Glass Fibre Manufacturing Plant Comprising Oxy-Burner Having Cooling Unit

Abstract

The present invention concerns a glass fibre manufacturing plant comprising a forehearth (31) comprising a longitudinal wall provided with at least one burner assembly comprising: (A) a burner block (20) made of a refractory material and comprising a through-passage and comprising a hot surface (20H) forming a portion of the longitudinal wall (31 L); and (B) a burner sub-assembly comprising: (a) an oxy-burner (1) comprising a downstream end ending at a free end of the downstream end, wherein a cross-sectional area of said downstream end of the oxy-burner body decreases towards the free end of the downstream end; characterized in that, the burner sub-assembly further comprises: (b) a cooling unit (3) comprising: a cooling plate (5) comprising an aperture which geometry matches the geometry of the downstream end of the oxy-burner which is inserted in said aperture to form a thermal contact therewith; a cooling channel (3C) defined by walls and comprising an inlet (3U) and an outlet (3D) for circulating a refrigerating fluid, wherein a cooling wall (5W) of said cooling channel is formed by a portion of the cooling plate, and in that, the cooling plate is encased in the through-passage.

Claims

1. Glass fibre manufacturing plant comprising a forehearth (31) forming a passage for conveying molten glass (30) and defined by a first and second opposite longitudinal walls (31L), a ceiling (31T), a bottom floor (31B) and an end wall (31E), each longitudinal wall being provided with at least one burner assembly comprising: (A) a burner block (20) made of a refractory material and comprising a cold surface (20C) and a hot surface (20H) opposite the cold surface, the cold surface being fluidly connected to the hot surface by a through-passage extending along a passage axis, Xp, and wherein the hot surface (20H) forms a portion of the corresponding longitudinal walls (31L); and (B) a burner sub-assembly comprising: (a) an oxy-burner (1) comprising a body extending along a burner body axis, Xb, and comprising a downstream end ending at a free end of the downstream end, said body enclosing a fuel line (1F) and an oxygen line (1Ox) separate from the fuel line, both fuel line and oxygen line having a separate outlet at or adjacent to the free end of the downstream end (1D) of the oxy-burner, wherein a cross-sectional area normal to Xb of said downstream end of the oxy-burner body decreases towards the free end of the downstream end; characterized in that, the cooling plate is encased in the through-passage, and in that, the burner sub-assembly further comprises: (b) a cooling unit (3) comprising: a cooling plate (5) made of a thermally conductive material, defined by a first and a second main surfaces separated by a thickness of said cooling plate, and an aperture extending from a large opening at the first main surface to a narrow opening to the second main surface, wherein the aperture is defined by an aperture wall which geometry matches the geometry of the downstream end of the oxy-burner which is inserted in the aperture to form a thermal contact therewith; a cooling channel (3C) defined by walls and comprising an inlet (3U) and an outlet (3D) for circulating a refrigerating fluid, wherein a cooling wall (5W) of said cooling channel is formed by a portion of the cooling plate, and

2. Glass fibre manufacturing plant according to claim 1, wherein the cooling plate is massive and the cooling wall is formed by a portion of the first main surface.

3. Glass fibre manufacturing plant according to claim 2, wherein the cooling channel comprises an annular cavity portion extending along the burner body axis, Xb, from an upstream end closed by an upstream wall pierced by a first and second openings bringing the cavity portion in fluid communication with the inlet and the outlet, to a downstream end closed by the cooling wall, wherein said cooling wall surrounds the large opening of the aperture of the cooling plate.

4. Glass fibre manufacturing plant according to claim 3, wherein the annular cavity portion defines a prismatic passage (3P), which extends along the burner body axis, Xb, and is contiguous with the aperture of the cooling plate, said prismatic passage being so dimensioned as to accommodate a portion of the body of the oxy-burner, with the downstream end of the oxy-burner in thermal contact with the aperture wall of the cooling plate.

5. Glass fibre manufacturing plant according to claim 1, wherein the cooling plate is hollow, forming a cavity surrounding the aperture and forming part of the cooling channel, said cavity being in fluid communication with both inlet and outlet.

6. Glass fibre manufacturing plant according to any of the preceding claims, wherein the cooling plate is made of an austenite nickel-chromium-based superalloy, preferably inconel.

7. Glass fibre manufacturing plant according to any of the preceding claims, wherein the burner block (20) comprises three portions: (a) A burner portion (21B), opening at the cold surface, and having a prismatic geometry of cross-section suitable for accommodating the cooling unit (3) with the oxy-burner's downstream end inserted in the aperture of the cooling plate; (b) A flame portion (21F), opening at the hot surface and converging along the passage axis, Xp; in the direction of the cold surface until meeting (c) A joining portion (21J), fluidly joining the flame portion to the burner portion

8. Glass fibre manufacturing plant according to claim 7, wherein the burner block is made of a refractory material composed of at least 90 wt. % alumina, preferably of at least 95 wt. % alumina, more preferably of at least 99 wt. %.

9. Glass fibre manufacturing plant according to claim 7 or 8, wherein the burner block comprises a hot cuboid portion comprising the hot surface, and a cold cuboid portion comprising the cold surface, wherein the cross-sectional area normal to the passage axis, Xp, of the hot cuboid portion is smaller than the one of the cold cuboid portion.

10. Glass fibre manufacturing plant according to any of claims 7 to 9, wherein the flame portion and the joining portion of the burner block through-passage have a geometry of revolution around the passage axis, Xp, whilst the geometry of the cross-section normal to the passage axis, Xp, of the burner portion is not of revolution, and either is polyhedral, preferably rectangular or square, or has an overall geometry of revolution with respect to xp, comprising a protrusion or a recess.

11. Glass fibre manufacturing plant according to any one of the preceding claims, wherein each longitudinal wall comprises at least two such burner assemblies aligned horizontally, the at least two burner assemblies of the first longitudinal wall facing the at least two burner assemblies of the second longitudinal wall in a staggered arrangement, the end wall being preferably also provided with at least one such burner assembly.

12. Use of a cooling unit (3) as defined in claim 1(b) for cooling a downstream end (1D) of an oxy-burner (1) mounted in a forehearth (31) of a glass fibre manufacturing plant.

Description

BRIEF DESCRIPTION OF THE FIGURES

[0032] For a fuller understanding of the nature of the present invention, reference is made to the following detailed description taken in conjunction with the accompanying drawings in which:

[0033] FIG. 1: shows an embodiment of a cooling unit for oxy-burner suitable for the present invention.

[0034] FIG. 2: shows an alternative embodiment of a cooling unit for oxy-burner suitable for the present invention.

[0035] FIG. 3: shows yet an alternative embodiment of a cooling unit for oxy-burner suitable for the present invention.

[0036] FIG. 4: shows (a) a burner block and (b)-(d) the same burner block supporting an oxy-burner and cooling unit according to FIGS. 1 to 3.

[0037] FIG. 5: shows a cut-off, perspective view of a burner block.

[0038] FIG. 6: shows a burner block with different oxy-burner orientations.

[0039] FIG. 7: shows a cross-section and a top view of a forehearth according to the present invention.

[0040] FIG. 8: shows a preferred embodiment wherein a burner block can be reversibly inserted into a cavity of a longitudinal wall.

DETAILED DESCRIPTION OF THE INVENTION

[0041] As shown in FIGS. 7, a glass fibre manufacturing plant according to the present invention comprises a forehearth (31) forming a passage for conveying molten glass (30) and defined by: [0042] a first and second opposite longitudinal walls (31L) having a hot longitudinal wall surface facing said passage and extending along a longitudinal direction, X1, having a longitudinal wall thickness extending along a first transverse direction, X2, normal to X1, and having a longitudinal wall height extending along a second transverse direction, X3, normal to both X1 and X2, [0043] a ceiling (31T), [0044] a bottom floor (31B) and [0045] an end wall (31E).

[0046] Oxy-burners are mounted in burner blocks (20) included in the masonry of the longitudinal walls and distributed along said longitudinal walls of the passage. Typically, a forehearth comprises hundreds of burner blocks aligned along the longitudinal axis, X1, of the longitudinal walls and each loaded with an oxy-burner. Examples of burner blocks (20) suitable for the present invention are represented in FIGS. 4 to 6. A burner block (20) is a block of refractory material which can be incorporated in the masonry of the longitudinal walls, and which comprises a hot surface (20H) which forms part of the hot longitudinal wall surface, and a cold surface (20C) opposite to the hot surface. The cold surface is connected to the hot surface by a through-passage extending along a passage axis, Xp, and comprising: [0047] (a) a burner portion (21B) opening at the cold surface, into which an oxy-burner can be loaded, [0048] (b) a flame portion (20F) opening at the hot surface, and usually [0049] (c) a joining portion (21j) fluidly joining the flame portion with the burner portion.

[0050] The flame portion and the joining portion of the burner block through-passage preferably have a geometry of revolution around the passage axis, Xp, the geometry of the cross-section normal to the passage axis, Xp, of the burner portion is not of revolution, and either is polyhedral, preferably rectangular or square, or has an overall geometry of revolution with respect to xp, comprising a protrusion or a recess.

[0051] As shown in FIGS. 4(a) and 5, a burner block preferably comprises a hot cuboid portion comprising the hot surface, and a cold cuboid portion comprising the cold surface, wherein the cross-sectional area normal to the longitudinal axis, X1, of the hot cuboid portion is smaller than the one of the cold cuboid portion. A cuboid geometry is defined as a convex polyhedron bounded by six quadrilateral faces, whose polyhedral graph is the same as that of a cube. A cuboid bounded by six rectangular faces, with each pair of adjacent faces meeting in a right angle is herein referred to as a rectangular cuboid. This more restrictive type of cuboid is also known as a right cuboid. In other words, if not rectangular, a cuboid may for example be bounded by two or more trapezia. The hot surface of the hot cuboid portion can have a width, w, measured at service temperature, hT, of the order of 1150 C.150 C., along the longitudinal axis, X1.

[0052] A burner block is preferably made of a refractory material composed of at least 90 wt. % alumina, preferably of at least 95 wt. % alumina, more preferably of at least 99 wt. %. The refractory material of the support block preferably comprises less than 10 wt. % silica, more preferably comprises less than 5 wt. % silica, most preferably comprises less than 2 wt. % silica. The bricks surrounding the cavity may be made of mullite, preferably of alumina enriched mullite.

[0053] As shown in the top views along a plane (X1, X2) of FIG. 6(a)&(b), the passage axis, Xp, forms an angle, a, with the longitudinal direction, X1, comprised between 30 and 90, preferably, between 45 and 90. In FIG. 6(a), a burner block having a passage axis, Xp, forming an angle, =90, is illustrated, such that the passage axis, Xp, is parallel to the first transverse direction, X2. In FIG. 6(b) an alternative embodiment with an angle, <90, is illustrated, the burner preferably pointing in the direction of the flow of molten glass.

[0054] In a preferred embodiment illustrated in FIG. 8, the burner block can be removed from the masonry and the same or a new burner block can be reintroduced into the cavity (28) left after withdrawal of the burner block. Because of the high service temperatures, hT, reigning in the passage, usually of the order of 1150 C.150 C., providing a cavity allowing the reversible insertion of a burner block is not so straightforward, because the dimensions of the cavity formed at room temperature during the building of the longitudinal wall vary substantially with the raising of the temperature to service temperature, hT, and thermal expansion of the spacer bricks (23) flanking either side of such cavities must be taken into account. A spacer element must be provided in the masonry abutting against the walls of the spacer bricks flanking each lateral side of a cavity in order to hinder the thermal expansion of the two spacer bricks, such that the distance between said two spacer bricks measured at room temperature along the longitudinal direction, X1, at the level of the hot longitudinal wall surface cannot be reduced below a predetermined hot cavity width, W, at said service temperature, hT. The predetermined hot cavity width, W, must be larger than the width, w, of the hot surface of the burner block. For example, (w+4 mm)W(w+8 mm)). For example, as shown in FIG. 8, a spacer element can be formed by a lintel (25) of length, WL>W, resting on the recessed surfaces of a right step cut off from the two opposite top edges of each spacer brick flanking the cavity and extending in the first transverse direction, X2. Alternatively, a brick of length, W, measured at service temperature, hT, can be laid at the bottom of the cavity, the ends of the brick abutting against a wall of the flanking bricks, defining the lateral walls of the cavity (not shown) and thus hindering their thermal expansion.

[0055] Because the longitudinal walls of a forehearth must be substantially impervious to gases, to prevent hot air flowing out of the passage, the gap formed between the burner block and the cavity must be filled with a resilient material (29), preferably provided in the form of a fibrous sheet, which is wrapped around external surfaces of the support block. The resilient material is preferably made of refractory fibres, typically alumina fibres, or fibres comprising at least 90 wt. %, more preferably at least 95 wt. %, most preferably at least 99 wt. % alumina. The resilient fibres preferably do not comprise more than 2 wt. % silica, and more preferably comprise no silica, as silica may form an eutectic with oxides of adjacent refractory bricks, which could contaminate the glass melt by sublimation at high temperatures. An example of resilient material supplied as a sheet which is suitable for the present invention comprises ceramic fibre paper such as supplied by Morgan Thermal Ceramics.

[0056] As illustrated in FIGS. 1(a) to 3(a), burners and, in particular, oxy-burners, comprise a body extending along the burner body axis, Xb, and comprising a downstream end ending at a free end of the downstream end, said body enclosing a fuel line (1F) and an oxygen line (10x) separate from the fuel line, both fuel line and oxygen line having a separate outlet at or adjacent to the free end of the downstream end (1D) of the oxy-burner, wherein a cross-sectional area normal to X1 of said downstream end of the oxy-burner body decreases towards the free end of the downstream end. The downstream end of an oxy-burner is often conical or trunco-conical.

[0057] Burners and, in particular, oxy-burners, are loaded into a burner block from the opposite side of the longitudinal walls from the passage, which defines a cold longitudinal wall surface. As discussed before, a burner can be mounted in the burner portion (21B) of the through-passage of a burner block with the tip of the downstream end of the burner protruding slightly in the joining portion (21j). The tips of the burners are therefore exposed directly to the temperature reigning in the flame portion (21F) of the through-passage and to the service temperature, hT, reigning in the passage beyond the opening of the flame portion at the hot longitudinal wall surface. Theoretically, this is not a problem because the fuel and oxygen flowing through the body and converging at the tip of a burner act as refrigerants and cool the downstream end of the burner, protecting it from over-heating. In case, however, of a low flow rate of oxygen and/or fuel, or in case of malfunction of one of the oxygen or fuel lines (1Ox, 1F) the downstream end of a burner might not be cooled down sufficiently and the temperature thereof may raise above cracking temperature of the fuel or even above a threshold limit beyond which the burner is damaged. The present invention provides a solution to this problem, and also to the prolongation of the service life of burners.

[0058] As illustrated in FIGS. 1 to 3, the gist of the present invention is to provide a cooling unit (3) in thermal contact with the downstream end of the burners (1). In particular, a cooling unit (3) according to the present invention comprises: [0059] a cooling plate (5) made of a thermally conductive material, defined by a first and a second main surfaces separated by a thickness of said cooling plate, and an aperture extending from a large opening at the first main surface to a narrow opening to the second main surface, wherein the aperture is defined by an aperture wall which geometry matches the geometry of the downstream end of the oxy-burner to form a thermal contact therewith when the downstream end is inserted in the aperture; [0060] a cooling channel (3C) defined by walls and comprising an inlet (3U) and an outlet (3D) for circulating a refrigerating fluid, wherein a cooling wall (5W) of said cooling channel is formed by a portion of the cooling plate.

[0061] The refrigerating fluid can be water, air, nitrogen or any refrigerating fluid known in the art. It flows into the cooling unit at a first temperature, T1, through the inlet (3U) of the cooling channel, contacts the cooling wall (5W) whence it extracts heat from the cooling plate, and flow out of the cooling unit at a temperature, T2>T1, through the outlet (3D) of the cooling channel.

[0062] For example, with burners having a conical or trunco-conical downstream end, the geometry of the aperture wall of the cooling plate is likely preferably trunco-conical, to match perfectly the geometry of the downstream portion and thus form an optimal thermal contact therewith. A cooling plate suitable for the present invention is preferably made of a highly thermally conductive material, such as an austenite nickel-chromium-based superalloy, for example, Inconel.

[0063] As illustrated in FIGS. 1&2, the cooling plate can be massive, in that it is not hollow. By sharing a wall with the cooling channel (3C), a portion of the first main surface of the cooling plate (5) forms the cooling wall (5W). Preferably the whole area of the first main surface forms the cooling wall (5W). In use, the temperature of the cooling wall (5W) is lowered by the refrigerating fluid flowing through the cooling channel (3C) and contacting said cooling wall, A temperature gradient is thus created within the cooling plate (5) between the cold surface of the cooling wall (5W) and hot surface of the second main surface of the cooling plate, which is exposed to higher temperatures than the cooling wall. In case of low or no flow of oxygen and/or fuel in the oxygen and fuel lines (1Ox, 1F) of the oxy-burner, the temperature of the downstream end of the oxy-burner will rise, thus creating a thermal gradient between the hot surface of the cavity wall and the cold surface of the cooling wall. Heat is therefore withdrawn from the hot surfaces of the second main surface and, if it applies of the cavity wall towards the cooling surface (5W) and is evacuated by the refrigerating fluid flowing out of the outlet (3D). This way, the temperature of the downstream end of the oxy-burner is ensured to remain below a threshold temperature above which gas cracking would occur or the burner tip would be degraded.

[0064] The cooling channel may comprise an annular cavity surrounding the body of the oxy-burner. A thermal contact between the cooling channel and the body of the oxy-burner is possible but not essential, since it is the downstream end of the oxy-burner which is exposed to the highest temperatures. The annular cavity portion extends along the burner body axis, Xb, from, [0065] an upstream end closed by an upstream wall pierced by a first and second openings bringing the cavity portion in fluid communication with the inlet and the outlet, to [0066] a downstream end closed by the cooling wall (5W), wherein said cooling wall surrounds the large opening of the aperture of the cooling plate.

[0067] If the passage defined by the annular cavity portion for receiving the body of the oxy-burner is contiguous with the aperture of the cooling plate, than the whole area of the first main surface of the cooling plate can form the cooling wall (5W).

[0068] One difference between the cooling units of the FIGS. 1 and 2 is the length of the annular cavity portion of the cooling channel: in FIG. 1, the annular cavity portion extends over substantially the whole length of the oxy-burner body, whilst in FIG. 2 the annular cavity portion is formed directly before the cooling wall (5W). The fluid and thermal flows characterizing the two cooling unit designs will vary depending on the dimensions of the annular cavity portion, in a manner well understood by a person skilled in the art.

[0069] As shown in FIGS. 2 and 9(a), the second main surface of the cooling plate (5) can be provided with a thermally insulating layer (5i). This embodiment has the advantage to reduce the temperature gradient, ATS, in the refractory of the burner block, between the burner portion (21B), which wall against which the cooling plate abuts is maintained at a low temperature (e.g., 20 to 100 C.), whilst a few centimetres further, in the flame portion (21F) a temperature of the order of 2500 C. can be reached (cf. FIG. 9(b)). As shown in FIG. 9(a), with an insulating layer (5i), the temperature of the refractory wall of the burner portion against which the cooling plate abuts can be maintained at a higher temperature of the order of 500-1000 C., thus decreasing considerably the slope of the thermal gradient, T5i, in the refractory material surrounding the joining portion (21J), over a few centimetres only.

[0070] In an alternative embodiment, the cooling plate (5) is not massive but hollow, as shown in FIG. 3, forming an annular cavity comprising the aperture wall defining the aperture and, at the same time, forming part of the cooling channel. The cavity is in fluid communication with both inlet and outlet to allow a flow of refrigerant fluid therethrough. The refrigerant fluid is therefore in direct contact with the cavity wall, thus enhancing the heat exchange efficacy.

[0071] Both an assembly comprising a sub-assembly, and a kit-of-parts are described herein, said sub-assembly and kit-of-parts comprising an oxy-burner (1) and a cooling unit (3) as defined above. In the sub-assembly, the downstream end (1D) of the oxy-burner is in thermal contact with the aperture wall of the cooling plate (5), as shown in FIGS. 1 to 3. The assembly and kit-of-parts can further comprise a burner block as discussed supra to form a burner assembly. In said burner assembly, the oxy-burner sub-assembly can be encased in the burner portion (21B) of the burner block through-passage. In order to ensure a reproducible positioning of the oxy-burner with respect to the burner block, it is advantageous if the cross-section of the burner portion (21B) normal to the passage axis, xp, does not form a geometry of revolution. The cross-section can have a polygonal geometry, such as a rectangle as illustrated in FIG. 5. Alternatively, the cross-section can have an overall geometry of revolution with respect to xp, comprising a protrusion or recess matching a corresponding recess or protrusion in the oxy-burner sub-assembly, for restricting to a single encasing position and for preventing rotation of the oxy-burner and oxy-burner sub-assembly about the passage axis, Xp.

[0072] In an alternative embodiment, a cooling unit can be permanently fixed in the burner portion of the burner block, e.g., with mortar, to ensure an optimal and reproducible positioning thereof. An oxy-burner can then be loaded into, or unloaded out of the thus sealed cooling unit.

[0073] As illustrated in FIG. 7, a fibre manufacturing plant according to the present invention comprises a forehearth (31) forming a passage for conveying molten glass (30) and defined by a first and second opposite longitudinal walls (31L), a ceiling (31T), a bottom floor (31B) and an end wall (31E). A system of axes, X1, X2, X3, is represented, wherein X1 is a longitudinal axis, parallel to the longitudinal walls of the passage, X2 is a first transverse axis, normal to X1, and X3 is a second transverse axis, normal to both X1 and X2.

[0074] Both longitudinal walls are provided with at least one burner assembly comprising an oxy-burner sub-assembly encased in a burner block as discussed supra, with a hot surface (20H) of the burner block forming a portion of the corresponding longitudinal walls (31L). It is clear that several burner assemblies are required in each longitudinal wall (31L) to maintain a controlled temperature in the passage, which can be several dozens of metres long. Consequently, as illustrated in FIG. 7(b), each longitudinal wall comprises at least two burner assemblies aligned horizontally, the at least two burner assemblies of the first longitudinal wall preferably facing the at least two burner assemblies of the second longitudinal wall in a staggered arrangement. In practice, each longitudinal wall may comprise a hundred or more burner assemblies, facing each other in a staggered arrangement, with an angle of the passage axis, xp, with the longitudinal axis, X1, preferably comprised between 30 and 90. The end wall is preferably also provided with at least one burner assembly.

[0075] The bricks adjacent to and surrounding the burner blocks preferably contain less than 5 wt. % of SiO.sub.2, more preferably less than 1 wt. % SiO.sub.2, most preferably less than 0.2 wt. % SiO.sub.2, or no SiO.sub.2. For example, the adjacent bricks of the longitudinal wall may be made of alumina enriched mullite. Alternatively or additionally, a sheet of refractory non-woven fibres (29), poor in SiO.sub.2 as discussed with respect to exchangeable burner blocks, as illustrated in FIG. 8, can also be wrapped around the hot cuboid portion of traditional, non-exchangeable burner blocks to form a barrier to migration of SiO.sub.2 from adjacent bricks. The non-woven fibres preferably comprise less than 5 wt. % SiO.sub.2, preferably less than 1 wt. % SiO.sub.2, more preferably less than 0.2 wt. % SiO.sub.2, or no SiO.sub.2. They preferably comprise substantial amounts of alumina.

[0076] The use of a cooling unit (3) as discussed supra for cooling a downstream end (1D) of an oxy-burner (1) mounted in a forehearth (31) of a glass fibre manufacturing plant has several advantages. First, in case of low gas flow rates, as can be common with oxy-burners, a cracking temperature of the fuel is not reached, preventing carbon deposition at the tips of the oxy-burners. It has been observed in preliminary tests on a full scale glass fibre production line, that oxy-burners provided with a cooling unit according to the present invention required three to ten times (3 to 10) less frequent cleaning operations than the same oxy-burners used in the same conditions, absent a cooling unit. Second, in case of accidental interruption of the flow of the oxygen or the fuel in an oxy-burner, the downstream end (1D) of the oxy-burner equipped with a cooling unit does not heat up above a threshold temperature which would degrade the oxy-burner. This means that the range of flow rates an oxy-burner can be used is increased, since it must not be above a certain flow rate value required for ensuring the cooling of the downstream end of the oxy-burner. Third, although oxy-burners are designed for working at relatively high temperatures (several hundreds of degrees Celsius), their service lifetime is increased when working at lower temperatures. A cooling unit according to the present invention permits to work with oxy-burners maintained at a lower temperature. Fourth, the handling of a thus cooled oxy-burner mounted in a burner block by an operator is facilitated if the temperature of the oxy-burner body is lower as allowed by the cooling unit.

TABLE-US-00001 REF DESCRIPTION 1 oxy-burner 1D downstream end of oxy-burner 1F fuel line 1Ox Oxygen line 3 cooling unit 3C cooling channel 3D outlet of cooling channel 3U inlet of cooling channel 5 cooling plate 5T trunco-conical aperture 5W cooling wall 20 burner block 20C cold surface of burner block 20H hot surface of burner block 21B burner portion of through-passage 21F flame portion of through-passage 21J joining portion of through-passage 23 Spacer brick 25 Lintel 28 Cavity 29 Resilient material 30 molten glass 31 passage 31B passage bottom floor 31E passage end wall 31L passage longitudinal wall 31T passage ceiling X1 Longitudinal axis X2 First transverse axis, normal to X1 and X3 X3 Second transverse axis, normal to X1 and X2 Xb Burner body axis Xp Passage axis