assembly 150 is in the first configuration, the cam follower roller bearing eccentricbushing orientation tab 194 is fixed via any suitable arrangement (e.g., a radial recess). Thus, theeccentric bushing 187 is not able to rotate within the mountingpassage 175. - Conversely, when the
eccentric bushing 187 is disposed so that thethicker side 188″ is disposed closer to the mounting assembly body passage 20 (such as shown inFIG. 5 ), the distance between thecam follower members 154 is at a minimum. This is the second configuration of the forming assembly moving assemblycam follower assembly 150. In this configuration, the distance between thecam follower members 154 is generally, or substantially, the same as the radial width W of thecam body ridge 338. This is the operational configuration of thecam follower assembly 150. In this configuration, any radial change in the position of thecam 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 thecam follower assembly 150. - In this configuration, the
bodymaker 10 solves the problem(s) stated above. That is, for example, theram drive assembly 300 is a “direct”ram drive assembly 300, as that term is defined above. That is, theram 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 adisk cam 330 has a configuration unlike known bodymakers. As noted above, eachram body 122 has a longitudinal axis L. Further, thecam body 332 axis of rotation is a “prime axis of rotation” for the bodymakerram drive assembly 300, as that term is defined above. Thus, thecam body 332 axis of rotation is also identified herein as the “ram drive assembly prime axis ofrotation 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., seeFIG. 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 ofrotation 333. In an exemplary embodiment, the formingassemblies 16 are generally evenly disposed about the ram drive assembly prime axis ofrotation 333. That is, for “N” number of formingassemblies 16, the formingassemblies 16 are disposed about 360°/N degrees apart. In an exemplary embodiment, there are two or more formingassemblies 16 disposed about the ram drive assembly prime axis ofrotation 333. That is, in an exemplary embodiment, the number of formingassemblies 16 includes between two and ten formingassemblies 16. Further, in an exemplary embodiment, the number of formingassemblies 16 includes one of two formingassemblies 16, four formingassemblies 16, six formingassemblies 16, eight formingassemblies 16 or ten formingassemblies 16. - Further, in an exemplary embodiment, when there is an even number of forming
assemblies 16, each formingassembly 16 may be disposed generally in opposition to another formingassembly 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 formingassemblies 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, abodymaker 10 includes only two formingassemblies 16 positioned only 45° apart about theprime axis 333. In another example, abodymaker 10 includes only two formingassemblies 16 positioned only 36° apart about theprime axis 333. Further, it is to be appreciated that the angular spacing between adjacent formingassemblies 16 of abodymaker 10 may differ among pairs of formingassemblies 16 within thebodymaker 10. As an example, without limitation, abodymaker 10 having three formingassemblies 16 may have two of the formingassemblies 16 positioned 90° apart about theprime axis 333, with the third forming assembly spaced 135° about theprime axis 333 relative to each of the other two formingassemblies 16. In any of these configurations, theram drive assembly 300 is a “single source/[X]-output ram drive assembly,” as that term is defined above. That is, for example, if the formingsystem 12 includes three formingassemblies 16, theram drive assembly 300 is a single source/3-output ram drive assembly. Thus, for a formingsystem 12 including one of four, five, six, seven, eight, nine or ten formingassemblies 16, theram 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 source/10-output ram drive assembly, respectively. An embodiment with eight formingassemblies 16 is shown inFIG. 13 . - In an exemplary embodiment, the forming
system 12 includes four formingassemblies 16. As shown inFIG. 2 , the four formingassemblies 16 are disposed about, or substantially, ninety degrees apart about theprime axis 333 of theram drive assembly 300. Further, in this configuration, the formingassemblies 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
FIG. 11 wherein the bodymaker is abarrel cam 330B, the axis of rotation of thecam body 332B defines a prime axis ofrotation 333B. In this embodiment, however, the longitudinal axis L of eachram body 122 extends generally parallel to the prime axis ofrotation 333B of thebarrel cam 330B. - Another aspect of the motion of the
ram assembly 120, i.e., theram body 122, caused by operative engagement by acam 330 of aram drive assembly 300 as described above is that no two ram bodies are in the same “medial position” at one time. That is, for example, no tworam bodies 122 are disposed with thepunch 124 entering thedie pack 56 associated therewith at the same time. It is noted, however, that tworam bodies 122 are, in certain configurations, disposed with thepunch 124 indie pack 56 associated therewith at the same time. That is, for example, the formingsystem 12 with thecam 330 in a specific orientation may have oneram body 122 with thepunch 124 at the upstream end of thedie pack 56 associated therewith while anotherram body 122 has thepunch 124 disposed at the downstream end of thedie pack 56 associated therewith. When the formingassemblies 16 are “asymmetrical forming assemblies,” the power needed, i.e., the size/power of themotor 310 is reduced because noram assemblies 120 are disposed at the same time in a location that generates the maximum resistance. This solves the problem(s) noted above. Further, thebodymaker 10, i.e., theram drive assembly 300, as described above is structured to, and selectively does, operate with less than the full set of forming assemblies. That is, thebodymaker 10 as described above has a number of formingassemblies 16. Whatever the maximum number of formingassemblies 16 associated with aspecific bodymaker 10 is, as used herein, a “full set” of formingassemblies 16. For example, in an embodiment wherein the maximum number of formingassemblies 16 is four, the “full set” of formingassemblies 16 means four formingassemblies 16. - Unlike prior art bodymakers which needed to balance the loads created by the forming
assemblies 16, thepresent bodymaker 10 is structured to, and, when required, does, operate with less than a “full set” of formingassemblies 16. For example, in an embodiment wherein the “full set” of formingassemblies 16 means four formingassemblies 16, thebodymaker 10, i.e., theram drive assembly 300, is structured to, and does, operate with three, two, or one formingassemblies 16. This solves the problem(s) 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 acam 330 eliminates the need for the drive assembly to be balanced. Thus, for example, if one of four formingassemblies 16 needs repaired, the defective formingassembly 16 is disengaged from thedrive assembly 300 and then the remaining three formingassemblies 16 are put back into operation. As used herein, abodymaker drive assembly 300 that is structured to operate with less than all formingassemblies 16 engaged thereby is a “limited load”drive assembly 300. Use of a limitedload drive assembly 300 solves the problem(s) noted above. - In an exemplary embodiment, such as shown in
FIGS. 3, 4 and 6 , the mountingassembly 14 further includes a number of formingassembly positioning assemblies 400. There is onepositioning assembly 400 associated with each formingassembly 16. When the mountingassembly body 18 is disposed in a generally horizontal plane, eachpositioning assembly 400 is substantially disposed below the mountingassembly body 18. Each formingassembly positioning assembly 400 is structured to, and does, move (and in this configuration lift/lower) a formingassembly 16. That is, each formingassembly positioning assembly 400 is structured to, and does, move a formingassembly 16 among a first (non-operational) position, such as shown inFIG. 6 , wherein the formingassembly 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 inFIG. 4 , wherein the formingassembly 16 is disposed within an associated mounting assembly planar bodyupper surface recess 34. - In the illustrated exemplary embodiment, each
positioning assembly 400 includes afluid pressure source 402 and a number ofactuators 404 coupled thereto viafluid conduits 406. Thefluid 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 orrigid conduits 406. Control of movement of each actuator 404 may be provided via any suitable control 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, eachpositioning assembly 400 may include one or more suitable locking mechanisms (not numbered, e.g., mechanical and/or electromagnetic arrangements) for securing each formingassembly 16 to mountingassembly 14. - It is to be understood that, when a forming
assembly 16 is being moved between the first and second positions, and when the formingassembly 16 is in the first (non-operational) position, thecam follower assembly 150 is in the first (widely spaced) configuration previously discussed. Further, when the formingassembly 16 is in the second (operational) position, thecam follower assembly 150 is in the second (closely spaced) 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 formingassembly 16 is moved into the machined mounting assembly planar bodyupper surface recess 34. Alternatively, after a formingassembly 16 is disposed in a mounting assembly planar bodyupper surface recess 34, a user brings the formingassembly 16 into the proper alignment by passing guide pins 39 through the associatedguide pin passages guide pin 39 is temporarily disposed in thealignment pin passage 178 of theslider 152 of thecam follower assembly 150 and thealignment passage 344 of thecam 330. Use of the guide pins 39 brings each formingassembly 16 into proper alignment with thecam 330. It is again noted that each formingassembly 16 is, in an exemplary embodiment, an aligned, unitary formingassembly 16; thus, the elements with each formingassembly 16 do not require further alignment. This solves the problem(s) noted above. - In one embodiment, the
bodymaker 10 includes a single formingassembly 16. In another embodiment, thebodymaker 10 includes a plurality of formingassemblies 16. In another embodiment, thebodymaker 10 includes an even number of formingassemblies 16. Thus, in an exemplary embodiment, the number of forming assemblies includes one of a single formingassembly 16, two formingassemblies 16, four formingassemblies 16, six formingassemblies 16, eight formingassemblies 16 or ten formingassemblies 16. Further, and as described above, with formingassemblies 16 disposed about thecam body 332 axis of rotation, the longitudinal axes of the formingassemblies 16 extend generally, or substantially, radially relative to the cam 320 axis of rotation. - Further, in a configuration disclosed above wherein the
bodymaker 10 includes more than two formingassemblies 16, thebodymaker 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 formingassemblies 16, thebodymaker 10 produces four can bodies per cycle. Moreover, with acam 330 rotating at 320 r.p.m., thebodymaker 10 with four formingassemblies 16, or alternately, the formingsystem 12 with four formingassemblies 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 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. Abodymaker 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. - 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,
FIG. 13 shows an overhead view of a layout of abodymaker 10′ in accordance with an exemplary embodiment of the disclosed concept having eight formingassemblies 16 and related machinery (e.g., trimmers). Such layout occupies/requires a floor space having dimensions of about D1′×D2′. In such example both D1′ and D2′ are 366 inches. Hence, the overall floor space occupied/required by such layout is 133,956 in2 or about 930 ft2. In comparison,FIG. 14 shows a layout of eight prior art bodymakers 1 (i.e., the number ofprior art bodymakers 1 needed to achieve the same or similar output asbodymaker 10′ ofFIG. 13 ) and related machinery. Such layout occupies/requires a floor space having dimensions of about D1×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 in2 or about 2,656 ft2, almost three times the floor space as thebodymaker 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 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 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 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 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.
Claims (20)
1. A can bodymaker comprising:
a mounting assembly;
a forming system including:
a plurality of forming assemblies, each forming assembly structured to form a can body independent of the other forming assemblies of the plurality of forming assemblies, each forming assembly coupled to the mounting assembly, each forming assembly including a ram assembly with an elongated ram body, and
a ram drive assembly operatively coupled to each forming assembly, wherein the ram drive assembly is a direct ram drive assembly.
2. The can bodymaker of claim 1 , wherein:
each ram body has a longitudinal axis;
the ram drive assembly includes a prime axis of rotation; and
the longitudinal axis of each ram body extends generally radially outward from the prime axis of rotation of the ram drive assembly.
3. The can bodymaker of claim 2 , wherein the longitudinal axis of each ram body extends generally perpendicular to the prime axis of rotation of the ram drive assembly.
4. The can bodymaker of claim 1 , wherein:
the ram drive assembly includes one of a disk cam or a barrel cam; and
the disk cam or the barrel cam is operatively coupled to each forming assembly.
5. The can bodymaker of claim 1 , wherein the plurality of forming assemblies comprises two forming assemblies with the ram body of each forming assembly positioned in opposition to the other forming assembly.
6. The can bodymaker of claim 1 , wherein:
the ram drive assembly includes a prime axis of rotation, and
the plurality of forming assemblies comprises two forming assemblies positioned relative to each other about the prime axis of rotation of the ram drive assembly at an angle other than 180°.
7. The can bodymaker of claim 1 , wherein:
the ram drive assembly includes a prime axis of rotation, and
the plurality of forming assemblies comprises two forming assemblies positioned relative to each other about the prime axis of rotation of the ram drive assembly at an angle of 180°.
8. The can bodymaker of claim 1 , wherein:
the ram drive assembly includes a disk cam structured to rotate about a prime axis of rotation; and
the plurality of forming assemblies includes four forming assemblies, each disposed about ninety degrees apart about said ram drive assembly prime axis of rotation.
9. The can bodymaker of claim 8 , wherein the forming assemblies are asymmetrical forming assemblies.
10. The can bodymaker of claim 8 , wherein:
the ram drive assembly is structured to move each ram body between a retracted, first position and an extended, second position as well as a number of medial positions between the first positon and the second position; and
no two ram bodies are in the same medial position at one time.
11. The can bodymaker of claim 8 , wherein the forming system is structured to produce 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.
12. The can bodymaker of claim 1 , wherein:
the ram drive assembly is structured to move each ram body between a retracted, first position and an extended, second position as well as a number of medial positions between the first positon and the second position; and
no two ram bodies are in the same medial position at one time.
13. The can bodymaker of claim 1 , wherein the forming assemblies are asymmetrical forming assemblies.
14. The can bodymaker of claim 1 , wherein:
each forming assembly includes a full set of forming assemblies; and
the ram drive assembly is structured to operate with less than the full set of forming assemblies.
15. The can bodymaker of claim 1 , wherein the ram drive assembly is a limited load drive assembly.
16. The can bodymaker of claim 1 , wherein:
each forming assembly includes a stationary assembly and a moving assembly; and
the stationary assembly of each forming assembly is a unified assembly.
17. The can bodymaker of claim 1 , wherein the forming system is structured to produce 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.
18. The can bodymaker of claim 1 , wherein the ram drive assembly is one of: a single source/3-output ram drive assembly, 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, or a single source/10-output ram drive assembly.
19. The can bodymaker of claim 1 , wherein:
the ram drive assembly includes a barrel cam structured to rotate about a prime axis of rotation; and
each ram body has a longitudinal axis extending generally parallel to the prime axis of rotation of the ram drive assembly.
20. The can bodymaker of claim 1 , wherein:
the ram drive assembly includes a prime axis of rotation,
the plurality of forming assemblies comprises at least three forming assemblies, and
the angular spacing about the prime axis of rotation between an adjacent two of the at least three forming assemblies is different than the angular spacing between another adjacent two of the at least three forming assemblies.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US17/726,874 US20220241839A1 (en) | 2020-05-28 | 2022-04-22 | Cam driven multi-output bodymaker |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US16/885,494 US11338351B2 (en) | 2020-05-28 | 2020-05-28 | Cam driven multi-output bodymaker |
US17/726,874 US20220241839A1 (en) | 2020-05-28 | 2022-04-22 | Cam driven multi-output bodymaker |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US16/885,494 Continuation US11338351B2 (en) | 2020-05-28 | 2020-05-28 | Cam driven multi-output bodymaker |
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US20220241839A1 true US20220241839A1 (en) | 2022-08-04 |
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US16/885,494 Active US11338351B2 (en) | 2020-05-28 | 2020-05-28 | Cam driven multi-output bodymaker |
US17/726,874 Pending US20220241839A1 (en) | 2020-05-28 | 2022-04-22 | Cam driven multi-output bodymaker |
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US16/885,494 Active US11338351B2 (en) | 2020-05-28 | 2020-05-28 | Cam driven multi-output bodymaker |
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US (2) | US11338351B2 (en) |
EP (1) | EP4157559A4 (en) |
JP (1) | JP2023527992A (en) |
CN (1) | CN115443196A (en) |
BR (1) | BR112022024237A2 (en) |
WO (1) | WO2021242358A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20210370382A1 (en) * | 2020-05-28 | 2021-12-02 | Stolle Machinery Company, Llc | Cam follower assembly for can bodymaker and can bodymaker including same |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3702559A (en) * | 1971-01-11 | 1972-11-14 | Stolle Corp | Can body making machine |
US3889509A (en) | 1974-04-08 | 1975-06-17 | Gulf & Western Mfg Co | Horizontal can ironing press |
US4774839A (en) | 1982-12-27 | 1988-10-04 | American National Can Company | Method and apparatus for necking containers |
US4519232A (en) * | 1982-12-27 | 1985-05-28 | National Can Corporation | Method and apparatus for necking containers |
US5735165A (en) | 1995-06-23 | 1998-04-07 | The Minster Machine Company | Bodymaker drive system |
US7434442B2 (en) | 2006-08-16 | 2008-10-14 | Werth Advanced Packaging Innovations, Ltd. | Container bodymaker |
JP4623335B2 (en) * | 2009-02-09 | 2011-02-02 | 東洋製罐株式会社 | Seamless can body and method for producing seamless can body |
US9162274B2 (en) | 2012-02-22 | 2015-10-20 | Suzhou SLAC Precision Equipment Co., Ltd. | Dual double-action can body maker |
BR112015021773B1 (en) | 2013-03-12 | 2021-03-30 | Stolle Machinery Company, Llc | BODY FORMER |
US10137490B2 (en) | 2013-08-28 | 2018-11-27 | Stolle Machinery Company, Llc | Outboard hydrostatic bearing assembly for can bodymaker |
-
2020
- 2020-05-28 US US16/885,494 patent/US11338351B2/en active Active
-
2021
- 2021-03-16 EP EP21812259.6A patent/EP4157559A4/en active Pending
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- 2021-03-16 BR BR112022024237A patent/BR112022024237A2/en unknown
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- 2022-04-22 US US17/726,874 patent/US20220241839A1/en active Pending
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20210370382A1 (en) * | 2020-05-28 | 2021-12-02 | Stolle Machinery Company, Llc | Cam follower assembly for can bodymaker and can bodymaker including same |
US11666961B2 (en) * | 2020-05-28 | 2023-06-06 | Stolle Machinery Company, Llc | Cam follower assembly for can bodymaker and can bodymaker including same |
Also Published As
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US20210370384A1 (en) | 2021-12-02 |
CN115443196A (en) | 2022-12-06 |
BR112022024237A2 (en) | 2022-12-27 |
JP2023527992A (en) | 2023-07-03 |
WO2021242358A1 (en) | 2021-12-02 |
US11338351B2 (en) | 2022-05-24 |
EP4157559A1 (en) | 2023-04-05 |
EP4157559A4 (en) | 2024-01-03 |
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