EP1828679A1

EP1828679A1 - Combustion method with cyclic supply of oxidant

Info

Publication number: EP1828679A1
Application number: EP05824047A
Authority: EP
Inventors: Rémi Tsiava; Benoit Grand; Patrick Recourt; Bertrand Leroux
Original assignee: Air Liquide SA; LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Current assignee: Air Liquide SA; LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Priority date: 2004-12-13
Filing date: 2005-12-05
Publication date: 2007-09-05
Anticipated expiration: 2025-12-05
Also published as: DE602005006321D1; US20090239182A1; DE602005006321T2; WO2006064144A1; ATE393359T1; JP4913747B2; US8231380B2; EP1828679B1; FR2879283B1; FR2879283A1; JP2008523346A

Abstract

The invention concerns a combustion method for industrial furnace comprising an arrangement of two substantially parallel and symmetrical burner assemblies (G, D). Each burner assembly comprises a fuel injector (10G, 10D) and three oxidant injectors (1G, 2G, 3G, 1D, 2D, 3D) arranged at increasing distances from the fuel injector. An oxidant supply system cyclically distributes a specific flow of oxidant among some at least of the second and third injectors of the burner assemblies (2G, 3G, 2D, 3D). The amount of nitrogen monoxide produced upon combustion is thus reduced, while ensuring a good distribution of the heating power in the furnace.

Description

Combustion process with cyclic feed of the oxidant.

The present invention relates to a combustion process for an industrial furnace. It also relates to an oven adapted to implement such a method.

The distribution of the heating power over a given furnace surface, the reduction of the quantity of nitrogen oxides produced and the stability of the combustion flame (s) generated in the furnace are among the principal stakes in the technology of combustion furnaces.

Indeed, the energy efficiency and the profitability of an industrial combustion furnace are higher for furnaces of great capacity. This is why the surface to be heated can be large. This is usually the top surface of a feed of raw materials or melt contained in a tank. It is then difficult to distribute the heating power delivered by the flame (s) of combustion in a substantially uniform manner over the entire surface, so as to avoid the formation of colder zones which would be harmful vis-à- screw of the melt or the subsequent process of treating it. For this, it is known to have several burners in an oven at specific locations above the tank. In particular, two burners can be arranged parallel to one another, with respective horizontal flames and directed in the same direction. Another possibility is to have the burners facing each other in pairs, with respective flames directed toward each other within each pair.

Furthermore, the amount of nitrogen oxides (NO _x) produced in a combustion flame depends on the local concentrations of oxygen and nitrogen, denoted [O _2] and [N _2]. In particular, an evaluation of the quantity of thermally produced nitric oxide (denoted [NO] _th ) is given by the following formula:

where k is a numerical constant, exp is the exponential function, E _a is a positive activation energy, R is the ideal gas constant and T is the local temperature.

In order to reduce the amount of thermal nitric oxide, it is known to use an oxidizer substantially free of nitrogen. Thus, an oxygen-enriched oxidant is used instead of air. Nevertheless, the resulting reduction of nitrogen oxides is insufficient compared to the regulations in force. To further reduce the amount of nitrogen oxides produced, it is also known, particularly according to US Pat. No. 5,522,721 and EP 0 524 880, to vary cyclically the oxidant flow rate and / or the fuel flow rate that feed the flame. The ratio between the instantaneous local concentrations of oxygen and fuel in the flame is then different from the stoichiometry of the combustion reaction. The local temperature is therefore lower, and, according to relation (1), a further reduction in the amount of thermally produced nitric oxide results therefrom. But the flow rate variation parameters, such as the amplitude, the frequency and the phase of the variations of each flow, are difficult to adjust to obtain a satisfactory heating efficiency and a low release of carbon monoxide (CO). Indeed, carbon monoxide is toxic and polluting, and comes from incomplete combustion when the instantaneous local concentration of oxygen in the mixture is too low compared to the instantaneous local concentration of fuel.

Another way to achieve further reduction in the amount of nitrogen oxides produced is to inject a major portion of the oxidant and the fuel at two locations in the furnace separated from each other by a relatively large distance. A combustion performed under these conditions is called "staged" (see for example EP 0 748 981). A small portion of the oxidant is further injected near the fuel outlet to stabilize the combustion regime. The main part of the oxidant and the fuel are then gradually mixed in a spread volume where the jets overlap. In this way, a gap effect is still obtained between the ratio of the local concentrations of fuel and oxidizer on the one hand, and the stoichiometry of the combustion reaction on the other hand. In addition, this stoichiometric difference effect is superimposed on a dilution effect. The local temperature, and therefore the amount of nitric oxide, are thus also reduced. But in this staged combustion configuration, the position of the flame in the vertical direction is particularly unstable. The heating efficiency of the fired material is then reduced and vault refractories can be damaged.

An object of the present invention is therefore to provide a combustion process which does not have the disadvantages mentioned above, or for which these disadvantages are reduced. Thus, the invention proposes a combustion process for an industrial furnace according to which two burner assemblies are arranged substantially horizontally, parallel to one another and symmetrically with respect to a median plane passing between the two assemblies. Each burner assembly comprises: - a fuel injector; first, second and third oxidizer injectors respectively arranged at increasing distances from the fuel injector.

An oxidizer feed system cyclically distributes a determined flow rate of oxidizing between at least the second and third injectors of the two burner units.

Since the burner assemblies are substantially horizontal, the flame produced in the furnace is itself contained in a horizontal plane. In this way, the heat generated by the flame is efficiently transferred to the furnace charge without excessively heating a vault structure disposed above the furnace at a particular location thereof. Premature wear of the arch structure is thus avoided.

The oxidant is thus introduced into the oven at three points for each of the two burner units. The first point of introduction of the oxidant is constituted by the first injector, which is the closest to the corresponding fuel injector. It allows to generate a first incomplete combustion of the fuel, which is then completed by the oxidant introduced by the second and third injectors. The first injector also generally stabilizes the combustion regime at its output. For each burner assembly, the third point of introduction of the oxidant is the farthest from the fuel injector, and the second oxidizer injector is located at a distance from the intermediate fuel injector between the distances of the first and third injectors .

The oxidant preferably has an oxygen content greater than 30% by volume, and even greater than 70% by volume. The total flow rate of oxidant introduced into the furnace is distributed between the first, second and third injectors of the two burner units. A determined part of this total flow is injected by the second and third oxidizer injectors, with a distribution between at least some of these which is variable cyclically. The determined part of the total flow rate of oxidant which is injected by the two second and the two third oxidizer injectors is substantially constant. It may possibly vary, but much more slowly than those of the individual flows of the second and / or third oxidizer injectors which are variable. Thus, a specific fraction of the oxidant is injected into the furnace by some of the second and / or third injectors at a given instant, then is injected by the other second and / or third injectors at a later time. The oxidant injection obtained by a device according to the invention is therefore alternated between some of said second and / or third injectors.

The cyclic distribution of the oxidant flow rate between some of the second and third injectors of the two burner units is preferably carried out at a frequency of less than 1 hertz. The oscillation period of the flame in the oven is then greater than 1 second. The inventors have observed that such conditions provide a particularly stable combustion. - AT -

In the staged combustion that is obtained, the fuel and the oxidant that are introduced into the furnace are diluted by recirculation of the exhaust gas in the combustion zone. For this, a main part of the oxidant is introduced into the furnace at a great distance from the fuel introduction locations. By thus delaying the mixing between the fuel and the oxidant, the oxidant is strongly diluted with ambient gases present in the furnace before entering the main combustion zone. However, to stabilize the flame, it is necessary to also introduce oxidant into the furnace near each fuel introduction location. The part of oxidant that is introduced near the fuel is called primary flow, and that which is introduced at a distance from the fuel is called secondary flow.

Advantageously, the oxidizer supply system feeds the first injectors respectively of each burner assembly with respective primary oxidant flow rates at each instant. Each burner assembly generates a flame in the furnace, but when the two burner units are not too far apart, their respective flames are united and form a single combustion volume. Such a single flame is obtained, in particular, when the distance between the respective fuel injectors of the two burner units is less than 30 times the diameter of each fuel injector. In the following, generally denote by flame the total volume in which combustion occurs, it being understood that this volume can be divided into two parts for a significant separation distance between the two burner units.

The cyclic variations in the distribution of the oxidant flow between at least some of the second and third injectors cause a horizontal displacement of the flame in the furnace. Depending on the separation distance between the two burner units and on the shape of the variation curves of the oxidant flow rates of the second and third injectors, the displacement of the flame consists of a flapping thereof between two positions or in an oscillation of the flame between two configurations. In general, the cyclic variations of the distribution of the gases in the furnace improve the stability of the flame, especially in the vertical direction, by moving the flame alternately in a substantially horizontal direction.

Finally, the displacement of the flame contributes to further improving the distribution of the heating power throughout the volume of the furnace: a heat transfer to the load of the furnace is obtained, which is more uniform thanks to an effect of average in the time of the thermal contributions taking place at each point of the furnace.

The invention also provides an oven adapted to implement a method as described above. Other features and advantages of the present invention will emerge in the following description of two nonlimiting exemplary embodiments, with reference to the appended drawings, in which:

- Figure 1 illustrates the configuration of an oven adapted to implement the invention; FIG. 2a is a variation diagram of the oxidizer flow rates of the first, second and third injectors of an oven according to FIG. 1, according to a first embodiment of the invention;

FIG. 2b illustrates two configurations of the flame obtained at different times for the flow rate variations shown in FIG. 2a; FIGS. 3a and 3b respectively correspond to FIGS. 2a and 2b for a second mode of implementation of the invention; and

FIG. 4 illustrates different flame configurations corresponding to improvements in the second embodiment of the invention.

For the sake of clarity of the figures, the dimensions of the devices shown are not in proportion with real dimensions. In particular, dimensions measured in these figures which are associated with distinct real directions are not transposed according to the same scale ratio.

Figure 1 shows a vertical wall 101 of a furnace 100, for example a melting furnace of raw materials. The furnace 100 may be batch-operated, with separate stages of loading, heating and discharging of the furnace, or continuous operation, with permanent flows of raw material loading and melt output. F denotes the trace of the free surface of material charged to the wall 101 of the oven.

The fuel and oxidizer injectors are disposed on the wall 101, with respective directions of fluid outlet substantially horizontal. They are aligned on a horizontal line located at a height h above the trace F. h is preferably between 250 mm (millimeters) and 550 mm.

The wall 101 is divided by a median vertical plane P in two parts, respectively left, denoted G, and right, denoted D. Injectors are located symmetrically on the two wall portions, as follows:

two fuel injectors, referenced 10 _G and 10 _D , are respectively disposed on the wall portions G and D, at the same distance di ₀ from the median plane P, measured horizontally;

three oxidizer injectors, referenced 1 _G , 2 _G and 3 _G , are aligned in the wall portion G, respectively at distances di, d ₂ and d ₃ of the median plane P. The distances of the injectors from the wall portion G at the median plane P satisfy, for example, the following relation: di <di ₀ <d ₂ <d ₃ . Injectors 10 _G , 1 _G , 2 _G and 3 _G are generally located on the same horizontal line; and

three injectors of oxidant _1D , _2D and _3D respectively identical to the injectors _1G , _2G and _3G and arranged symmetrically to these on the wall part D.

The injectors 10 _G , 1 _G , 2 _G and 3 _G form a first burner assembly, associated with the left part of the wall 101. For simplicity, this burner assembly is designated G in the following. Similarly, the injectors _10D , _1D , _2D and _3D form a second burner assembly, designated D and associated with the right portion of the wall 101.

The fuel introduced into the furnace 100 by the injectors _10G and _10D can be gaseous or liquid. In the case of a liquid fuel, the injectors 10 and _G 10 _D each incorporate a spray nozzle so as to produce jets of fuel droplets.

Preferably, the distance di ₀ between the fuel injector of each burner assembly, 10 _G or 10 _D , and the median plane P is less than 15 times the diameter of each injector 10 _G or 10 _D , noted Φi ₀ . Under these conditions, a single flame common to the two burner units G and D is generated in the furnace 100. The oxidant introduced by the injectors _1G , _2G , _3G , _1D , _2D and _3D is a gas having usually an oxygen content greater than 70% by volume.

Preferably, the third oxidizer injector of each burner assembly is located at a distance from the fuel injector of said assembly at least ten times greater than the output diameter of the third injector. In other words: d ₃ -di ₀ > 10. Φ ₃ , where Φ ₃ denotes the outlet diameter of injectors 3 _G and 3 _D. Thus, the oxidant jet of the injector 3 _G , respectively 3 _D , is sufficiently spaced from the fuel jet of the injector 10 _G , respectively 10 _D , to obtain a staged combustion.

All the injectors of each burner assembly are directed substantially horizontally, so that the flame produced is parallel to the surface of the melt bath contained in the furnace 100.

Advantageously, the oxidizer supply system supplies each of the first injectors respectively of each burner assembly, that is to say the injectors _1G and _1D , with a respective primary flow of constant oxidant. The oxidizer feed system is then simplified, as regards the feeding of injectors _1G and _1D . Preferably, the respective flow rates of the two injectors _1G and _1D are substantially equal: X _G = X _DJ designating by x _G and x _D the respective flow rates of the injectors _1G and _1D . By way of example, x _G and x _D each correspond to 10% of the total flow rate of oxidant injected into each burner assembly.

According to a first mode of implementation of the invention, described with reference to FIGS. 2a and 2b, the oxidizer flow rates of two injectors arranged symmetrically with respect to the median plane P are equal at each instant. Denoting by y _G, V _D, and z _D ZQ respective instantaneous flow rates of the injectors 2 _G, 2 _D, 3 _G and 3 _D, the following relationships are satisfied: y _G = Y _D and z _G = z _D. In other words, the oxidizer supply system feeds the second injectors respectively of each burner assembly with respective secondary flows of oxidant substantially equal at each instant, and feeds the third injectors respectively of each burner assembly with respective tertiary flows of oxidant substantially equal every moment. For example, the supply system of injectors _2G , _2D , _3G and _3D may comprise two identical distribution boxes respectively assigned to each burner assembly G and D. These distribution boxes are coupled to a common control member variable, and each box has a movable partition wall of oxidant flows directed respectively to the second or the third injector.

The flame obtained is then centered on the median plane P and is symmetrical with respect thereto at each instant.

FIG. 2a illustrates an example of variation of the rates y _G and y _D on the one hand, and the rates z _G and z _D on the other hand. The abscissa axis represents the time, indicated in seconds, and the ordinate axis represents the fraction of the oxidizer flow rate of each burner assembly that is introduced by each injector thereof. It is assumed that the total oxidant flow rate of each burner assembly G or D is constant, and that x _G and x _D are also constant and are each equal to 10% of the flow rate of the corresponding burner assembly.

For example, y _G and y _D vary substantially sinusoidally between 10% and 50%, and z _G and z _D vary between 40% and 80%. The period of these variations is 2 seconds. The extreme configurations of the flame then correspond to the following states:

- state 1, where y _G = y _D = 10% and z _G = z _D = 80%,

state 2, where y _G = y _D = 50% and Z ₆ = z _D = 40%.

The mixing volume is greater in state 1 than in state 2. According to FIG. 2b, which represents the periphery 200 of the flame in a horizontal plane passing through the injectors, state 1 corresponds to a flame extended, both in width and in length, and state 2 corresponds to a narrower and shorter flame. For the sake of clarity, the flow rate introduced into the furnace by each oxidizer injector is indicated in FIG. 2b. In the state

1, the fuel and the oxidant are more diluted within the flame. The temperature is then lower, but a better coverage of the entire surface of the material is obtained. The heat transfer of the flame to the furnace charge is then particularly homogeneous. Conversely, the flame is more concentrated and intense in state 2.

A second mode of implementation is now described in relation to the figures

3a and 3b. This second mode corresponds to an alternating oxidant feed between the two burner units. More particularly, the oxidizer feed system cyclically distributes a determined tertiary total flow of oxidant between said third injectors of the two burner units. The oxidizer supply system can further supply each of the second injectors respectively of each burner assembly with a respective secondary flow of constant oxidant. A particularly simple implementation of the alternate supply of oxidant is thus obtained. In addition, the secondary flows of oxidant may be substantially equal.

The furnace and the burner units used above for the first mode of implementation of the invention can be resumed without modification for operation with alternating supply of oxidant. With the same notations and references, we now have: X _G = X _D = x / 2 and Y _G = Y _D = y / 2, where x denotes the total flow rate of the oxidant introduced into the furnace 100 by the injectors _1G and 1 _D , and y denotes the total oxidant flow introduced by injectors _2G and _2D . x and y are respectively called primary and secondary total flows of the oxidant. Likewise, the tertiary total oxidant flow rate, that is to say the oxidant flow rate introduced by the injectors 3 _G and 3 _D , is noted. By way of example, x = 10%, y = 15% and z = 75%, expressed in percentages of the total flow rate of oxidant introduced into the oven. In general, x and y are substantially constant or vary much more slowly than the individual cyclically varying flow rates of injectors.

The oxidizer feed system may be a distribution box connected to the injectors 3 _G and 3 _D , which has a movable partition wall disposed between the oxidant flows directed respectively to the injectors 3 _G and 3 _D. FIG. 3a illustrates such an operation, according to which the relation z _G + z _D = z is satisfied at each instant. The ordinate axis of FIG. 3b is expressed as a percentage of the total oxidant flow introduced into the furnace, that is to say x + y + z. Z ₆ and z _D each vary between 10% and 65%. The period of flow variations is still 2 seconds.

The extreme configurations of the flame now correspond to the following states:

- state 1, in which z _G = 65% and z _D = 10%,

state 2, in which z _D = 10% and Z ₆ = 65%.

The mixing volume and the flame have symmetrical configurations between the preceding states 1 and 2 (FIG. 3b). In each of these states, the flame is moved to the side of the 3 _G OR 3 _D injector having the largest oxidant flow rate. Thus, the flame is moved to the left side in state 1, and to the right side in state 2. This lateral reciprocation of the flame stabilizes the height thereof, so that the flame remains at a substantially constant distance from the free surface of material charged on the one hand, and at a substantially constant distance from the vault of the oven on the other hand. These two distances can then be well controlled, which makes it possible to obtain a regular melting process and a slowing down of the refractory degradation of the vault.

In addition, the lateral back and forth of the flame provides a sufficient heat transfer uniformly between the flame and the furnace charge in a horizontal direction parallel to the wall 101.

Because of the velocity of the oxidant at the outlet of the injectors 3 _G and 3 _D , the flame is longer on the side of the injector 3 _G or 3 _D having the instantaneous flow rate of the highest oxidant. A good average coverage of the furnace surface by the flame results. For example, the oxidant is expelled by injectors 3 _G and 3 _D with a speed of between 20 m. s ^"1 (meter per second) and 160 m.s.sup.- ¹ , for example 90 m. s ^"1. In general, the average distance of mixture of fuel and oxidant, as well as the average distance at which combustion occurs, identified from the wall 101 of the furnace, are all larger than the speed expulsion of the oxidant by injectors 3 _G and 3 _D is high.

In addition, at each alternation, the high flow of oxidant introduced by one of the two injectors 3 _G OR 3 _D causes a significant dilution of the fuel on the side of the median plane P which corresponds to this injector. Conversely, the fuel is more concentrated in a zone of the flame offset from the median plane P on the side of the injector 3 _G OR 3 _D which has the instantaneous flow rate of the weakest oxidant. This zone is denoted by A in FIG. 3b, for the flame edges 200 corresponding to each of the two states 1 and 2. The zone A therefore moves at each alternation between two symmetrical positions situated on either side of the median plane P. Since the flame is richer in fuel in zone A, a larger amount of soot is produced there. At the same time, zone A corresponds to the part of the flame that contributes the most to the heat transfer to the load at every moment.

The existence of such a zone A inside the flame may be favorable or harmful to the material that is being melted, in particular as a function of the chemical behavior of this material when the temperature is not uniform. According to an improvement of the second mode of implementation of the invention, it is possible to mitigate or exacerbate the presence of such a zone A by varying the fuel flow of the injectors _10G and _10D at each alternation. For this, a fuel supply system can cyclically distribute a determined total flow of fuel between the fuel injectors of the two burner units.

Advantageously, the fuel supply system is coupled to the oxidizer supply system so that the total fuel flow is cyclically distributed between the fuel injectors of the two burner assemblies in phase or in phase opposition with respect to the distribution. cyclic tertiary total flow of oxidizer between the third injectors of the two burner units.

For example, another distribution box may be disposed at the inlet of injectors _10G and _10D . This other distribution box has a movable separation wall arranged between the fuel flows directed respectively to the injectors _10G and _10D .

The two distribution boxes, connected to the injectors 3 _G and 3 _D for the first, and the injectors 10 _G and 10 _D for the second, can then be controlled synchronously in opposition of phase: the fuel flow rate sent into the one of the two injectors 10 _G or 10 _D is maximum or minimum at the same time that the flow of oxidizer sent into the injector 3 _D or 3 _G on the opposite side is also maximum or minimum. A reinforcement of the zone A is thus obtained, which causes an increase in the brightness of the flame near the exit of the fuel injector _10G or _10D when the fuel flow therein is maximum. The fuel concentration is depleted on the side of the 3 _G or 3 _D injector for which the oxidizer flow rate is maximum. This increased depletion causes a shortening of the flame to its furthest point of the injectors.

Conversely, the two distribution boxes can be controlled synchronously in phase. The flow rate of fuel sent into one of the two injectors 10 _G or 10 _D is then maximum or minimum at the same time as the oxidizer flow rate sent into the injector 3 _G or 3 _D of the same side is also maximum or minimum. Zone A is then blurred and can be confused with the entire extent of the flame. It then oscillates between the two left and right sides with a greater amplitude of transverse displacement. At the same time, the flame is lengthened so that the two effects are combined to obtain an optimal scanning of the entire furnace surface by the flame. This results in an average heat transfer area with a particularly large load.

The flame edges obtained when the fuel flow distribution varies with the distribution of the oxidizer flow rates are shown in Figure 4. The traces 200a and 200b respectively correspond to in-phase and in-phase variations. The trace 200 corresponds to a constant distribution of the fuel flow, and balanced between the two injectors 10 _G and 10 _D. It is represented in dotted lines for comparison. The traces 200, 200a and 200b all correspond to the total flows of fuel and oxidant identical. For the sake of clarity in Figure 4, only the contour of the flame in state 1 defined above is shown for each case. It is understood that many modifications and adaptations of the invention can be introduced with respect to the modes of implementation which have been described in detail. Such modifications or adaptations may in particular take into account particular characteristics, in particular geometrical characteristics, of the furnace in which the invention is implemented. In addition, the rate of variation of the oxidizer flow rates can be adjusted in a manner known to those skilled in the art, in particular to obtain a maximum burn rate and to reduce the amount of carbon monoxide produced.

Claims

A combustion method in which two burner assemblies (G, D) are arranged substantially horizontally, parallel to each other and symmetrically with respect to a median plane (P) passing between the two assemblies, each burner assembly comprising:

a fuel injector (10 _G , 10 _D );

first (1 _G , 1 _D ), second (2 _G , 2 _D ) and third (3 _G , 3 _D ) oxidizer injectors respectively arranged at increasing distances from the fuel injector

and according to which an oxidizer feed system cyclically distributes a determined flow of oxidant between at least some of the second and third injectors of the two burner units (2 _G , 2 _D , 3 _G , 3 _D ).

2. Method according to claim 1, wherein the cyclic distribution of oxidant flow between some of the second and third injectors of the two burner units (2 _G , 2 _D , 3 _G , 3 _D ) is performed at a frequency less than 1 Hz .

3. The method of claim 1 or 2, wherein a distance between the respective fuel injectors of the two burner units (10 _G , 10 _D ) is less than 30 times the diameter of each fuel injector (Φi ₀ ).

4. Process according to any one of claims 1 to 3, wherein the oxidant has an oxygen content greater than 30% by volume.

5. A method according to any one of claims 1 to 4, wherein the third oxidizer injector of each burner assembly (3 _G , 3 _D ) is located at a distance from the fuel injector of said burner assembly (10 _G , _D ) at least ten times greater than the outlet diameter of said third injector (Φ ₃ ).

6. Method according to any one of claims 1 to 5, wherein the oxidizer supply system feeds each of the first injectors of each burner assembly (1 _G , 1 _D ) with a respective primary flow rate of oxidant (x _G , x _D ) constant.

7. Method according to any one of claims 1 to 6, wherein the oxidizer supply system feeds the first injectors respectively of each burner assembly (1 _G , 1 _D ) with respective primary oxidant flow rates (x _G , X _D ) substantially equal at each instant.

8. A method according to any one of claims 1 to 7, wherein the oxidizer supply system feeds the second injectors respectively of each burner assembly (2 _G , 2 _D ) with respective secondary flow rates of oxidant (y _G , V _D ) substantially equal at each instant, and feeds the third injectors respectively of each burner assembly (3 _G , 3 _D ) with respective tertiary flows of oxidizer (z _G , z _D ) substantially equal at each moment.

9. A method according to any one of claims 1 to 7, wherein the oxidizer feed system cyclically distributes a tertiary total flow rate determined oxidant between the third injectors of the two burner units (3 _G , 3 _D ).

10. The method of claim 9, wherein the oxidizer supply system feeds each of the second injectors respectively of each burner assembly (2 _G , 2 _D ) with a constant secondary flow rate of oxidant (y _G , y _D ).

11. The method of claim 9 or 10, wherein a fuel supply system cyclically distributes a determined total flow of fuel between the fuel injectors of the two burner units (10 _G , 10 _D ).

12. The method of claim 11, wherein the fuel supply system is coupled to the oxidizer supply system so that the total fuel flow is cyclically distributed between the fuel injectors of the two burner units (10 _G , 10 _D ) in phase or in phase opposition with respect to the cyclic distribution of tertiary total oxidant flow between the third injectors of the two burner units (3 _G , 3 _D ).