Burner

Abstract: A burner 10 for burning a fuel in an oxidant has a first nozzle 56 for producing a jet of the fuel adapted to burn within the oxidant with the flame extending outwardly from the fuel nozzle 56 and such that the particles of fuel become increasingly more buoyant along the length of the flame. The nozzle 56 is mounted at the front of a body member 20 centrally located within a duct 14 for oxidant. The duct 14 and the body member 20 provide surfaces 22 and 24 that define a convergent/divergent upper (third) nozzle 30 and also provide surfaces 26 and 28 that define a convergent/divergent lower (second) nozzle 32. The lower nozzle 32 is located below the fuel nozzle 56 and creates a lower jet of the oxidant that produces a low-pressure field below the fuel jet for downwardly spreading the fuel into the oxidant. The upper nozzle 30 is located above the nozzle 56 and creates an upper jet of the oxidant able to support combustion of the particles of the fuel. The velocities of the upper and lower oxidant jets can be adjusted independently of their mass flow rates to adjust the flame shape from sharp (convection dominated) to lazy (radiation dominated) without changing the chemical composition of the flame. The adjustment is made by moving the body 20 relative to the end of the duct 14.

Description: The present invention relates to a fuel-burner apparatus and method wherein a fuel is burned in an oxidant to heat a furnace heat-load, such as glass, ferrous and non-ferrous melts. More particularly, the present invention relates to a fuel-burner apparatus and method involving globally-enhanced mixing of the oxidant and fuel. Furnaces used in heating thermal loads such as glass and metal melts typically incorporate one or more burners set within burner blocks along the sides of the furnace. The burner produces the required heat by burning a liquid fuel, such as No. 2 or No. 6 fuel oil or a gaseous fuel such as natural gas in an oxidant such as oxygen or oxygen-enriched air. The resultant flame extends over the melt and heat is transferred from the flame to the melt by radiation and conduction. Globa-enhancement burners are known from US-A-4 927 357 in which the mixing of the oxidant and the fuel occurs over a large area as opposed to a localised mixing of the oxidant and fuel. As a result, a broad flame is produced having a controlled heat release pattern which can be quite uniform throughout the flame. A non-axisymmetric oxidant nozzle is located below a fuel nozzle to produce a low-pressure field of the oxidant below the fuel nozzle. The low-pressure field enhances aspiration of the fuel into the oxidant. The oxidant and fuel jets produced by the oxidant and fuel nozzles fan out from the burner so that the mixing between the two occurs over a wide area. The resultant flame produced by combustion of the fuel within the oxidant has quite a uniform heat distribution with the virtual elimination of hot spots. In some operating regimes, a long flame is produced in which unburned particles of fuel become increasingly more buoyant along the length of the flame. The disadvantage of this is that unburned particles of fuel at the end of the flame rise to burn outside of the oxidant provided directly through the burner in a controlled manner. This is typically observed as the flame licking up at its end. As a result, part of the heat released by the flame is diverted from the heat-load to the top or crown of the furnace. Another disadvantage of many prior art burners, including global-enhancement burners, is that it is difficult to control the mode of heat transfer to the melt without changing the stoichiometry of the flame. In this regard, certain types of melts are highly reflective of radiant heat. In such case, it is known that more effective heat transfer can be obtained with a convective-type flame. One way to achieve this is to increase the velocity of the oxidant jet and thereby sharpen the flame pattern from a lazy flame pattern. A sharp flame results in a lower degree of radiant and a higher degree of convective heat transfer than a lazy flame. However, it is difficult to control the oxidant velocity independently of oxidant mass flow rate without a sophisticated flow-control system. As such, an increase in oxidant velocity is accompanied by a decrease in oxidant mass flow-rate. The decreased oxidant mass-flow rate changes the mole ratio of fuel to the oxidant to change in turn the rate at which heat is released by the flame and may result in unburned fuel in the exhaust system of the furnace. US-A-1 513 828 discloses an oxy-fuel burner having a central fuel nozzle and upper and lower oxidant nozzles. The upper and lower oxidant nozzles are shaped and positioned for creating a fairly sharp oxidant jet which intersects the fuel jet thereby to create a relatively flat fuel/oxidant mixture that can be combusted to form a flat flame suitable for creating a heating effect over a large surface area. As will be discussed, the present invention aims at providing a burner that more effectively aspirates the fuel into the oxidant to prevent the more buoyant particles of fuel from burning outside the oxidant. Additionally, the invention aims at providing a burner that permits the velocity of the oxidant to be controlled independently of its mass flow rate selectively to produce either sharp or lazy flame patterns without affecting the mole ratio of the fuel to oxidant whereby the heat release characteristics of the flame can be adjusted from radiation dominated to convection dominated independently of the mole ratio. According to the present invention there is provided a burner for burning fuel in an oxidant comprising: first nozzle means for producing a jet of the fuel adapted to burn within the oxidant with an outwardly extending flame such that particles of the fuel become increasingly more buoyant along the length of the flame; second nozzle means located below the first nozzle means for creating a lower jet of the oxidant; and third nozzle means located above the first and second nozzle means for creating an upper jet of the oxidant that supports combustion of the particles of the fuel; characterised in that, said second nozzle means is shaped and positioned for creating a lower jet of the oxidant that produces a low-pressure field below the fuel jet for downwardly aspirating the fuel into the oxidant. The invention also provides a method of burning fuel in an oxidant, comprising: producing a jet of the fuel which burns with an outwardly extending flame such that particles of the fuel become increasingly more buoyant along the length of the flame; creating a lower jet of oxidant below the fuel; and creating above both the fuel jet and the lower jet an upper jet of oxidant of a shape to burn the particles of the fuel; characterised by the step of directing the lower jet such as to create a low pressure field below the fuel jet for downwardly aspirating the fuel into the oxidant. In use of a burner according to the invention the low pressure of the upper oxidant jet as compared with the fuel jet causes fuel to enter the upper oxidant jet. However, oxidant aspiration into the fuel from the lower oxidant jet is much more effective than that provided by the upper oxidant jet and thus, predominates. The second and third nozzle means can be formed in an oxidant duct having an open front end from which the upper and lower oxidant jets are discharged and an inlet typically spaced behind the open front end of the oxidant duct to receive the oxidant under pressure. A body member for fuel is recessed or set back within the oxidant duct and located between the open front end and the inlet of the oxidant duct. The body member is typically centrally located. The body member and the oxidant duct can have two opposed, spaced sets of top and bottom surfaces, separated by the body member and shaped to define converging/diverging passages through the second and third nozzles through which the oxidant is adapted to be urged so as to create the upper and lower oxidant jets. The third and second nozzles have a ratio of transverse cross-sectional areas of less than unity such that, in use, a greater mass flow of the oxidant passes through the second nozzle than the third nozzle and, thereby, the lower-pressure field is produced in the lower oxidant jet. The first nozzle is frontally located on the central fuel body such that the fuel jet is discharged through the open front end of the oxidant duct between the upper and lower oxidant jets. Fuel supply means are provided for supplying the fuel under pressure to the fuel nozzle. The open front end of the oxidant duct can be horizontally flared and shaped such that the upper and lower oxidant jets assume a horizontally divergent, fan-shaped configuration upon discharge therethrough. The first nozzle can also be configured such that the fuel jet has a complementary horizontally divergent, fan-shaped configuration. As a result, mixing between the oxidant and the fuel occurs globally, over a wide area and in quite a uniform manner. The central fuel body can be adapted for movement toward and away from the open front end of the oxidant duct. In such case, the transverse cross-sectional areas of the second and third nozzles are variable, decreasing and increasing as the fuel body is moved away from and toward the front end of the oxidant duct, respectively. The duct and the body member can be shaped such that the transverse cross-sectional area ratio of the third and second ducts remains constant at any location along the oxidant duct and at any position along the duct of the body member. Therefore, in any position of the body member, the lower oxidant jet produces the low-pressure field. In addition, selective movement of the body member away from and towards the open front end of the oxidant duct simultaneously increases and decreases oxidant jet velocity in accordance with the decrease and increase of the transverse, cross-sectional areas of the third and second nozzles selectively to impart to the flame sharp and lazy configurations. Additionally, the third and second nozzles can also be shaped such that at burner operating pressure, the oxidant follows the shape of the two opposed, spaced sets of top and bottom surfaces forming the upper and lower nozzles. The effect of this is that at a given burner operating pressures, the mass flow rate of oxidant remains essentially constant in any position of the central fuel body. Thus, sharp and lazy flame configurations can be selected at will without changing the mole ratio between the fuel and the oxidant. A burner according to the invention and its operation will now be described by way of example with reference to the accompanying drawings, in which: FIG. 1 is an elevational view of a burner in accordance with the present invention set within a burner block of a furnace with portions of the burner and burner block broken away; FIG. 2 is an enlarged end view of the burner illustrated in Fig. 1; FIG. 3 is an enlarged view of Fig. 1 taken along line 3-3 thereof; FIG. 4 is a fragmentary, top sectional view of an oxidant duct of the burner illustrated in FIG. 1; FIG. 5 is a graph showing the curvature of the inner surfaces of the oxidant duct; FIG. 6 is a graph showing the curvature of the upper and lower surfaces of a central fuel body of the burner illustrated in Fig. 1; FIG. 7 is a fragmentary, top view of Fig. 1 with the burner operating to produce a sharp flame and with the outline of the burner block shown as dashed lines.; FIG. 8 is a fragmentary, top view of Fig. 1 with the burner operating to produce a lazy flame and with the outline of the burner block shown as dashed lines; and FIG. 9 is a cross-sectional view of a furnace incorporating the burner of FIG. 1, heating a heat load of molten glass. With reference to Figures 1-3, a burner 10 in accordance with the present invention is illustrated in an operative condition, set within a burner block 12 of a furnace. Burner 10 is provided with an oxidant duct 14 having an open front end 16 from which the upper and lower oxidant jets are discharged along with the flame resulting from burning fuel within the oxidant. Oxidant enters the duct 14 under pressure through an inlet 18 spaced behind open front end 16 thereof. A central body member 20 is recessed within oxidant duct 14 and is located between open front end 16 and inlet 18. Central body 20 and oxidant duct 14 have two opposed sets of spaced top and bottom surfaces, 22 and 24; 26 and 28, respectively, shaped to define separate converging/diverging upper (third) and lower (second) nozzles 30 and 32. Oxidant is forced through upper and lower nozzles 30 and 32 by the pressure to create the upper and lower oxidant jets. Oxidant duct 14, at rear end 22, is provided with an axial bore 34 having threaded and unthreaded portions 36 and 38 for purposes that will become apparent. Near open front end 16 of oxidant duct 14, a pair of opposed tracks 40 and 42 are defined on the inside of oxidant duct 14. Central body 20 is provided with opposed, horizontal projections 44 and 46. Projections 44 and 46 are designed to slide within tracks 40 and 42 to allow central body 20 to slide in an axial direction of oxidant duct 14, forward and backward, while being supported in position. Central body 20 has an inner bore 48 within which a tubular vacuum jacket 50 projects at one end thereof. Vacuum jacket 50, in turn, encloses a fuel line 52 which passes through an opening 54 of vacuum jacket 50. Vacuum jacket 50, as may be appreciated, prevents heating or cooling of the fuel by conduction. A fuel nozzle (first nozzle) 56 is frontally located on central fuel body 20 and is in communication with fuel line 52. Fuel under pressure is supplied to nozzle 56 through fuel line 52 such that a fuel jet is discharged through open front end 16 of oxidant duct 14, between the upper and lower oxidant jets. Vacuum jacket 50 is surrounded by a sheath 58 having an unthreaded section 60, passing through axial bore 34 of oxidant duct 14, and a threaded section 62. A packing nut 64 having narrow and wide threaded portions 66 and 68 is engaged, at narrow threaded portion 66, within threaded portion 36 of axial bore 34. Packing nut 64 is tightened within threaded portion 36 of axial bore 34 to bear against a Teflon packing 68 that seals oxidant duct 14 at the entry of sheath 58. An adjustment nut 70 is threaded onto threaded section 62 of sheath 58. Adjustment nut 58 is retained by a lock nut 72 threaded onto wide threaded portion 68 of packing nut 64 so that rotation of adjustment nut 70 acts on sheath 58 and thus, vacuum jacket 50, to move central body 20 in either a forward or backward direction. The action of adjustment nut 70 is frozen by tightening lock nut 72 on packing nut 64. Fuel line 52 projects from the other end of vacuum jacketing 50 and is connected to a pipe fitting 73 which is configured to be connected to a pressurised fuel source. The upper and lower nozzles 30 and 32 or more exactly, the two opposed sets of top and bottom surfaces 22, 24; and 26, 28 of oxidant duct 14 and central fuel body 20 are specially shaped. At any location of oxidant duct 14 and at any position of central body 20, the ratio of transverse, cross-sectional areas between upper and lower nozzles 30 and 32 will be less than unity and will also remain the same. The result of this is that a greater mass flow rate of oxidant will be discharged from lower nozzle 32 than upper nozzle 30 and the the lower oxidant jet will produce a low-pressure field beneath the fuel jet which will downwardly aspirate the fuel jet into the oxidant jet to produce complete mixing between the two. The upper fuel jet, having a lower mass flow rate, does not have the same influence on the fuel jet. As stated previously, unburned fuel particles travel along the length of the flame and tend to become more buoyant as they are heated. The buoyancy of such unburned fuel particles causes the flame to lick up because fuel particles are either not burnt or are burned in airborne oxygen. The upper oxidant jet burns the more buoyant particles of fuel to prevent the flame from licking up at the end, and therefore wasting the heat value of this part of the fuel. With reference now to Fig 4 open front end 16 of oxidant duct 14 is horizontally and outwardly flared and specifically shaped such that the upper and lower oxidant jets will be of a horizontally divergent fan shaped configuration. Additionally, the upper and lower nozzles 30 and 32 are also of rectangular transverse cross-section such that divergence of the upper and lower oxidant jets in the vertical direction is minimised. Fuel nozzle 56 is designed such that the fuel jet issuing therefrom has the same configuration as the oxidant jets. In this regard, for liquid fuels fuel nozzle 56 can be a nozzle 500033 manufactured by Spraying Systems Co. of Wheaton, Il. 60188. The end result of the oxidant and fuel nozzle design is that the fuel mixes with the oxidant over a wide area and thus burner 10 can be said to be a global enhancement burner. As can be appreciated, fuel nozzle 56 could be designed for gaseous fuels. As central body 20 is moved rearwardly, away from open front end 16 of oxidant duct 14, the transverse cross-sectional areas of upper and lower nozzles 30 and 32 will simultaneously decrease. The decrease in areas will increase the velocities of the upper and lower oxidant jets. When central fuel body 20 is moved in a forward direction, toward open front end 16 of oxidant duct 14, the reverse action will take place, that is velocities of the upper and lower oxidant jets will decrease. Thus, adjustment of adjustment nut 70 will control the velocity of the upper and lower oxidant jets and thus will allow the flame configuration to be selected as either a sharp flame configuration (at increased oxidant jet velocity) or a lazy flame configuration (at reduced oxidant jet velocities). The upper and lower nozzles 30 and 32 are also specially shaped such that at a given pressure, the mass flow rates of the upper and lower oxidant jets will remain substantially constant at any position of central fuel body 20. It has been found that using pure oxygen as an oxidant and No. 2 fuel oil as fuel, at pressures up to 68'9 KPa (10 psig), there was at most about a 1% to 3% difference in the mass flow rate of the oxidant passing through burner 10 as the body member 20 was successively moved from a position in which the points of inflection of the curves of the body member 20 and the oxidant duct were lined up, to successive forward movements of the body member 20 of, 3mm and 6 mm. It is also to be noted that the shape of upper and lower nozzles 30 and 32 results in a quiet operation of burner 10. At 100% firing, that is a full 110 kW rated output of burner 10, a noise level of 88.7 dba was measured directly in front of burner 10 which increased to 89.9 dba at 30° off the centre line of burner 10, to 90.2 dba at 60° off centre line of burner 10, to 92.2 dba at 90° off centre line of burner 10. Prior art burners of equivalent output would be expected to generate a noise level of from anywhere of 100 dba to about 110 dba. The advantages inherent in the operation of burner 10, such as have been discussed above, arise from the fact that the oxidant tends to follow the curvatures of surfaces 22, 24, 26, and 28 without separation at the operating pressure range of burner 10 (13'78 to 68'9 KPa) (2 to 10 psig). Among other important advantages arising from such smooth flow is that the flame is stabilised with high turn-up and turn-down ratios. In other words, burner 10 produces a stable flame over wide mass flow ratios of oxidant and fuel, and therefore under wide ranges of heat output. Furthermore, the pressure drop at the oxidant is low and therefore, there is no need to compress oxygen by the use of oxygen compressors with the use of burner 10. With reference to Figs. 5 and 6, oxidant duct 14 and central fuel body 16 are machined so that the ratio between the transverse cross-sectional areas of upper and lower oxidant nozzle was 1 : 2. The exact machining specification is as follows: CENTRAL BODY MEMBER 20 MACHINING CO-ORDINATES xm (mm) yfbm (mm) yftm (mm) xm (mm) yfbm (mm) yftm (mm) 0 0 0 17 -8.654 -4.327 1 -.227 -.113 18 -8.88- -4.440 2 -.520 -.260 19 -9.055 -4.527 3 -.884 -.442 20 -9.180 -4.590 4 -1.325 -.663 21 -9.271 -4.635 5 -1.838 -.919 22 -9.332 -4.666 6 -2.415 -1.208 23 -9.373 -4.687 7 -3.058 -1.529 24 -9.399 -4.700 8 -3.798 -1.899 25 -9.417 -4.708 9 -4.440 -2.220 26 -9.426 -4.713 10 -5.083 -2.541 27 -9.433 -4.716 11 -5.822 -2.911 28 -9.436 -4.718 12 -6.465 -3.233 29 -9.438 -4.719 13 -7.043 -3.521 30 -9.439 -4.720 14 -7.555 -3.778 31 -9.440 -4.720 15 -7.996 -3.998 84 -9.440 -4.720 OXIDANT DUCT MACHINING CO-ORDINATES xm (mm) yobm (mm) yotm (mm) xm (mm) yobm (mm) yotm (mm) -24 0 0 51 9.846 4.923 0 0 0 52 9.819 4.910 1 .021 .011 53 9.786 4.893 2 .047 .024 54 9.745 4.873 3 .081 .040 55 9.695 4.847 4 .122 .061 56 9.633 4.817 5 .172 .086 57 9.560 4.780 6 .233 .117 58 9.471 4.736 7 .307 .154 59 9.367 4.684 8 .395 .120 60 9.246 4.623 9 .499 .250 61 9.105 4.552 10 .621 .311 62 8.943 4.471 11 .762 .381 63 8.759 4.380 12 .924 .462 64 8.553 4.276 13 1.108 .554 65 8.322 4.161 14 1.314 .657 66 8.069 4.034 15 1.544 .772 67 7.792 3.896 16 1.798 .899 68 7.492 3.746 17 2.075 1.038 69 7.171 3.585 18 2.375 1.188 70 6.830 3.415 19 2.696 1.348 71 6.473 3.236 20 3.037 1.518 72 6.101 3.051 21 3.394 1.697 73 5.718 2.859 22 3.766 1.883 74 5.328 2.664 23 4.149 2.074 75 4.933 2.467 24 4.539 2.270 76 4.539 2.270 25 4.933 2.467 77 4.149 2.074 26 5.328 2.664 78 3.766 1.883 27 5.718 2.859 79 3.394 1.697 28 6.101 3.051 80 3.037 1.518 29 6.473 3.236 81 2.696 1.348 30 6.830 3.415 82 2.375 1.188 31 7.171 3.585 83 2.075 1.038 32 7.492 3.746 84 1.798 .899 33 7.792 3.896 85 1.554 .772 34 8.069 4.034 86 1.314 .657 35 8.322 4.161 87 1.108 .554 36 8.553 4.276 88 .924 .462 37 8.759 4.380 89 .762 .381 38 8.943 4.471 90 .621 .311 39 9.105 4.552 91 .499 .250 40 9.246 4.623 92 .395 .198 41 9.367 4.684 93 .307 .154 42 9.471 4.736 94 .233 .117 43 9.560 4.780 95 .172 .086 44 9.633 4.817 96 .122 .061 45 9.595 4.847 97 .081 .040 46 9.745 4.873 98 .047 .024 47 9.786 4.893 99 .021 .011 48 9.819 4.910 100 0 0 49 9.846 4.923 50 9.867 4.933 For both oxidant duct 14 and central fuel body 12, "bm" denotes bottom machining co-ordinates, while "tm" denotes top machining co-ordinates. As may be appreciated, a great deal of heat is generated by burner 10, which is conducted within oxidant duct 14. This heat is carried away by cooling water flowing through a water jacket 74 surrounding oxidant duct 14. Water jacket has inlet and outlets 76 and 78 formed by appropriate fittings for cooling water to enter and leave water jacket 74 after circulating around oxidant duct 14. Burner 10 is mounted within burner block 12 by a clamp 80 connected to burner block 12 and clamped about water jacket 74. With reference to Figs. 7 and 8, burner 10 is shown to be emitting a sharp flame 81 and a lazy flame 82 both of which are horizontally divergent and fan-shaped. As can be seen in Fig. 9, burner 10 projects sharp flame 81 into an insulated enclosure 82 of a furnace 84. Insulated enclosure 82 has bottom, side and top walls 85, 86, 88 and 90. A melt 92 is confined between bottom wall 85 and sidewalls 86 and 88, below burner 10. As is apparent from this illustration, sharp flame 81 has very little vertical divergence and does not lick up at the end to heat top wall 90 of insulated enclosure 82. Although burner 10 is set in burner block 12 in a downward angle, this is peculiar to the illustrated furnace and as would be known, burner 10 could be used in a level orientation. Although not illustrated, but as would be well known in the art, furnace 84 would have an inlet for the raw material for the melt and an outlet for the melt. Moreover, a chimney would also be provided to discharge the combustion products of the burned fuel. As another embodiment, a burner could incorporate the structure of the preferred embodiment with a fixed central fuel body preset to burn fuel within an oxidant with either a sharp or a lazy flame.

Claims: A burner (10) for burning fuel in an oxidant comprising: first nozzle means (56) for producing a jet of the fuel adapted to burn within the oxidant with an outwardly extending flame such that particles of the fuel become increasingly more buoyant along the length of the flame; second nozzle means (32) located below the first nozzle means (56) for creating a lower jet of the oxidant; and third nozzle means (30) located above the first and second nozzle means (56, 32) for creating an upper jet of the oxidant that supports combustion of the particles of the fuel; characterised in that, said second nozzle means (32) is shaped and positioned for creating a lower jet of the oxidant that produces a low-pressure field below the fuel jet for downwardly aspirating the fuel into the oxidant. A burner according to claim 1, characterised in that the nozzles (56, 30, 32) are of a shape such that in use the fuel and oxidant jets and flame are outwardly divergent and fan shaped so as to enable mixing of the fuel into the oxidant occurs over a wide area. A burner according to claim 1 or claim 2, characterised in that the second and third nozzle means (32, 30) have selective velocity control means for simultaneously controlling upper and lower oxidant jet velocities independently of upper and lower oxidant jet mass flow rates selectively to produce lazy and sharp flame configurations. A burner according to any one of the preceding claims, characterised by a duct (14) for the supply of oxidant having an open front end and a body member (20) located within the duct (14) and having a passage therethrough for fuel terminating in the first nozzle (56). A burner according to claim 4, characterised in that the body member (20) is set back and has a central position in the duct (14). A burner according to claim 4 or claim 5, characterised in that the ratio of the transverse cross-sectional areas of the third and second nozzles (32, 30) is less than one to one, whereby, in use, a greater flow of the oxidant passes through the second nozzle (32) so as to create said low pressure field. A burner according to any one of claims 4 to 6, characterised in that the second and third nozzles (32, 30) each define a convergent-divergent passage. A burner according to claim 7, characterised in that the body member (20) is movable towards and away from the front end of the duct, so as respectively to increase and decrease the transverse cross-sectional area of the second and third nozzles (32, 30), whereby, in use, to impart to the flame respective lazy and sharp shape substantially independently of the mass flow rate of the oxidant, and wherein said co-operating surfaces are shaped such that the said ratio is essentially the same whatever the position of the body member. A burner according to any one of claims 4 to 8, characterised in that the front end (16) of the oxidant duct (14) is flared horizontally, having a shape such that, in use, the upper and lower oxidant jets assume a horizontally divergent, fan-shaped configuration complementary to that of the upper and lower oxidant jets, whereby mixing between the oxidant and the fuel occurs over a wide area of the flame. A burner according to any one of claims 4 to 9, characterised in that the second and third nozzles (32, 30) are each of rectangular transverse cross-section, whereby, in use, to limit vertical divergence of the oxidant jets and therefore the flame. A burner according to any one of claims 4 to 10, characterised in that the passage through the body member (20) communicates with a vacuum-insulated fuel supply pipe. A burner according to any one of claims 4 to 11, characterised in that the duct is surrounded by a water jacket. A method of burning fuel in an oxidant, comprising: producing a jet of the fuel which burns with an outwardly extending flame such that particles of the fuel become increasingly more buoyant along the length of the flame; creating a lower jet of oxidant below the fuel; and creating above both the fuel jet and the lower jet an upper jet of oxidant of a shape to burn the particles of the fuel; characterised by the step of directing the lower jet such as to create a low pressure field below the fuel jet for downwardly aspirating the fuel into the oxidant.

Inventors: YAP LOO T, YAP, LOO T.
Applicants: BOC GROUP INC, THE BOC GROUP, INC.
Application year: 1992
Main classification: F23C7
IPC codes: F23C7, F23D14, F23D1, F23C5