Lean gas burner

Abstract

A gas burner for burning a gas with a low calorific value. The gas burner may be for burning a synthesis gas issuing from the gasification of biomass.

Claims

1. A gas burner for burning a gas having a low calorific value, the gas burner comprising: a cylindrical body having: a first annular zone formed between an external wall thereof and an internal wall thereof, and which extends substantially parallel to the external wall wherein the external wall has a base at an upstream distal end thereof; a second annular zone formed downstream of the first zone between the external wall and the internal wall, wherein the first annular zone is separated from the second annular zone by a partition; a first opening formed in the base, to supply the gas, and which extends substantially parallel to a longitudinal axis of the cylindrical body; a second opening to supply primary air, and which is formed in the external wall in fluidic communication with the first annular zone; a third opening to supply secondary air, and which is formed in the external wall in fluidic communication with the second annular zone; an annular slot to introduce the primary air from the first annular zone into a combustion zone, the annular slot being formed between the external wall and an upstream end of the internal wall, and formed such that the primary air is supplied to the combustion zone in the form of a conical sheet of air, and creates a compression zone; and orifices formed in the internal wall to introduce the secondary air from the second annular zone into the combustion zone, and are disposed so as to allow swirling of the secondary air.

2. The gas burner of claim 1, wherein the cylindrical body further has an air-introduction piece which defines the annular slot, and which is situated at the upstream end of the internal wall.

3. The gas burner of claim 2, wherein the air-introduction piece has a conical part diverging from downstream to upstream, to form with the internal wall an angle of between 20 and 45, and a suction surface part terminating on a trailing edge, which is to direct the conical sheet of air according to a required profile in order to constitute a compression zone situated substantially on the longitudinal axis of the cylindrical body.

4. The gas burner of claim 3, wherein the air-introduction piece has a flat upstream edge perpendicular to the longitudinal axis of the cylindrical body and substantially parallel to a flat surface of the external wall, to thereby form an air flow extending perpendicular to the longitudinal axis of the cylindrical body.

5. The gas burner of claim 3, wherein the conical part is followed by a rounded part having a first radius of curvature, and which is followed by a planar upstream edge substantially perpendicular to the internal wall, and substantially parallel to the base of the cylindrical body formed by the external wall.

6. The gas burner of claim 5, wherein the suction surface part follows the planar upstream edge and is formed by a first rounded part having a second radius of curvature followed by a second part having a plurality of successive flat profiles forming respective angles with the plane of the upstream edge.

7. The gas burner of claim 5, wherein the angles are respectively between 30 and 80.

8. The gas burner of claim 1, wherein the orifices have a cylindrical or oblong cross-section, and have a unit diameter of between 3 and 15 mm.

9. The gas burner of claim 1, wherein the base has a fourth opening to introduce a fossil fuel.

10. The gas burner of claim 1, wherein the base has passages to equip the gas burner with an ignition burner, a pilot flame or a flame detector.

11. The gas burner of claim 1, further comprising a controller having a memory, and which is to regulate the flow of air introduced for each combustion rate and each ratio of lean gas to fossil fuel according to working points parameterised and stored in the memory.

12. The gas burner of claim 1, wherein the orifices have axes that are inclined at an angle substantially equal to 25 with respect to the plane perpendicular to the longitudinal axis of the burner.

13. The gas burner of claim 1, wherein the orifices have axes that are inclined at an angle substantially 15 with respect to the radius of the cylindrical body and passing through the orifice.

14. The gas burner of claim 1, wherein the gas burner is sized for a power of between 500 and 2000 kW.

15. The gas burner of claim 1, wherein the gas burner is used in furnaces, boilers, or dryers.

16. The gas burner of claim 15, wherein a speed of the primary air is 20 to 200 m/s at the annular slot.

17. The gas burner of claim 15, wherein a speed of introduction of lean gas in the gas burner is between 15 and 25 m/s.

18. A system, comprising: a biomass gasifier; and a gas burner for burning a gas having a low calorific value, the gas burner including a cylindrical body having: a first annular zone formed between an external wall thereof and an internal wall thereof, and which extends substantially parallel to the external wall, wherein the external wall has a base at an upstream distal end thereof; a second annular zone formed downstream of the first zone between the external wall and the internal wall, wherein the first annular zone is separated from the second annular zone by a partition; a first opening, formed in the base, to supply the gas, and which extends substantially parallel to a longitudinal axis of the cylindrical body; a second opening to supply primary air, and which is formed in the external wall in fluidic communication with the first annular zone; a third opening to supply secondary air, and which is formed in the external wall in fluidic communication with the second annular zone; an annular slot to introduce the primary air from the first annular zone into a combustion zone, the annular slot being formed between the external wall and an upstream end of the internal wall, and formed such that the primary air is supplied to the combustion zone in the form of a conical sheet of air, and creates a compression zone; and orifices formed in the internal wall to introduce the secondary air from the second annular zone into the combustion zone, and are disposed so as to allow swirling of the secondary air.

19. A gas burner, comprising: a gas burner body having: an external wall and an internal wall defining a combustion zone, wherein the external wall further has a base at an upstream distal end thereof; a partition extending from the external wall to the internal wall to define a first annular zone and a second annular zone formed downstream of the first zone; a first opening, formed in the base, to supply a gas to the combustion zone; a second opening formed in the external wall in fluidic communication with the first annular zone to supply primary air to the first annular zone; a third opening formed in the external wall in fluidic communication with the second annular zone to supply secondary air to the second annular zone; an annular slot formed between the external wall and an upstream end of the internal wall to introduce the primary air from the first annular zone into the combustion zone, the annular slot being formed to supply the primary air in the form of a conical sheet of air which forms a compression zone in the combustion zone; and orifices formed in the internal wall to introduce the secondary air from the second annular zone into the combustion zone, and are disposed to allow rotation and swirling of the secondary air.

Description

DRAWINGS

(1) FIGS. 1, 2 and 3 illustrate an embodiment of the burner according to the invention.

(2) FIG. 1 illustrates a front view of the burner according to the invention.

(3) FIG. 2 illustrates a view of the burner according to the invention in cross-section along the plane A-A in FIG. 1.

(4) FIG. 3 illustrates an enlarged view of detail B in FIG. 2.

DESCRIPTION

(5) The burner according to the invention was developed for the combustion of lean gas, and in particular synthesis gas (or syngas) issuing from the gasification of biomass.

(6) The burner according to the invention combines two air flows for staged combustion. Staged combustion consists of introducing either the combustion air or the fuel into the flame at different steps. During the staged combustion by staging of air, part of the combustion air, typically around 5% to 50%, is supplied to a primary combustion zone with the whole of the fuel. In this way a fuel-rich zone is obtained and the formation of nitrogen oxides is reduced. The rest of the air is injected further downstream, forming a secondary flame zone, where combustion is completed. In the burner according to the invention, the primary and secondary air flows are formed as follows:

(7) an axial primary air flow that makes it possible to attach the flame for any type of gaseous fuel: synthesis gas, natural gas and propane;

(8) a rotary secondary air flow that stabilises the flame without having recourse to supplementary equipment subject to fouling.

(9) Thus, the stability of the flame in the burner according to the invention is effective at all combustion rates by virtue of the combination of the axial and rotary modes of the primary and secondary oxidising air flows respectively.

(10) Furthermore, this combustion mode makes it possible to vary the relative contribution of the various fuels, in particular the synthesis gas, the natural gas and the propane, according to the power sought and the availability of said fuels. The burner may take a mixed supply of lean gas/fossil fuel in variable proportions from 100% lean gas to 100% fossil fuel.

(11) It is known that the quality of the combustion, measured in particular by the quality of unburnt residues and pollutants emitted, depends on the quality of the air/fuel mixture. More precisely, it is important to achieve an air/fuel mixture that is as uniform as possible in order to limit hot spots and thus minimise the formation of nitrogen oxides. Furthermore, the staged combustion used in the burner according to the invention also requires a rapid mixing of the fuel and air. Various devices are used in existing burners to improve the quality of the mixing, such as deflectors, fins, perforated plates or impact plates (impact plate means a screen placed perpendicular to the flow in its axial part). All these devices have the drawback of creating an obstacle to the flow and are consequently sensitive to fouling. One advantage of the burner according to the invention is that it affords an optimum air/fuel mixture while presenting no obstacle to flow. The quality of the mixing is ensured in particular by the particular form of the primary air flow. The annular slot has a form such that the primary air is supplied to the combustion zone in the form of a conical sheet of air taking over or entraining the flows of fuel (lean gas and fossil fuel).

(12) The burner according to the invention was designed to be able to burn mainly a lean gas and more particularly synthesis gas issuing from the gasification of biomass. However, in an advantageous embodiment, the burner according to the invention is also suitable for burning a traditional fuel such as natural gas, propane, or even domestic fuel oil. The burner according to the invention is therefore a mixed burner that can function either with synthesis gas, natural gas or propane or with a mixture of these various fuels (especially with a mixture of synthesis gas and fossil fuels). Furthermore, its particular design confers on it great flexibility of use, with possible change from functioning with 100% fossil fuel to functioning with 100% lean gas, in particular gas issuing from the conversion of biomass.

(13) At all combustion rates the quantity of oxidising air is adjusted to the mixture of fuels that is taken by the burner. Advantageously, this adjustment is achieved by virtue of a control means, such as an automatic controller which makes it possible to supply a flow of air calculated for each combustion rate and for each ratio between lean gas and fossil fuel, according to working points parameterised and stored in memory. In a particular embodiment, a lambda sensor also measures the oxygen content of the combustion fumes, which makes it possible to refine the adjustment of the flow of oxidising air. Preferably, the air flow rate is adjusted globally (total primary air and secondary air flow).

(14) Advantageously, the burner according to the invention is equipped with a pilot burner for flame lighting and safety. The pilot flame is obligatory in certain cases for safety reasons (EN 746-2).

(15) One embodiment of the burner according to the invention is described below in relation to FIGS. 1, 2 and 3. The burner according to the invention has a substantially cylindrical shape. It has an external wall 16, and an internal wall 17 separated from the wall 16 in order to form annular zones 5 and 8. These zones 5 and 8 are separated from each other by a partition 20. The first annular zone 5 is used for introducing primary air into the combustion zone 7. The second annular zone 8 is used for introducing secondary air into the combustion zone 7. The second annular zone 8 is used for introducing secondary air into the combustion zone 7.

(16) With reference to FIGS. 1 and 2, a pipe 1 enables lean gas to be introduced into the burner. Preferably, the pipe 1 introducing lean gas is cylindrical, and its diameter is calculated according to the quantity of lean gas to be accepted. The speed of introduction of lean gas into the burner is generally between 5 and 30 m/s, and preferable between 15 and 25 m/s.

(17) A pipe 2 enables fossil fuel (natural gas, propane or domestic fuel oil in particular) to be introduced. The pipe 2 introducing fossil fuel is preferably cylindrical. Its diameter is calculated according to the quantity of fuel gas to be accepted. The speed of introducing fossil fuel into the burner is between 5 and 30 m/s (preferably between 15 and 25 m/s). In the case of a liquid fuel (domestic fuel oil), this is atomised by a specific injector (not shown).

(18) A pipe 3 makes it possible to introduce primary air into the annular zone 5. The primary air introduced into the annular zone through the pipe 3 is then directed to an annular slot 6 which has a form such that it creates a conical sheet of air and a compression zone in the zone 7. It is this specific configuration of the burner according to the invention that affords a good mixing of the primary air with the fuel.

(19) The speed of the primary air is 20 to 200 m/s at the lip or annular slot 6. The flow of primary air takes place in laminar mode.

(20) Preferably, the air-introduction piece 14 has a flat upstream edge 19 perpendicular to the axis of the burner and substantially parallel to a flat surface of the external wall 16 of the burner, thus creating an air flow erected perpendicular to the axis of the burner. The profile of the air-introduction piece 14 takes over the air flow in order to direct it, without modification of its laminar mode, to a zone situated substantially on the axis of the burner.

(21) The conical sheet of air is intended mainly to produce a good air/fuel mixture, but it also protects the inner wall of burner, in particular in the case where the lean gas contains tars and particles.

(22) A pipe 4 enables secondary air to be introduced into the annular zone 8. The secondary air introduced into the annular zone 8 through the pipe 4 is directed to a set of injection orifices 9 for rotating and swirling the secondary air. The rotation of the secondary air makes it possible in particular to prevent detachment of the flame at high power. It also helps to avoid pulsing of the flame responsible for vibratory phenomena which otherwise could occur at certain powers and for certain air/fuel ratios.

(23) The orifices 9 are orifices with a cylindrical or oblong cross section. The orifices 9 for introducing secondary air pierced in the internal wall 17 of the burner preferably have a unit diameter of 3 to 15 mm, thus allowing the injection of secondary air at speeds of between 10 and 50 m/s and preferably between 20 and 40 m/s.

(24) Preferably, the internal wall 17 of the burner has a divergent conical form (i.e. broadening downstream) in its downstream part, at the secondary-air introduction zone. The orifices 9 are distributed in the conical part of the internal wall 17 of the burner. Preferably, the axes of the orifices 9 are inclined at angles of between 15 and 40, and preferably substantially equal to 25, with respect to the plane perpendicular to the axis of the burner. Preferably, the axes of the orifices 9 are also inclined at angles of between 10 and 25 and preferably substantially 15 with respect to the radius of the cylinder formed by the burner and passing through the orifice, so as to allow optimum swirling of the secondary air.

(25) The compression zone generally consists of a straight-line segment situated substantially on the axis of the burner.

(26) The compression zone is obtained by the flow of air in laminar mode, the path of which is straightened up by the profile of the lip (as a suction face). The straightened-up annular sheet of air forms a cone, the thickness of which increases as the vertex is approached.

(27) The passages 10, 11 and 12 depicted in FIG. 2 enable a conventional ignition member to be installed, such as an ionisation probe or a burner creating a pilot flame (not shown) or a flame detector. The passages 10, 11 and 12 may also serve to install one or more supplementary fossil-fuel inlets to enable the burner according to the invention to function with this type of fuel over a wide power range. These passages are not limited in number. Depending on the power of the burner, it is possible to imagine more passages for supplying fossil fuels, a pilot flame and/or a flame detector.

(28) Detail B in FIG. 1 is presented in detail in FIG. 3. It depicts a particular form of the annular slot 6 enabling primary air to be introduced into the combustion zone in the form of a conical sheet. The shape of the annular slot 6 depicted in FIG. 3 has been designed so as to minimise pressure drops.

(29) In the embodiment in FIG. 3, the annular slot 6 proper is formed by the space between a piece 14 referred to as the primary-air introduction piece in the burner, and the bottom of the external wall 16 of the burner. The primary-air introduction piece 14 is positioned at the upstream end 25 of the internal wall 17 of the burner. The primary-air introduction piece 14 is preferably formed in a single piece with the internal wall 17.

(30) The primary-air introduction piece 14 has a conical part 15 diverging from downstream to upstream forming with the internal wall 17 of the burner an angle , the conical part 15 creating a sheet of air. The angle is between 20 and 45. The conical part 15 prevents a significant recirculation of air in the annular zone and thus limits the pressure drop. The conical part 15 is followed by a rounded part 18 with a radius of curvature r1, preferably lying between 3 and 15 mm. The rounded part 18 also limits the recirculations of air in the annular zone 5. In addition, sharp corners interfere with the circulation of air through the creation of turbulence micro-zones that increase the pressure drop, and this is why it is preferred to use a rounded part 18 rather than a right angle.

(31) The rounded part 18 is itself followed by a flat upstream edge 19 substantially parallel to the bottom of the external wall 16 of the burner. This flat upstream edge is next followed by a part 13 having a so-called suction face form that directs the layer of air in the required profile, in order to constitute a compression zone on the axis of the burner. The suction face part 13 consists of a first part 21 rounded at a radius of curvature r2, preferably between 8 and 30 mm, followed by a second part consisting of three successive flat profiles 22, 23, 24 forming respective angles 1, 2 and 3 with the plane of the flat upstream edge 19, the angles 1, 2 and 3 preferably respectively aligned between 30 and 80. These successive flat profiles gradually increase the radius of the suction face, so as to obtain a detachment of the stream of air at the end of the lip profile, or air-introduction piece 14. The angle 3 is greater than the angle 2, which is greater than the angle 1.

(32) The burner according to the invention, in association with a gasifier and in particular in association with a biomass gasifier, allows total or partial replacement of a fossil fuel (fuel oil, natural gas, propane) by solid biomass for the production of heat. The fuels that can be used by way of biomass comprise in particular woodchips, ground pallets, wood granules and agricultural by-products.

(33) The co-current fixed-bed gasifier described in the patent application WO 2013/098525 in the name of Cogebio is particular suitable for functioning in association with the burner according to the invention. This co-current fixed-bed gasifier comprises a reactor body, said reactor body comprising a top part and a bottom part, and the biomass is introduced through an inlet pipe situated in the top of the top part of the gasifier body, the synthesis gas is discharged through a synthesis-gas discharge pipe, and the ashes are discharged in the lower part of the bottom part of the reactor body through an ash discharge pipe; said gasifier comprises, from top to bottom: a biomass pyrolysis zone, a biomass oxidation zone, a reduction zone and a grille comprising a plurality of openings through which the ash passes in order to be discharged, and said gasifier also comprises means for introducing a gasification agent, such as air or oxygen, and said gasifier being characterised in that said means for introducing the gasification agent comprise: a gasification agent diffusion cone situated at the top of the oxidation zone of the gasifier and above said oxidation zone, and gasification agent injection means situated in the oxidation zone of the gasifier.

(34) Furthermore, the majority of industrial burners integrated in furnaces, boilers or dryers can be replaced by a burner according to the invention in a power range from 500 to 2000 kW.

LIST OF REFERENCE NUMERALS

(35) 1 Pipe for introducing lean gas 2 Pipe for introducing fossil fuel 3 Primary-air inlet pipe 4 Secondary-air inlet pipe 5 Annular zone for the primary air 6 Slot 7 Combustion chamber 8 Annular zone for the secondary air 9 Secondary-air injection orifices 10,11,12 Additional passages allowing the implantation of an ignition member or a fossil-fuel inlet 13 Suction-face form of the slot 6 (primary-air inlet to the burner) 14 Primary-air introduction piece 15 Conical part of the piece 16 Cylindrical external wall of the burner 17 Internal wall of the burner 18 Rounded part according to a radius of curvature r1 of the piece 14 19 Flat upstream edge of the piece 14 (forming the annular slot in cooperation with the wall 16) 20 Separation between the primary-air inlet 5 and secondary air 8 zones 21 Part rounded according to r2 22,23,24 Successive flat profiles forming a respective angle 1, 2, 3 with the part 19 25 Upstream end of the internal wall 17 26 Base of the cylinder formed by the external wall