# Patent

## Title
Cooling tube assembly for cooling of the interior of a container

## Abstract

A cooling tube assembly is provided. The assembly includes a cylindrical cooling tube extending from a first end to a second end. The cooling tube has an inner surface, an outer surface, an inner diameter, and an outer diameter. The cooling tube includes a first plurality of throughbores and a second plurality of throughbores located axially between the first plurality of throughbores and the second end of the cooling tube. Each of the second plurality of throughbores is circumferentially offset from each of the first plurality of throughbores. The assembly includes a nozzle extending from a first end to a second end. The first end of the nozzle is located inside the cooling tube. The first plurality of throughbores is located axially between the second end of the cooling tube and the first end of the nozzle.

## Background
IDENTIFICATION OF RELATED PATENT APPLICATION
This patent application claims priority of U.S. Provisional Patent Application No. 62/065,210, which is entitled “Cooling Tube Assembly for Cooling of the Interior of a Container,” and which was filed on Oct. 17, 2014, which patent application is hereby incorporated herein by reference in its entirety.


BACKGROUND OF THE INVENTION
Field of the Invention
The present invention relates generally to and apparatus for manufacturing, and more particularly to an apparatus for manufacturing strong glass containers.
In making glass containers, molten glass may be cut into cylinders of glass, e.g., gobs, which fall into blank molds where they are formed into parisons. Parisons may be inverted and transferred to a mold in which the parisons are blown into the shape of a container. An annealing process may be used to strengthen the containers.
The subject matter discussed in this background of the invention section should not be assumed to be prior art merely as a result of its mention in the background of the invention section. Similarly, a problem mentioned in the background of the invention section or associated with the subject matter of the background of the invention section should not be assumed to have been previously recognized in the prior art. The subject matter in the background of the invention section merely represents different approaches, which in and of themselves may also be inventions.
SUMMARY OF THE INVENTION
One embodiment of the invention relates to a cooling tube assembly. The assembly includes a cylindrical cooling tube extending from a first end to a second end. The cooling tube has an inner surface, an outer surface, an inner diameter, and an outer diameter. The cooling tube includes a first plurality of throughbores and a second plurality of throughbores located axially between the first plurality of throughbores and the second end of the cooling tube. Each of the second plurality of throughbores is circumferentially offset from each of the first plurality of throughbores. The assembly includes a nozzle extending from a first end to a second end. The first end of the nozzle is located inside the cooling tube. The first plurality of throughbores is located axially between the second end of the cooling tube and the first end of the nozzle.
Another embodiment of the invention relates to an apparatus for thermally strengthening a glass container after it is formed in an I.S. machine. The apparatus includes an oven configured to reheat the glass container. The apparatus includes a cooling station configured to cool outer and inner surfaces of the glass container. The cooling station includes a cylindrical cooler extending from a first open end to a second end. The cooling station includes a bottom cooler configured to cool a base of the container. The cooling station includes a cooling tube extending from a first end to a second end. The cooling tube including a first row of throughbores and a second row of throughbores located between the first row of throughbores and the second end of the cooling tube. The throughbores in the first row are circumferentially offset from the throughbores in the second row. Each of the throughbores has a first cross-sectional area. The cooling station includes a nozzle coupled to the cooling tube. The nozzle extends from a first end located inside the cooling tube to a second end. The nozzle includes a dispensing bore. The dispensing bore has a second cross-sectional area from the first end of the nozzle to a junction. The junction is located axially between the second row of throughbores and the second end of the cooling tube.
Alternative exemplary embodiments relate to other features and combinations of features as may be generally recited in the claims.



DESCRIPTION OF THE DRAWINGS
This application will become more fully understood from the following detailed description, taken in conjunction with the accompanying figures, wherein like reference numerals refer to like elements in which:
FIG. 1 is a curve representing an optimal stress parabola plotted against the thickness of a side wall of a glass container;
FIG. 2 is a curve representing viscosity plotted against temperature;
FIG. 3 is a flow diagram illustrating a post-manufacture glass container thermal strengthening process according to an exemplary embodiment;
FIG. 4 is a schematic cross-sectional view showing a reheated glass container about to have a post-manufacture glass container thermal strengthening method performed upon it, with a cylindrical cooling shroud and a base cooling nozzle located below the glass container and a cooling tube having a nozzle at its bottom end being located above the glass container according to an exemplary embodiment;
FIGS. 5 and 6 are schematic diagrams showing the glass container shown in FIG. 4 disposed inside the cylindrical cooling shroud and above the base cooling nozzle located in the cooling shroud, with the cooling tube having the nozzle at its bottom end being located inside the glass container to perform the post-manufacture glass container thermal strengthening method according to an exemplary embodiment;
FIG. 7 is an isometric view of the cooling shroud illustrated in FIGS. 5 and 6 from the top and side thereof according to an exemplary embodiment;
FIG. 8 is a side plan view of the cooling shroud illustrated in FIGS. 5 through 7 according to an exemplary embodiment;
FIG. 9 is a top end view of the cooling shroud illustrated in FIGS. 5 through 8 according to an exemplary embodiment;
FIG. 10 is a first cross-sectional view of the cooling shroud illustrated in FIGS. 5 through 9 according to an exemplary embodiment;
FIG. 11 is a second cross-sectional view of the cooling shroud taken along the line 11-11 in FIG. 10 according to an exemplary embodiment;
FIG. 12 is an enlarged view of a portion of the cooling shroud illustrated in FIG. 10 according to an exemplary embodiment;
FIG. 13 is an isometric view of the tube cooling nozzle illustrated in FIGS. 5 and 6 from the top and side thereof according to an exemplary embodiment;
FIG. 14 is a top end view of the tube cooling nozzle illustrated in FIGS. 5, 6, and 13 according to an exemplary embodiment;
FIG. 15 is a cross-sectional view taken along the line 15-15 in FIG. 14 according to an exemplary embodiment;
FIG. 16 is an isometric view of the base cooling nozzle illustrated in FIGS. 5 and 6 from the top and side thereof according to an exemplary embodiment;
FIG. 17 is a top end view of the base cooling nozzle illustrated in FIGS. 5, 6, and 16 according to an exemplary embodiment;
FIG. 18 is a cross-sectional view of the base cooling nozzle illustrated in FIGS. 5, 6, 16, and 17 according to an exemplary embodiment;
FIG. 19 is an exploded isometric view of a post-manufacture glass container thermal strengthening apparatus for performing the cooling portion of the post-manufacture glass container thermal strengthening process according to an exemplary embodiment;
FIG. 20 is a side plan view of the post-manufacture glass container thermal strengthening apparatus illustrated in FIG. 19, also showing the distal end of a supply conveyor for providing reheated glass containers to the post-manufacture glass container thermal strengthening apparatus, as well as the proximal end of a discharge conveyor for conveying thermally strengthened glass containers discharged by the post-manufacture glass container thermal strengthening apparatus according to an exemplary embodiment;
FIGS. 21 through 28 are cross-sectional side views of portions of the post-manufacture glass container thermal strengthening apparatus and the ends of the supply and discharge conveyors showing the sequence of operations as a reheated glass container has the post-manufacture glass container thermal strengthening method used to thermally strengthen it according to an exemplary embodiment;
FIG. 29 is an isometric view of the takeout tongs operating assembly of the post-manufacture glass container thermal strengthening apparatus shown in FIG. 19 according to an exemplary embodiment;
FIG. 30 is a plan view of the cooling tube operating assembly of the post-manufacture glass container thermal strengthening apparatus shown in FIG. 19 according to an exemplary embodiment;
FIG. 31 is a an isometric view of two cooling shroud mechanisms of the cooling portion of the post-manufacture glass container thermal strengthening process illustrated in FIGS. 19 and 20, each of which cooling shroud mechanisms is for cooling two containers, showing one of the cooling shroud mechanisms raised and the other of the cooling shroud mechanisms lowered according to an exemplary embodiment;
FIGS. 32 through 35 are partially cutaway cross-sectional views of the cooling shroud mechanisms illustrated in FIG. 31, showing the telescoping mechanisms providing cooling air to the cooling shrouds and the base cooling nozzles according to an exemplary embodiment;
FIG. 36 is an isometric view showing an oven having a supply conveyer extending therethrough to deliver reheated glass containers to the cooling tube operating assembly shown in FIGS. 19 and 20 according to an exemplary embodiment;
FIG. 37 is an isometric view showing the cooling tube operating assembly and a deadplate, an exit conveyor, and a pusher mechanism and a portion of the oven from a side opposite the side shown in FIG. 36 according to an exemplary embodiment;
FIG. 38 is a top plan view showing the cooling tube operating assembly and a portion of the oven shown in FIG. 36 according to an exemplary embodiment;
FIG. 39 is an isometric view of an alternate embodiment bottom cooler for mounting in the bottom of the cooling shroud illustrated in FIGS. 5 through 11 from the top and side thereof according to an exemplary embodiment;
FIG. 40 is a top end view of the alternate embodiment bottom cooler illustrated in FIG. 39 according to an exemplary embodiment;
FIG. 41 is a cross-sectional view of the alternate embodiment bottom cooler illustrated in FIGS. 39 and 40 according to an exemplary embodiment;
FIG. 42 is a cross-sectional view of the alternate embodiment bottom cooler illustrated in FIGS. 39 through 41 in the bottom of the cooling shroud illustrated in FIGS. 5 through 12 according to an exemplary embodiment;
FIG. 43 is a schematic cross-sectional depiction of an alternate embodiment post-manufacture glass container thermal strengthening apparatus and method, showing cooling shrouds and cooling tubes mounted above some glass containers on an air permeable conveyor and schematically depicted bottom cooling apparatus located below the glass containers below the cooling shrouds and cooling tubes;
FIG. 44 is a schematic cross-sectional depiction of the alternate embodiment post-manufacture glass container thermal strengthening apparatus and method illustrated in FIG. 43, showing the cooling shrouds and cooling tubes lowered over some glass containers on the air permeable conveyor and the cooling apparatus located below the glass containers below the cooling shrouds and cooling tubes cooling the glass containers;
FIG. 45 is a cross-sectional view of another embodiment of a cooling station;
FIG. 46 is a side view of a cooling tube according to an exemplary embodiment;
FIG. 47 is a perspective view of a portion of a cooling tube assembly of the cooling station illustrated in FIG. 45 according to an exemplary embodiment;
FIG. 48 is a perspective view of a portion of a cooling tube of the cooling tube assembly illustrated in FIG. 46 according to an exemplary embodiment;
FIG. 49 is a detail view of the portion 49-49 illustrated in FIG. 46;
FIG. 50 is a cross-sectional view taken along the line 50-50 in FIG. 49;
FIG. 51 is a cross-sectional view taken along the line 51-51 in FIG. 49;
FIG. 52 is a perspective view of the nozzle of the cooling tube assembly illustrated in FIG. 46 according to an exemplary embodiment;
FIG. 52A is a cross-sectional view of the nozzle of the cooling tube assembly illustrated in FIG. 46 according to an exemplary embodiment; and
FIG. 53 is a cross-sectional view of the portion of the cooling tube assembly illustrated in FIG. 46 according to an exemplary embodiment.



DETAILED DESCRIPTION OF THE EXEMPLARY EMBODIMENTS
Referring to the Figures generally, an exemplary embodiment of a cooling tube assembly is provided. The cooling tube assembly includes a cooling tube and a nozzle coupled to the cooling tube. The cooling tube includes a plurality of throughbores through which cooling fluid is directed towards a sidewall of a glass container. The nozzle includes a bore therethrough configured to direct cooling fluid toward the base of the glass container. The cooling tube assembly is configured to effectively use the cross-sectional area of the cooling tube to deliver cooling air into the bottle. The configuration, shape, size, etc., of the cooling tube throughbores, the nozzle, and the nozzle bore are configured to provide balanced cooling fluid flow, e.g., between the cooling tube throughbores and the nozzle bore, minimum cooling fluid pressure losses, and enhanced cooling qualities resulting in low cooling times.
Thermal strengthening of a glass container rapidly cools the inner and outer surfaces of the glass container until the inner and outer surface temperatures are below the glass transition temperature, thereby “freezing” the surface structure of the glass container while allowing the inner glass to continue to flow until its temperature reaches the glass transition temperature, then letting the glass container cool to room temperature. When the glass container reaches room temperature, the inner and outer surfaces of the glass container will be in compression and the interior of the walls of the glass container will be in tension. In a properly controlled cooling process, the stress along the thickness of the walls of the glass container should thus vary from compression at the outer walls to tension in the interior of the walls to compression at the inner walls, with very little or no net radial stress.
FIG. 1 illustrates a stress parabola that represents the ideal theoretical stress distribution throughout its wall varying from compression at the outer wall of a glass container to tension in the interior of the wall of the glass container (including the midpoint of the wall) to compression at the inside wall of the glass container. The stress profile through the glass is ideally parabolic in shape, having the area under the horizontal axis equal to the area above the horizontal axis, wherein the sum of surface compression is balanced by sandwiched tension to result in a net stress of zero. Ideally, the surface compression zone thickness is typically 21% of the total glass wall thickness on each side, therefore 42% is in compression and 58% in tension. The maximum tension level is typically half of the surface compression stress.
The compression stress levels that are imparted on both inside and outside surfaces of glass containers usually range between −20 MPa and −60 MPa. Industry standard levels for Annealed glass are 0 MPa (±5 MPa), for Heat Strengthened glass are −24 MPa to −52 MPa, for Tempered glass are −69 MPa to −103 MPa, and for Safety Glass are −103 MPa to −152 MPa. Embodiments of the post-manufacture glass container thermal strengthening process described herein are capable of producing glass containers having an outside compressive stress of 20 to 60 MPa which results in a buried tensile stress of 10 to 30 MPa.
In order to achieve a balanced stress profile having such compressive stress levels on the inner and outer surfaces of a glass container, both surfaces are cooled uniformly. Thin sections may be the most difficult to temper due to the difficulty of obtaining a large temperature differential between the inner and outer surfaces and the core. Thin sections may use higher heat transfer coefficients than do thicker areas.
FIG. 2 depicts an exemplary viscosity to temperature curve that illustrates several key temperature-dependent characteristics of a typical glass container having the depicted viscosity to temperature curve. After the glass container is fully blown and has been removed from its mold, it must remain cooler than its Softening Point 60, which is typically approximately 748 degrees Centigrade. The glass material of the glass container is a viscous liquid at temperatures above the Softening Point 60, as illustrated by a viscous liquid range characterization 62.
Following the molding process, the glass containers are annealed in a temperature controlled kiln or oven, e.g., conventional Lehr, by gradually cooling them across a Glass Transition range 64 which is located in a wider Glass Viscoelastic range 66 in which the glass of the glass container exhibits viscoelastic characteristics. The Glass Transition range 64 is the range of temperatures in which the glass in the glass containers goes from being a super-cooled liquid to being a solid.
An Annealing Point 68 is shown in the Glass Transition range 64, and this Annealing Point 68 represents the temperature at which stresses in the glass container will be relieved in a selected predefined time period, typically a few minutes. For a typical glass container, the Annealing Point 68 temperature may typically be approximately 555 degrees Centigrade. At a temperature below approximately 550 degrees Centigrade, it would take hours instead of minutes to relieve the stresses in the glass container.
At temperatures in the Glass Transition range 64 that are higher than the selected Annealing Point 68, it would take less time to relieve the stresses in the glass container. The stresses in the glass containers are locked in by cooling them to a temperature below the Strain Point 70, which is typically approximately 532 degrees Centigrade, although it can vary to as low as approximately 480 degrees Centigrade, depending upon particular glass formula used to make the glass containers. The thickest areas on the glass containers may typically cool slower than the thinner areas of the glass containers.
Referring next to FIG. 3, an embodiment of the post-manufacture glass container thermal strengthening process is illustrated in a flow diagram showing a thermal strengthening process 75 located intermediate a hot end process 76 and a cold end process 77. The process begins at a melt glass materials step 78 in which the materials used to make the molten glass are melted together in a furnace. The molten glass is supplied to the hot end process 76, beginning with the molten glass being distributed to blank or parison molds of an I.S. machine in a distribute gobs to blank molds step 79. Parisons are formed in the parison molds in a form parisons in blank molds step 80.
The parisons are placed within blow molds and blown in a place parisons in blow molds and blow glass containers step 81. The blown glass containers are initially cooled below the Softening Point in the molds in a cool glass containers in blow molds step 82, which ends the operations of the hot end process 76. The hot glass containers are then moved to the Lehr conveyer in a move glass containers to Lehr conveyer step 83, where in a conventional process they would begin the controlled heating and cooling that constitutes the conventional annealing glass container annealing process. As depicted in FIG. 3, however, the hot glass containers are instead subjected to the embodiment of the thermal strengthening process 75, e.g., as further described below.
The hot glass containers (they are typically 500 degrees Centigrade to 600 degrees Centigrade at this point) entering the thermal strengthening process are initially subjected to a reheat glass containers to higher temperature in a kiln or oven, e.g., special tempering Lehr step 84. The special tempering Lehr is hotter than a conventional Lehr, and may be, for example, set at approximately 600 degrees Centigrade at its entrance and approximately 715 degrees Centigrade at its exit. In the example presented herein, the special tempering Lehr may have a length of sixteen feet (4.9 meters) and may have four independent temperature controlled zones.
The typical time spent by the glass containers in the special tempering Lehr is approximately two and one-half minutes to three and one-half minutes, and the glass containers will be heated to a temperature of between approximately 620 degrees Centigrade and approximately 680 degrees Centigrade (but always to a temperature that is less than the Softening Point). If the glass containers are less than approximately 620 degrees Centigrade adequate compressive stresses may not be obtained, and if the glass containers are over approximately 680 degrees Centigrade they may become deformed.
Following the reheat glass containers to higher temperature in a special tempering Lehr step 84, the reheated glass containers are subjected to a thermal strengthening cooling process 85, in which the glass containers are cooled to a temperature below the Strain Point, preferably to a range of between approximately 400 degrees Centigrade and approximately 450 degrees Centigrade. In one embodiment, in the thermal strengthening cooling process 85 all areas of the glass containers are cooled below the Strain Point, including the thicker areas that typically take longer to cool. This cooling will be discussed in more detail below in conjunction with the discussion of the steps contained in the thermal strengthening cooling process 85.
Following the thermal strengthening cooling step 85, the thermal strengthening process 75 finishes in a glass containers further cooling step 86 in which the temperature of the glass containers is reduced to a temperature of approximately 100 degrees Centigrade to approximately 150 degrees Centigrade. The glass containers further cooling step 86 may be accomplished by the use of fan arrays located over a conveyer transporting the thermally strengthened glass containers as they move from the thermal strengthening process 75 to the cold end process 77.
Alternately, if the post-manufacture glass container thermal strengthening process is integrated into an existing glass container production line in which the first section of the Lehr is used to perform the reheat glass containers to higher temperature in a special tempering Lehr step 84, the remaining sections of the Lehr may be used to cool the glass containers in the glass containers further cooling step 86.
Another alternative would be to use the thermal strengthening process 75 as an operation wholly separate from the glass container manufacturing operation in which finished, fully cooled glass containers would be reheated in the reheat glass containers to higher temperature in a special tempering Lehr step 84, strengthened in the thermal strengthening cooling step 85, and then cooled in the glass containers further cooling step 86.
Returning to the thermal strengthening cooling process 85, one embodiment of this process is shown in the steps illustrated in FIG. 3. The glass containers coming from the special tempering Lehr in the reheat glass containers to higher temperature in a special tempering Lehr step 84 are picked up from the conveyer belt exiting the special tempering Lehr with tongs and are lifted to a position above cooling shrouds in a glass containers picked up and lifted above cooling shrouds step 87. Next, cooling shrouds having cooling nozzles are raised to surround the glass containers in a cooling shrouds with cooling nozzles raised around glass containers step 88, and cooling tubes are lowered into the interiors of the glass containers in a cooling tubes lowered into glass containers step 89.
Cooling air is then supplied to the cooling shrouds, the cooling nozzles, and the cooling tubes in a cooling air supplied to cooling shrouds, cooling nozzles, and cooling tubes step 90, while the cooling shrouds are optionally rotated and the cooling tubes are oscillated in a cooling shrouds rotated and cooling tubes oscillated step 91 to simultaneously cool the exterior surfaces and the interior surfaces of the glass containers. It may be noted that the outside surfaces of the glass container finishes are conductively cooled with tong inserts in the tongs supporting the glass containers throughout the thermal strengthening cooling step 85.
The glass containers are cooled to a temperature below the Strain Point in a glass container interior and exterior surfaces temperature simultaneously lowered step 92, in one embodiment to the range of between approximately 400 degrees Centigrade and approximately 450 degrees Centigrade. Cooling times may be relatively fast in order to allow the process to be used in commercial manufacturing operations, and thus may be less than approximately fifteen to approximately twenty seconds for typical glass containers. Typical cooling times have been found to range from approximately nine seconds to approximately twelve and one-half seconds for glass containers weighing from 155 grams to 284 grams, respectively.
When the glass containers have been cooled sufficiently to set the strain in them, the cooling tubes are raised and the cooling shrouds and cooling nozzles are lowered in a cooling tubes raised and cooling shrouds lowered step 93. Next, the thermally strengthened glass containers are lowered to an outgoing conveyer belt in a glass containers lowered to outgoing conveyer belt step 94. This completes the thermal strengthening cooling step 85, and the glass containers then proceed to the glass containers further cooling step 86 which has been previously mentioned.
Following the thermal strengthening process 75, the glass containers may be provided to the cold end of the glass container manufacturing line for application of the cold end process 77. If the glass containers are to be coated, they must be at a temperature of between approximately 100 degrees Centigrade and 150 degrees centigrade. They may be coated, for example, with a lubricious coating in a cold end coating step 95. The glass containers are then transported to an inspection area in a glass containers moved to inspection area step 96, and they are inspected in an inspect glass containers step 97 (where they are typically at a reduced temperature of between approximately 25 degrees Centigrade and 80 degrees Centigrade). The thermally strengthened glass containers are then complete, as indicated in a strengthened glass containers complete termination step 98.
Moving next to FIG. 4, several of the components of an embodiment of the post-manufacture glass container thermal strengthening process are illustrated in conjunction with a glass container 100. The glass container 100 is supported throughout the post-manufacture glass container thermal strengthening process by tongs 102 that have removed the glass container 100 from a kiln or oven, e.g., a special tempering Lehr (not shown), that has reheated the glass container 100.
In FIG. 4, the glass container 100 is shown located directly above a cylindrical cooling shroud 104 and above a bottom cooling nozzle 110 that is located inside the cooling shroud 104 nearer the bottom than the top thereof. A cooling tube 106 having a tube nozzle 108 located at its distal end is shown with the tube nozzle 108 being located above the glass container 100. More detailed descriptions of the cooling shroud 104, the bottom cooling nozzle 104, the cooling tube 106, and the tube nozzle 108 will be provided below in conjunction with FIGS. 7 through 18.
Referring next to FIGS. 5 and 6, an embodiment of the post-manufacture glass container thermal strengthening apparatus is shown with the glass container 100 lowered entirely into the cooling shroud 104 so that the bottom of the glass container 100 is located above the bottom cooling nozzle 110 to provide cooling air to cool the bottom of the glass container 100. The orthogonal apertures 112 in the cooling shroud 104 direct the flow of cooling air onto the neck and finish of the glass container 100, and the angled apertures 114 direct cooling air onto the lower portion of the neck, the shoulders, and the body of the glass container 100. The cooling shroud 104 may optionally be rotated, e.g., moving the sources of cooling air relative to the surface of the glass container 100, to “smear” the jets of cooling air from the orthogonal apertures 112 and the angled apertures 114, with the rotation either being continuous or oscillating.
The hole pattern in the cooling shroud 104, the size of the cooling shroud 104 (i.e., the inside diameter and the outside diameter), the number of the apertures 112 and 114, the diameters of the apertures 112 and 114, the pressure setting, and whether the apertures 112 and 114 are radial and/or angled can all be modified to optimize the strength of the glass container 100 by tailoring the compression stress profile on the outer surface of the glass container 100. In this way, strength can be maximized for whatever type of performance requirement that is desired—be it burst, drop, vertical load, impact, or thermal shock resistance. Typical cooling air pressure provided to the cooling shroud 104 may be approximately 75 mbar to approximately 150 mbar.
Cooling air is also supplied through the cooling tube 106 to the tube nozzle 108, which directs cooling air onto the inside surfaces of the glass container 100. The cooling tube 106 and the tube nozzle 108 may be oscillated between the position shown in FIG. 5 near the bottom of the neck of the glass container 100 (or optionally from a position higher up in the neck of the glass container 100) and the position shown in FIG. 6 nearer the bottom of the glass container 100 (or optionally a higher or slightly lower position in the glass container 100). The cooling tube 106 and the tube nozzle 108 may be oscillated between these two positions up to approximately six times per glass container 100, or, optionally, only once to the position shown in FIG. 6. The speed of the oscillation may be constant, or it may vary during the stroke depth, and it may also optionally be paused briefly at any position.
The plunging of the cooling tube 106 inside the glass container 100 sets up beneficial air flow patterns. These flow patterns are enhanced by the engineered geometry of the tube nozzle 108 at the distal end of the cooling tube 106. The feed area (the inside diameter of the cooling tube 106) and the exhaust area (the inside diameter of the finish of the glass container 100 minus the outside diameter of the cooling tube 106) may be carefully balanced to provide for maximum airflow into and out of the glass container 100. The size of the cooling tube 106 may thus be determined.
The position, speed, stroke, and pressure setting of the cooling tube 106 can all be modified to optimize the strength of the glass container 100 by tailoring the compression stress profile on the inner surface. In this way, strength can be maximized for whatever type of performance requirement that is desired—be it burst, drop, vertical load, impact or thermal shock resistance, or adjusted to compensate for bottle geometry considerations (e.g., challenging shapes, wall thickness variations). Typical cooling air pressure provided to the tube nozzle 108 may be approximately 2.7 bar±0.7 bar, and the stroke of the cooling tube 106 and the tube nozzle 108 may be up to approximately 180 mm.
The design of the bottom cooling nozzle 110 may also be modified to facilitate the optimization of the strength of the glass container 100. The bottom cooling nozzle 110 is positioned and to cool the outside bottom of the glass container 100. Typical cooling air pressure provided to the bottom cooling nozzle 110 may be approximately 0.7 bar.
Referring now to FIGS. 7 through 12 in addition to FIGS. 4 through 6, it may be seen that the cooling shroud 104 is open both on the top end and on the bottom end thereof, and has the pluralities of the orthogonal apertures 112 and the angled apertures 114 located in the side walls thereof, each of which may be approximately 2 mm in diameter. The cooling shroud 104 thus functions to cool the outside surfaces of the glass container 100, other than the bottom of the glass container 100. The outer side of the cooling shroud 104 will be supplied with air pressure in an annular cavity formed between the outer surface of the cooling shroud 104 and an enclosing member not shown in FIGS. 7 through 12.
The cooling shroud 104 uses tiny hole patterns (for example, approximately 18 sets of each of the orthogonal apertures 112 and the angled apertures 114) in the side walls thereof to evenly cover the exterior surfaces of the glass container 100. It may be best seen in FIGS. 6 and 10 that the large plurality of angled apertures 114 in the side walls of the cooling shroud 104 are angled downwardly, for example at an angle of approximately 45 degrees. These angled apertures 114 will cool the shoulders and the side wall of the glass container 100. Located above the angled apertures 114 are a large plurality of orthogonal apertures 112 that will cool the neck and outside of the finish of the glass container 100.
The air pressure in the angled apertures 114 and the orthogonal apertures 112 is preferably approximately 75 mbar to 300 mbar (30 to 120 inches of water) as measured in each individual annulus. A large number of tiny angled apertures 114 and the orthogonal apertures 112 are used to evenly cover the exterior surfaces of the glass container 100. In addition, the cooling shroud 104 is rotationally oscillated, and may be axially oscillated instead of or in addition to the rotation, to smooth out the cooling pattern on the glass container 100.
Referring now to FIGS. 13 through 15 in addition to FIGS. 4 and 5, it may be seen that the tube nozzle 108 has an annular upper portion 120 that fits within the interior of the end of the cooling tube 106, and an annular lower portion 122 that abuts the bottom of the cooling tube 106. Located below the annular lower portion 122 is an outwardly flaring frustroconical segment 124 that may be at an angle of approximately 30 degrees from vertical, and may be, for example, approximately 12 mm wide at its widest diameter. A centrally located aperture 126 that may be, for example, approximately 4 mm in diameter, extends through the annular upper portion 120, the annular lower portion 122, and the frustroconical segment 124. Eight radially spaced apart longitudinal apertures 128 that may be, for example, approximately 2.3 mm in diameter, extend through the annular upper portion 120 and the annular lower portion 122.
In one embodiment, the cooling tube 106 has an approximately twelve millimeter outside diameter and an approximately ten millimeter inside diameter when it will be used with a 330 milliliter single serving beer-container-type finish, and may have an approximately 19.05 millimeter outside diameter and an approximately 16.56 millimeter inside diameter when it will be used with a 500 milliliter glass container of the size typically used for ice tea or juice. Both the cooling tube 106 and the nozzle 108 are easily and quickly replaceable while installed on the post-manufacture glass container thermal strengthening equipment. The cooling tube 106 is mounted in a straight, vertical position, and may be lowered into the interior of the glass container 100.
Air pressure is supplied through the cooling tube 106 to the nozzle 108, and exits the nozzle 108 through the centrally located aperture 126 and the longitudinal apertures 128. In one embodiment, the air pressure feeding the cooling tube 106 is approximately 2.0 bar±0.7 bar (30 psi±10 psi). The cooling air exiting the nozzle 108 through the centrally located aperture 126 cools the inside of the glass container 100 at the bottom, while the cooling air exiting the nozzle 108 through longitudinal apertures 128 is dispersed and directed radially outwardly by the frustroconical segment 124.
By oscillating the cooling tube 106 up and down, the entire length of the interior surfaces of the glass container 100 may be cooled. In one embodiment, the nozzle 108 can be cycled up and down in an approximately 180 millimeter stroke for a typical long neck beer container. The cooling air supplied by the cooling tube 106 through the nozzle 108 exits the glass container 100 through the finish of the glass container 100.
Referring now to FIGS. 16 through 18 in addition to FIGS. 4 through 6, it may be seen that the bottom cooling nozzle 110 is mounted in a stationary position coaxially within the cooling shroud 104 near the bottom thereof. The position of the bottom cooling nozzle 110 is adjustable in height for accommodating different bottle sizes within the cooling shroud 104. The bottom cooling nozzle 110 is supplied with cooling air to a chamber 130 located in the bottom thereof by a duct not shown in these figures. The bottom cooling nozzle 110 has a centrally located aperture 132 oriented upwardly which is surrounded by six radially spaced apart angled apertures 134 that may be, for example, at angles of approximately 30 degrees from vertical, with the top of the bottom cooling nozzle 110 being frustroconical and beveled at an angle of approximately 60 degrees from vertical. The centrally located aperture 132 and the angled apertures 134 may be, for example, approximately 3.2 mm in diameter.
Cooling air is supplied to the chamber 130 in the bottom cooling nozzle 110, and then exits the bottom cooling nozzle 110 through the centrally located aperture 132 and the six radially spaced apart angled apertures 134. The air pressure supplied to the bottom cooling nozzle 110 is preferably approximately 0.34 bar to 0.69 bar (5 to 10 psi). The spray pattern of the centrally located aperture 132 and the six radially spaced apart angled apertures 134 covers the bottom surface of the glass container 100. The cooling air supplied by the bottom cooling nozzle 110 exits the cooling shroud 104 at the bottom of the cooling shroud 104. In one embodiment, the bottom cooling nozzle 110 is configured such that it will not serve as a catch point for broken glass that might shatter during the cooling process, since it may be desirable for such broken glass to have a path to fall clearly out of the cooling shroud 104.
In one embodiment, the tongs 102 (shown in FIGS. 4 through 6) holding the glass container 100 hold it sufficiently rigidly to prevent it from swinging while it is located in the cooling shroud 104. Alternatively, although they are not shown in the figures, it may be desirable to have a plurality of alignment pins located inside the cooling shroud 104 to prevent the glass container 100 from swinging. The alignment pins may be made of a material capable of withstanding the high temperatures while not causing checks in the glass of the glass container 100. In one embodiment, the alignment pins may also be easily replaceable. Since there will be a scrubbing action between the alignment pins and the glass container 100 due to the rotation of the cooling shroud 102, the alignment pins may be designed with a gap.
Referring next to FIG. 19, components of an embodiment of the post-manufacture glass container thermal strengthening apparatus are illustrated. In one embodiment, the apparatus includes an assembly including eight subassemblies. Four of these subassemblies function to move the glass containers, one of the subassemblies functions to cool the outside of the glass containers, one of the subassemblies functions to support a subassembly that cools the interiors of the glass containers, and the last subassembly functions to cool the interiors of the glass containers.
The first subassembly that functions to move the glass containers is a support member 140 located on the floor on which the post-manufacture glass container thermal strengthening apparatus is located that has two upright drive covers 142 and 144 mounted extending upwardly near opposite ends of a base member 146 and an operating mechanism cover 145 located between the upright drive covers 142 and 144. The second subassembly that functions to move the glass containers is a tongs arm support apparatus 148 that is mounted adjacent the upright drive cover 142 and is supported by the base member 146 of the support member 140, and the third subassembly that functions to move the glass containers is a second tongs arm support apparatus 150 that is mounted adjacent the upright drive cover 144 and is supported by the base member 146 of the support member 140.
The tongs arm support apparatus 148 has a support post 152 that supports a tongs drive arm 154 mounted at its proximal end at the top of the support post 152. Located at the distal end of the tongs drive arm 154 is a tongs arm mounting member 156. Similarly, the tongs arm support apparatus 150 has a support post 158 that supports a tongs drive arm 160 mounted at its proximal end at the top of the support post 158. Located at the distal end of the tongs drive arm 160 is a tongs arm mounting member 162.
The fourth subassembly that functions to move the glass containers is a tongs support member 166 having a tongs bar 164 mounted at one end onto the tongs arm mounting member 156 of the tongs drive arm 154 and at the other end onto the tongs arm mounting member 162 of the tongs drive arm 160. Four sets of tongs operating apparatus 168 are supported by the tongs bar 164, with each set of the tongs operating apparatus 168 supporting a pair of the tongs 102 only a portion of one of which pairs is visible in FIG. 19).
The tongs arm support apparatuses 148 and 150 function to drive the tongs support member 166 through an approximately 180 degree arc that will pick up the glass containers 100 from a conveyor exiting a kiln or oven, e.g., special tempering Lehr (not shown in FIG. 19), that reheats the glass containers 100, to move the glass containers 100 to a position in which an embodiment of the post-manufacture glass container thermal strengthening method is performed, and finally to move the glass containers 100 to a conveyor removing the glass containers 100 from the post-manufacture glass container thermal strengthening apparatus.
The tongs arm support apparatus 148 and the tongs arm support apparatus 150 are arranged and configured to operate together, maintaining the tongs bar 164 of the tongs support member 166 parallel to the base member 146 of the support member 140 and a surface upon which the support member 140 is mounted. As the tongs arm support apparatuses 148 and 150 drive the tongs support member 166, the tongs operating apparatus 168, and the tongs 102 through the approximately 180 degree arc, the tongs 102 are all maintained in a vertical position such that the glass containers 100 carried by the tongs 102 will be maintained directly below the tongs operating apparatus 168, irrespective of the angular position of the tongs arm support apparatuses 148 and 150 and the tongs support member 166, the tongs operating apparatus 168, and the tongs 102.
In one embodiment, the subassembly that functions to cool the outside of the glass containers is a cooling shroud mechanism 170 that is mounted on the base member 146 of the support member 140 in a location intermediate the upright drive cover 142 and the upright drive cover 144. The cooling shroud mechanism 170 has two shroud mechanism subassemblies 172 and 174 that are located side-by-side on the floor on which the post-manufacture glass container thermal strengthening apparatus is located and between the tongs arm support apparatus 148 and 150, each of which has two cooling shrouds 104 contained therein (and two bottom cooling nozzles 110 not shown in FIG. 19 contained therein). The cooling shroud mechanism 170 also contains apparatus for operating the cooling shrouds 104 and the bottom cooling nozzles 110.
The shroud mechanism subassemblies 172 and 174 have two positions: a first, retracted position in which they are lowered, which is the position shown for the shroud mechanism subassembly 172 in FIG. 19, and a second, extended position in which they are raised, which is the position shown for the shroud mechanism subassembly 174 in FIG. 19. In the lowered position, the tongs support member 166 and the tongs 102 can freely move glass containers either into position for thermal tempering, or away from the cooling position after thermal tempering. In the raised position, glass containers supported by the tongs 102 on the tongs support member 166 with the tongs arm support apparatus 148 and 150 in position for thermal tempering will be contained within cooling shrouds 104 and above bottom cooling nozzle 110 located in the shroud mechanism subassemblies 172 and 174 for thermal tempering.
While the shroud mechanism subassembly 174 is shown in its upwardly extended position and the shroud mechanism subassembly 172 is shown in its downwardly retracted position, it will be appreciated that in operation the shroud mechanism subassemblies 172 and 174 will move together between their downwardly retracted and upwardly extended positions. Other aspects of the cooling shroud mechanism 170 will be discussed below in conjunction with the discussion of FIGS. 31 through 35.
The subassembly that functions to support a subassembly that cools the interiors of the glass containers in one embodiment is a cooling tube support assembly 176 that has two support arms 178 and 180, the bottom ends of which are respectively mounted onto the support post 152 of the tongs arm support apparatus 148 and the support post 158 of the tongs arm support apparatus 150. The support arms 178 and 180 extend upwardly above the cooling shroud mechanism 170, and have a cooling tube assembly support bridge 182 mounted at their respective top ends and extending therebetween above the cooling shroud mechanism 170. The cooling tube assembly support bridge 182 and the support arms 178 and 180 are mounted in a fixed position and are arranged and configured to allow the tongs arm support apparatus 148 and 150 to drive the tongs support member 166 through its approximately 180 degree arc.
Finally, the subassembly that functions to cool the interiors of the glass containers in one embodiment is a cooling tube assembly 184 that is mounted on the cooling tube assembly support bridge 182 above the shroud mechanism subassemblies 172 and 174. The cooling tube assembly 184 supports four of the cooling tubes 106 each having a tube nozzle 108 located at the bottom thereof. The cooling tube assembly 184 has a base plate 186 that is mounted on the cooling tube assembly support bridge 182 of the cooling tube support assembly 176.
Two vertically extending support rails 188 and 190 extend upwardly from the respective ends of the base plate 186. A support plate 192 is mounted between the top ends of the support rails 188 and 190. A crossbar 194 is slidably mounted on the support rails 188 and 190 and is driven in a vertical direction between the support plate 192 and the base plate 186 by a screw mechanism 196 that is operated by a motor 198.
Extending downwardly from the crossbar 194 at spaced-apart intervals are four tube support sleeves 200 (only two of which are shown in FIG. 19) each of which support a cooling tube 106 (only two of which are shown in FIG. 19). The cooling tube assembly 184 is arranged and configured so that the cooling tubes 106 are respectively above and coaxial with the cooling shrouds 104 located in the shroud mechanism subassemblies 172 and 174 of the cooling shroud mechanism 170. Cooling air may be supplied to the cooling tube assembly 184 so that it will be provided to each of the cooling tubes 106.
The cooling tube assembly 184 is operable to drive the cooling tubes 106 between two positions: a first, raised position, and a second, lowered position. In the raised position, the tongs support member 166 and the tongs 102 can freely move glass containers 100 either into position for thermal strengthening, or from the position for thermal tempering after thermal tempering is complete, with the bottom ends of the cooling tubes 106 and the nozzles 108 being located above the tongs support member 166 and the tongs 102 when the cooling tube assembly 184 is in the raised position. In the lowered position, the bottom ends of the cooling tubes 106 and the nozzles 108 will be respectively located deep within glass containers 100 that are supported by the tongs support member 166 and the tongs 102 for thermal tempering.
Referring next to FIG. 20, in one embodiment, the post-manufacture glass container thermal strengthening apparatus is shown with a source of reheated glass containers 100 and with the apparatus onto which the thermally strengthened glass containers 100 exit the post-manufacture glass container thermal strengthening apparatus. The post-manufacture glass container thermal strengthening apparatus will move the glass containers 100 between three positions: a first position in which they will be picked up from a supply conveyor 210 after they have been reheated, a second position at which the glass containers 100 will be thermally cooled, and a third position at which the glass containers 100 will be deposited on a deadplate 212. While in the exemplary embodiment illustrated herein the tongs support member 166 has four sets of tongs 102 mounted therefrom, each of which tongs 102 may be used to pick up and move a single glass container 100, it will be appreciated that any number of sets of tongs 102 may instead be used.
The supply conveyor 210 provides the reheated glass containers 100 to the post-manufacture glass container thermal strengthening apparatus, and the tongs 102 of the tongs drive arm 154 picks up the glass containers 100 and moves them in an arc by the rotation of the tongs arm support apparatus 148 and 150 (the latter of which is not shown in FIG. 20). The reheated glass containers 100 are moved in a counterclockwise arc approximately 90 degrees to a position in which they are thermally strengthened.
The thermally strengthened glass containers 100 continue to be moved counterclockwise in an arc by the rotation of the tongs arm support apparatus 148 and 150 for an additional approximately 90 degrees, at which point the thermally strengthened glass containers 100 are deposited by the tongs 102 on the deadplate 212. After the tongs 102 are raised, the thermally strengthened glass containers 100 are pushed onto an exit conveyor 214 by a pusher mechanism 216. The thermally strengthened glass containers 100 may then be conveyed away from the post-manufacture glass container thermal strengthening apparatus, and may optionally be further cooled by fans or a subsequent cooling unit (not shown in FIG. 20).
Referring now to FIGS. 21 through 28, a sequence of the post-manufacture glass container thermal strengthening method is illustrated. These figures are all shown as cross-sections along the centerline of the post-manufacture glass container thermal strengthening apparatus. In FIG. 21, the reheated glass containers 100 are shown exiting a kiln or oven, shown as special tempering Lehr 220, adjacent to the post-manufacture glass container thermal strengthening apparatus on the supply conveyor 210. In one embodiment, the special tempering Lehr 220 is located immediately downstream of the I.S. Machine (not shown in FIGS. 21 through 28) as closely as possible to minimize cooling of the glass container 100 before they enter the special tempering Lehr 220. The tongs support member 166 is being rotated clockwise in an arc with the tongs 102 shown just above a reheated glass container 100. It will continue to rotate clockwise until the tongs drive arm 160 is approximately horizontal, at which time the tongs 102 will grasp the finish of a reheated glass container 100, the position of the tongs 102 at that time being illustrated in phantom lines.
Following the tongs 102 grasping the finish of a reheated glass container 100, the tongs support member 166 will begin to be rotated counterclockwise in an arc with the tongs 102 lifting the reheated glass container 100 off of the supply conveyor 210 in a counterclockwise arc as shown in FIG. 22. The tongs support member 166 will continue to rotate counterclockwise in an arc with the tongs 102 until the tongs support member 166 is vertical, in which position the reheated glass container 100 is located above the cooling shroud 104 and below the cooling tube 106 and the tube nozzle 108, as shown in FIG. 23.
As shown in FIG. 24, the cooling shroud 104 will be raised by the shroud mechanism subassembly 174 of the cooling shroud mechanism 170 to surround the reheated glass container 100, with the bottom cooling nozzle 110 located just below the bottom of the reheated glass container 100, and the cooling tube 106 and the tube nozzle 108 will be lowered by the cooling tube assembly 184 until the tube nozzle 108 is in the neck of the reheated glass container 100. At this point, cooling air will be provided by one or more cooling air sources to the cooling shroud 104, to the cooling tube 106 and the tube nozzle 108, and to the bottom cooling nozzle 110.
The cooling shroud 104 optionally is rotated and/or oscillated up and down slightly to smear cooling air coming in from the orthogonal apertures 112 and the angled apertures 114 (both of which are shown in FIGS. 5 and 6) onto the outer surfaces of the reheated glass container 100 to cool them. Simultaneously, the bottom cooling nozzle 110 will direct cooling air onto the bottom of the reheated glass container 100 to cool it. Also simultaneously, the cooling tube 106 and the tube nozzle 108 will be oscillated between the higher position shown in FIG. 24 and a lower position shown in FIG. 25 to cool the inner surfaces of the reheated glass container 100. As mentioned previously, the cooling tube 106 and the tube nozzle 108 may be oscillated between one and approximately six times.
At this point, in one embodiment, the glass container 100 surfaces are cooled quickly and uniformly, setting up a temperature profile through the glass which results in a permanent stress profile once all of the glass is cooled below the Strain Point, preferably to a range of between approximately 400 degrees Centigrade and approximately 450 degrees Centigrade. Since all areas of the glass containers 100 are cooled below the Strain Point, including the middle of the thicker areas that typically take longer to cool, the stress profile throughout the glass containers 100 will be closer to an ideal theoretical stress distribution throughout the walls of the glass container 100, varying from compression at the outer wall of a glass container to tension in the interior of the wall of the glass container to compression at the inside wall of the glass container. This results in the glass containers 100 being stronger, and also makes possible the manufacture of thinner walled and lighter glass containers that still have excellent strength characteristics.
Following the performance of the post-manufacture glass container thermal strengthening method as shown in FIGS. 24 and 26, the cooling shroud 104 and the bottom cooling nozzle 110 will be lowered by the shroud mechanism subassembly 174 of the cooling shroud mechanism 170 to positions below the thermally strengthened glass container 100, and the cooling tube 106 and the tube nozzle 108 will be raised by the cooling tube assembly 184 until the tube nozzle 108 is above the neck of the thermally strengthened glass container 100, as shown in FIG. 26.
The tongs support member 166 will then be rotated counterclockwise in an arc with the tongs 102 delivering the thermally strengthened glass container 100 where its bottom is resting on the deadplate 212, as shown in FIG. 27. At this point, the tongs drive arm 160 is approximately horizontal, and the tongs 102 will release the finish of the thermally strengthened glass container 100 and begin to rotate clockwise, leaving the thermally strengthened glass container 100 on the deadplate 212. As the tongs drive arm 160 continues to rotate clockwise, the pusher mechanism 216 will push the thermally strengthened glass container 100 onto the exit conveyor 214, as shown in FIG. 28.
Referring next to FIG. 29, the installation of the tongs arm support apparatus 148 and 150 onto the support member 140 and the installation of the tongs support member 166 onto the tongs drive arms 154 and 160 are illustrated. The support member 140 is shown with both the operating mechanism cover 145 and the upright drive covers 142 and 144 (all of which are shown in FIG. 19) removed for clarity. The support post 152 of the tongs arm support apparatus 148 is mounted onto the base member 146 at end thereof, and the support post 158 of the tongs arm support apparatus 150 is mounted onto the base member 146 at the other end thereof. The tongs drive arm 154 of the tongs arm support apparatus 148 is supported for rotation at the top end of the support post 152, and the tongs drive arm 160 of the tongs arm support apparatus 150 is supported at the top end of the support post 158.
A drive motor 230 is mounted on the base member 146 of the support member 140 at the center thereof, and operates to rotate a drive shaft 232 having toothed pulleys 234 and 236 mounted on the respective ends thereof and supported for rotation by four bearing support members 238. The toothed pulley 234 drives a toothed pulley 240 that rotates the tongs drive arm 154 through a toothed belt 242. The toothed pulley 236 drives a toothed pulley 244 that rotates the tongs drive arm 160 through a toothed belt 246. Located on and moving with the tongs drive arm 154 is a tongs support rotation member indicated generally by the reference numeral 248, and located on and moving with the tongs drive arm 160 is a tongs support rotation member indicated generally by the reference numeral 250.
The tongs support rotation member 248 and 250 operate to maintain the tongs support member 166 in its vertical orientation as the tongs drive arms 154 and 160 drive the tongs support member 166 through the arc as described in conjunction with FIGS. 21 through 28. Mounted on the outer side of the support post 152 of the tongs arm support apparatus 148 is a support bracket 252, and mounted on the outer side of the support post 158 of the tongs arm support apparatus 150 is a support bracket 254. The support brackets 252 and 254 will support the cooling tube support assembly 176 and the cooling tube assembly 184 (both of which are shown in FIG. 19).
Referring next to FIG. 30, the crossbar 194 is mounted onto the support rail 188 and 190 for vertical movement between the support plate 192 and the base plate 186. The crossbar 194 is driven by the motor 198, which drives the screw mechanism 196 that extends through a threaded aperture 260 in the crossbar 194. Two of the tube support sleeves 200 are mounted on a tube support plate 262, and the other two tube support sleeves 200 are mounted on a tube support plate 264. The two tube support plates 262 and 264 are in turn mounted onto the crossbar 194.
Referring next to FIG. 31, portions of the shroud mechanism subassembly 172 and the shroud mechanism subassembly 174 are shown, again with the shroud mechanism subassembly 172 in its lowered or inactive position and the shroud mechanism subassembly 174 in its raised or cooling position (although in operation typically both the shroud mechanism subassemblies 172 and 174 would operate together in the same positions). It may be seen that each of the shroud mechanism subassemblies 172 and 174 have a pair of cooling shrouds 104 respectively mounted in shroud housings 270 and 272. The shroud housings 270 and 272 are respectively raised and lowered with electromechanically actuator mechanisms 274 and 276 (which may each be a servo-driven screw mechanism) mounted on the operating mechanism cover 145 of the support member 140 (both of which are shown in FIG. 19) on which the post-manufacture glass container thermal strengthening apparatus is located.
Referring now to FIG. 32, a portion of the shroud mechanism subassembly 174 is cut away to show some of the mechanisms contained therein. Specifically, a telescopic shroud air supply tube 280 and a telescopic base air supply tube 282 are shown that respectively supply cooling air to the cooling shroud 104 and the bottom cooling nozzle 110. Thus, as the shroud mechanism subassembly 174 is raised and lowered, the supply tubes 280 and 282 will extend and contract. The shroud air supply tube 280 leads to a passageway 284 supplying cooling air to a shroud cooling cavity 286 located intermediate the shroud housing 272 and both of the cooling shrouds 104 located in the shroud housing 272.
Preferably, the cooling shrouds 104 are installed in the shroud housing 272 such that the shroud cooling cavity 286 is sealed at the top and bottom of the cooling shrouds 104 so that all cooling air supplied through the shroud air supply tube 280 will be delivered through the orthogonal apertures 112 and the angled apertures 114 in the cooling shroud 104 (which are best shown in FIGS. 5 and 6). The cooling shroud 104 is optionally rotated during the cooling operation, as will become evident below in conjunction with a discussion of FIG. 35. (If desired, the cooling shrouds 104 may optionally be mounted for axial rotation in the shroud housing 160 as well.)
The base air supply tube 282 leads to a nozzle supply tube 288 that rigidly supports the bottom cooling nozzle 110 in position within the cooling shroud 104. Cooling air delivered through the base air supply tube 282 will be delivered to the centrally located aperture 132 and the angled apertures 134 in the bottom cooling nozzle 110 (shown in FIGS. 16 through 18).
Referring next to FIGS. 33 and 34, additional detail of an embodiment of the shroud mechanism subassembly 172 is illustrated. The location of a shroud rotation mechanism is indicated with the reference numeral 290. Also, the location of a cullet chute 292 below the cooling shrouds 104 in the shroud housing 270 is indicated. It should be noted that since the cooling shrouds 104 are open at the bottom (as well as at the top), and since the nozzle supply tubes 288 and the bottom cooling nozzles 110 are sized and placed so as to leave the opening at the bottom of the cooling shrouds 104 largely unobstructed, should glass containers 100 break while inside the cooling shrouds 104, the broken glass may freely fall out of the cooling shrouds 104 and into the cullet chute 292, from which is may be directed to a collection area (not shown in FIG. 33 or 34).
Referring now to FIG. 35, additional hardware for use in an embodiment in which the cooling shrouds 104 are rotated during the cooling operation is shown. Upper and lower bearings 300 and 302, respectively, are used to rotatably support the cooling shrouds 104 in the shroud housing 270. Located below the upper bearing 300 is an upper sealing member 304, and located above the lower bearing 302 is a lower sealing member 306. If desired, the shroud air supply tube 280 (shown in FIG. 32) can also provide cooling air through an additional passageway 308 (in addition to the passageway 284 shown in FIG. 32). A mounting surface 310 is shown in the side of the shroud housing 160. Finally, a locating pin 312 for rotation of the cooling shroud 104 is shown near the bottom thereof. The motor and the linkage driving 312 are not shown in FIG. 35.
Referring next to FIGS. 36 through 38, an exemplary manufacturing line for an embodiment of the post-manufacture glass container thermal strengthening process that is located downstream of the hot end (the I.S. machines molding the glass containers, not illustrated herein) and upstream of the cold end (the coating and inspection machines, not illustrated herein) is illustrated. The special tempering Lehr 220 has the supply conveyor 210 running therethrough. Glass containers 100 formed in an I.S. machine (not shown) are placed onto the supply conveyor 210 at the right side of the special tempering Lehr 220 as illustrated in FIG. 36 after having been discharged from the I.S. machine. As the glass containers 100 enter the special tempering Lehr 220, they may be between approximately 500 degrees Centigrade and approximately 600 degrees Centigrade.
The special tempering Lehr 220 may be set at temperatures ranging from approximately 600 degrees Centigrade at the entrance zone (on the right side as illustrated in FIG. 36) to approximately 715 degrees Centigrade at the exit zone (on the right side as illustrated in FIG. 37). In one embodiment, the special tempering Lehr 220 is approximately sixteen feet (4.9 meters) long. The special tempering Lehr 220 may have, for example, four independent temperature controlled zones. The glass containers 100 may spend between two and one-half to three and one-half minutes in the special tempering Lehr 220, and will be heated to a temperature of approximately 620 degrees Centigrade to approximately 680 degrees Centigrade in the special tempering Lehr 220. If the glass containers are below 620 degrees Centigrade adequate compressive stresses may not be obtained in embodiments of the post-manufacture glass container thermal strengthening process, and if the glass containers are above approximately 680 degrees Centigrade deformations may occur in them.
Following the performance of the post-manufacture glass container thermal strengthening process, the thermally strengthened glass containers 100 are deposited on the deadplate 212. The thermally strengthened glass containers 100 are then pushed by the pusher mechanism 216 onto the exit conveyor 214, which takes them away from the post-manufacture glass container thermal strengthening apparatus. Since the thermally strengthened glass containers 100 are still quite hot (although they are uniformly well below the Strain Point 70), they may be subjected to cooling air from a schematically illustrated fan array 320 for cooling them more completely before they reach the cold end equipment (not shown herein). Also shown in FIGS. 37 and 38 is the cullet chute 292 for collecting broken glass falling out of the post-manufacture glass container thermal strengthening apparatus, which broken glass is collected in a collection bin 322.
Referring next to FIGS. 39 through 41, an alternate embodiment bottom cooler 340 for mounting in the bottom of the cooling shroud 104 as shown in FIG. 42 is illustrated. Instead of using the bottom cooling nozzle 110 best shown in FIGS. 5 and 6 which is centrally located directly under the bottom of the glass container 100, the bottom cooler 340 may be advantageous in that is offers excellent bottom cooling characteristics while presenting less of an obstruction to pieces of a glass container 100 that may break during the performance of embodiments of the post-manufacture glass container thermal strengthening method described herein due to defects. Those skilled in the art will realize that if a piece of broken glass hangs up on the bottom cooling nozzle 110, the apparatus may have to be stopped to manually remove the broken glass.
The bottom cooler 340 instead is of a design which is entirely located close to the inner wall of the cooling shroud 104 near the bottom thereof, and as such is entirely open under the bottom of a glass container 100 that is being thermally strengthened. The bottom cooler 340 includes a hollow cylindrical outer adjustable sleeve 342, a hollow cylindrical inner sleeve 344, and an annular locking element 346. The upper portion of the outside of the inner sleeve 344 is curved inwardly at the top thereof in a cross-sectionally arcuate manner as indicated by the reference numeral 348. The bottom portion of the inner sleeve 344 is threaded on the outer surface thereof.
The upper portion of the inside of the outer adjustable sleeve 342 is curved inwardly at the top thereof in a cross-sectionally arcuate manner as indicated by the reference numeral 350. The inside of the outer adjustable sleeve 342 has an annular recess 352 located therein immediately below the inwardly curved portion 350. The outer adjustable sleeve 342 also has an inlet 354 leading from the outer surface of the outer adjustable sleeve 342 to the interior of the annular recess 352. The bottom portion of the outer adjustable sleeve 342 is threaded on the inner surface thereof a short distance below the annular recess 352.
The outer adjustable sleeve 342 is screwed onto the inner sleeve 344 so that the inwardly curved portion 350 in the outer adjustable sleeve 342 and the inwardly curved portion 348 in the inner sleeve 344 define a gap 356 therebetween which will be the air outlet from the bottom cooler. The size of the gap 356 may be adjusted by rotating the outer adjustable sleeve 342 with respect to the inner sleeve 344. Once the gap 356 has been adjusted as desired, the annular locking element 346 is screwed onto the threads on the outside of the inner sleeve 344 until it engages and locks further rotation of the outer adjustable sleeve 342 on the toothed pulley 244.
Referring now to FIG. 42, the bottom cooler is shown installed into a sleeve 360 located inside the bottom portion of the cooling shroud 104. It may be seen that the sleeve 360 has a passageway 362 located in the bottom portion thereof that communicates between the inlet 354 in the outer adjustable sleeve 342 and an air supply tube 364 extending from the bottom of the sleeve 360. Thus, cooling air is supplied from the air supply tube 364 to the bottom cooler, from which it is directed through the gap 356 between the inwardly curved portion 350 of the outer adjustable sleeve 342 and the inwardly curved portion 348 of the inner sleeve 344 at a high velocity onto the bottom of the glass container 100.
The bottom cooler shown in FIG. 39 through uses the Coanda effect, which causes the entrainment of ambient air around a fluid jet. Thus, the fluid jet emitted from the gap 356 between the inwardly curved portion 350 of the outer adjustable sleeve 342 and the inwardly curved portion 348 of the inner sleeve 344 will entrain ambient air located near the inner diameter of the inner sleeve 344 near the top thereof to thereby increase the amount of air that is directed onto the bottom of the glass container 100, thereby increasing the efficiency of the cooling of the bottom of the glass container 100.
Referring finally to FIGS. 43 and 44, an alternate embodiment post-manufacture glass container thermal strengthening apparatus and related method are schematically illustrated. Rather than using an apparatus that removes the reheated glass containers 100 from a supply conveyor, thermally strengthens the glass containers 100, and then deposits the thermally strengthened glass containers 100 onto an exit conveyor, the method schematically illustrated in FIGS. 43 and 44 maintains the glass containers 100 on an air-porous conveyor 370 throughout the thermal strengthening process.
Instead, the cooling shrouds 104 and the cooling tube 106 and the tube nozzle 108 are lowered onto the reheated glass containers 100, until the bottoms of the cooling shrouds 104 are just above the upper surface of the porous conveyor 370. Bottom cooling elements 372 are located below the porous conveyor 370 and the cooling shrouds 104, and direct cooling air upwardly onto the bottoms of the reheated glass containers 100. Simultaneously, cooling air is supplied to the sides of the reheated glass containers 100 along their entire height to cool their outside surfaces, and the cooling tube 106 and the tube nozzle 108 are lowered into the interior of the reheated glass containers 100 to cool their interiors. The cooling tube 106 and the tube nozzle 108 may be oscillated as described above.
Two different methods are contemplated by this alternate embodiment. In one embodiment, the bottom cooling elements 372 is stopped while the thermal strengthening process is performed, after which the bottom cooling elements 372 is moved to advance the next set of reheated glass containers 100 to be thermally strengthened. In the other embodiment, the post-manufacture glass container thermal strengthening apparatus moved together with the bottom cooling elements 372, in which case there must be a sufficient longitudinal number of thermally strengthening sets to allow the bottom cooling elements 372 to continue without stopping.
With reference to FIG. 45, another embodiment of a cooling station 400 for cooling a glass container 402 after it is formed in an I.S. machine is illustrated. The cooling station 400 includes some similarities to the coolers described above. Therefore, differences are the focus of the description that follows.
In one embodiment, the cooling station 400 includes a cooling tube assembly 404. The cooling tube assembly 404 includes a cooling tube 406 (only a portion of the cooling tube 406 illustrated in FIG. 45) and a nozzle 408. The cooling station 400 also includes a cylindrical cooler shown as cylindrical cooling shroud 410. The cooling station 400 also includes a bottom cooler shown as annular bottom cooler 412. The annular bottom cooler 412 is coupled to the cooling shroud 410 and configured to cool the base of the container 402 when the container 402 is located in the cooling shroud 410.
With reference to FIGS. 46 and 47, in one embodiment, the cooling tube 406 extends a length L1 from a first end 414 to a second end 416. In one embodiment, the length L1 is between 300 millimeters and 500 millimeters. In another embodiment, the length L1 is between 350 millimeters and 450 millimeters. In another embodiment, the length L1 is between 397 millimeters and 413 millimeters. In another embodiment, the length L1 is 405 millimeters. The nozzle 408 is located at the second end 416 of the cooling tube 406, with a portion of the nozzle 408 located inside the cooling tube 406.
With reference to FIGS. 48 through 51, in one embodiment, the cooling tube 406 includes a first plurality of throughbores, shown as a first row of throughbores 418. The throughbores 418 extend from an inner surface 420 of the cooling tube 406 to an outer surface 422 of the cooling tube 406. The cooling tube 406 also includes a second plurality of througbores, shown as a second row of throughbores 424. The throughbores 424 extend from the inner surface 420 of the cooling tube 406 to the outer surface 422 of the cooling tube 406.
Each of the first plurality of througbores 418 is circumferentially offset relative to each of the second plurality of througbores 424. The cooling tube 406 also includes a third plurality of throughbores, shown as a third row of throughbores 426 The throughbores 426 extend from the inner surface 420 of the cooling tube 406 to the outer surface 422 of the cooling tube 406. Each of the third plurality of throughbores 426 is circumferentially offset relative to each of the second plurality of throughbores 424. Each of the third plurality of throughbores 426 is circumferentially aligned with one of the first plurality of the throughbores 418.
The third row of throughbores 426 is located axially between the first row of throughbores 418 and the second end 416 of the cooling tube 406. The second row of throughbores 424 is located axially between the first row of throughbores 418 and the third row of throughbores 426. In the illustrated embodiment, eight throughbores 418 in the first row are provided. In other embodiments, other suitable numbers of throughbores may be used. In the illustrated embodiment, eight throughbores 424 in the second row are provided. In other embodiments, other suitable numbers of throughbores may be used. In the illustrated embodiment, eight throughbores 426 in the third row are provided. In other embodiments, other suitable numbers of throughbores may be used.
With reference to FIGS. 50 and 51, in one embodiment, the throughbores 424 of the second row are evenly spaced apart around the circumference of the cooling tube 406. The center of each throughbore 424 is located an angular distance θ1 from the center of the throughbore 424 on either side. In one embodiment, the angular distance θ1 is 45°. The throughbores 426 of the third row are evenly spaced apart around the circumference of the cooling tube 406. The center of each throughbore 426 is located an angular distance θ2 from the center of the throughbore 426 on either side.
In one embodiment, the angular distance θ2 is 45°. The center of each throughbore 424 of the second row is located an angular distance θ3 from the center of the throughbore 426 of the third row located on either side. In one embodiment, the angular distance θ3 is 22.5°. The throughbores 418 of the first row are also evenly spaced apart around the circumference of the cooling tube 406. The throughbores 418 of the first row are each circumferentially aligned with one of the throughbores 426 of the third row and circumferentially offset from the throughbores 424 of the second row.
With further reference to FIGS. 50 and 51, in one embodiment, the cooling tube 406 has an inner diameter D1 and a flowpath with a cross-sectional area of π(D1/2)2. In one embodiment, the diameter D1 is between 5 millimeters and 15 millimeters. In another embodiment, the diameter D1 is 10 millimeters. The cooling tube 406 also has an outer diameter D2. In one embodiment, the outer diameter D2 is between 7 millimeters and 17 millimeters. In another embodiment, the outer diameter D2 is 12 millimeters.
With further reference to FIG. 50, in one embodiment, the throughbores 424 of the second row each have a diameter D3 and a flowpath with a cross-sectional area of π(D3/2)2. In one embodiment, the diameter D3 is between 0.5 millimeters and 2.5 millimeters. In another embodiment, the diameter D3 is between 1.4 millimeters and 1.6 millimeters. In another embodiment, the diameter D3 is 1.5 millimeters. With reference to FIG. 51, in one embodiment, the throughbores 426 of the third row each have a diameter D4 and flowpath with a cross-sectional area π(D4/2)2. In one embodiment, the diameter D4 is between 0.5 millimeters and 2.5 millimeters. In another embodiment, the diameter D4 is between 1.4 millimeters and 1.6 millimeters. In another embodiment, the diameter D4 is 1.5 millimeters. In one embodiment, the throughbores 418 of the first row each have the same diameter as the throughbores 424 of the second row and the throughbores 426 of the third row.
With reference to FIG. 49, in one embodiment, the center of each of the throughbores 418 of the first row is located a distance D5 from the second end 416 of the cooling tube 406. In one embodiment, the distance D5 is between 10 millimeters and 15 millimeters. In another embodiment, the distance D5 is between 12.8 millimeters and 13.2 millimeters. In another embodiment, the distance D5 is 13 millimeters. The center of each of the throughbores 424 of the second row is located a distance D6 from the second end 416 of the cooling tube 406.
In one embodiment, the distance D6 is between 6 millimeters and 11 millimeters. In another embodiment, the distance D6 is between 8.3 millimeters and 8.7 millimeters. In another embodiment, the distance D6 is 8.5 millimeters. The center of each of the throughbores 426 of the third row is located a distance D7 from the second end 416 of the cooling tube 406. In one embodiment, the distance D7 is between 2 millimeters and 6 millimeters. In another embodiment, the distance D7 is between 3.8 millimeters and 4.2 millimeters. In another embodiment, the distance D7 is 4 millimeters.
With reference to FIGS. 52 and 53, an embodiment of a nozzle 408 is illustrated. The nozzle 408 extends from a first end 428 to a second end 430. The nozzle 408 includes a dispensing bore shown as bore 432 therethrough extending along a longitudinal axis A. The bore 432 has a first portion 434 having a constant diameter D8 and a flowpath having a constant cross-sectional area π(D8/2)2. The bore 432 includes a junction 435 between the first portion 434 and a second portion 436. In one embodiment, the cross-sectional area of each of the throughbores 418, 424, and 426 (see FIGS. 49 through 51) is between 5% and 15% of the cross-sectional area of the bore 432 at the junction 435.
In another embodiment, the cross-sectional area of each of the throughbores 418, 424, and 426 (see FIGS. 49-51) is between 8% and 12% of the cross-sectional area of the bore 432 at the junction 435. In another embodiment, the cross-sectional area of each of the throughbores 418, 424, and 426 (see FIGS. 49 through 51) is 9% of the cross-sectional area of the bore 432 at the junction 435. In one embodiment, the sum of the cross-sectional area of all of the throughbores 418, 424, and 426 (see FIGS. 49 through 51) is between 100% and 300% of the cross-sectional area of the bore 432 at the junction 435.
In another embodiment, the sum of the cross-sectional area of all of the throughbores 418, 424, and 426 (see FIGS. 49 through 51) is between 200% and 250% of the cross-sectional area of the bore 432 at the junction 435. In another embodiment, the sum of the cross-sectional area of all of the throughbores 418, 424, and 426 (see FIGS. 49 through 51) is 216% of the cross-sectional area of the bore 432 at the junction 435. In one embodiment, the sum of the cross-sectional area of all of the throughbores 418, 424, and 426 (see FIGS. 49 through 51) is between 30 square millimeters and 50 square millimeters.
In another embodiment, the sum of the cross-sectional area of all of the throughbores 418, 424, and 426 (see FIGS. 49 through 51) is between 42 square millimeters and 43 square millimeters. In another embodiment, the sum of the cross-sectional area of all of the throughbores 418, 424, and 426 (see FIGS. 49 through 51) is 42.5 square millimeters. In one embodiment, the cross-sectional area of the bore 432 at the junction 435 is between 10 square millimeters and 30 square millimeters. In another embodiment, the cross-sectional area of the bore 432 at the junction 435 is between 18 square millimeters and 21 square millimeters.
In another embodiment, the cross-sectional area of the bore 432 at the junction 435 is 19.6 square millimeters. In one embodiment, the ratio of the sum of the cross-sectional area of all of the throughbores 418, 424, and 426 and the cross-sectional area of the bore 432 at junction 435 is balanced to provide for balanced cooling of the sidewall and bottom wall of a glass container which may be desirable.
In one embodiment, the cooling tube 406 and nozzle 408 are configured such that 50%±10% of the cooling fluid provided to the cooling tube assembly 404 exits the cooling tube assembly 404 through the throughbores 418, 424, and 426 and 50%±10% of the cooling fluid provided to the cooling tube assembly 404 exits the cooling tube assembly 404 through the bore 432 of the nozzle 408. In another embodiment, the cooling tube 406 and nozzle 408 are configured such that 50%±less than 8% of the cooling fluid provided to the cooling tube assembly 404 exits the cooling tube assembly 404 through the throughbores 418, 424, and 426 and 50%±less than 8% of the cooling fluid provided to the cooling tube assembly 404 exits the cooling tube assembly 404 through the bore 432 of the nozzle 408. In another embodiment, the cooling tube 406 and the nozzle 408 are configured such that 44% of the cooling fluid provided to the cooling tube assembly 404 exits the cooling tube assembly 404 through the throughbores 418, 424, and 426 and 56% of the cooling fluid provided to cooling tube assembly 404 exits the cooling tube assembly 404 through the bore 432 of the nozzle 408.
The diameter of the second portion 436 increases from the junction to the second end 430. The wall defining the second portion 436 of the bore 432 extends at an angle θ4 relative to the longitudinal axis A. In one embodiment, the angle θ4 is between 10° and 30°. In another embodiment, the angle θ4 is 20°.
With reference to FIG. 52A, the outer surface of the nozzle 408 includes a first portion 438 extending away from the first end 428 at an angle θ5 relative to the longitudinal axis A. In one embodiment, the angle θ5 is between 5° and 15°. In another embodiment, the angle θ5 is 10°. The first portion 438 extends from the first end 428 to a junction 440. The outer surface of the nozzle 408 includes a second portion 442 extending parallel to the longitudinal axis A from the junction 440 to a transition portion 444. The outer surface also includes a radially outwardly extending portion 446 extending radially outwardly perpendicular to the longitudinal axis A from the transition portion 444 to an interface portion 448 configured to abut the inner surface 420 of the cooling tube 406 (see FIG. 53).
The interface portion 448 extends parallel to the longitudinal axis A from the outwardly extending portion 446 to an angularly inwardly extending portion 450. The angularly inwardly extending portion 450 extends from the interface portion 448 to a relief portion 452. The relief portion 452 extends from the angularly inwardly extending portion 450 to a radially outwardly extending flange portion 454 configured to abut the second end 416 of the cooling tube 406 (see FIG. 53). The outer surface of the nozzle 408 includes an outer portion 456 extending from the flange portion 454 to the second end 430 of the nozzle 408. The outer portion 456 is configured to be located outside of the cooling tube 406 (see FIG. 53).
With further reference to FIG. 52A, the nozzle 408 has a diameter D9 at the second portion 442 of the outer surface. In one embodiment, the diameter D9 is between 5 millimeters and 10 millimeters. In another embodiment, the diameter D9 is between 8.3 millimeters and 8.7 millimeters. In another embodiment, the diameter D9 is 8.5 millimeters. The diameter D9 is less than the inner diameter D1 of the cooling tube 406 (see FIG. 50), allowing a portion of the nozzle 408 to be located inside of the cooling tube 406 (see FIG. 53).
With further reference to FIG. 52A, the nozzle 408 has a diameter D10 at the outer portion 456. In one embodiment, the diameter D10 is between millimeters and 15 millimeters. In another embodiment, the diameter D10 is 12 millimeters. The diameter D10 is greater than the inner diameter D1 of the cooling tube 406 (see FIG. 50), preventing the outer portion 456 from being located inside of the cooling tube 406 (see FIG. 53). In one embodiment, the diameter D10 is the same as the outer diameter D2 of the cooling tube 406 (see FIG. 50). In one embodiment, the diameter D10 is greater than the inner diameter D1 of the cooling tube 406 but less than or equal to the outer diameter D2 of the cooling tube 406.
With further reference to FIG. 52A, the nozzle 408 has a diameter D11 at the interface portion 448. In one embodiment, the diameter D11 is between 9 millimeters and 11 millimeters. In another embodiment, the diameter D11 is 10 millimeters. In one embodiment, the diameter D11 is the same as the inner diameter D1 of the cooling tube 406, with the interface portion 448 configured to abut the inner surface 420 of the cooling tube 406 (see FIG. 53). In one embodiment, the nozzle 408 is coupled to the cooling tube 406 by welding. In another embodiment, the nozzle 408 may be coupled to the cooling tube 406 by another suitable mechanism or method.
With further reference to FIG. 52A, the nozzle 408 extends a length L2 from the first end 428 to the second end 430. In one embodiment, the length L2 is between 10 millimeters and 25 millimeters. In another embodiment, the length L2 is 17 millimeters. The outer portion 456 of the nozzle 408 extends a length L3. In one embodiment, the length L3 is between 2 millimeters and 4 millimeters. In another embodiment, the length L3 is between 2.8 millimeters and 3.2 millimeters. In another embodiment, the length L3 is 3 millimeters.
With further reference to FIG. 52A, the outwardly extending portion 446 is a distance L4 from the flange portion 454. In one embodiment, the length L4 is between 2 millimeters and 4 millimeters. In another embodiment, the length L4 is between 2.8 millimeters and 3.2 millimeters. In another embodiment, the length L3 is 3 millimeters.
With further reference to FIG. 52A, the flange portion 454 is a distance L5 from the first end 428 of the nozzle. In one embodiment, the distance L5 is between 10 millimeters and 20 millimeters. In another embodiment, the distance L5 is 14 millimeters. In one embodiment, the distance L5 is greater than the distance D5 (see FIG. 49). With reference to FIG. 53, in one embodiment, the nozzle 408 is configured such that the first end 428 of the nozzle 408 is located past the throughbores 418 of the first row when the nozzle 408 is located in the cooling tube 406. In one embodiment, the throughbores 418 of the first row are located axially between the first end 428 of the nozzle 408 and the second end 416 of the cooling tube 406.
The cooling tube 406 has a flow path with an area, e.g., cross-sectional area. In one embodiment, the nozzle 408 is configured to use between 55% and 90% of the cross-sectional area of the flow path. In another embodiment, the nozzle 408 is configured to use between 75% and 85% of the cross-sectional area of the flow path. In another embodiment, the nozzle 408 is configured to use 79% of the cross-sectional area of the flow path.
In one embodiment, the nozzle 408 is configured to pass cooling fluid, e.g., air, at a pressure of 1.5 bar through the bore 432 of the nozzle 408 from the first end 428 to the second end 430 at a rate of between 50 standard cubic feet per minute and standard cubic feet per minute. In another embodiment, the nozzle 408 is configured to pass cooling fluid, e.g., air, at a pressure of 1.5 bar through the bore 432 of the nozzle 408 from the first end 428 to the second end 430 at a rate of 56 standard cubic feet per minute.
In one embodiment, the nozzle 408 is shaped and configured to minimize pressure loss while balancing the flow between the throughbores 418, 424, and 426 in the cooling tube 406 and the bore 432 in the nozzle 408.
In one embodiment, the throughbores 418, 424, and 426 are sized and configured to provide for high velocity cooling fluid flow therethrough to provide for turbulence and desirable cooling quality. In one embodiment, the cooling fluid exiting the bore 432 of the nozzle 408 has a velocity of between 20 meters per second and 30 meters per second and the cooling fluid exiting the throughbores 418, 424, and 426 has a velocity of between 70 meters per second and 80 meters per second. In another embodiment, the cooling fluid exiting the bore 432 of the nozzle has a velocity of 25 meters per second and the cooling fluid exiting the throughbores 418, 424, and 426 has a velocity of 75 meters per second.
It is desired that the cooling tube 406 and nozzle 408 be configured to provide 56 standard cubic feet per minute of air at 1.5 bar to reduce the temperature of the inner surface of a glass bottle having a 330 milliliter capacity, weighing 200 grams, and having a maximum diameter of 63 millimeters from 1166° Fahrenheit to 572° Fahrenheit in less than 9 seconds. Optimally, the cooling tube 406 and nozzle 408 can be configured to provide 56 standard cubic feet per minute of air at 1.5 bar to reduce the temperature of the inner surface of the glass bottle described above from 1166° Fahrenheit to 572° Fahrenheit in 7 seconds. Embodiments of cooling tube assemblies described above may also be used to cool bottles having different dimensions, configurations, etc.
Although the foregoing description of the present invention has been shown and described with reference to particular embodiments and applications thereof, it has been presented for purposes of illustration and description and is not intended to be exhaustive or to limit the invention to the particular embodiments and applications disclosed. It will be apparent to those having ordinary skill in the art that a number of changes, modifications, variations, or alterations to the invention as described herein may be made, none of which depart from the spirit or scope of the present invention. The particular embodiments and applications were chosen and described to provide the best illustration of the principles of the invention and its practical application to thereby enable one of ordinary skill in the art to utilize the invention in various embodiments and with various modifications as are suited to the particular use contemplated. All such changes, modifications, variations, and alterations should therefore be seen as being within the scope of the present invention as determined by the appended claims when interpreted in accordance with the breadth to which they are fairly, legally, and equitably entitled.
While the current application recites particular combinations of features in the claims appended hereto, various embodiments of the invention relate to any combination of any of the features described herein whether or not such combination is currently claimed, and any such combination of features may be claimed in this or future applications. Any of the features, elements, or components of any of the exemplary embodiments discussed above may be claimed alone or in combination with any of the features, elements, or components of any of the other embodiments discussed above.

## Claims

1. A cooling tube assembly comprising:
a cylindrical cooling tube extending from a first end to a second end, the cooling tube having an inner surface, an outer surface, an inner diameter, and an outer diameter, the cooling tube including a first plurality of throughbores and a second plurality of throughbores located axially between the first plurality of throughbores and the second end of the cooling tube, each of the second plurality of throughbores being circumferentially offset from each of the first plurality of throughbores;
a nozzle extending from a first end to a second end, the first end of the nozzle being located inside the cooling tube with the first plurality of throughbores being located axially between the second end of the cooling tube and the first end of the nozzle;
wherein the nozzle includes a first portion with an outer diameter less than the inner diameter of the cooling tube and a second portion with an outer diameter greater than the inner diameter of the cooling tube;
wherein the nozzle includes a bore extending from the first end to the second end, the bore having a first cross-sectional area in a first portion extending from the first end to a junction; and
wherein each individual one of the first plurality of throughbores has a cross-sectional area; and
wherein the cross-sectional area of each individual one of the first plurality of throughbores is between 5% and 15% of the first cross-sectional area of the bore of the nozzle.

2. The cooling tube of claim 1, wherein the cross-sectional area of each individual one of the first plurality of throughbores is between 8% and 12% of the first cross-sectional area of the bore of the nozzle.

3. The cooling tube of claim 1, wherein the first plurality of throughbores are evenly spaced around the circumference of the cooling tube.

4. The cooling tube assembly of claim 1, wherein each of the second plurality of throughbores has a cross-sectional area; and
wherein the second plurality of throughbores are evenly spaced around the circumference of the cooling tube.

5. The cooling tube assembly of claim 4, further comprising a third plurality of throughbores each having a cross-sectional area and being located between the second plurality of throughbores and the second end of the cooling tube.

6. The cooling tube assembly of claim 5, wherein the sum of the cross-sectional areas of all of the first, second, and third pluralities of throughbores is between 100% and 300% of the first cross-sectional area of the first portion of the bore.

7. The cooling tube assembly of claim 1, wherein the cross-sectional area of the bore increases from the junction to the second end.

8. The cooling tube assembly of claim 1, wherein the bore of the nozzle extends along a central axis;
wherein the outer surface of the nozzle includes a first portion extending from the first end to a junction; and
wherein the first portion forms an angle of between 5° and 15° with the central axis.

9. The cooling tube assembly of claim 1, wherein the outer surface of the nozzle includes a first portion, wherein the first portion forms an angle of 10° with the central axis.

10. The cooling tube assembly of claim 1, wherein the nozzle is configured to pass air at a pressure of 1.5 bar through the nozzle from the first end to the second end at a rate of between 50 standard cubic feet per minute and 60 standard cubic feet per minute.

11. The cooling tube assembly of claim 10, wherein the nozzle is configured to pass air at a pressure of 1.5 bar through the nozzle from the first end to the second end at a rate of 56 standard cubic feet per minute.

12. A cooling tube assembly comprising:
a cylindrical cooling tube extending from a first end to a second end, the cooling tube having an inner surface, an outer surface, an inner diameter, and an outer diameter, the cooling tube including a first plurality of throughbores and a second plurality of throughbores located axially between the first plurality of throughbores and the second end of the cooling tube, each of the second plurality of throughbores being circumferentially offset from each of the first plurality of throughbores;
a nozzle extending from a first end to a second end, the first end of the nozzle being located inside the cooling tube with the first plurality of throughbores being located axially between the second end of the cooling tube and the first end of the nozzle;
wherein the nozzle includes a first portion with an outer diameter less than the inner diameter of the cooling tube and a second portion with an outer diameter greater than the inner diameter of the cooling tube;
wherein the nozzle includes a bore extending from the first end to the second end, the bore having a first cross-sectional area in a first portion extending from the first end to a junction;
wherein each of the second plurality of throughbores has a cross-sectional area, and wherein the second plurality of throughbores are evenly spaced around the circumference of the cooling tube;
further comprising a third plurality of throughbores each having a cross-sectional area and being located between the second plurality of throughbores and the second end of the cooling tube; and
wherein the sum of the cross-sectional area of all of the first, second and third pluralities of throughbores is 216% of the first cross-sectional area of the first portion of the bore.

13. A cooling tube assembly comprising:
a cylindrical cooling tube extending from a first end to a second end, the cooling tube having an inner surface, an outer surface, an inner diameter, and an outer diameter, the cooling tube including a first plurality of throughbores and a second plurality of throughbores located axially between the first plurality of throughbores and the second end of the cooling tube, each of the second plurality of throughbores being circumferentially offset from each of the first plurality of throughbores;
a nozzle extending from a first end to a second end, the first end of the nozzle being located inside the cooling tube with the first plurality of throughbores being located axially between the second end of the cooling tube and the first end of the nozzle; and
wherein a center of each of the first plurality of throughbores are spaced 45° from a center of each of the ones of the first plurality of throughbores on either side relative to a center axis of the cooling tube.

14. A cooling tube assembly comprising:
a cylindrical cooling tube extending from a first end to a second end, the cooling tube having an inner surface, an outer surface, an inner diameter, and an outer diameter, the cooling tube including a first plurality of throughbores and a second plurality of throughbores located axially between the first plurality of throughbores and the second end of the cooling tube, each of the second plurality of throughbores being circumferentially offset from each of the first plurality of throughbores;
a nozzle extending from a first end to a second end, the first end of the nozzle being located inside the cooling tube with the first plurality of throughbores being located axially between the second end of the cooling tube and the first end of the nozzle; and
wherein a center of each of the second plurality of throughbores are spaced 45° from a center of each of the ones of the second plurality of throughbores on either side relative to a center axis of the cooling tube.

15. A cooling tube assembly comprising:
a cylindrical cooling tube extending from a first end to a second end, the cooling tube having an inner surface, an outer surface, an inner diameter, and an outer diameter, the cooling tube including a first plurality of throughbores and a second plurality of throughbores located axially between the first plurality of throughbores and the second end of the cooling tube, each of the second plurality of throughbores being circumferentially offset from each of the first plurality of throughbores;
a nozzle extending from a first end to a second end, the first end of the nozzle being located inside the cooling tube with the first plurality of throughbores being located axially between the second end of the cooling tube and the first end of the nozzle, wherein the nozzle includes a first portion with an outer diameter less than the inner diameter of the cooling tube and a second portion with an outer diameter greater than the inner diameter of the cooling tube, wherein the outer diameter of the second portion defines a maximum outer diameter of the nozzle, and wherein the second portion terminates at a seat interposed between the first and second ends, the seat seating against an axial face of the cooling tube at the second end of the cooling tube; and
wherein a center of each of the first plurality of throughbores are circumferentially offset by 22.5° from a center of each of the second plurality of throughbores closest proximate on either side relative to a center axis of the cooling tube.

16. The cooling tube assembly of claim 15, wherein each of the third plurality of throughbores is circumferentially aligned with one of the first plurality of throughbores relative to a center axis of the cooling tube.