巴西专利BR112014013142B1 fluid-cooled lances for submerged top injection

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专利摘要:
FLUID COOLED SPEARS FOR TOP SUBMERGED INJECTION. The invention relates to a TSL lance having an outer housing of three substantially concentric lance tubes, at least one additional lance tube concentrically inside the housing, and an annular end wall at an exit end of the lance which joins the outermost boom tube and innermost boom tube ends of the casing together at an output end of the boom and is spaced from an output end of the middle boom tube of the housing. Refrigerant fluid can be circulated through the housing, by flowing to and away from the outlet end. The spacing between the end wall and the outlet end of the intermediate tube provides for a constriction of refrigerant flow so as to increase the velocity of refrigerant flow. The additional lance tube defines a central hole and is spaced from the innermost lance tube of the housing so as to define an annular passage, whereby materials passing through the hole and passage are mixed adjacent to the outlet end of the lance. . The wall (...).
公开号:BR112014013142B1
申请号:R112014013142-2
申请日:2012-11-26
公开日:2021-05-18
发明作者:Matusewicz Robert；Reuter Markus
申请人:Outotec Oyj；
IPC主号:

专利说明:

Field of Invention
[0001] This invention relates to submerged top injection lances for use in melt bath pyrometallurgical operations. Background of the Invention
[0002] Melt-bath smelting operations or other pyrometallurgical operations that require interactions between the bath and an oxygen-containing gas source utilize several different arrangements for the gas supply. In general, these operations involve direct injection into the molten metal/metal scrap. This can be done by means of bottom blow fans as in a type of Bessemer oven or by side blow fans as in a type of Peirce-Smith converter. Alternatively, gas injection can be by means of a lance to provide either top blow injection or submerged injection. Examples of top blow lance injection are the KALDO and BOP steelmaking plants in which pure oxygen is blown from above the bath to produce steel from cast iron. Another example is the Mitsubishi top copper process, in which the injection lances provoke jets containing oxygen, the injection of the blow lance is provided by the smelting stages and metal residue conversion of gas such as air or oxygen-enriched air , to impinge on and penetrate the upper surface of the bath, respectively, to produce and convert copper metallic residue. In the case of submerged lance injection, injection takes place inside rather than above a bath slag layer in order to provide top submerged punch injection (TSL), a well-known example of this is the Outotec Ausmelt TSL technology which is applied to a wide variety of metal processing.
[0003] With both forms of injection from above, that is, with both top blowing and TSL injection, the lance is subjected to the high temperatures that prevail in the bath. The top blowing in the Mitsubishi copper process uses a number of relatively small steel lances that feature an inner tube of about 50 mm in diameter and an outer tube of about 100 mm in diameter. The inner tube ends near the level of the furnace roof, well above the reaction zone. The outer tube, which is rotatable to prevent it from becoming attached to a water-cooled collar on the oven roof, extends down into the oven's gas space to position its lower end about 500-800 mm above the top surface of the bath. in fusion. The particulate feed contained in the air is blown through the inner tube, while oxygen-enriched air is blown through the ring between the tubes. Despite the spacing of the lower end of the outer tube above the bath surface, and any cooling of the lance that passes through it, the outer tube burns at about 400mm per day. In this way, the outer tube is slowly reduced and, when required, new sections are fixed on top of the consumable outer tube.
[0004] TSL injection lances are much larger than those for top blowing, such as in the Mitsubishi process described above. A TSL boom typically has at least one inner and one outer tube, as assumed below, but has at least one other tube concentric with the inner and outer tubes. Typical large-scale TSL lances feature the outer tube with a diameter of 200 to 500 mm or more. Also, the boom is much longer and extends down through the roof of a TSL reactor, which can be about 10 to 15 m high, such that the lower end of the outer tube is immersed to a depth of about 300 mm or more in a molten bath slag phase, but is protected by a solidified slag coating formed and held on the outer surface of the outer tube by the cooling action of the injected gas stream. The inner tube may end at about the same level as the outer tube, or at a higher level up to about 1000 mm above the lower end of the outer tube. In this way, only the lower end of the outer tube can be submerged. In either case, a helical blade or other flow shaping device can be mounted on the outer surface of the inner tube to cover the annular space between the inner tube and the outer tube. The blades produce a strong swirling action to an air stream or oxygen-enriched stream along this ring and serve to enhance the cooling effect as well as ensure that the gas is well mixed with the fuel and feed material supplied through of the inner tube with the mixing taking place substantially in a mixing chamber defined by the outer tube, below the lower end of the inner tube where the inner tube ends at a sufficient distance above the lower end of the outer tube.
[0005] The outer tube of the TSL boom wears and burns at its lower end, but at a rate that is considerably reduced by the solidified slag protective coating than would be the case without the coating. However, this is controlled to a substantial degree by the mode of operation with TSL technology. The mode of operation makes the technology viable despite the lower end of the boom being submerged in a highly reactive and corrosive environment of the molten slag bath. The inner tube of a TSL lance can be used to supply feed materials such as concentrate, fluxes and reducers to be injected into a bath slag layer, or it can be used for fuel. An oxygen-containing gas, such as air or oxygen-enriched air, is supplied through the ring between the tubes. Before submerged injection into the bath slag layer is started, the lance is positioned with its lower end, ie the lower end of the outer tube, spaced a suitable distance above the slag surface. Gases containing oxygen and fuel, such as fuel oil, fine coal or hydrocarbon gas, are supplied to the boom and a resulting oxygen/fuel mixture is combusted to generate a jet of flame that impinges on the slag. This causes the slag to be spattered to form, on the outer lance tube, the slag layer which is solidified by the gas stream passing through the lance to provide the solid slag coating mentioned above. The lance is then able to be lowered to obtain injection into the slag, with the ongoing passage of oxygen containing gas through the lance keeping the lower lance extension at a temperature at which the solidified slag coating is maintained and protects the outer tube.
[0006] With a new TSL boom, the relative positions of the lower ends of the outer and inner tubes, that is, the distance from the lower end of the inner tube is set back, if applicable, from the lower end of the outer tube, to an optimal length for a particular pyrometallurgical operating window determined during design. The optimal length may be different for different uses of TSL technology. Thus, in a two-stage batch operation for converting copper metal waste with oxygen transfer through slag to metal waste, a continuous single-stage operation for converting copper metal waste to blister copper (impure copper ), a process for reducing lead-containing slag, or a process for smelting an iron oxide feed material to produce pig iron, all have different optimum mixing chamber lengths. However, in each case, the length of the mixing chamber progressively drops below the optimum for pyrometallurgical operation as the lower end of the outer tube wears out and burns slowly. Similarly, if there is zero displacement between the ends of the outer and inner tubes, the lower end of the inner tube may be exposed to the slag, also being worn down and subjected to burning. In this way, at intervals, the lower end of at least the outer tube needs to be cut to provide a clean edge to which a length of tube of appropriate diameter is welded, in order to re-establish the optimal relative positions of the lower ends of the tube in order to optimize casting conditions.
[0007] The rate at which the lower end of the outer tube is abraded and burns varies with the molten bath pyrometallurgical operation being conducted. Factors that determine this rate include feed processing rate, operating temperature, bath fluidity and chemistry, boom flow rates, etc. In some cases the corrosion and burn wear rate is relatively high and can be such that in the worst case several hours of operation can be lost in a day due to the need to interrupt processing to remove a worn boom from operation and replace it. by another while the worn boom taken out of service is repaired. Such outages occur multiple times in a day with each outage being added to the non-processing time. Although TSL technology offers significant benefits, including cost savings, over other technologies, any uptime lost to port boom replacement carries a significant cost penalty.
[0008] With both the top blow and TSL lances, there have been proposals for fluid cooling to protect the lance from the high temperatures found in pyrometallurgical processes. Examples of fluid cooled lances for top blowing are described in US patents: 3223398 to Bertram et al, 3269829 to Belkin, 3321139 to De Saint Martin, 3338570 to Zimmer, 3411716 to Stephan et al, 3488044 to Shepherd, 3730505 to Ramacciotti et al, 3802681 from Pfeifer, 3828850 from McMinn et al, 3876190 from Johnstone et al, 3889933 from Jaquay, 4097030 from Desaar, 4396182 from Schaffar et al, 4541617 from Okane et al; and 6565800 from Dunne.
[0009] All of these references, with the exception of 3223398 by Bertram et ale 3269829 by Belkin, use concentric outer tubes arranged to allow fluid flow to the exit tip of the lance along a supply passage and back from the tip to the along a return passage, although Bertram et al use a variant in which such flow is limited to a nozzle part of the lance. Although Belkin provides cooling water, it passes through outlets along the length of an inner tube to mix with supplied oxygen along an annular passage between the inner tube and outer tube so that it is injected as steam with oxygen. . The heating and evaporation of water provides cooling to the Belkin lance, while the current generated and injected is said to return heat to the bath.
US patents 3521872 to Themelis, 4023676 to Bennett et al and 4326701 to Hayden, Jr. et al purport to describe lances for submerged injection. Themelis' proposition is similar to that of US patent 3269829 to Belkin. Both use a lance cooled by adding water to the gas stream and rely on evaporation in the injected stream, an arrangement that is not the same as cooling the lance with water by heat transfer in a closed system. However, the Themelis arrangement does not feature an internal tube and gas and water are supplied along a single tube in which the water is vaporized. The proposal by Bennett et al, although referring to a spear, is more aimed at a fan because it injects, under the surface of the molten ferrous metal, through the peripheral wall of a furnace in which the molten metal is contained. In the proposal by Bennett et al, concentric injection tubes extend inside a ceramic sleeve while cooling water is circulated through the tubes contained in the ceramic. In the case of Hayden, Jr. et al, provision of a coolant is made only in the upper extension of the lance, while the lower extension of the submersible outlet end comprises a single tube embedded in a refractory cement.
[0011] The limitations of the prior art proposals are highlighted by Themelis. The discussion is in relation to copper refining by oxygen injection. Although copper has a melting point of about 1085°C, it is pointed out by Themelis that refining is conducted at a superheated temperature of about 1140°C to 1195°C. At such temperatures, the lances of the best stainless steels or steel alloys show little strength. Thus, even top blow lances typically use circulated cooling fluid or, in the case of the submerged lances by Bennett and Hayden, Jr, et al, a refractory or ceramic coating. The advancement of US patent 3269829 to Belkin, and the improvement over Belkin provided by Themelis, is to utilize the powerful cooling capable of being achieved by evaporation of water mixed within the injected gas. In each case, evaporation must be achieved within, and to cool, the lance. Themelis' improvement over Belkin is in atomizing the coolant water before it is supplied to the boom, avoiding the risks of structural failure of the boom from an explosion caused by the injection of liquified water into the molten metal.
[0012] The US patent 6565800 to Dunne describes a solid injection lance for the injection of solid particulate material in molten material, using a non-reactive vehicle. That is, the lance is simply for use in transporting particulate matter in the melt, rather than as a device that enables mixing of materials and combustion. The boom features a central core tube through which particulate material is blown and, in direct thermal contact with the outer surface of the core tube, a double-walled jacket through which coolant such as water is able to be circulated. The jacket extends along a portion of the length of the enclosing tube to leave a projected length of the enclosing tube at the exit end of the boom. The boom has a length of at least 1.5 meters and from the realistic designs it is apparent that the outer diameter of the jacket is on the order of about 12 cm, with the inner diameter of the core tube on the order of about 4 cm. The jacket comprises successive lengths welded together, with the main lengths of steel and the end section closest to the exit end of the boom being copper or copper alloy. The projecting outlet end of the inner tube is stainless steel which, in order to facilitate replacement, is connected to the main length of the inner tube by a threaded coupling.
[0013] The lance of US patent 6565800 to Dunne is said to be suitable for use in the HIsmelt process for the production of molten ferrous metal, with the lance enabling the injection of iron oxide feed material and carbonaceous reducer. In this context, the boom is exposed to hostile conditions, including operating temperatures on the order of 1400°C. However, as indicated above with reference to Themelis, copper has a melting point of about 1085°C and even at temperatures of about 1140°C to 1195°C, stainless steels show very low strength. Perhaps Dunne's proposal is suitable for use in the context of the HIsmelt process, given the high ratio of about 8:1 in the cooling jacket cross section to the core tube cross section, and the small overall cross sections involved. Dunne's spear is not a TSL spear, nor is it suitable for use in TSL technology.
[0014] Examples of lances for use in pyrometallurgical processes based on TSL technology are provided by US patents 4251271 and 5251879, both by Floyd and in patent US 5308043 by Floyd et al. As detailed above, the slag is initially sprayed by using the top blowing lance over a layer of molten slag to obtain a protective coating of slag on the lance which is solidified by high velocity butt blown gas which generates the spray. The solid slag coating is maintained although the lance is then lowered to submerge the lower outlet end into the slag layer so as to enable the required top submerged punch injection into the slag. The lances of patents US 4251271 and 5251879, both by Floyd, operate in this way with cooling to maintain the solid slag layer only by gas injected in the case of patent US 4251271 and by this gas plus gas blown through a protective tube ( "shroud tube") in the case of US patent 5251879. However, with the cooling of US patent 5308043 by Floyd et al, additional to that provided by the injected gas and gas blown through a protective tube, provided by cooling fluid circulated through annular passages defined by the three outer tubes of the boom. This is made possible by the provision of an annular solid steel alloy tip which, at the exit end of the boom, joins the outermost and innermost of the three tubes around the circumference of the boom. The annular tip is cooled by injected gas and also by refrigerant fluid flowing through an upper end face of the tip. The solid shape of the ring tip, and its manufacture from alloy steel, result in the tip having a good level of wear and burn resistance. The arrangement is such that a practical operational lifetime is possible to be achieved with the lance before it is necessary to replace the tip in order to safeguard against a risk of lance failure by enabling coolant to be discharged into the molten bath.
[0015] The present invention relates to an improved fluid-cooled top submerged injection lance for use in TSL operations. The lance of the present invention provides an alternative choice to the lance of US Patent 5308043 to Floyd et al, however, at least in the preferred forms, it may provide benefits over the lance of this patent. Invention Summary
[0016] The present invention provides operable top submersible injection lance for use in a top submerged punch injection, within a slag layer of a molten bath, in a pyrometallurgical process, where the lance has an outer shell of three substantially concentric lance tubes comprising an outermost tube, an innermost tube and an intermediate tube, the lance including at least one additional lance tube disposed substantially concentric within the housing, the housing further including an annular end wall in a lance output end joining a respective end of the outer and inner jib tubes of the housing to an output end of the lance and is spaced from an output end of the intermediate lance tube of the housing; where, at the location remote from the exit end, such as adjacent to an upper or exit end, the lance has a structure by which it can be suspended so as to remain vertically downward, and the housing is adapted in such a way that fluid refrigerant is able to be circulated through the casing, by flow between the intermediate lance tube and one of the inner and outer lance tubes to the outlet end and then back along the lance away from the outlet end, by the flow between the intermediate lance tube and the other of the inner and outer lance tubes, the spacing between the end wall and the output end of the intermediate tube provides a construction for the refrigerant flow operable in the direction to cause an increase in the velocity of the flow of refrigerant fluid between the end wall and the outlet end of the intermediate tube; wherein the at least one additional lance tube defines a central orifice and has an outlet end spaced from the outlet end of the outer casing, whereby a mixing chamber is defined by the outer casing between the outer ends of the outer casing at the at least one additional tube, and the at least one additional lance tube is spaced from the innermost lance tube of the housing, so as to define an annular passage between them, whereby combustible material passing through the orifice and oxygen-containing gas passing through along the annular passage they are able to form a combustible mixture in the mixing chamber and is adjacent to the outlet end of the lance for combustion of the mixture being injected into the slag layer.
[0017] The TSL spear of the invention necessarily features large dimensions. Also, at a location remote from the exit end, such as adjacent to a top or exit end, the boom features a structure by which it is capable of being suspended so as to remain vertically downward within a TSL reactor. The boom has a minimum length of about 7.5 meters, just like a small special purpose TSL reactor. The boom can be up to about 25 meters long, or even longer, for a large special-purpose TSL reactor. Most commonly, the spear ranges from about 10 to 20 meters in length. These dimensions refer to the total length of the boom to the exit end defined by the end wall of the casing. The at least one additional lance tube may extend to the outlet end and thus be of similar overall length as the lance to the outlet end defined by the end wall of the housing. The at least one additional boom tube may extend to the outlet end and thus be of similar overall length. However, the at least one additional boom tube can end at a short distance, within the exit end, for example, up to about 1000 mm. The lance typically has a large diameter, as established by an inner casing diameter of about 100 to 650 mm, preferably about 200 to 6500 mm, and an overall diameter of 150 to 700 mm, preferably about 250 to 550 mm .
[0018] The end wall is spaced from the outlet end of the intermediate boom tube of the housing. However, the spacing between this outlet end and the end wall is such as to provide a constriction of the flow of refrigerant which causes an increase in the velocity of the flow of refrigerant through and between the end wall and the outlet end of the intermediate boom tube. The arrangement may be such that the flow of coolant fluid through the end wall is in the form of a relatively thin film or stream, with the film or stream preferably operable to suppress turbulence in the coolant. In order to increase such flow, the end of the intermediate lance tube of the housing can be suitably shaped. Thus, in one arrangement, the end of the intermediate boom tube may define a peripheral bead that has a radially curved convex surface that faces toward the end wall. With such an account, the end wall can be of complementary concave shape. For example, in basilar cross sections, the bead may be bulbous or bull-snout shaped, or it may be teardrop-shaped, or similar rounded shape, while the end wall may have a concave hemi-toroidal shape. With such opposite convex and concave shapes, the constriction between the outlet end of the intermediate lance tube and the end wall is capable of being a substantial radial extension of the lance (i.e., in planes containing the longitudinal axis of the lance). This allows for an increased ratio of surface to surface contact between the refrigerant and each between the bill and the end wall, per unit of refrigerant mass flow, relative to the refrigerant flow along the lance to the constriction, and thus provides for increased thermal energy extraction from the output end of the boom.
[0019] In one arrangement, the bead at the outlet end of the intermediate boom tube is teardrop-shaped, or substantially circular, in cross-sections (ie, in planes containing the longitudinal axis of the boom). In such cases, the concave hemi-toroidal shape of the end wall, whereby the end wall is complementary in shape to that of the bead, may be substantially semicircular in cross sections in these planes. As a consequence, the bead and the end wall can be closely adjacent so as to provide a constriction in the refrigerant flow path that is capable of extending through an angle of about 180°, such as 90° to 180° , whereby the flow path of refrigerant fluid is changed from flow towards the outlet end of the lance to flow away from the outlet end. Inevitably the flow is changed by an angle of about 180° simply due to a reversal in direction. However, unlike an arrangement in which the intermediate lance tube does not provide a flow constriction, the provision of the constriction restricts flow to a relatively thin film or stream that sweeps arcuately from the outer surface of the innermost lance tube of the housing. to the inner surface of the outermost boom tube of the housing.
[0020] The constriction may continue from the bead between the outer surface of the intermediate boom tube and the inner surface of the outermost boom tube. The constriction can extend for at least the axial length of the replaceable boom tip assembly, and results in the intermediate boom tube being of increased thickness by such axial length relative to the thickness of the innermost and outermost boom tubes. In such a case, constriction between the intermediate and outermost lance tubes may be circumferentially continuous, or it may be discontinuous. In the latter case, the outer surface of the intermediate boom tube may define ribs extending from the outlet end. The ribs may rest against the inner surface of the outermost boom tube, with the possibility of restricted flow occurring between successive ribs. Alternatively, the ribs may be spaced slightly apart from the inner surface of the outermost boom tube, with the possibility of restricted flow occurring between the ribs and the outermost boom tube, and the possibility of unrestricted or less restricted flow occurring between successive ribs. The ribs may extend parallel to the boom axis or helically around this axis.
[0021] The shaping of the output end of the intermediate lance tube, so as to provide an adequate constriction in the flow of refrigerant fluid, may be less pronounced in such a way that it results from the provision of a bead. For at least the axial length of the replaceable boom tip assembly, the intermediate boom tube can be of increased thickness relative to the inner and outer boom tubes, such as rounding the end of the intermediate boom tube at the output end. , around the outer surface of the thickened length. The constriction may extend through the edge of the intermediate boom tube to the outer surface of the thickened length. This outer surface may be circumferentially continuous or circumferentially discontinuous such as by providing ribs parallel to the axis of the lance or extending helically around this axis, as detailed above. In this way, the constriction is able to extend through an angle of at least 90°, with the curvature of the end wall able to assist in that this angle is greater than 90°, such as up to about 120°.
[0022] In a second aspect, the lance of the present invention presents a protection through which the lance extends. The shield features three substantially concentric shield tubes of which an inner shield tube has an inside diameter that is larger than the outermost boom tube of the TSL boom. At one outlet end of the shield, there is an annular end wall which joins the respective exit end of the outermost and innermost protective tubes and is spaced from the outlet end of the intermediate protective tubes. The arrangement is such that refrigerant is able to be circulated through the shield, such as along the shield to the outflow end by flow between the inner shield tubes and the intermediate shield tubes and then back along the shield , away from the outlet end, by flow between the intermediate and outermost protective tubes, or the reversal of this flow arrangement. The end wall, and an adjacent smaller portion of the length of each of these three shield tubes, may comprise a replaceable shield. In this way, a burn or wear tip shield assembly can be cut from the greater part of the length of each of the three shield tubes to enable a new or repaired tip shield assembly to be welded in place.
[0023] The end wall is spaced from the outlet end of the protective intermediate tube. However, the spacing between this outlet end and the end wall is such as to provide a constriction to the flow of refrigerant which causes an increase in the velocity of refrigerant fluid flow through and between the end wall and the outlet end of the tube. protection intermediary. The arrangement may be such that the flow of coolant fluid through the end wall is in the form of a relatively thin film or stream, with the film or stream preferably operable to suppress turbulence in the coolant. In order to increase such flow, the end of the protective intermediate tube can be properly shaped. In this way, in an arrangement, the end of the protective intermediate tube can define a bead that has a radially curved convex surface that faces towards the end wall. With such an account, the end wall can be of a complementary concave shape. For example, the bead may be teardrop-shaped, while the end wall may have a concave hemi-toroidal shape. With such opposite convex and concave shapes, the constriction between the outlet end of the protective intermediate tube and the end wall is capable of being a substantial radial extension of the shield (ie, in planes containing the longitudinal axis of the shield). This allows for an increased proportion of surface to surface contact between the refrigerant and each between the bill and the end wall, per unit of mass flow of the refrigerant, relative to the refrigerant along the protection to constriction , and thus provides increased thermal energy extraction from the output end of the protection.
[0024] In one arrangement, the bead at the outlet end of the intermediate shield tube is teardrop-shaped, or substantially circular, in cross sections (ie, in planes containing the longitudinal axis of the shield). In such cases, the concave hemi-toroidal shape of the end wall, whereby the end wall is complementary in shape to that of the bead, may be substantially semicircular in cross sections in these planes. As a result, the bead and the end wall can be closely adjacent so as to provide a constriction in the refrigerant flow path that can extend through an angle of up to about 180°, such as from 90° to 180', whereby the flow path of refrigerant fluid is changed from flow towards the outlet end of the shield to flow away from the outlet end. Unlike an arrangement in which the protective intermediate tube does not provide a flow constriction, the provision of the constriction restricts flow to a relatively thin film or stream that sweeps in an arcuate fashion from the outer surface of the innermost protective tube to the inner surface of the outermost protective tube.
[0025] In parallel with the boom of the present invention, the constriction can continue from the bead, between the outer surface of the intermediate protection tube and the inner surface of the outermost protection tube. The constriction may extend for at least the axial length of the replaceable end shield assembly, and result in the intermediate shield tube being of increased thickness by such axial length relative to the thickness of the innermost and outermost shield tubes. In such a case the constriction between the intermediate and outermost protective tubes can be circumferentially continuous, or it can be discontinuous. In the latter case, the outer surface of the protective intermediate tube may define ribs that extend away from the outlet end. The ribs may rest against the inner surface of the outermost protective tube, with the possibility of restricted flow occurring between successive ribs. Alternatively, the ribs may be slightly spaced from the inner surface of the outermost protective tube, with the possibility of restricted flow occurring between the ribs and the outermost protective tube, and the possibility of unrestricted or less restricted flow occurring between successive ribs . The ribs can extend parallel to the shield axis or helically around this axis.
[0026] The shaping of the outlet end of the protective intermediate tube, to provide an adequate constriction in the flow of refrigerant fluid, may be less pronounced as a result of the provision of a bead. For at least the axial length of the replaceable outermost tip protection tube assembly, the intermediate protection tube can be of increased thickness relative to the innermost and outermost protection tubes, as detailed above. The shaping may comprise a rounding of the end of the protective intermediate tube at the exit end, around the outer surface of the thickened length. The constriction may extend through the edge of the protective intermediate tube to the outer surface of the thickened length. This outer surface may be circumferentially continuous or circumferentially discontinuous such as by providing ribs parallel to the shield axis or extending helically around this axis, as detailed above. In this way, the constriction can extend over an angle of at least 90°, with the curvature of the end wall being able to assist in the fact that this angle is greater than 90°, such as up to about 120°.
[0027] In a third aspect, the present invention provides a boom according to the first aspect, in combination with a guard according to the second aspect, with the boom and guard being in an assembly in which the boom extends through the shield so as to define an annular passage between the outermost of the three boom tubes of the boom housing and the innermost shield tube, with the shield exit disposed intermediate the boom ends and opening towards the boom exit end .
[0028] A nose assembly in accordance with the present invention features concentric inner and outer sleeve members that, at one end of the nose assembly, are joined by the annular end wall. The nose assembly also features an intermediate sleeve member comprising a baffle which is located between the inner and outer sleeve members adjacent to the end wall. The baffle has at least one surface portion which cooperates with at least portion of an opposing surface of the at least one end wall and the inner and outer sleeve members to control the velocity of flow of refrigerant fluid between them to obtain extraction of thermal energy from the assembly.
[0029] The inner and outer sleeve members and the end wall by which they are joined may be integrally formed to comprise a single component of the nose assembly. For this purpose, they can be formed from a single piece of a suitable metal, such as a billet. Nose mounting is required to facilitate cooling, and the inner and outer sleeve members and the end wall thereof are preferably of a suitable material. In many cases, high thermal conductivity materials are suitable, for example copper or a copper alloy.
[0030] The deflector can also be of a material of high thermal conductivity, such as copper or a copper alloy. However, the thermal conductivity of the deflector is less important since, in use, it is contacted by the fluid refrigerant substantially over its entire surface area. The baffle temperature, in this way, will not rise above that of the coolant fluid. In this way, the material from which the deflector is made can be chosen for other reasons, such as cost, strength and ease of fabrication. The deflector can, for example, be made of a suitable steel, such as stainless steel. The baffle can be formed from a suitable piece of material, or it can be molded and, if necessary, surface-finished at least in the areas where its surface must cooperate to control the velocity of the flow of coolant.
[0031] In tip mounting, the deflector is held in the required position, in relation to the inner and outer sleeve members and the end wall, by being connected in relation to these members and the wall. For this purpose, the deflector can be attached to the end wall, one of the inner and outer sleeve members, or an annular extension of the sleeve members. As far as practice is concerned, it is more convenient to provide attachment to a glove member, or an extension of a glove member. However, in each case, the attachment preferably is such as to allow fluid to flow between the deflector and the member, extension or wall to which it is attached. For this purpose, the fixation is provided in a plurality of conveniently the fixation is through a fin, block or locking device at each location where it is fixed, such as by welding, to the deflector and to the member, extension or wall to which the baffle is fixed. However, in an alternative arrangement, with the nose assembly connected as part of a boom, the deflector can be longitudinally adjustable to allow for variation in the level at which the constriction is able to reduce the velocity of the coolant flow. Such adjustment can, for example, be made possible by the fact that the intermediate boom tube, to which the deflector is connected, is longitudinally adjustable in relation to the innermost and outermost boom tubes.
[0032] In a suitable arrangement, the deflector is fixed such that its outer and end peripheral surfaces are adjacent to the opposite inner peripheral surface of the outer sleeve member and the inner surface of the end wall, respectively. Additionally, with the baffle thus attached, part of its inner peripheral surface adjacent to the opposite outer peripheral surface portion of the inner sleeve member. The respective opposite surfaces can be evenly separated. The separation preferably is less than the separation between part of the inner peripheral surface of the deflector which is spaced apart from the end surface and the outer peripheral surface of the inner sleeve member. The arrangement is such that the refrigerant fluid is able to flow through the end assembly, passing between the deflector and the inner sleeve member towards the end wall, through the end wall and then between the spaced end surface baffle. and the outer sleeve member away from the end wall. With such flow, the velocity of flow of refrigerant fluid passing between adjacent opposing surfaces increases relative to the flow through a wider spacing between the deflector and the inner sleeve member. However, it should be noted that the flow of refrigerant fluid may be in the opposite direction as indicated, with the arrangement between the deflector and the inner and outer sleeve members also changed correspondingly.
[0033] The outer peripheral surface of the deflector may be of substantially uniform circular cross-section where it is adjacent to the opposite inner surface of the outer sleeve member. Likewise, there can be a substantially uniform passage of annular cross-section between these adjacent surfaces, designed to obtain adequate flow and velocity in order to promote heat transfer that ensures that the surface temperature of the tip material remains below the temperature. in which damage occurs. For example, the separation between these surfaces can be from about 1 to 25 mm and more precisely from 1 to 10 mm, and this will vary according to the fluid used and the required heat removal rate. However, in alternative arrangements, the external surface of the deflector may be other than a substantially circular cross-section.
[0034] In a first alternative arrangement, the outer surface of the deflector can be "girded" such that the spacing between the opposing surfaces increases in a direction away from the end surface of the deflector. In additional alternatives, the outer surface of the deflector may feature a single- or multiple-start helical rib or groove formation that acts to generate a helical flow of coolant fluid. In another alternative, the outer surface of the deflector may have alternating ribs and grooves that extend in a direction away from the end surface of the deflector.
[0035] The nose assembly can be provided only on the output end of a lance. Alternatively, with a shielded boom, a nose mount can define the discharge end of either the boom or its shield or both.
[0036] Both the boom and shield are elongated in shape, with the boom frame and shield being of similar construction. The shield, in fact, has a larger diameter, although it also has a shorter length than the boom housing. However, both the shield and the boom housing feature three concentric tubes, comprising outer and inner tubes and an intermediate tube. Also, both the shield and the housing may feature a tip mounting provided at its discharge end. For ease of further description, the concentric tubes of both the shield and the boom housing are referred to by the term "housing".
[0037] Where a nose assembly defines the discharge end of a housing (of a shield or boom), the inner and outer tubes of the housing are joined in end-to-end relationship with the inner and outer sleeve members, respectively, of the high end mounting. Also, the intermediate tube of the housing is coupled to the nose assembly deflector.
[0038] As indicated above, the inner and outer sleeve members and the end wall of the tip assembly may be of a material of high thermal conductivity, such as copper or a copper alloy. However, the tubes in a shell need not have such high thermal conductivity. In this way they can be made from a material chosen to meet other criteria, such as cost and/or strength. In a convenient arrangement, the inner and intermediate tubes are stainless steel, such as 316L, with the outer tube of carbon steel. With the outer tube, exposure to high temperatures and process gases rather than refrigerant such as water is more likely to be a determinant of its effective service life, while corrosion resistance by the refrigerant is the relevant factor. for the inner and intermediate tubes.
[0039] The inner and outer tubes are most preferably joined with the inner and outer sleeve members of the tip assembly by welding. Each tube can be welded directly to the respective sleeve member. However, for at least one tube and the respective sleeve member, but preferably for each tube and its sleeve member, each tube and sleeve member can be welded to an extension tube provided between them. At least, for example, where a solder is provided between a copper or copper alloy member and a steel member, a consumable aluminum bronze material is preferably used in the solder. The way in which the middle tube of the housing and the nose assembly baffle cooperate can be similar.
[0040] With both the lance and the protection of the present invention, the refrigerant mass flow rate may be lower than would be required without the constriction. In this way, lower output pumps are able to be used for a given refrigerant fluid. A suitable mass flow rate will vary with the chosen coolant. The refrigerant mass flow rate for a given lance and a given refrigerant is adjusted by the refrigerant capacity required for a given pyrometallurgical process. In this way, the mass flow rate can vary substantially. In a preferred form of the invention, the flow of refrigerant fluid is linked to the outlet temperature of the refrigerant fluid. The lance, for this reason, can be provided with a sensor to monitor this temperature. The arrangement is preferably such that the energy used to circulate the refrigerant fluid is minimized, based on the demand for heat removal at any given time.
[0041] With the use of water as the coolant, the mass flow rate can be in the range of 500 to 2000 1/min for the boom and a similar flow for the shield, depending on both the fluid used and the application. Again, with water as the coolant, the constriction is preferably such that it results in a fluid flow rate through the constriction that is higher than the flow rate upstream of the constriction by a factor of about 6 a. Again, for water like refrigerant, constriction to the shield preferably results in an increase in flow rate of the same order as to the boom. Detailed Description of the Invention
[0042] In order that the invention may be more easily understood, reference is now made to the attached drawings, in which:
[0043] Figure 1 - is a schematic representation of a shape of a lance according to the present invention;
[0044] Figure 2 - is a sectional view of the underside of a protected lance assembly according to the present invention; and
[0045] Figures 3 to 7 - show perspective views of respective alternative shapes of alternative shapes for a component of the protected lance assembly of Figure 2.
[0046] Figure 1 schematically illustrates a TSL lance (L) according to an embodiment of the present invention. The lance (L) has four concentric tubes (Pl) to (P4) of which the tubes (Pl) to (P3) form a main part of a housing (S) which also includes an annular end wall (W). In the illustrated arrangement, the lance (L) allows submerged top injection into the slag layer of a molten bath, for a required pyrometallurgical process, by injecting fuel through the tube orifice (P4) and injecting air and/or oxygen through the annular passage (A) between tubes (P3) and (P4). As shown, the tube (P4) ends above the lower outlet end (E) of the lance (L) in order to provide a mixing chamber (M) in which fuel and air and/or oxygen are able to mix. for fuel combustion. The fuel to oxygen ratio is controlled in order to generate the required oxidizing, reducing or neutral conditions in the slag. Any fuel that has not been consumed is injected into the slag to form part of the reducing requirements when reducing conditions are required.
[0047] The end wall (W) of the housing (S) joins the ends of the tubes (Pl) and (P3) around the entire circumference of the tubes (Pl) and (P3) at the outlet end (E) of the spear (L) . Also, the lower end of the tube (P2) is spaced from the end wall (W). As shown, the refrigerant fluid is capable of being circulated through the housing (S). In Figure 1, refrigerant fluid is shown as being supplied downward between tubes (P2) and (P3) to flow around the lower end of tube (P2) and return upward between tubes (P1) and (P2). However, the reverse of this flux can be used if a lower level of thermal energy extraction from (Pl), in particular, is appropriate.
[0048] Except at the lower end (E) of the boom (L), the frame (S) has horizontal cross sections substantially constant in normal in use in the orientation shown. However, at the end (E), the constriction (C) is provided by the shape of the lower end of the tube (P2) and its cooperation with the tube (P3) and the end wall (W) . As shown, the lower end of the tube (P2) has an enlarged bead (B) substantially shaped like a torus so as to be tear-shaped, or substantially circular, in radial cross sections (i.e., in planes containing the longitudinal axis X of the boom (L)). Also, the annular end wall surface (W) of the housing (S) counted for the bead (B) is of complementary hemi-toroidal concave shape and the bead (B) is positioned such that its lower convex surface is adjacent , but not in contact, with the concave surface of the end wall (W) . The arrangement is such that the flow velocity of the refrigerant fluid is substantially constant in downward flow between the tubes (P2) and (P3) until reaching the upper convex surface of the bead (B), after which the flow velocity progressively increases. The increase occurs in the flow at an angle of about 90°, around the top of the bead (B), to a maximum around the bottom half of the bead in the flow between the bead (B) and the end wall (W ) . The maximum flow velocity is maintained in the refrigerant flow at an angle of about 180°, around the lower half of the bead (B) . Thereafter the flow velocity is reduced as the refrigerant fluid passes over the upper half of the bead (B) until it drops to a minimum in the upward flow between the tubes (P1) and (P2). The constriction (C) is mainly defined by the spacing between the lower half of the bead (B) and the end wall (W), however the constriction (C) starts with 90° of tube flow (P3) around the top surface of the account (B).
[0049] Increasing the speed of the refrigerant flow in constriction (C) increases the surface-to-surface contact ratio between the refrigerant and the bill (B) and the end wall (W) per unit rate of refrigerant mass flow. As a consequence, the extraction of thermal energy from the output end (E) of the boom (L) is increased. This is particularly beneficial as burnout and wear of the submerged lower end of the boom (L) tends to be higher and determines the time interval between outages for boom repair.
[0050] The sectional view of Figure 2 shows a guarded boom assembly (10) in an in-use orientation. As shown, the assembly (10) includes a plurality of concentric tubular members. These consist of members of an annular guard (12), and members of a lance (14) which extends through the guard (12) so as to define an annular passage (16) therebetween. Figure 2 shows only the bottom of the assembly (10). However, as is evident in Figure 2, the boom (14) is longer than the shield (12) and protrudes beyond the shield (12) at the lower end of the assembly (10). The extent to which the boom (14) protrudes beyond the shield (12) is not evident in Figure 2, due to the fact that a section of the boom (14) below the shield (12) is omitted in the in-use orientation shown.
[0051] The tubular members of the boom (14) include an innermost tube (18), and an outer casing (20) around the tube (18) ending in a ring tip assembly (22) at the lower end of the casing (20) . Tube (18) is shorter than lance (14) so that it extends and terminates in the ring tip assembly (22). The tube (18) defines a central passage (24). Also an annular passage (26) is defined between the tube (18) and the housing (20). The arrangement is such that carbonaceous fuel and oxygen-containing gas can be passed under pressure along the respective passages (24) and (26), and mixed in a mixing chamber (27) at the end of the tube (18) within the assembly. (22) for combustion of the fuel and generating a combustion region extending from the chamber (27) and beyond the assembly (22).
[0052] The housing (20) of the boom (14) is formed by an inner tube (28), an outer tube (30) and an intermediate tube (32), and an annular end wall (40) joining the ends of tubes (28) and (30) around the entire circumference of the nose assembly (22). An annular passage (42) is defined between the inner tube (28) and the intermediate tube (32) of the housing (20). Also, an annular passage (44) is defined between the intermediate tube (32) and the outer tube (30) of the housing (20). The passages (42) and (44) are in fluid communication due to the spacing between the end wall (40) and the adjacent end of the intermediate tube (32). In this way, the refrigerant fluid can be passed along the passage (42) through the housing (20) and its assembly (22) and then back along the passage (44).
[0053] The intermediate tube (32) of the nose assembly (22) has a cylindrical outer surface that is adjacent to the outer tube (30). Thus, the passage (44) is relatively narrow in its radial extent, at least within the assembly (22), but preferably also along the entire length of the housing (20). Although it varies with the diameter of the lance, the spacing between the intermediate and outer tubes (32) and (30) within the assembly (22), but preferably also along the entire length of the housing (20), can be about 5 mm to 10 mm, such as about 8 mm, and slightly greater than a short distance above the bottom wall to the lower end of the intermediate tube (32). In contrast, the passage (42) is relatively wide, such as between 15 and 30 mm between the inner tube and the intermediate (28) and (32) of the housing (20). However, the inner peripheral surface of the intermediate tube (32) within the nose assembly (22) is frustro-conical tapered in order to increase in thickness and decrease in internal diameter in a direction that extends to the end wall ( 40). As a result, the radial extension of the passage (42) is progressively reduced within the assembly (22). The reduction preferably is on a radial extent of passage (42) which is similar to that of passage (44). Also, the spacing between the end wall (40) and the adjacent end of the tube (38) is similar to the radial extent of the passage (44). In this way, the refrigerant supplied under pressure along the passage (42) progressively increases its velocity in its flow between the tubes (28) and (32), and to flow at a high velocity through the end wall (40) and along the passage (44). Likewise, the refrigerant is capable of achieving a high level of thermal energy extraction from the external surfaces of the boom (14), in its housing (20) and tip assembly (22) and thus protect against the effect of the boom. high temperatures to which the boom is exposed in use.
[0054] The end of the lance (14) that defines the tip assembly (22) is in the region most exposed to wear and burn. The arrangement is such that the lower ends of the tubes (28, 30, 32) can be cut and a replacement tip assembly (22) can be installed, such as by welding. The length of cut and replacement can vary, as can the depth to which the lance outlet (14) is submerged.
[0055] The intermediate tube (32) of the lance (14) can be maintained in a fixed relationship with the tubes (28) and (30), and with the end wall (40). This can be achieved by any convenient arrangement. A fixed relationship retains the flow path for the cooling fluid along passage (42) and then back along passage (44) such that a required rate of thermal energy extraction by the refrigerant fluid is possible to be maintained, if necessary by varying the rate of supply of refrigerant to the passage (42). Establishment and maintenance of the fixed relationship can be ensured by a few small undulations or other adequately spaced apart shape provided at locations around the upper surface of the wall (40) or the end face of the tube (32). Such spacers can also help to prevent the unjustified development of vibrations in the boom (14) .
[0056] With reference now to the protection (12), it should be noted that apart from the respective larger diameters of the tubes from which it is formed and the length of the protection (12), its construction is the same as the housing (20) and its assembly of tip (22). Therefore, the protection components (12) have the same numerical reference used for the frame (20) and its assembly (22), plus 100. In this way, an additional description of the protection (12) is not necessary, in addition to note that it has a housing (120) and a nose assembly (122).
[0057] With the use of the lance assembly (10), the outer surface of the lance (14) up to the shield (12) is provided with a solidified slag coating, as described above, although such a coating may also be formed on the external extension of the outer surface of the guard (12). After which, the lower end of the lance (14) is submerged to a required depth in a bath of slag from which the casing is formed, but with the lower extension of the shield (12) spaced above the bath.
[0058] The pyrometallurgical reactions conducted in a reactor containing the slag bath usually result in combustible gases, mainly carbon monoxide and hydrogen, released from the slag into the reactor space above the bath. If required, these gases can be subjected to post-combustion from which it is possible to recover the thermal energy by the slag. For this, oxygen-containing gas can be supplied to the reactor space from the lower end of the passage (16).
[0059] The main cooling of the shield (12) is by refrigerant circulated along the passage (142) and back along the passage (144), although some cooling is achieved by gas injected through the passage (16), above of the surface of the slag bath. With the lance (14), it is possible to achieve substantial cooling by the high-speed, subsonic gas injected through passage (26), although substantial additional cooling is achieved by the refrigerant fluid circulated along passage (42) and from back along the passage (44). The balance between the two cooling actions for the lance (14) can be varied by changing the mass flow rate at which the refrigerant fluid is circulated. Again, an increased flow rate of the refrigerant, relative to the flow rate in the passage (42), caused by a constriction provided by the narrowing of the passage (44) (at least within the assembly (22)), increases the extraction of thermal energy from the assembly (22) and the lower extension of the housing (20). As a consequence, the operating life of the boom is increased by a resulting reduction in wear and burn, particularly in the assembly (22).
[0060] The arrangement with lance (L) of Figure 1 and lance (10) of Figure 2 is such that the refrigerant fluid is able to be circulated through the lance housing, such as along the housing to the outlet end by flow between the innermost tube and the intermediate tube of the carcass lance and then back along the lance, away from the outlet end, by flow between the outermost tube and the intermediate tube of the carcass lance, or in the reverse of this flow arrangement. The respective end wall (W, 40) and an adjacent smaller part of the length of each of the three lance tubes of the housing (S, 20) comprises a replaceable lance tip assembly, whereby a lance burnt tip assembly or worn can be cut from a greater portion of the length of each of the three boom tubes in order to enable a new or repaired boom tip assembly to be welded in place. The end wall (W, 40) of the housing (S, 20) is at and defines the exit end of the lance. Also, the at least one additional lance tube (P4, 18) defines a central orifice (24), and the at least one additional lance tube (P4, 18) is spaced from the innermost lance tube of the housing (S, 20) so as to define an annular passage (A, 42) therebetween, whereby materials passing along the orifice and passage can be mixed adjacent to the outlet end of the lance being injected into the slag layer.
[0061] The TSL lance (L, 10) is necessarily large. Also, at a location remote from the outlet end, such as adjacent to a top or inlet end, the lance has a structure (not shown) by which it can be suspended so that it hangs vertically down into the TSL reactor. The boom (L, 10) has a minimum length of about 7.5 meters, but can be up to about 20 meters long or even longer for a large special purpose TSL reactor. Most commonly, the spear ranges from about 10 to 15 meters in length. These dimensions refer to the total length of the lance through the exit end defined by the end wall of the housing. The at least one additional boom tube (P4, 18) may extend to the exit end and thus be of similar overall length, however, as shown, may terminate at a short distance, internally from the end. output, such as up to about 1000 mm. The lance typically has a large diameter, as established by an inner diameter for the carcass of about 100 to 650 mm, preferably about 200 to 500 mm, and an overall diameter of 150 to 700 mm, preferably about 250 to 550 mm.
[0062] Each of Figures 3 to 7 schematically illustrates a respective alternative shape for the deflector comprising the tube (38) of the tip assembly (22) of the lance (14) and/or the tube (138) of the protection (12) , although the deflector used in the boom (14) does not need to be of the same type as the one used in the protection (12). The tube (60) of Figure 3 differs from the tube (38) or tube (138) of Figure 2. Each of the tubes (38) and (138) has a cylindrical outer surface that is at substantially constant spacing from the respective outer tube. (36, 136), such that a substantially constant flow rate of refrigerant fluid is maintained in the passage (44). In contrast, the outer surface of the tube (60) is profiled in such a way that, by flowing upwards in the passage (44), a progressive reduction in fluid flow is made possible after the reduction in flow velocity resulting from the larger outer diameter in the lower end of tube (60) . Provided the reduction does not proceed below a level that provides the required removal of thermal energy from the outer tube (36) and/or (136), a good removal of energy from the lower end of the nose assembly (22) and/or (122) can be obtained.
[0063] The respective tubes (62) and (64) of Figures 4 and 5 also differ in the external surface of the tube arrangement (38, 138). Although the tubes (62) and (64) have the respective shapes, they achieve a similar result. In the case of tube (62), an elevated spiral, bead or rib (63) extends in a helical formation around the cylindrical outer surface and may be continuous or intermittent, such as when a fan arrangement is employed. In contrast, the outer surface of the tube (64) has a helical groove (65) formed therein. In each case, the refrigerant fluid is caused to flow helically in the passage (44) and/or (144), at least within the tip assembly (22) and/or (122). The bead or rib (63) around the tube (62) is shown to be of round cross section and may be provided by soldering a wire to the tube (62). However, the bead or rib (63) may have other cross-sectional shapes, although the groove (65) of the tube (64) may have a cross-sectional shape other than the rectangular shape shown.
[0064] The tube (66) of Figure 6 is similar in overall shape to the tubes (38) and (138). However, it differs in that it presents a circumferential set of holes (67) adjacent to its lower end. Refrigerant fluid is able to pass through the orifices (67), in addition to the flow passing around the lower end of the tube (66). In this way, thermal energy can be more effectively removed from the lower end of a lance (14) and/or (114) provided with a tube (66).
[0065] The tube (68) of Figure 7 is provided on its outer surface with a set of longitudinal grooves or grooves (69), resulting in longitudinal ribs (70). In this case, the extent of the refrigerant flow velocity increase is less than if the grooves (69) are not formed. That is, the flow velocity is dependent on the mean radius of the outer surface of the tube (68).
[0066] The respective tubes (38) and (138) of the arrangement of Figure 2, and the respective tubes (60, 62, 64, 66, 68) of Figures 3 to 7, can be produced in any suitable way. For example, tubes can be machined or forged from a piece of a suitable metal, or by molding a suitable metal into substantially final shape.
[0067] The refrigerant fluid can be any suitable liquid or gas. A liquid cooling agent is preferred, and liquid refrigerants that can be used include water, ionic liquids and suitable polymeric materials, including organosilicon compounds such as siloxanes. Examples of specific silicone polymers that can be used include heat transfer fluids available under the brand name SYLTHERM, owned by Dow Corning Corporation.
[0068] Finally, it should be understood that various changes, modifications and/or additions may be made to the constructions and arrangements of the parts previously described without departing from the spirit or scope of the invention.

权利要求:
Claims (17)
[0001]
1. Top submersible injection lance (14) for use in lance injection (14) submerged within a layer of slag from a molten bath in a pyrometallurgical process, said lance (14) having an outer shell (20) of three concentric lance tubes comprising an outermost tube (30), an innermost tube (28) and an intermediate tube (32), the lance (14) including at least one additional concentrically disposed lance tube (14) inside the housing (20), and further including an annular end wall (40) at an exit end of the lance (14) which joins a respective end of the outermost (30) and innermost (28) lance tube (28) of the housing (20) at an output end (40) of the lance (14) and is spaced from an output end (40) of the intermediate lance tube (32) of the housing (20), where, at a location away from the end of outlet (40), adjacent to an upper or outlet end, the lance (14) has a structure that makes it possible to be hung down vertically, and the housing (20) being adapted so that refrigerant fluid is circulated through the housing (20) by flow between the intermediate lance tube (32) and one of the innermost lance tubes (28 ) and outermost (30) to the outlet end (40) and then back along the lance, away from the outlet end (40), by flow between the intermediate lance (14) tube (32) and the another of the innermost (28) and outermost (30) lance tubes (14), the spacing between the end wall and the outlet end (40) of the intermediate tube (32) provides a constriction (C) for the flow of refrigerant operable to cause an increase in the velocity of the flow of refrigerant between the end wall and the outlet end (40) of the intermediate tube (32); where the at least one additional lance tube (14) defines a central hole and has an outlet end spaced from the outlet end (40) of the outer shell (20), characterized in that a mixing chamber (27) is defined. ) by the outer casing (20) between the outlet ends of the outer casing (20) and the at least one additional tube, and the at least one additional lance tube (14) is spaced from the innermost lance tube (14) ( 28) of the housing (20) to define an annular passage between them, whereby the combustible material passing through the orifice and oxygen-containing gas passing along the annular passage are capable of forming a combustible mixture in the mixing chamber ( 27) and adjacent to the outlet end (40) of the lance (14) for combustion of the mixture within the slag layer.
[0002]
2. Top submersible injection lance according to claim 1, characterized in that the constriction (C) is operable to provide a flow of refrigerant fluid through the end wall in the form of a thin film or stream in relation to the flow before and after constriction (C).
[0003]
3. Top submersible injection lance according to claim 1 or 2, characterized in that at the end of the intermediate lance tube (14) (32) a bead (B) is defined which has a radially convex curved surface facing the direction of the end wall, the bead (B) being teardrop-shaped or round-shaped, with the end of the complementary concave shape.
[0004]
4. Top submersible injection lance according to claim 3, characterized in that the constriction (C) between the outlet end of the intermediate tube (32) and the end wall extends radially from the lance (14) in planes containing a lance shaft (14), such as with the bead (B) and the end wall providing the constriction (C) through an angle of up to 180°.
[0005]
5. Top submersible injection lance according to claim 3 or claim 4, characterized in that the constriction (C) continues from the bead (B), between the outer surface of the intermediate lance tube (14) (32) and an inner surface of the outermost tube (30) for at least part of the length of the lance (14) along which the intermediate tube (32) has increased wall thickness.
[0006]
6. Top submersible injection lance according to claim 1 or claim 2, characterized in that the constriction (C) is defined at least in part from a rounding of the end of the intermediate tube (32) and between the outer surface of the intermediate tube (32) and the inner surface of the outermost tube (30), for at least part of the length of the lance (14) along which the intermediate tube (32) has increased wall thickness with constriction (C) extending through an angle of at least 90o.
[0007]
7. Top submersible injection lance according to any one of claims 1 to 6, characterized in that it includes an annular protection (12) arranged concentrically around an upper extension of the housing (20) spaced from the outlet end (40).
[0008]
8. Top submersible injection lance according to claim 7, characterized in that the protection (12) has an outer casing (120) of three concentric protection tubes comprising an outermost tube (130), an innermost tube ( 128) and an intermediate tube (132), and additionally including an annular end wall (140) at an outlet end of the shield (12) joining a respective end of the outermost and innermost shield tubes of the housing (120) and is spaced from an outlet end of the intermediate tube (132) protecting the casing (120), whereby refrigerant fluid is circulated through the casing (120) along the casing (120) to the outlet end by flow between the innermost protection tube and the intermediate protection tube (132) and then back along the protection (12), away from the outlet end, by flow between the intermediate protection tube (132) and the outermost one ( 130), or the reverse of this flu xed, and where the spacing between the end wall and the outlet end of the intermediate tube (132) provides a constriction (C) of operable refrigerant flow to cause an increase in the velocity of refrigerant flow between the end wall and the output end of the intermediate tube (132).
[0009]
9. Top submersible injection according to claim 8, characterized in that the constriction (C) of the shield (12) is operable to provide a flow of refrigerant fluid through the end wall (140) of the shield (12) in the form of a thin film or current in relation to the flow before and after the constriction (C).
[0010]
10. Submersible top injection according to claim 8 or claim 9, characterized in that at the end of the intermediate boom tube (14) (132) a bead (B) is defined which has a radially curved convex surface facing in the direction of the end wall (140), such as in that the bead (B) is teardrop-shaped or of similar round shape, with the end of the complementary concave shape.
[0011]
11. Submersible top injection according to claim 10, characterized in that the constriction between the outlet end of the intermediate tube (132) and the end wall (140) is radially extending the lance (14) in planes containing a lance shaft (14), as with the bead and end wall providing the constriction through an angle of up to 180°.
[0012]
12. Top submersible injection according to claim 10 or claim 11, characterized in that the constriction continues from the bead, between the outer surface of the intermediate lance tube (14) (132) and an inner surface of the outermost tube (130) for at least part of the length of the lance (14) along which the intermediate tube (132) has increased wall thickness.
[0013]
13. Submersible top injection according to claim 8 or claim 9, characterized in that the constriction is defined at least in part from a rounding of the end of the intermediate tube (132) and between the outer surface of the intermediate tube (132 ) and the inner surface of the outermost tube (130), for at least part of the length of the lance (14) along which the intermediate tube (132) has increased wall thickness, with the constriction extending through an angle of hair. minus 90th.
[0014]
14. Top submersible injection lance according to any one of claims 1 to 7, characterized in that the constriction results in a refrigerant flow rate that is greater than the flow rate upstream of the constriction (C) in a factor from 6 to 20.
[0015]
15. Top submersible injection lance according to any one of claims 1 to 7 and 15, characterized in that the lance (14) is 7.5 to 25 meters long.
[0016]
16. Top submersible injection lance according to any one of claims 1 to 7, 14 and 15, characterized in that the housing (20) of the lance (14) has an internal diameter of 100 mm to 650 mm, and a outside diameter from 150 mm to 700 mm.
[0017]
17. Top submersible injection lance according to any one of claims 1 to 7 and 14 to 16, characterized in that the additional lance tube ends inside the housing (20) within 1000 mm of the output end (40).

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引用文献:

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

GB876687A|1959-06-24|1961-09-06|Wellman Smith Owen Eng Co Ltd|An improved lance for blowing fluids|

US3223398A|1963-02-20|1965-12-14|Kaiser Ind Corp|Lance for use in a basic oxygen conversion process|

US3269829A|1963-09-24|1966-08-30|United States Steel Corp|Method and apparatus for introducing steam and oxygen into a bath of molten steel|

BE648779A|1963-10-23|1964-10-01|

FR84791E|1963-11-25|1965-04-16|Siderurgie Fse Inst Rech|Adjustable insufflation lance for fine particles in suspension|

GB1130845A|1966-04-13|1968-10-16|Noranda Mines Ltd|Method and apparatus for controlling the temperature of metal lances in molten baths|

US3411716A|1966-05-11|1968-11-19|United States Steel Corp|Oxygen lance for steelmaking furnaces|

US3488044A|1967-05-01|1970-01-06|Nat Steel Corp|Apparatus for refining metal|

US3876190A|1969-06-25|1975-04-08|Commw Ind Gases|Method and apparatus for feeding particulate materials to furnaces and the like|

US3730505A|1970-07-01|1973-05-01|Centro Speriment Metallurg|Double delivery lance for refining the steel in the converter processes|

FR2131674A5|1971-04-10|1972-11-10|Messer Griesheim Gmbh|

US3828850A|1973-07-12|1974-08-13|Black Sivalls & Bryson Inc|High temperature material introduction apparatus|

US3889933A|1974-02-28|1975-06-17|Int Nickel Canada|Metallurgical lance|

BE849582R|1976-01-07|1977-04-15|Rene Desaar|POCKET CAST IRON DESULFURATION LANCE|

US4023676A|1976-09-20|1977-05-17|Armco Steel Corporation|Lance structure and method for oxygen refining of molten metal|

GB1599366A|1977-05-09|1981-09-30|Commw Scient Ind Res Org|Submerged injection of gas into liquid pyro-metallurgical bath|

FR2432552B1|1978-08-03|1982-10-01|Siderurgie Fse Inst Rech|

US4326701A|1979-09-29|1982-04-27|Kaiser Steel Corporation|Lance apparatus|

FR2496699B1|1980-12-22|1985-06-21|Siderurgie Fse Inst Rech|BLOWING NOZZLE FOR OXIDIZING GAS, ESPECIALLY OXYGEN, FOR THE TREATMENT OF FUSED METALS|

IN178636B|1989-09-29|1997-05-24|Ausmelt Ltd|

AT154950T|1991-09-20|1997-07-15|Ausmelt Ltd|METHOD FOR PRODUCING IRON|

IN181041B|1991-09-20|1998-04-18|Ausmelt Ltd|

US5199867A|1991-09-30|1993-04-06|The Boc Group, Inc.|Fuel-burner apparatus and method for use in a furnace|

AU707438B2|1993-04-06|1999-07-08|Ausmelt Limited|Smelting of carbon-containing material|

US5431709A|1993-09-21|1995-07-11|Gas Research Institute|Accretion controlling tuyere|

US5615626A|1994-10-05|1997-04-01|Ausmelt Limited|Processing of municipal and other wastes|

US5788920A|1995-01-31|1998-08-04|Kawasaki Steel Corporation|Oxygen blowing lance capable of being used in an electric furnace|

US5680766A|1996-01-02|1997-10-28|General Electric Company|Dual fuel mixer for gas turbine combustor|

CN2331936Y|1998-03-19|1999-08-04|李勇敏|Multifunction spray gun for electric furnace steel making|

JP3541271B2|1999-03-09|2004-07-07|日本酸素株式会社|Cooling jacket structure of lance or burner|

JP2002048315A|2000-08-07|2002-02-15|Nippon Sanso Corp|Cooling jacket|

GB0209364D0|2002-04-24|2002-06-05|Boc Group Plc|Injection of particulate material into liquid|

RU2395772C2|2004-07-27|2010-07-27|Текнолоджикал Ресорсиз Пти Лимитед|Facility for injection of solid loose material into container|

WO2006105578A1|2004-10-18|2006-10-12|Technological Resources Pty Limited|Apparatus for injecting solid particulate material into a vessel|

JP2009139081A|2007-11-13|2009-06-25|Jfe Steel Corp|Burner lance for charging powdery and granular matter of smelting reduction furnace and manufacturing method of molten metal by smelting reduction|

AU2012276276B2|2011-06-30|2015-01-22|Outotec Oyj|Top submerged injecting lances|

PE20141641A1|2011-11-30|2014-11-18|Outotec Oyj|REFRIGERATED FLUID LANES FOR TOP SUBMERGED INJECTION|PE20141641A1|2011-11-30|2014-11-18|Outotec Oyj|REFRIGERATED FLUID LANES FOR TOP SUBMERGED INJECTION|

AU2013204818B2|2013-04-12|2015-02-19|Outotec Oyj|Molten bath temperature measurement for a top submerged lance injection installation|

WO2015056143A1|2013-10-16|2015-04-23|OutotecOy|Top submerged injection lance for enhanced submerged combustion|

WO2015056142A1|2013-10-16|2015-04-23|OutotecOy|Top submerged injection lance for enhanced heat transfer|

US9932940B2|2015-03-30|2018-04-03|Honeywell International Inc.|Gas turbine engine fuel cooled cooling air heat exchanger|

CN106931790B|2015-12-30|2019-09-27|江西瑞林稀贵金属科技有限公司|Top-blown spray gun|

US10830150B2|2016-01-28|2020-11-10|Rolls-Royce Corporation|Fuel heat exchanger with leak management|

US11118784B2|2016-01-28|2021-09-14|Rolls-Royce North American Technologies Inc.|Heat exchanger integrated with fuel nozzle|

CA2955613A1|2016-01-28|2017-07-28|Rolls-Royce North American Technologies, Inc.|Heat exchanger integrated with fuel nozzle|

WO2017195105A1|2016-05-10|2017-11-16|Tenova South AfricaLtd|Lance for use in a top submerged lance furnace|

US10113800B2|2016-10-04|2018-10-30|China Enfi Engineering Corporation|Lance|

US10260815B2|2016-12-19|2019-04-16|China Enfi Engineering Corporation|Lance and multi-fluid lance device equipped with the same|

US10775046B2|2017-10-18|2020-09-15|Rolls-Royce North American Technologies Inc.|Fuel injection assembly for gas turbine engine|

CN111926280B|2020-09-03|2021-09-14|昆明理工大学|High-entropy alloy coating of long-life spray gun for Isa smelting and preparation method thereof|

法律状态:
2018-12-04| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|

2019-11-05| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|

2020-08-18| B06A| Notification to applicant to reply to the report for non-patentability or inadequacy of the application [chapter 6.1 patent gazette]|

2021-03-09| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|

2021-05-18| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 26/11/2012, OBSERVADAS AS CONDICOES LEGAIS. |

优先权:

申请号 | 申请日 | 专利标题

AU2011904988|2011-11-30|

AU2011904988A|AU2011904988A0|2011-11-30|Fluid cooled lances for top submerged injection|

PCT/IB2012/056714|WO2013080110A1|2011-11-30|2012-11-26|Fluid cooled lances for top submerged injection|

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