MXPA97000834A - Flux lubrication ring laminar in prensade planch - Google Patents

Abstract

The present invention relates to a lubrication ring for use in a manufacturing press that includes an assembly having a main cavity and a die tip disposed on a surface of said cavity for ironing a work piece passing through said cavity, consisting of: a groove surrounding a periphery of said main cavity and an opening within said cavity, and at least one passage for introducing a fluid into said groove so that it flows into said groove; centrifugal force in said fluid flowing in said slot exceeds a gravitational force acting in said fluid

Description

LAMINAR FLOW LUBRICATION RING IN IRONING PRESS BACKGROUND OF THE INVENTION FIELD OF THE INVENTION The present invention relates generally to stretch and iron presses (DSI) such as those used to form drawn and pressed containers, and more particularly to an improved lubrication ring for use in such presses.

DESCRIPTION OF THE RELATED TECHNIQUE In the formation of a container, it has been common to use dice cooperating with a punch to convert, for example, metal or circular metal discs, commonly known as preforms, into finished cans or other forms of containers. Typically, this is accomplished in a two-step procedure. The circular disk is first formed in a cup and then the cup is stretched and pressed through dice to make thinner and stretch the side walls. The step of forming the disk in a cup is typically carried out in a cup forming press, while the conversion of the cup to the finished product is carried out by a press or body former D &I. In a typical application, the cup can be forced through multiple ironing dies. The body formed uses a punch to force the cup through the ironing dice to form the finished container. In the ironing of the side wall of the cup to create the finished container, the work piece is severely worked while passing through the dice. Typically, body formers operate at very high speeds to efficiently produce the required volume of economically terminated containers. For example, a single body former can be operated to produce 300 to 500 or more finished containers per minute. Such high-speed operation is added to the voltage in the dice and to the heat generated during the process. In order to minimize the amount of friction between the workpiece and the die components, as well as the associated heat generated therein, it is common to lubricate the surfaces of the dice that actually contact the workpiece, i.e. the tips of the workpieces. dices. The tip may be formed of carbide or other suitable strength material for the desired application. The lubricant reduces the friction between the tip and the work piece during the formation of a container and also serves as a coolant. Without proper lubrication and cooling, the workpiece can be deformed or broken, and the die tips can be damaged or their life reduced during the processing of the container. Additionally, the fine particles or accumulated metal peelings from the work piece can be produced, thus reducing the life and / or effectiveness of the lubricant itself and the lubricant filter. Furthermore, if the cooling is sufficient, the distance between the opposite surfaces of the tip and the punch may increase or decrease, depending on the materials of the tip and the punch, to an undesirable level, making it impossible to produce containers having the thickness of Side wall required. For example, if a carbide die tip and a steel punch are used, the punch will have a higher coefficient of expansion than the tip. Consequently, by increasing the heat generated during workpiece making, the distance between the punch and the tip of the die will decrease to an unacceptable level. On the other hand, if both the punch and the tip are formed of carbide, the punch will typically remain a little colder than the tip. As the heat generated during the workpiece is increased, the distance between the punch and the tip can actually increase to an unacceptable level. In a typical can making application, if the distance between tip and punch diameters is out of tolerance by more than 0.005Q8 rnrn, eg, more than 0.00254 m on each side, the finished container will have either thin or very thick side walls formed. If the side walls are too thin, the container will generally not be able to meet the customer's specification. If it is very thick, the resulting finished container could have side walls of insufficient length as to provide sufficient excess material to allow the end of the finished container to be cut to form a smooth edge surface. Numerous techniques have been proposed to lubricate and cool the dice and the work piece. Such techniques have generally provided a continuous flow of lubrication fluid during the operation of the body former so that the flow can continue even when a work piece is not being processed by the press. Lubrication rings formed as part of a die assembly with internal drip dies, or formed separate from, but arranged adjacent to the dies in a tool bundle assembly, are commonly used to direct lubricant into the die cavity. through which the work piece will be stretched and ironed to form the finished container. The lubrication rings work to orient and direct the lubricant flow towards the die tips. More particularly, the holes, channels or grooves are machined within the lubrication ring to direct pressurized lubrication fluid to the portion of the die tips that will contact the workpiece to thin and stretch the side walls of the cup and thus forming the desired finished container. The lubricant may, for example, be composed of water in combination with oils, fats or other materials having suitable qualities. In practice, the orientation and direction of the lubricant flow is not an easy task, because the working surface of the tip is at the inner periphery of the cavity of the tool assembly or die assembly through which the Workpiece is stretched by the punch. The internal diameter of the lubrication ring must be greater than the diameter of the work surfaces of the tips to avoid interference with the work piece as it passes through the cavity. Therefore, it is extremely difficult to direct a spray of fluid on the work surface of the tip. The lubrication rings have been proposed with a circular arrangement of small holes that are angled to direct a spray of fluid as close as possible to the work surface of the tips. Other proposed lubrication rings have a groove machined within the ring, which is formed so that the lubricant is squeezed out of the groove at a certain angle to direct a spray of lubricant as close as possible to the working surface of each tip. . Still other proposed lubrication rings include a circular arrangement of notches machined within the ring to direct a spray of fluid to the working surface of the tips. In each case, the fluid spray is directed at a high velocity into the main cavity of the die assembly or tool pack of the press and the work surface of the points. Such lubrication rings, ideally, provide less than optimal lubrication to the working surface of the tip. This is because the proposed lubrication rings fail to release the lubricant so that the tips of the die are completely and uniformly coated. In addition, a slightly improper orientation of the ring (s) or a minor change in the velocity of the fluid coming from the outlet (s) may result in the application of the lubricant jet pass or otherwise skip the work surface of the tips. Therefore, neither sufficient lubrication nor cooling will be provided. The key to preventing undesirable stresses and heat in the die components and the workpiece, is to uniformly and completely and consistently coat the working surface of each tip of the ironing die with the desired lubricant. Therefore, there is a need for an improved lubrication and cooling technique for use in stretching and ironing workpieces.

OBJECTS OF THE INVENTION Accordingly, it is an object of the present invention to provide a lubrication ring for lubricating and cooling die tips and workpieces without the aforementioned problems. It is also another object of the present invention to provide a lubrication ring in which the orientation of the lubricant outlets and the exit velocity of the lubrication fluid from the ring is less critical than in previously proposed lubrication rings. It is another object of the present invention to provide a lubrication ring that provides a flow of the lubricating fluid to uniformly and completely coat the working surface of the tip of a die. The applicable objects, advantages and novel features of the present invention will become apparent to those skilled in the art from this description, including the following detailed description, as well as by practicing the invention. Although the invention is described below with reference to the preferred embodiments, it should be understood that the invention is not limited thereto. Those skilled in the art having access to the teachings herein will recognize that applications, modifications and additional embodiments in other fields which are within the scope of the invention are described and claimed herein with respect to which the invention It can be of significant utility.

BRIEF DESCRIPTION OF THE INVENTION In accordance with the present invention, a lubrication ring is provided for use in a manufacturing press. The manufacturing press includes an assembly having a main cavity and at least one tip disposed on a surface of the cavity for ironing a material that is forced by a punch through the cavity. The assembly also includes one or more lubrication rings. Each lubrication ring has a groove that surrounds a periphery of the main cavity and opens inside the cavity. One or more passages are provided to introduce a fluid into the slot. The passages are preferably formed tangentially to the slot, so that fluid through each passage is directed in the same radial direction within the slot. The fluid is introduced into the groove at a rate sufficient to cause a centrifugal force to act on the fluid flowing into the groove so that the fluid remains in contact with the surface of the groove. That is, the speed must be sufficient to overcome the gravitational forces that will tend to separate the fluid from the groove surface. Preferably, the centrifugal force exceeds the gravitational force exerted on the fluid flowing within the groove. The necessary speed can be calculated in a conventional manner. When a volume of fluid is introduced into the slot, the fluid will be forced to flow out of the slot opening and onto the surface of the die tips extending from the main cavity of the assembly. The speed must be sufficient to compensate for any decrease in the flow velocity of the fluid resulting from, for example, friction and gravitational forces exerted on the fluid between the inlets of the slots and the tip surface. This will ensure that a centrifugal force in the fluid flowing from the groove will maintain a laminar flow, even after it has left the slot opening. The fluid flowing from the slot opening therefore remains in continuous contact with the cavity and tip surfaces. In typical application, the main cavity of the assembly is cylindrical and consequently the groove is formed circumferentially around the cavity. Therefore, the fluid is introduced such that it flows in a single radial direction circumferentially around the periphery of the cavity. Under operation, the lubrication ring introduces a fluid that not only lubricates the tip surfaces to reduce the coefficient of friction between the tips and the workpiece, but also serves as a coolant and a cleaner to remove heat and fine particles from the tips and work piece generated during the operation of the press. Preferably, the fluid is applied continuously during the period of operation of the press, regardless of whether or not a work piece is being made. In this way, the continuous cooling of the press die is carried out in a beneficial manner. In this way, introducing a fluid into the main cavity of the die assembly and lubrication ring under an applied pressure force that causes the fluid to flow at a velocity around the periphery of the main cavity assembly sufficient to develop a centrifugal force in the fluid that exceeds the gravitational force in the fluid, it can be achieved that the fluid maintains a laminar flow on the tip surface. By continuously providing fluid at the proper speed within the groove during the operation of the press, the fluid will beneficially maintain continuous contact with the surfaces of the tip.

BRIEF DESCRIPTION OF THE DRAWINGS Figure .1 is a perspective view of a typical can body form that provides a suitable environment for the laminar flow lubrication ring of the present invention. Figures 2A-2C illustrate exemplary side sectional views of the cavity of the die assembly and lubrication ring during the stretching and ironing of a container in the body former of Figure 1. Figures 3A-3D illustrate portions of the assembly shown in Figures 2A-2C in greater detail. Figure 4 is a more detailed view in side section of the assembly illustrated in Figures 2A-2C showing the lubrication ring of the present invention. Figure 5 is an expanded view in side section of a die arrangement and lubrication ring in accordance with the present invention. Figure 6 illustrates a cross-sectional view of the lubrication ring illustrated in the arrangement of Figure 5 in accordance with the present invention. Figure 7 illustrates the lubricant flow on the tips of the die in accordance with the present invention. Figures 8a ~ 8f illustrate alternative configurations of lubrication ring groove in accordance with the present invention.

DESCRIPTION OF THE PREFERRED MODALITY Figure 1 illustrates a typical can press or body former 10 which can serve as a background, in which a lubrication ring of the present invention can be used. The body former 10 includes a typical die or tool pack assembly 20 for stretching and ironing-work pieces in the desired finished container. It will be understood that the body former 10 is simply a type of stretching and ironing device in which the present invention can be used. The lubrication ring of the present invention can be used with virtually any die or tool pack assembly, and virtually any type of manufacturing machinery that requires a lubricant to be formed between a machine part or work piece. Accordingly, the body former 10 and assembly 20, which is detailed more extensively below, are practically typical of the type of devices in which the present invention can be used. Figures 2A-2C illustrate a schematic partial side sectional view of the assembly 20 during various stages of operation of the body forger 10. It should be noted that the body former 10 can be continuously operated, whether or not a work piece is stretched and ironed by the assembly 20. Figure 2A illustrates the assembly 20 supporting die tips 110a ~ e, a mandrel or punch 130 and a cup-holder sleeve 140 engaging the work piece 150. The sleeve 140 presses the cup against the face of the first die tip 110a, which is part of a die commonly referred to as the die or re-routing ring. Accordingly, the workpiece 150 will be pressed by the punch 130 in the direction indicated by the arrow within the cavity 160 of the assembly 20. Figure 2B illustrates the punch 130 while moving the workpiece 160 within the cavity 160. of the assembly 20. The workpiece 150 is stretched beyond the initial die tip 110a and toward the die tips 1.10b, 1.10c and HOd, normally and respectively mentioned as the tips in the first and second ironing means and the pilot, or the first and second die rings and the pilot die ring. As shown in FIG. 2C, the workpiece 150 is pressed by the punch 130 m beyond the tip of the pilot die 1.10d. The tip of the pilot die HOd protects the last ironing die tip 110e, which is commonly referred to as a part of the extreme ironing die or the third die ring, maintaining the centering of the punch even when the work piece is of a chopped length as it passes the die tip 110c of the second ironing die ring 110c and prevents the breaking of the edge on the longer length side of the workpiece. As indicated, the ironing is carried out exclusively by the die tips 110b, 110c and llOe. It should be noted, that the work piece 150 can be metallic, metalloplastic or some other malleable material. The workpiece 150 is typically shaped into a cup as shown in Figure 2A before being pressed into the cavity 160 of the assembly 20. Figures 3A-3D illustrate portions of the assembly shown in Figures 2A-2C in greater detail. As shown in Figure 3A, the workpiece 150 has an initial side wall thickness of about 0.300 mm, while this is pressed by the punch 130 past the re-routing die 110a, which is part of the resurfacing ring. 100th At this point, the workpiece 150 is still engaged by the fastening sleeve 140. In Figure 3B the main portion of the side walls of the workpiece. 150 has passed through the ironing tip 110b of the first ironing ring 100b and has been thinned to 0.241 mrn. As shown in FIG. 3B, the thinning of the side walls of the workpiece 150 is not carried out by the restoring die 100a. Figure 3C illustrates the work piece 150 as it passes through the second die ring 100c supporting the tip 110c and the pilot die ring 100d supporting the tip 110d. As indicated, the side walls of the workpiece 150 are further overshadowed by the second die ring 100c at 0.176 nm. The pilot die ring 11Od performs a centering operation to keep the punch centered regardless of whether the work piece is of unequal length and also protects the workpiece from breaking the edge of the longer side. As indicated, the annulus of the pilot die 100 d does not further thin the side wall of the work piece 150, which remains at 0.176 rn even after the tip has passed. Figure 3D illustrates the work piece 150 just before passing through the third die ring 100e that supports the point llOe. Although not indicated, it will be understood that the final thinning of the work piece 150 is carried out by the third die ring 100 before the work piece is forced by the punch. 130 out of the cavity with a finished container. Figure 4 is a more detailed side sectional view of the assembly 20 with the punch 130 illustrated by the dotted lines. The assembly 20 is formed from tungsten carbide dies 110a to llOe through lOOe in the die support rings 100a to lOOe, which are separated by spacers or sleeves 320a-320c including lubrication rings 300. The sleeves 320a -320c may have beneficially increasing lengths as shown. It should be understood that when stretching a workpiece through the cavity 160 of the assembly 20, the workpiece may or may not be in contact with two successive die tips after first coming into contact with the die tip 110b. Each sleeve includes one or more ports 330 for introducing a lubricating and cooling fluid 340, or a water-based lubricant including oils or fats, into one or more passages 350, which feed the fluid 340 into a slot 360. in the lubrication ring 300 from which the lubricant flows into the main cavity 160 of the assembly 20. The lubrication ring 300 is described in more detail below.

It should be noted that a lubrication ring is not located between the second die ring and the pilot die ring in the preferred embodiment shown in FIG. 4. However, it is understood that if desired, the lubrication ring should be used. -Lation 300 can be arranged in + re the die ring 100c and the die ring lOOd. Figure 5 is an expanded view of the resurfacing ring + or 100a and of the first die ring 100b with the mandrel + or 320a disposed therebetween. As shown in Figure 5, lubricant 340 is aligned at port 330 and directed through passage 350 into slot 360. Passages 350 are formed to fuse tangentially with lubrication ring 300. Although the preferably use four passages 350 in the preferred embodiment, for specific applications a greater or lesser number of passages can be efficiently used. Slot 360 is formed in part by bushing 420 to avoid the need for complex machining to form the slot. In this manner, as shown in FIG. 5, the substantially cylindrical cavity 160 is defined by a toroid die ring 100b, a die tip 110b, a sleeve 320a, a bushing 420, a restoring ring 100a, and a die tip 110a, while the annular groove 360, which opens within the cavity 160, is defined by the sleeve 320 Á and ε? bushing 420. Fluid 340 enters port 330 at an inlet speed of 25.4 cm per second. The fluid travels through passage 350 and into slot 360, which is contiguous around the periphery of cavity .160. At the above mentioned entry speed, the lubricant 340 will be subjected to a centrifugal force of about 20g as it travels circumferentially around the groove 360 of the lubrication ring 300. The centrifugal force will cause the fluid 340 entering the slot 360 to be in continuous contact with the groove surface 360a while the fluid remains in the groove 360. The lubricant 340 is continuously accessed on the ports 330 and thus is continuously introduced by the passage 350 into the groove 360 during the operation of the groove form. body 10. Although slot 360 is illustrated in a teardrop shape, virtually any size or shape of slot can be used in accordance with the present invention. For example, a groove in a semicircular or rectangular shape can be used. Figures 8a-8f illustrate several alternative exemplary groove shapes that may be preferred for certain applications. In the embodiment detailed herein, the slot opening 400 is preferably no larger than the diameter or the widest portion of the passage 350. It is also preferable that the depth of the slot 360 is approximately twice the diameter or the widest dimension of passage 350. Although the passages 350 are illustrated as cylindrical, the shape of the passage is not necessarily limited thereto, but could have any shape that is considered desirable for the present application. As shown, passage 350 has a diameter of approximately 71.37 cm. The depth of the slot 360 is slightly greater than 12.7 crn. The length of the passages is preferably at least twice the diameter or the widest portion of the passage 350. In the preferred embodiment, the passages 350 have a length close to 25.4 nm. Figure 6 illustrates a cross-sectional view of the separator 300a. As shown in Figure 6, the lubrication ring 300 includes a single continuous groove 360 that surrounds the periphery of the cavity 160. The fluid 340 is fed at a high speed in the passages 350 through inlet ports 330. fluid is directed by the passages 350 into the groove of the lubrication ring 360 at a sufficient velocity to develop a centrifugal force in the fluid flowing around the groove 360 which exceeds the gravitational forces in the fluid. This causes the fluid to have a laminar flow around the groove 360 of the lubrication ring 300 to maintain contact with the fluid., that is, do not separate from, the surface in the slot 360, even in the upper portions of the ring. As more and more fluid 340 is introduced into the groove 360 through the passages 350, the fluid is forced from the groove of the lubrication ring 360 through the opening 400 in the lubrication ring 300. As mentioned above, the The width of the slot 360 does not necessarily have to decrease towards the opening 400. The velocity of the fluid as it enters the slot 360 must be sufficient to overcome any loss of velocity. fluid enters its entrance in the slot 360 from the passages 350 until it flows over the tip 1.10b. Such losses can be caused, for example, by the friction and gravitational forces acting on the fluid as it flows through the lubrication ring 300 and on the tip 110b. Therefore, the inlet speed of the lubrication fluid 340 should be such that a centrifugal force at least equal to the force of gravity continues to act on the fluid as it flows over the tip 110b to ensure a laminar flow over the tip 110b . As shown in Figure 5, the lubricant exiting the slot 360 through the opening 400 first contacts a small portion of the cavity surface 410 before flowing over the tip 110b. However, if desired, the lubricant can flow directly from the opening 400 on the surface of the tip 110b without first contacting the cavity surface 4.10. In each case, the lubricant maintains a laminar flow through the opening 400 and over the tip 110b. The laminar flow continues beneficially towards a discharge port (not shown) if the entry velocity is properly selected in a manner that will be well understood by those skilled in the art. As mentioned above, the fluid enters the slot 360 in a tangent manner through the four passages 350. The velocity of the fluid entering the port 340 in each passage 350 is at a rate of approximately 2.54 crn per second. The fluid introduced into the slot 360 immediately conforms to the curvature of the radius of the grooves and is therefore subject to a centrifugal force that exceeds the gravitational force in the fluid as it surrounds the periphery of the cavity 160. In the preferred embodiment, the input velocity of the lubricating fluid has been set so that the fluid is subjected to approximately 1.3 gs of centrifugal force as it surrounds the periphery of the cavity 160. As can be better seen in FIG. 6, the fluid flowing in the slot 360 crosses the fluid path entering the slot while passing the exit port of each passage 350. The additional fluid that is entering through the passages 350 forces the fluid particles that are flowing into the opening 400 in the passageway. lubrication ring 300 of the slot. In effect, the fluid particles form a spiral towards the opening 400 of the groove 360. The tangent velocity of the fluid remains essentially constant as it spirals backwards, although slight frictions and gravitational losses can be experienced. The rotational speed of the fluid, ie the revolutions per minute, increases as it spirals in that the radius of the circumferential flow continues to decrease while the fluid particles move towards the opening 400. When the fluid is discharged from the opening 400, The centrifugal forces in the fluid are approximately 20g. As a result of the high centrifugal forces caused by the input speed of the lubricant 340, as the fluid flows from the opening 400, it remains contiguous and follows the surface 410 of the cavity 160 on the surface of the tip 110b. Fluid 340 completely covers the entire surface of the tip regardless of changes in the diameter of the various tip surfaces. Contrary to conventional education, those water-like fluids can not maintain an inar flow with Reynolds numbers greater than 2000, the present invention results in a laminar flow of a lubricating fluid consisting mainly of water, along the surface 360a of the slot 360 and continuing on the surface 410 of the cavity 160 and subsequently on the surface of the tip 110b at a high Reynolds number of about 20,000. Due to this laminar flow, the fluid is kept in intimate contact with the lubrication ring 300 and the cavity and Isa tip surfaces. To obtain this laminar flow on the surface of the tip 110b, the velocity of the fluid flowing over the tip must be sufficient to develop a centrifugal force that is equal to or exceeds the gravitational force in the fluid as it flows over the surface of the fluid. tip. In testing the present invention, it has been shown that this intimate contact continues as the fluid flows over the orthogonal or perpendicular surfaces towards the upstream surfaces in which the fluid flows. Although conventional fluid mechanics shows that the transfer of heat to a fluid with laminar flow is deficient, the lubrication ring 300 provides exceptional heat transfer qualities. This is because the laminar flow is maintained at a very high Reynolds number, as will be understood by those skilled in fluid heat transfers. Figure 7 is similar to Figure 5, but illustrates the flow of the fluid 340 over the tip 1.10b, the surfaces 410 of the cavity 160 and the outer surfaces 700 and 750 of the assembly 20. In Figure 7, the surface of the tip 110b includes an inlet angle surface 710, a flat surface 720 and an outlet angle surface 730. In normal operation of assembly 20, workpiece 150 strikes at the inlet angle surface 710 of tip 110b and it rests against the entry angle and the flat surfaces 710 and 720 of the tip 110b to form the side walls of the workpiece. Accordingly, it is particularly important from the point of view of lubrication and cooling that the fluid has a laminar flow on the surfaces 710 and 720. As illustrated in Figure 7, in the laminar flow test of the fluid 340, it is it maintained after flowing from the opening 400 of the lubrication ring 300. The thickness of the flow the surface of the cavity 410 and tip surfaces 7.10, 720 and 730 remained substantially constant. Virtual entity no turbulence was detected. As indicated in Figure 7, the fluid 340 also maintained a laminar flow on the surfaces of the outer side 700 of the die / lubrication ring assembly, which is shown in Figure 7 as only a portion of the complete assembly. Additionally, a laminar flow was maintained even when the fluid continued to flow from the surfaces of the outer side of the assembly toward the upper and lower surfaces of the assembly. Notably, the assembly could be rotated or oriented in any way without carrying out the stable laminar flow as illustrated in Figure 7 on the surfaces of the assembly. Although the invention has been described in terms of a preferred embodiment with a horizontally oriented lubrication die / ring assembly, as mentioned above the orientation of the assembly will not materially effect the laminar flow on the surfaces of the assembly according to the invention as shown in FIG. describes in the present. Although it is common for the die / lubrication ring assembly to have a horizontal orientation within the body trimmer, if desired the assembly can be arranged vertically, diagonally or otherwise in the body trimmer. With such an alternative orientation, the forces tending to separate the lubricating fluid from the surfaces of the groove 360 and tip 110b and from the cavity wall surface 410 and may be reduced to some extent. In consecuense, the speed of the lubrication fluid introduced into the groove could in theory also be reduced, since the centrifugal force required to maintain a laminar flow of the lubrication fluid on the surface of the groove 360 and tip 110b and on the wall surface of cavity 410 could be reduced in correlation with the reduction of the forces acting to separate the fluid from these surfaces. However, as described above, preferably the rate of introduction of the lubrication fluid into the groove is such that the corresponding centrifugal force developed in the fluid sufficiently exceeds the gravitational force acting on the fluid and therefore, in the In practice, the orientation of the die / lubrication ring assembly does not need to effect the selected rate of fluid introduction or other aspects of the invention described herein. As described above, the present invention provides a laminar flow of lubricant on the tips of the die rings thereby providing improved lubrication and cooling characteristics during the operation of the body formations. Due to the use of centrifugal forces, the orientation of the opening or openings in the lubrication ring and the speed of the lubricant introduced into the lubrication ring, as long as it is equal to or exceeds a minimum required speed for '-; tD develop the necessary centrifugal force, they are not critical for the application of lubricant on the tips of the die rings. A continuous laminar flow of lubricants is provided at the tip surfaces thus providing a continuous lubrication, cooling and cleaning of those surfaces while the body photometer is working, that is, both during the machining of the workpiece to form the finished container , as during other periods of operation. Due to the speed at which the lubricant enters the assembly cavity, the lubricant flow is directed along and against the tip surface without relying on the workpiece that distributes the lubricant into the cavity. In the test of the invention described above, a significant reduction in tip wear and breakage of work pieces was experienced. The degradation of the punch was also reduced. The decreases in the rupture of the piece of work reached 50% as they did in the life of the tip. In addition, the volume of lubricant required to carry out the necessary lubrication, cooling and cleaning was reduced by approximately 50%. Accordingly, the present invention provides a significant improvement over lubrication systems in conventional manufacturing presses. Although the invention has been described in terms of the preferred embodiment, the invention is limited thereto and the clauses appended hereto, which embrace other embodiments, are within the scope of the invention described herein. Those skilled in the art will recognize other applications in which the techniques described herein can be used. The novel features and applications of the invention are set forth in the appended claims. The invention itself, however, as well as other features, advantages and benefits thereof, will be better understood by far from the above detailed description and the accompanying drawings.

Claims (11)

NOVELTY OF THE INVENTION CLAIMS

1. - A lubrication ring for use in a manufacturing press that includes an assembly having a main cavity and a die tip disposed on a surface of said cavity for ironing a work piece passing through said cavity, consisting of of: a groove surrounding a periphery of said main cavity and an opening within said cavity; and at least one passage for introducing a fluid into said slot to flow into said slot; wherein the force centrifuged in said fluid flowing in said groove exceeds a gravitational force acting on said fluid.

2. A lubrication ring according to claim 1, further characterized in that said passage is adapted to introduce said fluid into said slot at a speed and said centrifugal force corresponds to said speed.

3. A lubrication ring according to claim 1, further characterized in that said passage is adapted to introduce a volume of said fluid into said slot for a portion of said fluid to flow from said slot.

4. A lubrication ring according to claim 3, further characterized in that a centrifugal force in said portion of the fluid flowing from said slot opening is equal to or greater than a gravitational force in said portion of the fluid.

5. A lubrication ring according to claim 3, further characterized in that said groove is adapted for the portion of said fluid to flow from said groove opening and along a surface of said die tip, and said portion of said groove. fluid has a laminar flow from said groove and on said tip surface.

6. A lubrication ring according to claim 3, further characterized in that said portion of the fluid flows contiguously between said slot opening and a surface of said die tip.

7. A lubrication ring according to claim 3, further characterized in that said portion of the fluid flows on said die tip and a centrifugal force in said portion of the fluid flowing on said tip is equal to or exceeds a gravitational force acting in said portion of the fluid.

8. A lubrication ring according to claim 1, further characterized in that said at least one passage is four passages.

9. A lubrication ring according to claim 1, further characterized in that at least one passage is a plurality of passages.

10. - A lubrication ring according to claim 1, further characterized in that said at least one passage is adapted to introduce a continuous flow of fluid into said slot.

11. A lubrication ring according to claim 1, further characterized in that said at least one passage is arranged substantially tangent to said slot. 1.2.- A lubrication ring according to claim 1, further characterized in that said at least one passage is arranged so that said introduced fluid flows in said groove in a single radial direction circumferentially around the periphery of said cavity. 13. An ironing press consisting of: an assembly having a cylindrical main cavity with a substantial horizontal main shaft and a plurality of die tips disposed on a surface of said cavity; a press for forcing a work piece through said cavity; a slot surrounding said main cavity and forming a continuous opening in the surface of said cavity; and a plurality of passages disposed substantially tangent to said slot to introduce a continuous flow of fluid into said slot at a speed for said fluid to flow in a single radial direction within said slot and a centrifugal force corresponding to said speed and exceeding a gravitational force acts on said fluid flowing in said groove; further characterized in that fluid flowing from said slot opening maintains a substantially laminar flow over said die tip. 14. A method of lubrication in a sheet metal forming press having walls defining a main cavity having a longitudinal axis, a toroidal die tip disposed on the inner surface of the cavity to form a workpiece that passes axially through the cavity, and a groove that surrounds and opens within the cavity, said method consists of the steps of: introducing a fluid into the groove in such a direction and at such a rate as to cause the fluid in the groove rotate circumferentially around the axis of the cavity, the speed of the rotating fluid being sufficient to create a high centrifugal force causing the fluid to come into continuous contact with the radial outer surface of the groove, and to make the rotating fluid flow out of the slot and above the tip, the speed of the rotating fluid being sufficient to create a high cetrifugal force causing the fluid to enter into a contact continuous and intimate with the radial inner surface of the tip, thus completely and uniformly coating the tip surface with a layer of rotating fluid. 15. - A method according to claim 14, further characterized in that said centrifugal forces, both before and after the fluid flows out of the groove, exceed the gravitational forces in the fluid. 16. A method according to claim 14, further characterized in that said fluid flows both inside and outside the slot, and is substantially laminar. 17.- A method according to the claim 14, further characterized in that the fluid flows continuously during a period of operation of the press. 18. A method according to claim 14, further characterized in that the cavity is substantially cylindrical, the groove is substantially circular and continuous and the fluid is introduced into the groove in a direction tangent to the groove, through a passage that It extends through the wall. 19. A method according to claim 14, further characterized in that said fluid flows out of the groove and forms a fluid layer along the interior surface of the cavity. 20.- A method in accordance with the claim 19, further characterized in that the shape and dimensions of the layer are determined by the shape of the cavity and by said centrifugal forces, rather than by the surface of the workpiece.