JP2019505393A - Outboard hydrostatic bearing assembly used in can body making machine - Google Patents

Abstract

[Solution]
A hydrostatic / dynamic pressure fluid bearing assembly for the can body making machine 10 is provided. The hydrostatic / dynamic fluid bearing assembly is separate from the ram body 50. Outboard guide bearing assembly 60 includes a carriage assembly 62 and a number of elongated journals 64. The carriage assembly 62 includes a ram coupling 72, a crank coupling 74, and a body 70 that defines a number of journal passages 80. The ram body 50 is coupled to the ram coupling 72. The crank coupling 74 is configured to be coupled to the crank arm 32. Each journal 64 extends through a journal passage 80 in the carriage assembly body. In this configuration, the ram body 50 may form the can body 3 in a conventional manner, but fluid bearing assembly fluid is not applied to the ram body 50. Instead, fluid bearing assembly fluid is supplied to the journal 64.
[Selection] Figure 11

Description

[Cross-reference of related applications]
This application claims the benefit of US patent application Ser. No. 14 / 993,159, filed Jan. 12, 2016, which is hereby incorporated by reference. The US patent application is a continuation-in-part of US patent application No. 14 / 470,987, filed on August 28, 2014, and entitled “OUTBOARD HYDROSTATIC BEARING ASEMBLY FOR CAN BODYMAKER”. The application is incorporated herein by reference. The continuation-in-part application claims the benefit of US Patent Application No. 61 / 870,831, filed on August 28, 2013, which is hereby incorporated by reference.

  The disclosed and claimed concept relates to a can body making machine, and more particularly, a ram assembly comprising an outboard bearing and a shortened ram body. Including can body making machine.

  In general, aluminum cans begin as disk-shaped aluminum (also known as “blanks”) stamped from sheet-like or coiled aluminum. That is, the sheet is fed into a dual action press and a disc-shaped “blank” is cut out of the sheet by the movement of the outer slide / ram. Then, through the drawing process, the inner slide / ram presses the “blank” to produce a cup. The cup has a bottom and a bottom and associated side walls. The cup is fed into one of several body making machines that perform redrawing and ironing operations. More specifically, the cup is placed in the can of the die pack at the entrance of a die pack having a substantially circular opening. The cup is held in place by a redraw sleeve that is part of the redraw assembly. The redraw sleeve is a hollow tubular structure that is disposed inside the cup and biases the cup against the die pack. More specifically, the first die in the die pack is a redraw die but is not part of the redraw assembly. The cup is biased against the redraw die by the redraw sleeve. The other die, that is, the ironing die, is disposed behind the redraw die and is aligned with the redraw die in the axial direction. The ironing die and the redraw die are not part of the redraw assembly. The elongated cylindrical ram assembly 1 shown in FIGS. 1 and 1A includes a carriage 2. The carriage 2 supports a ram body 3 having a punch 4 at the front distal end. The ram and punch are aligned with the apertures of the redraw die and ironing die and are configured to move through the apertures. At the tip of the die pack on the opposite side of the ram is a domer. A dormer is a die configured to form a recessed dome at the bottom of the cup / can.

  Thus, during operation, the cup is placed at one end of the die pack. Cups are usually larger in diameter and wall thickness than a finished can. The redraw sleeve is disposed inside the cup and biases the bottom of the cup against the redraw die. The opening in the redraw die has a smaller diameter than the cup. The elongate ram body, more specifically the punch, passes through the hollow redraw sleeve and contacts the bottom of the cup. As the ram body continues to move forward, the cup moves through the redraw die. Since the aperture of the redraw die is smaller than the original diameter of the cup, the cup is deformed and stretched to become smaller in diameter. As the cup passes through the redraw die, the wall thickness of the cup usually remains the same. As the ram continues to move forward, the stretched cup passes through several ironing dies. Each squeeze die reduces the wall thickness of the cup, thereby extending the cup. The stretched cup bottom engages the dormer, and a recessed dome is formed at the bottom of the cup for final shaping of the can body. At this point, compared to the original shape of the cup, the can body is stretched and has a thinner wall and a dome-shaped bottom.

  During this operation, heat is generated by friction in both the ram assembly and the die pack. This heat is dissipated by the cooling fluid passing through the component and over its surface. The cooling fluid at the surface of the ram body is mostly collected in a seal assembly that is placed between the hydrostatic / hydrodynamic bearing assembly and the re-throttle (or hold down) assembly. . The seal assembly includes a number of seals that conform to the cross-sectional shape of the ram body. As the ram body passes through the seal assembly, the cooling fluid is collected and recirculated.

  When the can body forming operation is completed, the can body is removed from the ram, more specifically from the punch, and is not limited thereto, but is subjected to further steps such as trimming, cleaning, printing, flange forming, inspection, etc. And sent to a filler. In the filling device, the can is removed from the pallet, the contents are injected and the end is attached. The filled cans are repackaged in 6-pack and / or 12-pack cases.

  The ram body moves periodically many times every minute. To achieve this movement, the body making machine also includes a crank assembly having a crank arm. The crank arm is connected to the ram assembly and reciprocates the ram assembly. The ram body is substantially aligned axially with the hollow redraw sleeve and die pack. This alignment is important because misalignment causes the ram to wear out the die and vice versa. As shown in FIG. 1A, ram body alignment is improved by a ram guide assembly 5 (hereinafter referred to as a “ram guide”) that guides the ram body through tooling. There are additional hydrostatic / dynamic fluid bearing assemblies 6 on either side of the ram assembly carriage, but these bearings do not "guide" the ram. These hydrostatic / dynamic pressure fluid bearing assemblies 6 are arranged in channels and have ports 7. Ports 7 are disposed on the top, side and bottom surfaces to provide lubricating fluid. Due to various factors, such as, but not limited to, the static / dynamic fluid bearing assemblies 6 being immediately adjacent to each other and the relatively short length of the carriage, these additional static / dynamic The hydrodynamic bearing assembly 6 is prevented from controlling the orientation and alignment of the ram body. That is, a small “wobble” amount of the carriage in the channel prevents the carriage and hydrostatic / dynamic pressure fluid bearing assembly 6 from guiding the ram body.

  Thus, as used herein, “guide” when used with respect to ram body bearings means controlling the orientation and alignment of the ram body. Thus, as used herein, a “guide bearing” or “guide bearing assembly” is configured to control and control the orientation and alignment of the ram body. Bearings such as the prior art hydrostatic / dynamic pressure fluid bearing assembly 6 on either side of the carriage of the ram assembly may have a minor effect or may only affect the orientation and alignment of the ram body. And not a “guide” bearing assembly as used herein. In other words, noting that the ram body must be guided, if the ram body does not have a guide, the bearing assemblies on both sides of the ram carriage are “guide bearing assemblies”. However, if the ram body has a guide, the bearing assemblies on both sides of the ram carriage are not “guide bearing assemblies”.

  The guide assembly is typically located immediately upstream of the redraw assembly (near the crank arm). The fluid bearing assembly includes a body that defines a passage. The ram body extends through the passage of the fluid bearing assembly. Further, the fluid bearing assembly introduces fluid, but not limited to oil, between the body of the fluid bearing assembly and the ram body. By controlling the amount and pressure of the fluid, the alignment of the ram body with the hollow redraw sleeve and die pack can be accurately controlled. The fluid in the fluid bearing assembly is collected and reused by the seal assembly.

  A disadvantage of this configuration is that the fluid in the fluid bearing assembly is not completely removed by the seal assembly. Thus, when cooling fluid is used, a portion of the fluid in the fluid bearing assembly remains in the ram body. In addition, the fluid mixes and the collected cooling fluid becomes contaminated. This also means that fluids in the fluid bearing assembly, which can be expensive oil, are gradually lost.

  Another disadvantage is that the ram body must be long enough to extend through the seal and fluid bearing assemblies as well as the die pack. A typical 12 fluid ounce can body would have a ram body length of about 50 inches to 52 inches when using a 24 inch stroke for a typical 12 fluid ounce can. The length of the ram depends on the length of the stroke, thereby supporting different sized can bodies. For example, the following is a table showing typical ram lengths and associated strokes.

  Any of these lengths of ram body are susceptible to damage due to wear from normal use.

  As described above, the ram body passes through the die pack in a first direction when forming the can body, and then reverses the die pack after the can body is formed. A die pack of a body manufacturing machine has a plurality of dies spaced apart from each other, and each die has an opening. The opening of each die is slightly smaller than the adjacent upstream die. Subsequent die openings in the die pack have a smaller inner diameter, ie, a smaller opening. Therefore, when the ram passes aluminum through the rest of the die pack, the aluminum cup becomes thinner. The space between the punch and the redraw die is typically an unknown gap (0.001 to 2 inches per side) exceeding the metal thickness, and less than 0.004 inches for the last ironing die. A typical aluminum gauge used to make a typical 12 fluid ounce can is today 0.0108 inches in practice. However, such a narrowing of the space is disadvantageous especially in the return process.

Depending on the can diameter, can height and machine model, this elongated horizontal ram whose stroke length varies from 22 to 30 inches and the throughput frequency ranges from 210 to 450 strokes per minute (SPM) And the punch is accompanied by sagging or bending of the ram. In its simplest form, the ram is depicted as being cantilevered at one end and free at the other end. The upper theorized beam type shows ram deflection due to the weight of the tungsten carbide punch. The lower theorized beam type shows the deflection of a long steel ram due to its own weight. The total deflection of the horizontal ram in known body making machines is a combination of these two effects. The typical weight of the ram and punch assembly is approximately 50 lbf in total. The maximum values of deflection (δ), or ram droop, are an elongated light steel ram (ρ _steel = 0.284 lb / in ³ ) and heavy tungsten carbide at the ram tip (ie WC−ρ _WC = 0. 567 lb / in ³ ) linearly proportional to the weight of the punch (point load P or distributed load ω). However, the maximum value of deflection or ram sag (conceptualized as a cantilever) is the length (l), that is, the length of its fourth power for an elongated steel ram, and that for a heavy carbide punch at the ram tip It depends on the length of the cube. As is well known, I is an area moment of inertia. Thus, if the ram can be shortened, deflection or ram droop can be significantly reduced. The concept of outboarding the hydrostatic / dynamic ram bearings outside the main ram itself is essential to reduce the length of the ram. This is because the ram no longer requires an additional length to be supported by the bearing throughout the can body manufacturing process. Lamb sag is a problem in the return process where no can is formed. In the return process, the punch and ram tend to come into contact with the tooling, which causes wear and damage. One major reason for this is the contact between the punch and ironing die (mainly the third or final iron) in the return process of the machine.

  Further, as described above, the ram body passes through a hydrostatic / dynamic pressure fluid bearing assembly. The hydrostatic / dynamic pressure fluid bearing assembly is secured to the bulkhead of the housing assembly of the can body making machine. This means that the length of the cantilevered portion of the ram body changes during the body manufacturing cycle. That is, when the ram body is retracted and is in the first position, the length of the cantilevered portion of the ram body is relatively short. Conversely, when the ram body extends and is in the second position, the length of the cantilevered portion of the ram body is relatively long. The dynamic nature of the length of the cantilevered portion of the ram body means that the amount of sag changes dynamically as well. This means that the system must compensate for sag drooping or be dynamic.

  In addition, the ram droop and other contact between the ram body and the die pack prevents the ram body from aligning with the die pack. In other words, the contact between the ram body and the die pack creates an offset force that acts in various directions around the center of gravity of the ram assembly. These offset forces create a torque around the center of gravity of the ram assembly, resulting in the aforementioned “wobble”. This is a drawback.

  Accordingly, there is a need for a ram assembly that includes a ram body that is less susceptible to ram drooping. More specifically, there is a need for a ram body that is short in length. That is, the length of the ram body is a defined problem.

  These needs and others are met by at least one embodiment of the present invention. The present invention, in one embodiment, has a diameter of, for example, about 2.0 to 2.5 inches and a length of about 30.0 inches to 32.0 inches for a typical 12 fluid ounce can. Alternatively, a ram assembly having a ram body that is approximately 31.0 inches is provided. In another exemplary embodiment, a ram seal assembly is used and the length of the ram body is from about 33.0 inches to about 36.0 inches, or about 34.5 inches. In this embodiment, the diameter of the ram body is about 1.5 to about 3.5 inches, or about 2.5 inches for a typical 12 fluid ounce can.

  In another embodiment, the ram assembly of the can body making machine includes an outboard guide bearing assembly. The outboard guide bearing assembly is "outboard", i.e., spaced from the ram body as used herein. The outboard guide bearing assembly includes a carriage assembly and a bearing assembly. The bearing assembly includes two bearings disposed on opposite sides of the carriage assembly in the exemplary embodiment. In the exemplary embodiment, the bearing assembly is a hydrostatic / dynamic pressure bearing assembly. Using an outboard guide bearing assembly allows the ram body to be shortened because the ram body need not extend through the bearing assembly and die pack.

  In another embodiment, a ram assembly of a can body making machine includes an elongated, generally hollow ram body and a tensioning assembly. The ram body includes a proximal end, a central portion and a distal end. The tension assembly includes an elongated support member. The support member of the tension assembly includes a proximal end and a distal end. The tension assembly support member is mostly disposed within the ram body, the proximal end of the tension assembly support member is coupled to the proximal end of the ram body, and the distal end of the tension assembly support member is coupled to the ram body. Coupled to one of the central portion or the distal end of the ram body.

  In another embodiment, the guide bearing assembly of the carriage assembly is configured to direct the ram body into a passage through the die pack. That is, the guide bearing assembly of the carriage assembly includes fluid producing elements that are adapted to move over a selected path of travel (aligned with the longitudinal axis of the die pack passage). Sufficiently spaced to change the orientation of the ram body or punch in a manner intended to position the longitudinal axis of the ram body. The guide bearing assembly of the carriage assembly generates a sufficient but reasonable amount of fluid to establish an aligning fluid bearing stiffness.

  A full understanding of the invention can be obtained by reading the following description of the preferred embodiments in conjunction with the accompanying drawings, in which:

FIG. 1 is an isometric view of a prior art ram assembly. FIG. 1A is an isometric view of a prior art ram assembly. FIG. 1B is a side view of a prior art ram assembly. FIG. 2 shows a longitudinal section of the body making machine with the ram assembly in the first position. FIG. 3 shows a longitudinal section of the body making machine with the ram assembly in an intermediate position. FIG. 4 shows a longitudinal section of the body making machine with the ram assembly in the second position. FIG. 5 shows a top view of the body making machine with the ram assembly in the first position. FIG. 6 shows a plan view of the body making machine with the ram assembly in an intermediate position. FIG. 7 shows a top view of the body making machine with the ram assembly in the second position. FIG. 8 is an isometric view of the outboard guide bearing assembly. FIG. 9 is an isometric view of the outboard carriage assembly. FIG. 10 is a cross-sectional view of another embodiment of a ram body. FIG. 10A is a detailed cross-sectional view of the central portion of the ram body. FIG. 10B is a detailed cross-sectional view of the proximal end of the ram body. FIG. 11 is a first isometric view of another embodiment of an outboard guide bearing assembly. FIG. 12 is a second isometric view of another embodiment of an outboard guide bearing assembly. FIG. 13 is a plan view of another embodiment of an outboard guide bearing assembly. FIG. 14 is a cross-sectional view of another embodiment of a ram body. FIG. 14A is a detailed cross-sectional view of another embodiment of a central portion and a distal portion of a ram body. FIG. 15 is a top view of another embodiment of an outboard guide bearing assembly. FIG. 16 is a cross-sectional view of the outboard guide bearing assembly. FIG. 17 is a table showing formulas related to ram deflection. FIG. 18 is a table showing the load equation of the cantilever beam. FIG. 19 is an isometric view of another embodiment. FIG. 20 is another isometric view of another embodiment. FIG. 21 is an exploded isometric view of another embodiment. FIG. 22A is a top view of the ram assembly showing the center of gravity of the ram assembly. FIG. 22B is a side view of the ram assembly showing the center of gravity of the ram assembly. FIG. 22C is a front view of the ram assembly showing the center of gravity of the ram assembly.

  For example, “clockwise”, “counterclockwise”, “left”, “right”, “top”, “bottom”, “upward”, “downward”, and derivatives thereof are used herein. Reference to orientation relates to the orientation of elements shown in the drawings and does not limit the scope of the claims, unless explicitly stated in the claims.

  As used herein, the singular forms “a” and “the” include plural references unless the context clearly dictates that the plural is not included.

  As used herein, a statement that two or more parts or components are “coupled” is used directly or indirectly, ie, one or more, as long as the link occurs. It is meant that the parts are joined or operate together via the middle part or component of the. As used herein, “directly coupled” means that two elements are in direct contact with each other. As used herein, “fixedly coupled” or “fixed” means that two components are coupled to move as one while maintaining a constant orientation relative to each other. Means that Thus, when two elements are combined, all parts of these elements are combined. However, a description of a particular portion of the first element that is coupled to the second element, such as the first end of the mandrel that is coupled to the first wheel, A part means that it is located closer to the second element than the other part. Furthermore, if an object placed on another object is held in place only by gravity, it will be “coupled” to the lower object unless the upper object is substantially maintained in place. It has not been. That is, for example, the book on the table is not coupled to the table, but the book bonded to the table is coupled to the table.

  As used herein, a statement that two or more parts or components “engage” each other means that the element is directly or via one or more intermediate elements or components. Means exerting or energizing each other.

  As used herein, the term “unitary” means that the components are made as a single piece or unit. That is, a component that includes pieces that are made separately and then joined together as a unit is not an “integral” component or object.

  As used herein, the term “some” means one or an integer greater than one (ie, a plurality).

  As used herein, a “coupling assembly” includes two or more couplings or coupling components. Multiple components of a coupling or coupling assembly are generally not part of the same or other components. Accordingly, multiple components of the “coupling assembly” may not be described simultaneously in the following description.

  As used herein, a “coupling” or “coupling component” is one or more components of a coupling assembly. That is, the coupling assembly includes at least two components configured to be coupled together. The components of the coupling assembly are understood to be compatible with each other. For example, in a coupling assembly, if one coupling component is a snap socket, the other coupling component is a snap plug. Or, if one coupling component is a bolt, the other coupling component is a nut.

  As used herein, “related” means that the elements are part of the same assembly and / or cooperate or operate in some way / with each other. . For example, an automobile has four tires and four hub caps. While all elements are combined as part of the vehicle, each hub cap is understood to be “associated” with a particular tire.

  As used herein, “corresponding” indicates that two structural elements are sized and shaped similar to each other and can be coupled to each other with a minimum amount of friction. Thus, the opening "corresponding" to the member is slightly larger than the member so that the member can pass through the opening with the least amount of friction. This definition is changed when two components are said to “snugly” fit or “just correspond” to each other. In such a situation, the difference in component sizes is even smaller, which increases the amount of friction. If the element defining the opening and / or the component inserted into the opening is made of a deformable or compressible material, the opening may be slightly smaller than the component inserted into the opening. This definition is further modified when two components are said to be “mostly corresponding”. “Almost corresponding” means that the size of the opening is very close to the size of the element inserted therein. That is, it is not close enough to cause significant friction, as in the case of a close fit, but has more contact and friction than a “corresponding fit”, ie “slightly larger” fit. Further, as used herein, “loosely correspond” means that the slot or opening is made larger than the element disposed therein. This means that an increase in the size of the slot or opening is intentional and is greater than the manufacturing tolerance. Furthermore, with respect to a surface formed by two or more elements, a “corresponding” shape means that the surface shape, eg, curvature, is similar.

  As used herein, “configured to [verb]” means that a particular element or assembly is shaped, sized and arranged to perform a particular verb. , And / or having a structured structure. For example, a member “configured to move” is movably coupled to another element and includes an element that moves the member. Alternatively, the member is otherwise configured to move in response to other elements or assemblies. Thus, as used herein, “[configured to be a verb or“ become [X] ”] refers to a structure, not a function. Further, as used herein, “[configured to be a verb or“ become [X] ”] means that a particular element or assembly performs a particular verb. Or it is intended and designed to be [X]. Therefore, an element that may perform a specific verb, but not so intended or set, is “configured to be a [verb or“ become [X] ”]. Absent.

  As used herein, “at” means above or near.

  As used herein, “cantilever” means a protruding beam or other horizontal member that is supported at one or more points.

  As used herein, a “tensile member” is a structure that has a maximum length when subjected to tension, or is otherwise quite flexible, such as a chain or cable. However, it is not limited to these.

  As shown in FIGS. 2-7, the can body making machine 10 is configured to convert the cup 2 (FIG. 2) into a can body 3 (FIG. 2). As described below, the cup 2, the ram body 50, the passage through the die pack 16, and other elements are assumed to have a generally circular cross-section. However, it is understood that the cup 2 and the resulting can body 3 and the elements that interact with the cup 2 or the can body 3 may have shapes other than substantially circular. The cup 2 has a bottom 4 and an associated side wall 5 defines a substantially enclosed space (not shown). The end of the bottom 4 of the cup is open.

  The can body making machine 10 includes a housing assembly 11, a reciprocating ram assembly 12, a drive mechanism 14, a die pack 16, a redraw assembly 18, and a cup feeder 20. Each element identified here is coupled to the housing assembly 11. In the exemplary embodiment, drive mechanism 14 includes a crank assembly 30 that includes a reciprocating crank arm 32. As is well known, in each cycle, the cup feeder 20 places the cup 2 in front of the die pack 16 with the open end facing the ram assembly 12. The die pack 16 defines a passage 17 through several dies (not shown). When the cup 2 is in front of the die pack 16, the redrawing sleeve 40 biases the cup 2 against the redrawing die 42. As is well known, the drive mechanism 14 drives the redraw sleeve 40, eg, via several secondary crank arms 36 (FIG. 5), so that the ram assembly 12 advances immediately after the redraw sleeve 40 advances. The timing is set. In the exemplary embodiment, housing assembly 11 does not include a seal assembly for ram body 50. That is, since the ram is not lubricated, the ram body 50 does not extend through a seal assembly configured to collect lubricant.

  In general, the ram assembly 12 includes an elongated, generally circular ram body 50 that has a proximal end 52, a distal end 54, and a longitudinal axis 56. The distal end 54 of the ram body includes a punch 58. The proximal end 52 of the ram body is connected to the drive mechanism 14. The drive mechanism 14 provides a reciprocating motion to the ram body 50 that moves back and forth generally along its longitudinal axis 56. That is, the ram body 50 is configured to reciprocate between the first retracted position and the second advanced position over the selected movement path. In the first retracted position, the ram body 50 is separated from the die pack 16. In the second extended position, the ram body 50 extends through the die pack 16. Thus, the reciprocating ram assembly 12 passes through the redraw sleeve 40, engages the cup 2 and advances forward (to the left in the figure). The cup 2 moves through a redraw die 42 and several ironing dies (not shown) in the die pack 16. The cup 2 is converted into the can body 3 in the die pack 16 and then taken out therefrom. As used herein, “cycle” is understood to mean a cycle of the ram assembly 12 that begins at the first retracted position of the ram assembly 12.

  Therefore, when the punch 58 carrying the can body 3 passes through the die pack 16, the can body 3 is deformed. More specifically, the can body 3 becomes elongated and the side wall 5 becomes thinner. At the end of the forming process, a dome may be formed on the bottom 4 of the can by known methods. Further, at the beginning of the return process, the can body 3 is removed from the punch 58, which may be any known method or device, for example, a gas that is compressed inside the stripper device or the can body 3. However, it is not limited to these methods. At the start of the next forming step, a new cup 2 is placed over the end of the punch 58.

  As shown in FIGS. 5-9, in the exemplary embodiment, the ram assembly 12 also includes an outboard guide bearing assembly 60. In the first exemplary embodiment, the outboard guide bearing assembly 60 includes a carriage assembly 62 and several elongated journals 64. In some embodiments not shown, a single journal 64 is positioned vertically below the ram body 50 and is aligned with the ram body 50, i.e., parallel to the ram body 50 but spaced apart. ing. In the illustrated embodiment, there are two journals 64, a first journal 66 and a second journal 68, which are aligned substantially horizontally with the ram body 50, ie, the ram. It lies in the same horizontal plane as the main body 50. In the exemplary embodiment, the first journal 66 and the second journal 68 are coupled to the body assembly housing assembly 11 slightly longer than the stroke length of the ram assembly 12.

  The carriage assembly 62 includes a generally rectangular body 70 that includes a ram coupling 72 and a crank coupling 74 in an embodiment having two journals 66, 68, which defines several journal passages 80. To do. In the exemplary embodiment, ram coupling 72 is configured to support ram body 50 in a substantially horizontal direction. Crank coupling 74 is a generally circular bearing 76 configured to extend through a generally circular opening (not shown) in crank arm 32 in the exemplary embodiment.

  In the exemplary embodiment, the number of journal passages 80 includes a first pair 82 of substantially aligned journal passages and a second pair 84 of substantially aligned journal passages. The journal passages 80 in each pair of journal passages 82, 84 are spaced apart. In the exemplary embodiment, the journal passages 80 in each pair of journal passages 82, 84 are spaced apart about 8.0 to 12.0 inches, or about 10.25 inches longitudinally. The first journal 66 extends through a first pair 82 of substantially aligned journal passages, and the second journal 68 extends through a second pair 84 of substantially aligned journal passages. In the exemplary embodiment, journal passages 80 are disposed at each corner of the rectangular body 70 of the carriage assembly.

  Each journal passage 80 in each pair of journal passages 82, 84 includes a bearing assembly 90. In certain embodiments, the bearing assembly 90 includes a carbon fiber bearing (not shown). Such carbon fiber bearings do not require a lubricant and do not include, but are not limited to, moving elements such as ball bearings. Thus, in some embodiments, the bearing assembly 90 is a “static bearing assembly”. That is, a “static bearing assembly” as used herein is a bearing assembly that does not require a lubricant and does not include moving elements.

  In such a configuration, the carriage assembly body 70 is configured to move substantially in a plane and reciprocate between a first retracted position and a second advanced position. When the carriage assembly body 70 is in the first position, the ram body 50 is in its first position, and when the carriage assembly body 70 is in the second position, the ram body 50 is in its second position. It is understood that there is. Thus, the carriage assembly body 70 has an axis of motion 78 that is substantially aligned with the longitudinal axis 56 of the ram body. That is, the axis of motion 78 of the carriage assembly body may be parallel to and spaced from the longitudinal axis 56 of the ram body, or may be disposed substantially on the longitudinal axis 56.

  In another embodiment, each bearing assembly 90 is a hydrostatic / dynamic pressure bearing assembly 100, as best shown in FIGS. As used herein, a “hydrostatic / dynamic pressure bearing assembly” is either a static pressure bearing assembly, a dynamic pressure bearing assembly, or a combination thereof. As is well known, the hydrostatic / dynamic bearing assembly 100 includes a housing 102 and a bearing 104. The bearing 104 is disposed in the housing 102. The bearing 104 defines a passage 80 through which the journal 64 extends as described above. The hydrostatic / dynamic bearing assembly 100 or outboard guide bearing assembly 60 further includes a lubricant sump 106, a pump assembly 108, and a plurality of conduits 110, all shown schematically. The hydrostatic / dynamic bearing assembly conduit 110 includes a conduit that extends through the housing 102 and the bearing 104 of the hydrostatic / dynamic bearing assembly. As is well known, a lubricant, such as but not limited to, oil passes through the conduit 110 and is disposed between the bearing surface and the journal 64. Alternatively, linear motion of the bearing 104 draws fluid to the inner surface of the bearing 104 to form a lubricating wedge or fluid lift below or around the journal 64.

  Since the hydrostatic / dynamic bearing assembly 100 is remote from the ram body 50 in the exemplary embodiment, cross-contamination between the coolant and the hydrostatic / dynamic bearing assembly lubricant is greatly reduced. Thus, in the exemplary embodiment, the outboard guide bearing assembly 60 does not include a seal assembly that collects lubricant and returns the lubricant to the lubricant sump 106 or filter assembly. Rather, a portion of the housing assembly 11, ie, the lower portion of the outboard guide bearing assembly 60, is generally hollow and defines an enclosed space that acts as a sump 106. In such a configuration, lubricant from journal 64 enters sump 106. Further, unlike the ram body 50, the journal 64 is not heated to the temperature at which cooling fluid is required. Thus, there is no cooling assembly associated with journal 64 and / or hydrostatic / dynamic bearing assembly 100. There is also no filter assembly associated with the journal 64 and / or the hydrostatic / dynamic bearing assembly 100 because the lubricant need not be separated from the cooling fluid.

  In the exemplary embodiment, when assembled, the first journal 66 and the second journal 68 are aligned horizontally, i.e., in the same generally horizontal plane, as previously described. Furthermore, the first journal 66 and the second journal 68 extend through two pairs 82, 84 of journal passages. Thus, the carriage assembly body 70 is configured to move substantially in a horizontal plane. Furthermore, the ram body 50 is also coupled, directly coupled, or fixed to the ram coupling 72 of the carriage assembly in the exemplary embodiment. More particularly, the proximal end 52 of the ram body is coupled to, directly coupled to, or secured to the ram coupling 72 of the carriage assembly. Further, in the exemplary embodiment, ram body 50 is disposed in a horizontal plane defined by first journal 66 and second journal 68. The ram body 50 and the carriage assembly body 70 move in a direction substantially aligned with the longitudinal axis 56 of the ram body and, more specifically, reciprocate. Thus, the ram coupling 72 of the carriage assembly is configured to support the ram body 50 substantially in the plane of travel.

  By utilizing the outboard guide bearing assembly 60, the can body making machine 10 can operate without the seal assembly being disposed around the ram body 50 as described above. Further, the ram body 50 does not pass through the hydrostatic / dynamic bearing assembly or ram guide. Thus, unlike known ram bodies that must be long enough to pass through these elements / assemblies and die pack 16, the ram body 50 of the exemplary embodiment is sufficient to pass through the die pack 16. It just needs a long length. This reduction in the length of the ram body 50 reduces the amount of ram sag, thereby reducing wear on the ram body 50 and the die pack 16. In the exemplary embodiment, the length of the ram body 50 is about 30.0 inches to 32.0 inches, and in another embodiment, the length is about 31.0 inches. That is, the change in size improves the disadvantages known in the known art.

  There are several sizes of known ram body 50. The dimensions specified above are associated with a ram body 50 sized for an exemplary embodiment, such as a standard 12 fluid ounce can. In the prior art, the length of such a ram body was about 50 inches to 52 inches when using a 24 inch stroke. Accordingly, it is understood that the disclosed invention allows the length of the ram body to be reduced by about 40% plus or minus about 1 inch. Other known ram body lengths include 45.387 inches, 50.0 inches, 51.0 inches and 57.0 inches, including those plus or minus about 1 inch. Thus, the disclosed invention also provides ram bodies (not shown) that are all about plus or minus about 1 inch and are about 27.0 inches, 30.0 inches, and 34.2 inches long. Alternatively, broadly speaking, the length of the reduced ram body 50 is approximately 26.0 inches to 36.0 inches, all of which are shorter than known ram body lengths. That is, the length of the “reduced length ram body” as used herein is about 26.0 inches to 36.0 inches.

  In another exemplary embodiment, as shown in FIGS. 11-13 and 19-20, outboard guide bearing assembly 160 includes a carriage assembly 162, which includes a ram cup. It includes a body 170 having a ring 172, a crank coupling 174 and several guide bearing assemblies 180, as well as a pump assembly 108 and a plurality of conduits 110 as before. As described above, the guide bearing assembly 180 of the carriage assembly is spaced from the ram body 50. That is, as described above, the carriage assembly body 170 in the exemplary embodiment is generally rectangular and includes a front axial surface 171, a first side 173, and a second side 175. The ram coupling 172 is disposed on the front axial surface 171 of the carriage assembly body, ie, the front surface through which the axis of motion passes. The ram coupling 172 is configured to support the ram body 50 in a substantially horizontal direction. As described above, the carriage assembly body 170 is configured to move substantially in a plane and reciprocate between a first retracted position and a second advanced position.

  In the exemplary embodiment, the guide bearing assembly 180 of the carriage assembly includes two guide bearing assemblies 180 of the carriage assembly, namely, a first guide bearing assembly 180A of the carriage assembly and a second guide bearing assembly 180B of the carriage assembly. including. In the exemplary embodiment, the first guide bearing assembly 180A of the carriage assembly is disposed and coupled to the first side 173 of the body of the carriage assembly, and the second guide bearing assembly 180B of the carriage assembly is coupled to the carriage assembly. Disposed on and coupled to the second side 175 of the body. It will be further appreciated that the elements of the first guide bearing assembly 180A and the second guide bearing assembly 180B of the carriage assembly are also coupled to the body assembly housing assembly 11, as described below. Note that the ram body 50 is coupled to the front shaft surface 171 of the carriage assembly body, and the first and second guide bearing assemblies 180A and 180B of the carriage assembly include the first side surface 173 of the carriage assembly body. Note that the guide bearing assemblies 180A, 180B of the carriage assembly are separated from the ram body 50, and coupled to the second side 175.

  Since the first guide bearing assembly 180A and the second guide bearing assembly 180B of the carriage assembly are almost similar, only one will be described. However, each guide bearing assembly 180A, 180B of the carriage assembly includes elements that will be described hereinafter, and those elements associated with the first guide bearing assembly 180A of the carriage assembly are denoted by the reference letter “A” by the carriage character “A”. The elements associated with the second guide bearing assembly 180B of the assembly are identified by the reference letter “B”, but those elements are identified even if their indication is not given in the first description for each element. It should be understood to be included. Further, hereinafter, the names of the components of each guide bearing assembly 180 of the carriage assembly may be shortened to “first [X]” and “second [X]”. For example, in the exemplary embodiment, each of the first guide bearing assembly 180A and the second guide bearing assembly 180B of the carriage assembly includes a saddle 186 described below. Saddle 186 may hereinafter be identified as “first saddle 186A” or “second saddle 186B”. It is understood that the terms “first” and “second” identify the guide bearing assembly 180 of the carriage assembly with which the part is associated.

  In the exemplary embodiment, guide bearing assembly 180 of the carriage assembly includes a first component 182 and a second component 184. The first component 182 of the guide bearing assembly of the carriage assembly is a saddle 186 and the second component 184 of the guide bearing assembly of the carriage assembly is a journal channel 188. In other words, the journal channel 188 used in this specification is a channel that defines a movement route, and is similar to the journals 66 and 68 described above. Further, as used herein, a “saddle” is a sized structure that approximately matches the associated channel 188. That is, the cross-sectional shape of saddle 186 is similar to channel 188, but is slightly smaller and has a reduced longitudinal dimension. In this instrument configuration, saddle 186 is configured to travel through channel 188. In the exemplary embodiment, each saddle 186 is integral with the body 170 of the carriage assembly.

  In the exemplary embodiment, journal channel 188 is formed of several substantially flat surfaces to form a generally square, C-shaped channel. That is, the channel 188 has a substantially rectangular cross section. Accordingly, the corresponding saddle 186 has a substantially rectangular cross section as well. Further, as shown in FIG. 12, in the exemplary embodiment, saddle 186 is a substantially parallelepiped structure. In another embodiment not shown, the channel 188 and saddle 186 have a trapezoidal cross-sectional shape.

  Further, in an exemplary embodiment, guide bearing assembly 180 of the carriage assembly is a hydrostatic / dynamic bearing assembly. In this embodiment, the first component 182 of the bearing assembly is coupled to the lubricant sump 106 and is configured to be in fluid communication with the lubricant sump 106. That is, the saddle 186 includes a number of fluid ports 190 coupled to the lubricant sump 106 and in fluid communication with the lubricant sump 106. As previously described, several conduits 110 provide lubricant fluid communication, and pump assembly 108 can pump lubricant from sump 106 through fluid port 190. Several conduits 110 pass through the carriage assembly body 170 in an exemplary embodiment. In this configuration, a layer of lubricant is disposed between the first component 182 of the guide bearing assembly of the carriage assembly and the second component 184 of the guide bearing assembly of the carriage assembly.

  In the exemplary embodiment, the second component 184 of the guide bearing assembly of the carriage assembly includes a gib assembly 192. The jib assembly 192 includes several, typically two generally parallel, flat members (not shown) that are spaced apart adjustable coupling components such as, but not limited to, screws. They are joined by a bar (not shown). The relative spacing and angle of the flat members may be adjusted by actuating adjustable coupling components. For example, if the journal channel 188 is a generally square, C-shaped channel having three generally flat surfaces, each surface may be formed by a jib assembly 192, respectively. That is, one of the flat members of each jib assembly 192 forms each flat surface of a square, C-shaped channel. In this configuration, characteristics such as channel surface or journal channel 188 cross-sectional area alignment can be adjusted.

  In the exemplary embodiment, guide bearing assembly 180 of the carriage assembly is configured to direct ram body 50 or punch 58 into a passage through die pack 16. As used herein, “configured to orient the ram body” to the longitudinal axis of the die pack passage 17 aligns the longitudinal axis of the ram body 50 with the axis of the die pack 16. By changing the orientation of the ram body or the punch in a way intended, this means that the ram body 50 does not need to be supported by the guide bearing. The orientation of the ram body 50 reduces misalignment between the punch 58 and the die pack 16 and reduces the above-described “wobble”. That is, prior art bearing assemblies, including hydrostatic / dynamic bearing assemblies, affect the orientation of the associated ram body 50 or punch 58, but other assemblies such as, but not limited to, guide assemblies The orientation of the main body 50 or the punch 58 was substantially controlled. That is, the hydrostatic / dynamic bearing assembly 100 has a compensation effect. For example, in a carriage assembly body 170 that includes a hydrostatic / dynamic pressure bearing assembly 100, any offset of the carriage assembly 62 relative to the channel 188 is such that the first component 182 of the carriage assembly guide bearing assembly and the carriage assembly guide bearing assembly. The gap between the second component 184 and the second component 184 is narrowed at one place and increased at another place. This change in the gap changes the fluid pressure at those locations, i.e., increases the pressure that narrows the gap and decreases the pressure that increases the gap. This in turn causes the carriage assembly 62 to be reoriented to balance the pressure. As shown in FIG. 1, the compensation effect of a prior art hydrostatic / dynamic pressure bearing assembly 100 in which pads are positioned adjacent to each other, as used herein, is “to direct the ram body. "Not configured to".

  In other words, various features of prior art bearing assemblies, including but not limited to manufacturing tolerances, including static / dynamic bearing assemblies, and static / dynamic bearings immediately adjacent to each other. The position of the assembly allowed the ram body or punch to swing relative to the housing assembly of the can body making machine. Thus, prior art hydrostatic / dynamic bearing assemblies required a ram guide. As used herein, “configured to direct the ram body” means to substantially control the orientation of the ram body 50 or punch 58. In order to substantially control the orientation of the ram body 50 or punch 58, the bearing assembly, including the guide bearing assembly 180, controls the orientation of the ram body 50 or punch 58 in a manner intended as a result of exceeding the compensation effects described above. Must. As used herein, “controlling the orientation of the ram body or punch” (50, 58) means that the hydrostatic / dynamic pressure bearing assembly 100 includes the following features. (1) In a manner intended to position the longitudinal axis of the ram body 50 so that the fluid generating elements of the guide bearing assembly 180 of the carriage assembly are “sufficiently spaced” and move over a selected travel path. The direction of the ram body 50 or the punch 58 changes. (2) The guide bearing assembly 180 of the carriage assembly generates a sufficient but reasonable amount of fluid to establish the robustness of the aligning fluid bearing. As described below, in the exemplary embodiment, the fluid generating element of the guide bearing assembly 180 of the carriage assembly is a thrust pad assembly 400.

  As used herein, “generating” means passing fluid through the pump assembly 108, the plurality of conduits 110, and the guide bearing assembly 180 of the carriage assembly. That is, “occurrence” does not mean “generation”. Further, “generation” refers to passing the fluid as a sufficient amount of bearing fluid through the pump assembly 108, the plurality of conduits 110, and the guide bearing assembly 180 of the carriage assembly so that the bearing fluid passes through the guide bearing assembly 180. Means to act, i.e., to act harder. Accordingly, with respect to “generating a reasonable amount of fluid sufficient to establish the robustness of the aligning fluid bearing”, the first component 182 and the second component 184 of the guide bearing assembly The fluid disposed therebetween effectively eliminates wobbling of the ram body 50 or punch 58 relative to the can assembly machine housing assembly 11 and is sufficient to align the longitudinal axis of the ram body 50 with the axis of the die pack 16. It is understood that it is pressure. This is not possible with the hydrostatic / dynamic bearing assembly 100 in any configuration. As an impossible example, the hydrostatic / dynamic bearing assembly 100 including the pump and the hydrostatic / dynamic bearing assembly 100 shown in FIG. 1 (and immediately adjacent to each other) is substantially infinite. Such a hydrostatic / dynamic pressure bearing assembly can generate a large amount of fluid to establish the robustness of the aligning fluid bearing. However, it is understood that the fluid flow characteristics of the pump assembly 108, the optional conduit 110, and the hydrostatic / dynamic bearing assembly 100 are limited by physics and current technology, so nearly infinite fluid flow is It is not “valid”. Thus, as used herein, “creating a sufficient amount of fluid that is sufficient to establish the strength of a self-aligning fluid bearing” means that the fluid in the bearing assembly is It means that the pressure is sufficient to effectively eliminate wobble of the ram body 50 or punch 58 against the housing assembly 11 of the can body making machine using known components. Thus, for example, given a nearly infinite fluid flow rate, a “hydrostatic / dynamic pressure bearing assembly” that is “surfaceally capable of“ establishing the strength of a self-aligning fluid bearing ”” can be used to “direct the ram body” Is not "configured". This is because such a fictitious hydrostatic / dynamic bearing assembly is “sufficient to establish the strength of a self-aligning fluid bearing but does not generate a reasonable amount of fluid”. In other words, infinite fluid flow is not “reasonable”. Further, for clarity, the hydrostatic / dynamic pressure bearing assembly 100, as shown in FIG. 1, immediately adjacent to each other, as used herein, “makes the alignment fluid bearing robust. It is sufficient to establish, but cannot produce a reasonable amount of fluid.

  Furthermore, “sufficiently spaced” as used herein with respect to the guide bearing assembly 180 of the carriage assembly means that the guide bearing assemblies 180 of the carriage assembly are not immediately adjacent to each other. The ability of the guide bearing assembly 180 to direct the ram body 50 or punch 58 into the path through the die pack 16, as described above, is the first component 182 of the guide bearing assembly of the carriage assembly and the first of the guide bearing assembly of the carriage assembly. It is understood that this is a function of the fluid pressure between the two components 184, the spacing of the guide bearing assembly 180 of the carriage assembly, and the distance of the guide bearing assembly 180 from the center of gravity of the ram assembly 12. Other characteristics of the ram assembly 12 also affect the orientation, but are not as important here and are negligible in this case. 22A-22C, the center of gravity of the ram assembly 12 is located at the boundary between the ram body 50 and the carriage assembly body 170, approximately at the longitudinal axis 56 of the ram body. Further, it will be appreciated that the further the guide bearing assembly 180 of the carriage assembly is from the center of gravity of the ram assembly 12, the greater the effect that the fluid passing through the thrust pad assembly 400 has on the position of the ram body 50, as will be described. . That is, the farther the thrust pad assembly 400 is from the center of gravity of the ram assembly 12, the larger the lever arm. Thus, “sufficient to establish the robustness of the aligning fluid bearing but generate a reasonable amount of fluid” also depends on the position of the thrust pad assembly 400 relative to the center of gravity of the ram assembly 12. Further, as used herein, “sufficiently spaced” refers to the amount of fluid generated in the thrust pad assembly 400 for the thrust pad assembly 400, ie, the guide bearing assembly 180 of the carriage assembly. The thrust pad assembly 400 is spaced apart to be configured to change the orientation of the ram body 50 or punch 58 to position the longitudinal axis of the ram body 50 to move over the selected travel path. It means that Thus, in a “sufficiently spaced” thrust pad assembly 400, the known pump assembly 108 and the known conduit 110 are “sufficient to establish the robustness of the aligning fluid bearing, but with a reasonable amount of fluid. Can occur ". Thus, having the “sufficiently spaced” thrust pad assembly 400 solves the aforementioned problems associated with “wobble”.

  For example, generally speaking, with a relatively short ram assembly 12, less force is required to direct the ram body 50 or punch 58 into the path through the die pack 16. Accordingly, the guide bearing assembly 180 of the carriage assembly may be reasonably spaced and the outboard guide bearing assembly 160 is configured to generate a moderate amount of guide fluid. Further, the amount of fluid generated in the thrust pad assembly 400 that is relatively close to the center of gravity of the ram assembly 12 is greater than the amount of fluid generated in the thrust pad assembly 400 that is relatively far from the center of gravity of the ram assembly 12.

  If the same relatively short ram assembly 12 is used and the spacing of the carriage bearing guide bearing assembly 180 is increased, i.e., the rear thrust pad assembly 400 is further away from the center of gravity of the ram assembly 12, the outboard Guide bearing assembly 160 is configured to generate a smaller amount of guide fluid. Conversely, with a relatively long ram assembly 12, the guide bearing assembly 180 of the carriage assembly requires a greater spacing compared to the outboard guide bearing assembly 160 that supports the relatively short ram assembly 12, and the outboard The guide bearing assembly 160 will need to generate a greater amount of guide fluid.

  Accordingly, the guide bearing assembly 180 “configured to direct the ram body 50” is a guide bearing assembly 180 that “generates a sufficient amount of fluid to establish the robustness of the aligning fluid bearing”. The fluid generating elements of the guide bearing assembly 180 of the carriage assembly are “sufficiently spaced” from each other. Therefore, the converse is also true: “generates a sufficient amount of fluid to establish the robustness of the aligning fluid bearing” and the fluid generating elements of the guide bearing assembly 180 of the carriage assembly are sufficiently spaced apart from each other. The guide bearing assembly 180 is “configured to orient the ram body 50”.

  Further, as described above, in order to be “configured to be a [verb or“ becomes [X] ”], the configuration is to execute a specific verb or [X]. Need to be designed and designed. Thus, as used herein, a lubricated bearing assembly that simply uses a lubricating fluid is not “configured to orient the ram body 50” unless specifically described as such. In other words, prior art bearing assemblies that may be able to change the orientation of the ram body 50 or punch 58 in the intended manner are “configured to orient the ram body” as used herein. Does not “generate enough fluid to establish the robustness of the aligning fluid bearing” and includes a “sufficiently spaced” fluid generating element of the guide bearing assembly 180 of the carriage assembly. Not in. The “sufficiently spaced” fluid generating element of the guide bearing assembly 180 of the carriage assembly is “configured to direct the ram body” to “establish the robustness of the aligning fluid bearing” To generate a sufficient amount of fluid, the guide bearing assembly 180 must be described as being able to orient the ram body 50, or designed or intentionally oriented to the ram body 50. Must be shown.

  Again, note that the first guide bearing assembly 180A and the second guide bearing assembly 180B of the carriage assembly are substantially the same and only one will be described. However, it can be appreciated that each bearing assembly 180A, 180B of the carriage assembly guide includes the elements described below. In the exemplary embodiment shown in FIGS. 19-21, each saddle 186 includes a number of thrust pad assemblies 400. As described below, although the integral body component may extend across the individual thrust pad assemblies 400, the thrust pad assembly 400 is still a separate and separate assembly. In the exemplary embodiment, saddle 186 has a generally rectangular cross section, ie, a parallelepiped cross section. Thus, each saddle 186 has an upper surface 181, an outer side surface 183, and a lower surface 185. In this configuration, each thrust pad assembly 400 includes an upper pad portion 402, a lateral pad portion 404, and a lower pad portion 406. The upper pad portion 402 is disposed on the saddle upper surface 181. The lateral pad portion 404 is disposed on the saddle outer side surface 183. The lower pad portion 406 is disposed on the saddle lower surface 185.

  Each pad portion 402, 404, 406 is substantially the same and only one will be described. The pad portions 402, 404, and 406 include a substantially flat pad body 410. The body 410 of each pad portion defines a recessed slot 412 in the exemplary embodiment. The pad body slot 412 has a fluid passage 414 and several coupling passages (not shown). The fluid passages 414 of each pad portion body are configured or arranged to be aligned with the passages 452 of the fluid distribution assembly described below.

  In the exemplary embodiment, each saddle 186 includes a front thrust pad assembly 400 ′, at least one intermediate thrust pad assembly 400 ″, and a rear thrust pad assembly 400 ″ ″. Including at least one intermediate thrust pad assembly 400 ″ in addition to the front thrust pad assembly 400 ′ and the rear thrust pad assembly 400 ′ ″, that is, adding each intermediate thrust pad assembly 400 ″ As described above, it provides additional orienting forces and a better ability to provide the resulting reaction moment to the offset force. Further, adding at least one intermediate thrust pad assembly 400 '' adds the burden of "sufficient to establish the robustness of the aligning fluid bearing but generate a reasonable amount of fluid" It is distributed among the thrust pad assemblies. That is, the state of the art pump assembly 108 and conduit 110 are “sufficient to establish alignment fluid bearing robustness but generate a reasonable amount of fluid” in a poorly spaced thrust pad assembly. Is not enough. That is, for example, the required fluid pressure will not be obtained or the conduit will rupture. By including at least one intermediate thrust pad assembly 400 ″, this required fluid pressure is reduced and the current art pump assembly 108 and conduit 110 are able to “establish alignment fluid bearing robustness. Sufficient but sufficient to produce a reasonable amount of fluid. Thus, the inclusion of at least one intermediate thrust pad assembly 400 '' solves the aforementioned problems associated with wobble described above.

  The three thrust pad assemblies 400 ′, 400 ″, 400 ′ ″ are merely exemplary, and each saddle 186 has more than one thrust pad and the thrust pad 400 is as described above. It is understood that any number of thrust pads may be included as long as they are “sufficiently spaced” from each other. As shown, in the exemplary embodiment, there is one intermediate thrust pad assembly 400 ″. Hereinafter, the number of “′” symbols indicates components of the individual pad assemblies 400 ′, 400 ″, 400 ″ ″. As shown in FIG. 19, in each of the front thrust pad assembly 400 ′ and the intermediate thrust pad assembly 400 ″, the upper pad portions 402 ′, 402 ″, the lateral pad portions 404 ′, 404 ″, and the lower pads. The portions 406 ′, 406 ″ are generally aligned. That is, for example, the front edge and the rear edge of each pad portion body 410 in each of the front thrust pad assembly 400 ′ and the intermediate thrust pad assembly 400 ″ are generally disposed in the same plane. In the rear thrust pad assembly 400 ″ ″, the upper pad portion 402 ″ ″ and the lower pad portion 406 ″ ″ are longitudinally offset from the lateral pad portion 404 ″ ″. In this configuration, a pin 33 that couples the crank arm 32 of the crank assembly to the carriage assembly body 170 is disposed between the upper pad portion 402 "" and the lower pad portion 406 "".

  In the exemplary embodiment, the front thrust pad assembly 400 ′, the at least one intermediate thrust pad assembly 400 ″, and the rear thrust pad assembly 400 ′ ″ include several integral pad members 430, 432, 434. Share That is, each guide bearing assembly 180 of the carriage assembly includes an integral upper pad member 430, an integral lateral pad member 432, and an integral lower pad member 434. The unitary upper pad member 430 includes an elongated, generally flat, unitary body 448 that includes an upper pad portion 402 ′ of the front thrust pad assembly, an upper pad portion 402 ″ of the intermediate thrust pad assembly, It is defined as the upper pad portion 402 '' 'of the rear thrust pad assembly. That is, the generally flat upper pad member 430 includes a depression, ie, a thin portion of the pad member body 448, thereby defining a thicker portion as the body 410 of the various pad portions. Similarly, the integral lateral pad member 432 includes a lateral pad portion 404 ′ of the front thrust pad assembly, a lateral pad portion 404 ″ of the intermediate thrust pad assembly, and a lateral pad portion 404 of the rear thrust pad assembly. '' 'And the integrated lower pad member 434 includes a lower pad portion 406' of the front thrust pad assembly, a lower pad portion 406 '' of the intermediate thrust pad assembly, and a rear thrust pad. A lower pad portion 406 ″ of the assembly.

  In the exemplary embodiment, each guide bearing assembly 180 of the carriage assembly includes a fluid distribution assembly 450 configured to provide a balanced fluid flow to the associated saddle thrust pad assembly 400. Thus, each saddle 186, ie, each fluid distribution assembly 450, includes several passages 452. Each passage 452 of the fluid distribution assembly is coupled to and in fluid communication with the fluid passage 414 of the pad body and the lubricant sump 106. In this configuration, the lubricant is delivered to the guide bearing assembly 180 of the carriage assembly.

  Further, the fluid distribution assembly passage 452 is configured to “provide a balanced fluid flow” to the associated saddle thrust pad assembly 400. As used herein, “providing a balanced fluid flow” means that the passage 452 of the fluid distribution assembly provides sufficient fluid flow to the associated portions 402, 404, 406. The guide bearing assembly 180 of the carriage assembly, as described above, “generates a sufficient amount of fluid to establish the robustness of the aligning fluid bearing” and the fluid pressure at each fluid port 190 is approximately the same. Means that fluid is generated at such a flow rate. Thus, it is understood that the configuration of the passage 452 of the fluid distribution assembly depends on the weight and configuration of the can body making machine 10 and the ram assembly 12. To be configured to “provide a balanced fluid flow”, the fluid distribution assembly has been described as being able to “provide a balanced fluid flow” or deliberately “balanced” It must be designed or shown to “provide a good fluid flow”. That is, a fluid distribution assembly that simply provides fluid flow is described as being able to “provide balanced fluid flow” or intentionally designed to “provide balanced fluid flow” Or, unless indicated, does not “provide a balanced fluid flow” as described herein.

  In addition, some fluid passages 452 of the fluid distribution assembly can be selectively closed. For example, some fluid passages 452 of the fluid distribution assembly are configured to have plugs (not shown) installed therein. The plug seals the fluid passage 452 of the individual fluid distribution assembly. In the exemplary embodiment, the plug is disposed in the carriage assembly body 170 at an opening configured to interface the conduit 110 and the sump 106. Alternatively, a plug may be disposed in the passage 414 of the pad body. In another embodiment not shown, some fluid passages 452 of the fluid distribution assembly include a valve assembly (not shown) that operates between an open position and a closed position.

  In this configuration, the first saddle 186A and the second saddle 186B are configured to generate a sufficient amount of fluid to establish the robustness of the aligning fluid bearing. That is, as used herein, the first saddle 186A and the second saddle 186B comprise a front thrust pad assembly 400 ′, at least one intermediate thrust pad assembly 400 ″, and a rear thrust pad assembly 400. The thrust pad assemblies 400 ', 400' ', 400' '' are coupled to a passage 452 of a fluid distribution assembly configured to "provide a balanced fluid flow". The first saddle 186A and the second saddle 186B generate a sufficient amount of fluid to establish the robustness of the aligning fluid bearing.

  In this embodiment, the housing assembly 11 may include a seal assembly 196 for the ram body 50, which is illustrated. That is, the seal assembly 196 includes two cup seals (not shown) as is well known. That is, one cup seal is configured to remove the coolant from the ram body 50 when the ram body moves from the second position to the first position, and the other cup seal is configured so that the ram body 50 is the first. The lubricant is configured to be removed from the ram body 50 as it moves from the second position to the second position. It should be noted that the seal assembly 196 is not a bearing assembly and does not support the ram body 50 and therefore does not change the “cantilever length” of the ram body 50 as will be described below.

  In this embodiment, unlike the known ram body, which must be long enough to pass through the bearing assembly, the ram body 50 of this exemplary embodiment passes through the seal assembly 196 and the die pack 16. It just needs to be long enough. This reduction in the length of the ram body 50 reduces the amount of ram sagging, thereby reducing wear on the ram body 50 and die pack 16. In exemplary embodiments, the ram body 50 is about 33.0 inches to about 36.0 inches, or about 34.5 inches long. That is, the change in size improves the shortcomings of known techniques.

  Using either embodiment of the outboard guide bearing assembly 60, 160, the proximal end 52 of the ram body is coupled to, directly coupled to, or secured to the ram coupling 72 of the carriage assembly. The body 50 extends therefrom. The ram body 50 is cantilever members 120 and 220 (FIGS. 8 and 13). Note that the assembly on the right side of the redraw sleeve 40 shown in FIG. 3, for example, but not limited to, the air blade 44 and the mechanical stripper 46 do not support the ram body 50.

  Further, the cantilever member 120 has a “cantilever length”, which is the length of the cantilever member beyond the support closest to the unsupported end. As described above, in the prior art where the ram body 50 moves through the bearing assembly 60, the cantilevered length of the prior art ram body had a dynamic cantilevered length. That is, the cantilever length was determined by the length of the ram body 50 extending through the bearing assembly 60. Since the ram body 50 of the exemplary embodiment does not extend through the bearing assembly 60, the cantilevered length of the cantilever member 120 remains constant during the reciprocating movement of the carriage assembly 62.

  In another exemplary embodiment, shown in FIGS. 10, 10A, and 10B, the ram assembly 12 includes an elongated, generally circular, generally hollow ram body 50A. As previously described, the ram body 50A includes a proximal end 52, a distal end 54 and a longitudinal axis 56, and an intermediate portion 59. In the exemplary embodiment, and at the intermediate portion 59 of the ram body, the inner surface of the hollow ram body 50A includes a flange 130 that extends inwardly. In this exemplary embodiment, the ram body flange 130 is the boundary between the ram body distal end 54 and the ram body intermediate portion 59.

  The punch 58 is disposed at the distal end 54 of the ram body beyond the inwardly extending flange 130. That is, the radius of the ram body distal end 54 is reduced relative to the ram body proximal end 52 and the ram body intermediate portion 59. The punch 58 is substantially cylindrical and includes a hollow main body 57. The outer diameter of the punch body 57 is substantially the same as the outer diameter of the intermediate portion 59 and the proximal end 52 of the ram body. The punch 58 is positioned beyond and coupled to the distal end 54 of the ram body. In this configuration, the outer transition between the punch 58 and the intermediate portion 59 of the ram body is substantially smooth. In the exemplary embodiment, ram assembly 12 also includes a tension assembly 140.

  The tension assembly 140 is configured to reduce ram sagging by tensioning the ram body 50A. In the exemplary embodiment, tension assembly 140 includes an elongated support member 142, a proximal coupling assembly 144, and a distal coupling assembly 146. Support member 142 includes a proximal end 150, a distal end 152 and a longitudinal axis 154. The support member 142 is one of a rigid member or a tension member in the exemplary embodiment. The support member 142 is substantially disposed within the ram body 50A.

  The proximal coupling assembly 144 of the tension assembly is disposed at the proximal end 52 of the ram body. The proximal coupling assembly 144 of the tension assembly is an adjustable coupling assembly 148 in the exemplary embodiment. That is, in the exemplary embodiment, the proximal end 150 of the support member and the proximal coupling assembly 144 of the tension assembly are threadedly coupled, for example, a threaded rod 143 and a mooring nut 145, respectively. As shown, the proximal end 150 of the support member extends through an axial passage 149 within the proximal end 52 of the ram body. As shown, an axial passage 149 at the proximal end of the ram body is disposed in a collar 147 that defines an inwardly extending flange.

  The distal coupling assembly 146 of the tension assembly is disposed on one of the ram body intermediate portion 59 or the ram body distal end 54. In the exemplary embodiment, the distal coupling assembly 146 of the tension assembly is disposed on the flange 130 of the ram body. In the exemplary embodiment, tension assembly distal coupling assembly 146 includes a mount 260 and a mount coupling assembly 262. That is, the mount coupling assembly 262 includes the coupling components described below, which couple the mount 260 to the ram body 50A. The tension assembly distal coupling assembly mount 260 includes a body 264 that defines an axial first coupling assembly 266 and a radial second coupling assembly 268. Otherwise, the mount body 264 of the distal coupling assembly of the tension assembly is sized and shaped to fit within the ram body 50A at the ram body flange 130. The first coupling assembly 266 of the mounting body of the distal coupling assembly of the tension assembly includes a threaded cavity 270 in the exemplary embodiment. In another embodiment, cavity 270 includes a radial pin and its passage (not shown). The cavity 270 of the first coupling component of the mount body of the distal coupling assembly of the tension assembly corresponds to the distal end 152 of the support member. Thus, by disposing the distal end 152 of the support member threadably into the cavity 270 of the first coupling component of the mount body of the distal coupling assembly of the tension assembly, the support member 142 is Coupled to the mount body 264 of the distal coupling assembly of the tension assembly.

  The tension assembly distal coupling assembly mount body 264 is coupled to the ram body 50A by the tension assembly distal coupling assembly mount body second coupling assembly 268. In the exemplary embodiment, the second coupling assembly 268 of the mount body of the distal coupling assembly of the tension assembly includes a threaded hole 290 that is generally radially extending from the distal cup of the tension assembly. Extends into the mount body 264 of the ring assembly. The second coupling assembly 268 of the mount body of the distal coupling assembly of the tension assembly also includes a fastener 292 and a radial passage 294 through the intermediate portion 59 of the ram body at the flange 130. Mount body 264 of the distal coupling assembly of the tension assembly is disposed within ram body 50A at flange 130. The fastener coupling 292 of the mount body of the distal coupling assembly of the tension assembly passes through the radial passage 294 of the second coupling component of the mount body of the distal coupling assembly of the tension assembly. Passing through and threaded into the screw hole 290 of the second coupling component of the mount body of the distal coupling assembly of the tension assembly, the mount 260 of the tension coupling distal coupling assembly becomes the ram body 50A. To be fixed.

  The support member 142 extends between and is coupled to the proximal coupling assembly 144 of the tension assembly and the distal coupling assembly 146 of the tension assembly. The support member 142 receives tension. The coupling of the distal end 152 of the support member to the distal coupling assembly 146 of the tension assembly has been previously described. As described further above, in the exemplary embodiment, the proximal end 150 of the support member and the proximal coupling assembly 144 of the tension assembly are threaded couplings, each of which is, for example, a threaded rod. 143 and a mooring nut 145. That is, the proximal end 150 of the support member is threaded. In this device configuration, the tension in the support member 142 can be easily adjusted. That is, the mooring nut 145 is threaded into the proximal end 150 of the support member and pulled out against the collar 147 at the proximal end of the ram body. The mooring nut 145 is withdrawn against the collar 147 at the proximal end of the ram body, creating tension at the support member 142. And the tension | tensile_strength of the support member 142 is increased / decreased by rotating the mooring nut 145 of the screw rod 143. FIG.

  Further, in the exemplary embodiment, support member 142 is disposed above and aligned with longitudinal axis 56 of the ram body. That is, the longitudinal axis 154 of the support member is generally parallel to and spaced from the longitudinal axis 56 of the ram body.

  In another exemplary embodiment shown in FIGS. 14 and 14A, the tension assembly 340 is configured to be substantially enclosed. That is, in this embodiment, the structure that couples the mount body to the ram body 50A is not exposed on the outer surface of the ram body 50A. In this configuration, the structure that couples the mount body 264 to the ram body 50A is not in a position to cause wear in the seal assembly 196. Thus, as shown in FIG. 14, the support member 142 and the proximal coupling assembly 144 of the tension assembly are generally as described above. However, in this embodiment, the distal coupling assembly 146 of the tension assembly is as follows.

  In the exemplary embodiment, distal coupling assembly 146 of the tension assembly includes a mount 360 and a mount coupling assembly 362. That is, the mount coupling assembly 362 includes a coupling component described below, which couples the mount 360 to the ram body 50A. The tension assembly distal coupling assembly mount 360 includes a body 364. The body 364 has a first distal end 363 and a second proximal end 365 and defines an axial first coupling assembly 366 and a radial second coupling assembly 368. . The mount body 264 of the distal coupling assembly of the tension assembly is sized and shaped to fit within the ram body 50A and extend across the flange 130 of the ram body. That is, when mounted, the distal end 363 of the mount body of the distal coupling assembly of the tension assembly is positioned distal to the flange 130.

  The first coupling component 266 of the tension assembly distal coupling assembly mount body is disposed at the proximal end 365 of the tension assembly distal coupling assembly mount body, and in one exemplary embodiment, a screw A padded cavity 370. The cavity 370 of the first coupling component of the mount body of the distal coupling assembly of the tension assembly corresponds to the distal end 252 of the support member. In this exemplary embodiment, the distal end 252 of the support member includes a screw 374. Accordingly, the distal end 252 of the support member is threadably connected to the cavity 370 of the first coupling component of the mount body of the distal coupling assembly of the tension assembly.

  The tension assembly distal coupling assembly mount body 364 is coupled to the ram body 50A by the tension assembly distal coupling assembly mount body second coupling assembly 368. In the exemplary embodiment, the second coupling assembly 368 of the distal assembly of the tension assembly has a threaded hole extending substantially radially in the mount body 364 of the distal coupling assembly of the tension assembly. 390. The mounting body second coupling assembly 368 of the distal coupling assembly of the tension assembly also includes a fastener 392 and a radial passage 394 through the distal end 54 of the ram body at a location distal to the flange 130. including. Mount body 364 of the distal coupling assembly of the tension assembly is disposed within ram body 50A at flange 130. The fastener coupling 392 of the tension coupling distal coupling assembly mount body second coupling component 392 passes through the radial passage 394 of the tension coupling distal coupling assembly mount body second coupling component. By passing through and threaded into the screw hole 390 of the second coupling component of the mount body of the distal coupling assembly of the tension assembly, the mount 260 of the tension coupling distal coupling assembly becomes the ram body 50A. To be fixed.

  It is noted that the distal coupling assembly 146 of the tension assembly is positioned below / inside the punch 58 when the ram assembly 12 is assembled. In other words, the punch 58 covers the distal coupling assembly 146 of the tension assembly. Thus, in operation, the distal coupling assembly 146 of the tension assembly is not exposed and cannot contact the seal assembly 196 as the ram body reciprocates between the first and second positions. As used herein, a coupling assembly that is not visible from the outside of the ram body 50A is a “hidden coupling”. That is, in this embodiment, the second coupling assembly 368 of the mount body of the distal coupling assembly of the tension assembly is a hidden coupling.

  While specific embodiments of the invention have been described in detail, those skilled in the art will recognize that various modifications and substitutions may be made to those details in light of the overall teachings of the present disclosure. . Accordingly, the specific configuration disclosed is intended to be exemplary only and is not a limitation on the appended claims and the scope of the invention given as the full scope of any and all equivalents thereof. Absent.

Claims (21)

A guide bearing assembly (180) of a carriage assembly for a can body making machine (10), comprising:
The can body making machine (10) includes an elongated ram body (50), a crank assembly (30), a housing assembly (11), a die pack (16), and a carriage assembly (62);
The die pack has a passage (17) therethrough;
The carriage assembly (62) includes a body (70) having a ram coupling (72), a crank coupling (74), a first side (173) and a second side (175);
The crank assembly (30) includes a reciprocating crank arm (32);
The crank arm (32) is coupled to a crank coupling (74) of the body of the carriage assembly;
The ram body (50) is coupled to a ram coupling (72) of the body of the carriage assembly;
The guide bearing assembly (180) of the carriage assembly includes:
A first guide bearing assembly (180A) of the carriage assembly including a first component (182A) and a second component (184A);
A second guide bearing assembly (180B) of the carriage assembly including a first component (182B) and a second component (184B);
With
The first component (182A) of the first guide bearing assembly of the carriage assembly is coupled to the first side (173) of the body of the carriage assembly;
A second component (184A) of the first guide bearing assembly of the carriage assembly is coupled to the housing assembly (11) of the can body making machine;
A first component (182B) of a second guide bearing assembly of the carriage assembly is coupled to a second side (175) of the body of the carriage assembly;
A second component (184B) of a second guide bearing assembly of the carriage assembly is coupled to a housing assembly (11) of the can body making machine;
A first guide bearing assembly (180A) of the carriage assembly and a second guide bearing assembly (180B) of the carriage assembly are configured to direct the ram body (50) to a passage (17) of the die pack. A guide bearing assembly (180) of the carriage assembly. The first component (182A) of the first guide bearing assembly of the carriage assembly is a saddle (186A);
The second component (184A) of the first guide bearing assembly of the carriage assembly is a journal channel (188A);
The first component (182B) of the second guide bearing assembly of the carriage assembly is a saddle (186B);
The guide bearing assembly (180) of the carriage assembly of claim 1, wherein the second component (184B) of the second guide bearing assembly of the carriage assembly is a journal channel (188B). The first saddle (186A) includes several thrust pad assemblies (400A);
The second saddle (186B) includes several thrust pad assemblies (400B);
The first saddle (186A) is configured to generate an amount of fluid that is sufficient to establish the robustness of the aligning fluid bearing;
The guide bearing assembly of a carriage assembly according to claim 2, wherein the second saddle (186B) is configured to generate an amount of fluid sufficient to establish the robustness of the aligning fluid bearing. (180). The first saddle (186A) includes a front thrust pad assembly (400A ′) and a rear thrust pad assembly (400A ′ ″),
The second saddle (186B) includes a front thrust pad assembly (400B ′) and a rear thrust pad assembly (400B ′ ″),
The first saddle front thrust pad assembly (400A ′) is sufficiently spaced from the first saddle rear thrust pad assembly (400A ′ ″);
The carriage assembly of claim 3, wherein the second saddle front thrust pad assembly (400B ') is sufficiently spaced from the second saddle rear thrust pad assembly (400B'''). Guide bearing assembly (180).   The first saddle (186A) includes one intermediate thrust pad assembly (400A '') and the second saddle (186B) includes one intermediate thrust pad assembly (400B ''). A guide bearing assembly (180) of the carriage assembly according to claim 4. The first journal channel (188A) includes a substantially square C-shaped channel;
The second journal channel (188B) includes a substantially square C-shaped channel;
The first saddle (186A) has a parallelepiped cross section having an upper surface (181A), an outer side surface (183A) and a lower surface (185A);
The second saddle (186B) has a parallelepiped cross section having an upper surface (181B), an outer side surface (183B) and a lower surface (185B);
Each thrust pad (400A) of the first saddle includes an upper pad portion (402A), a lateral pad portion (404A), and a lower pad portion (406A),
The carriage assembly of claim 5, wherein each thrust pad (400B) of the second saddle includes an upper pad portion (402B), a lateral pad portion (404B) and a lower pad portion (406B). Guide bearing assembly (180). The first guide bearing assembly (180A) of the carriage assembly includes an integral upper pad member (430A), an integral lateral pad member (432A), and a single lower pad member (434A). And
The first upper pad member (430A) includes an upper pad portion (402A ′) of the front thrust pad assembly, an upper pad portion (402A ″) of the intermediate thrust pad assembly, and an upper side of the rear thrust pad assembly. Define the pad (402A ''')
The first lateral pad member (432A) includes a lateral pad portion (404A ′) of the front thrust pad assembly, a lateral pad portion (404A ″) of the intermediate thrust pad assembly, and the rear thrust pad. Defining the lateral pad portion (404A ''') of the assembly;
The first lower pad member (434A) includes a lower pad portion (406A ′) of the front thrust pad assembly, a lower pad portion (406A ″) of the intermediate thrust pad assembly, and the rear thrust pad. Defining the lower pad portion (406A ''') of the assembly;
The second guide bearing assembly (180B) of the carriage assembly includes an integral upper pad member (430B), an integral lateral pad member (432B), and a single lower pad member (434B). And
The second upper pad member (430B) includes an upper pad portion (402B ′) of the front thrust pad assembly, an upper pad portion (402B ″) of the intermediate thrust pad assembly, and an upper side of the rear thrust pad assembly. Define the pad (402B ''')
The second lateral pad member (432B) includes a lateral pad portion (404B ′) of the front thrust pad assembly, a lateral pad portion (404B ″) of the intermediate thrust pad assembly, and the rear thrust pad. Defining the lateral pad portion (404B ''') of the assembly;
The second lower pad member (434B) includes a lower pad portion (406B ′) of the front thrust pad assembly, a lower pad portion (406B ″) of the intermediate thrust pad assembly, and the rear thrust pad. The guide bearing assembly (180) of a carriage assembly according to claim 6, defining a lower pad portion (406B ''') of the assembly. The first guide bearing assembly (180A) of the carriage assembly includes a fluid distribution assembly (450A) configured to provide a balanced fluid flow to the thrust pad assembly (400A) of the first saddle. And
The second guide bearing assembly (180B) of the carriage assembly includes a fluid distribution assembly (450B) configured to provide a balanced fluid flow to the thrust pad assembly (400A) of the first saddle. The guide bearing assembly (180) of the carriage assembly according to claim 3, wherein The first fluid distribution assembly (450A) includes a number of fluid passages (452A);
The second fluid distribution assembly (450B) includes a number of fluid passages (452B);
Some fluid passages (452A) of the first fluid distribution assembly can be selectively closed;
The guide bearing assembly (180) of a carriage assembly according to claim 8, wherein several fluid passages (452B) of the second fluid distribution assembly are selectively closable. The first saddle (186A) includes a front thrust pad assembly (400A ′), at least one intermediate thrust pad assembly (400A ″), and a rear thrust pad assembly (400A ′ ″). ,
The second saddle (186B) includes a front thrust pad assembly (400B ′), at least one intermediate thrust pad assembly (400B ″), and a rear thrust pad assembly (400B ′ ″). A guide bearing assembly (180) of a carriage assembly according to claim 2,. A die pack (16) defining a passage (17);
A housing assembly (11);
A crank assembly (30) coupled to the housing assembly (11) and including a reciprocating crank arm (32);
A ram assembly (12) including an elongated ram body (50) and an outboard guide bearing assembly (60);
With
The carriage assembly (62) includes a body (70) having a ram coupling (72), a crank coupling (74), and several guide bearing assemblies (180);
The ram body (50) is coupled to the ram coupling (72);
The crank coupling (74) is configured to couple to the crank arm (32);
The carriage assembly body (70) is configured to move substantially in a plane and reciprocate between a retracted first position and an advanced second position;
A guide bearing assembly (180) of the carriage assembly is configured to direct the ram body (50);
A guide body assembly (180) in the carriage assembly, wherein the guide body assembly (180) is configured to direct the ram body (50) in the die pack passage (17). The several guide bearing assemblies (180) include a first guide bearing assembly (180A) of the carriage assembly and a second guide bearing assembly (180B) of the carriage assembly;
The first guide bearing assembly (180A) of the carriage assembly includes a first component (182A) and a second component (184A);
The second guide bearing assembly (180B) of the carriage assembly includes a first component (182B) and a second component (184B);
The first component (182A) of the first guide bearing assembly of the carriage assembly is coupled to the first side (173) of the body of the carriage assembly;
A second component (184A) of the first guide bearing assembly of the carriage assembly is coupled to the housing assembly (11) of the can body making machine;
A first component (182B) of a second guide bearing assembly of the carriage assembly is coupled to a second side (175) of the body of the carriage assembly;
The can body making machine (10) of claim 11, wherein a second component (184B) of a second guide bearing assembly of the carriage assembly is coupled to a housing assembly (11) of the can body making machine. ). The first component (182A) of the first guide bearing assembly of the carriage assembly is a saddle (186A);
The second component (184A) of the first guide bearing assembly of the carriage assembly is a journal channel (188A);
The first component (182B) of the second guide bearing assembly of the carriage assembly is a saddle (186B);
The can body maker (10) of claim 12, wherein the second component (184B) of the second guide bearing assembly of the carriage assembly is a journal channel (186B). The first saddle (186A) includes several thrust pad assemblies (400A);
The second saddle (186B) includes several thrust pad assemblies (400B);
The first saddle (186A) is configured to generate an amount of fluid that is sufficient to establish the robustness of the aligning fluid bearing;
A can body making machine (10) according to claim 13, wherein the second saddle (186B) is configured to generate an amount of fluid sufficient to establish the strength of a self-aligning fluid bearing. ). The first saddle (186A) includes a front thrust pad assembly (400A ′) and a rear thrust pad assembly (400A ′ ″),
The second saddle (186B) includes a front thrust pad assembly (400B ′) and a rear thrust pad assembly (400B ′ ″),
The first saddle front thrust pad assembly (400A ′) is sufficiently spaced from the first saddle rear thrust pad assembly (400A ′ ″);
15. Can body manufacturing according to claim 14, wherein the second saddle front thrust pad assembly (400B ′) is sufficiently spaced from the second saddle rear thrust pad assembly (400B ′ ″). Machine (10).   The first saddle (186A) includes one intermediate thrust pad assembly (400A '') and the second saddle (186B) includes one intermediate thrust pad assembly (400B ''). The can body manufacturing machine (10) according to 15. The first journal channel (188A) includes a substantially square C-shaped channel;
The second journal channel (188B) includes a substantially square C-shaped channel;
The first saddle (186A) has a parallelepiped cross section having an upper surface (181A), an outer side surface (183A) and a lower surface (185A);
The second saddle (186B) has a parallelepiped cross section having an upper surface (181B), an outer side surface (183B) and a lower surface (185B);
Each thrust pad (400A) of the first saddle includes an upper pad portion (402A), a lateral pad portion (404A), and a lower pad portion (406A),
17. Can body manufacture according to claim 16, wherein each thrust pad (400B) of the second saddle includes an upper pad portion (402B), a lateral pad portion (404B) and a lower pad portion (406B). Machine (10). The first saddle (186A) includes an integral upper pad member (430A), an integral lateral pad member (432A), and a single lower pad member (434A);
The upper pad member (430A) of the first saddle includes an upper pad portion (402A ′) of the front thrust pad assembly, an upper pad portion (402A ″) of the intermediate thrust pad assembly, and the rear thrust pad assembly. The upper pad portion (402A ″ ′) of
The lateral pad member (432A) of the first saddle includes a lateral pad portion (404A ′) of the front thrust pad assembly, a lateral pad portion (404A ″) of the intermediate thrust pad assembly, and the rear side. Defining the lateral pad portion (404A ''') of the thrust pad assembly;
The lower pad member (434A) of the first saddle includes a lower pad part (406A ′) of the front thrust pad assembly, a lower pad part (406A ″) of the intermediate thrust pad assembly, and the rear side. Defining the lower pad portion (406A ''') of the thrust pad assembly;
The second saddle (186B) includes an integral upper pad member (430B), an integral lateral pad member (432B), and a single lower pad member (434B);
The upper pad member (430B) of the second saddle includes an upper pad portion (402B ′) of the front thrust pad assembly, an upper pad portion (402B ″) of the intermediate thrust pad assembly, and the rear thrust pad assembly. The upper pad portion (402B ′ ″) of
The lateral pad member (432B) of the second saddle includes a lateral pad portion (404B ′) of the front thrust pad assembly, a lateral pad portion (404B ″) of the intermediate thrust pad assembly, and the rear side. Defining the lateral pad portion (404B ′ ″) of the thrust pad assembly;
The lower pad member (434B) of the second saddle includes a lower pad part (406B ′) of the front thrust pad assembly, a lower pad part (406B ″) of the intermediate thrust pad assembly, and the rear side. The can body making machine (10) according to claim 17, wherein the lower pad portion (406B ''') of the thrust pad assembly is defined. The first guide bearing assembly (180A) of the carriage assembly includes a fluid distribution assembly (450A) configured to provide a balanced fluid flow to the thrust pad assembly (400A) of the first saddle. Including
The second guide bearing assembly (180B) of the carriage assembly includes a fluid distribution assembly (450B) configured to provide a balanced fluid flow to the thrust pad assembly (400A) of the first saddle. 15. A can body making machine (10) according to claim 14 comprising. The first fluid distribution assembly (450A) includes a number of fluid passages (452A);
The second fluid distribution assembly (450B) includes a number of fluid passages (452B);
Some fluid passages (452A) of the first fluid distribution assembly can be selectively closed;
20. Can body maker (10) according to claim 19, wherein several fluid passages (452B) of the second fluid distribution assembly are selectively closable. The first saddle (186A) includes a front thrust pad assembly (400A ′), at least one intermediate thrust pad assembly (400A ″), and a rear thrust pad assembly (400A ′ ″). ,
The second saddle (186B) includes a front thrust pad assembly (400B ′), at least one intermediate thrust pad assembly (400B ″), and a rear thrust pad assembly (400B ′ ″). The can body manufacturing machine (10) according to claim 13.

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