EP1436546B1 - Burner for synthesis gas - Google Patents

Description

Technical application

The present invention relates to a burner for operation in a combustion chamber, preferably in combustion chambers of gas turbines, consisting essentially of a swirl generator for a combustion air flow and means for introducing fuel into the combustion air flow, the swirl generator having combustion air inlet openings for the combustion air flow entering the burner and the means for introducing fuel into the combustion air stream comprises one or more fuel feeds having a group of first fuel outlets disposed distributed about the burner axis at a combustion chamber end of the burner.

A preferred application for such a burner is in gas and steam turbine technology.

State of the art

From the EP 0 321 809 B1 is a consisting of several shells conical burner, a so-called. Double cone burner, according to the preamble of claim 1 known. By means of the conical swirl generator composed of several shells, a closed swirl flow is generated in a swirl space, which becomes unstable due to the increasing swirl in the direction of the combustion chamber and merges into an annular swirl flow with backflow in the core. The shells of the swirl generator are such composed that tangential air inlet slots for combustion air are formed along the burner axis. Feeds for the premix gas, ie the gaseous fuel, are provided at the inflow edge of the conical shells at these air inlet slots, which have outlet openings for the premix gas distributed along the direction of the burner axis. The gas is injected through the outlet openings or bores transversely to the air inlet gap. This injection, in conjunction with the swirl generated in the swirl space of the combustion air-fuel gas flow to a good mixing of the fuel or premixed gas with the combustion air. Good mixing in these premix burners is the prerequisite for low NO _x values during the combustion process.

To further improve such a burner is from the EP 0 780 629 A2 a burner for a heat generator known, which has an additional mixing section for further mixing of fuel and combustion air following the swirl generator. This mixing section may, for example, be designed as a downstream piece of pipe, into which the flow emerging from the swirl generator is transferred without appreciable flow losses. Through the additional mixing section, the degree of mixing can be further increased and thus the pollutant emissions can be reduced.

The WO 93/17279 shows another known premix burner, in which a cylindrical swirl generator used with a conical inner body becomes. In this burner, the premix gas is also injected via feeders with corresponding outlet openings in the swirl space, which are arranged along the axially extending air inlet slots. The burner has in the conical inner body in addition to a central supply of fuel gas, which can be injected near the burner outlet for piloting into the swirl space. The additional pilot stage is used to start the burner and an extension of the operating range.

From the EP 1 070 915 A1 a premix burner is known in which the fuel gas supply is mechanically decoupled from the swirl generator. As a result, voltages are avoided due to thermal expansions when using not or only slightly preheated fuel gases. The swirl generator is in this case provided with a series of openings through which the swirl generator mechanically decoupled fuel lines for the gas pre-mixing into the interior of the swirl generator protrude and there supply the vaporized flow of combustion air gaseous fuel.

These known premix burners of the prior art are so-called spin-stabilized premix burners in which a fuel mass flow prior to combustion is distributed as homogeneously as possible in a mass flow of combustion air. The combustion air flows in these burner types via tangential air inlet slots in the swirl generators. The fuel, especially natural gas, is typically injected along the air inlet slots.

In gas turbines, in addition to natural gas and liquid fuel, usually diesel oil or Oil # 2, also synthetically produced gases, so-called. Mbtu and Lbtu gases, lately used for combustion. These synthesis gases are produced by the gasification of coal or oil residues. They are characterized by the fact that they mainly consist of H ₂ and CO. In addition, there is a lower proportion of inerts, such as N ₂ or CO ₂ .

In the combustion of synthesis gas can not be maintained due to a high Rückzündgefahr proven for natural gas in the burners of the prior art injection.

Thus, in contrast to the use of natural gas, the following peculiarities and requirements arise for a burner which is to be operated with synthesis gas. Synthesis gas requires depending on a known in the art of known dilution of the synthesis gas about four times - in the case of undiluted synthesis gas to seven times or even higher - higher fuel volume flow compared to comparable natural gas burners, so that at the same Gasbelochung the burner significantly different Give impulse ratios. Due to the high proportion of hydrogen in the synthesis gas and the associated low ignition temperature and high flame velocity of the hydrogen, there is a high propensity to react with the fuel, so that in particular the Rückzündverhalten and the residence time of flammable fuel-air mixture must be examined near the burner. Furthermore, a stable and safe combustion of synthesis gases for a Depending on the process quality of the gasification and starting product, for example. Oil residues, the synthesis gas is composed differently. In order to achieve a premix and thus the typical low emissions during combustion under these conditions, these synthesis gases are usually diluted with the inert N ₂ or steam before combustion. This also improves the stability of the combustion and in particular reduces the inherent risk of re-ignition due to the high H ₂ content. The burner must thus be able to safely and stably burn syngas of different composition, in particular different dilution.

Furthermore, it is advantageous if, in addition to the synthesis gas from the burner and a reserve fuel, a so-called. Backup fuel can be safely burned. This requirement results (IGCC, I ntegrated G asification C ombined ycle- C) at the highly complex integrated Gassynthetisierungs- and power generation equipment from the demand for high availability. In such a case, the burner should function safely and reliably also in the mixed operation of synthesis gas and backup fuel, for example diesel oil, whereby the fuel mixture spectrum usable for burner operation in the mixed operation of a single burner must be maximized. Of course, low emissions (NO _x ≤ 25 vppm, CO ≤ 5 vppm) should be ensured for the specified and used fuels.

From the EP 0610 722 A1 a double-cone burner is known, in which a group of fuel outlet openings for a synthesis gas at a combustion chamber-side end of the burner are arranged distributed around the burner axis on the swirl generator. These outlet openings are supplied via a separate fuel line and allow the operation of the burner with undiluted synthesis gas.

Based on this prior art, the object of the present invention is to provide a burner that ensures safe and stable combustion both for undiluted and for diluted synthesis gas and has a long service life. The burner should in particular meet the requirements mentioned above and, in preferred developments, enable operation with a plurality of fuel types, even in mixed operation.

Presentation of the invention

The object is achieved with the burner according to claim 1. Advantageous embodiments of the burner are the subject of the dependent claims.

The present burner consists in a known manner of a swirl generator for a combustion air flow and means for introducing fuel into the combustion air stream. The swirl generator has combustion air inlet openings for the preferably tangentially entering the burner combustion air flow. The means for introducing fuel into the combustion air stream comprise one or more first fuel feeds with a group of first fuel outlet openings, which is arranged distributed at a combustion chamber end of the burner, ie at the burner outlet, around the burner axis. The present burner is characterized in that the one or more first fuel feeds with the group of first fuel discharge openings are mechanically decoupled from the swirl generator.

The geometry of the swirl generator as well as an optionally existing swirl space can be selected in various ways in the present burner and in particular have the geometries known from the prior art. Due to the distribution of the first fuel outlet openings exclusively at the combustion chamber end of the burner or swirl space around the burner axis, a reignition of the synthesis gas is reliably prevented. However, mixing with the combustion air leaving the burner is ensured. Synthesis gas with high hydrogen content (45 vol%) can be burned undiluted (Hu = 14000 kJ / kg). The burner thus enables safe and stable combustion of both undiluted and dilute syngas. This guarantees a high degree of flexibility when using a gas turbine equipped with burners according to the invention in an IGCC process. By a correspondingly adapted in cross-sectional configuration of the first fuel supply high volume flows, up to a factor of 7 compared to the supply of natural gas in known burners of the prior art, safely to the injection point at the burner outlet are passed.

In the present burner, the one or more first fuel feeds with the associated first fuel outlet openings are mechanically and thermally decoupled from the swirl generator or the burner bowls forming the swirl generator and significantly warmer during operation. As a result, the thermal stresses between the comparatively cold first fuel feeds, hereinafter also referred to as gas channels, and the warmer burner shells are avoided or at least significantly reduced. Thus, in one embodiment of the present invention, as explained in more detail in the embodiments, the injection area for the synthesis gas in the burner bowls is completely cut out. The first gas channel is anchored directly in this section of the burner bowls. Thus, gas duct and burner shells are thermally and mechanically decoupled from each other and the design problem at the joints of cold gas duct and warm burner shell is solved. Earlier constructions such as the EP 0610 722 A1 showed problems especially in the connection of relatively cold gas channel to hot burner shell, for example cracks due to the high concentration of stress at these connection points. With the decoupled solution and the presented design, the required service life of the burner is achieved.

The decoupling of individual fuel lances from the burner shells is already out of the EP 1 070 915 known. In the present burner, however, this mechanical decoupling is realized for the first time with integral gas ducts with extensive homogeneous gas introduction. Opposite from the EP 1 070 950 known gas injection impresses the invention homogeneous homogeneous gas injection by a much more uniform distribution of the fuel in the combustion air, and thus, especially when using Lbtu and Mbtu fuels, by a superior emission behavior with good flame stability. An elaborate special heat insulation of the gas channel relative to the hot burner shell - such as. By the well-known gas channel inserts - is not necessary.

Preferably, in addition to the first or the first fuel feeds, the burner also has one or more second fuel feeds with a group of second fuel outlets on the swirl body arranged substantially along the direction of the burner axis. Alternatively or in combination, a fuel lance arranged on the burner axis can also be provided for the injection of liquid fuel which projects into the swirl space in the axial direction. The arrangement and design of these additional fuel feeds can, for example. On the known premix burner technology according to the EP 321 809 or other types, such as. According to the EP 780,629 or the WO 93/17279 , based. Such burner geometries can be formed with the features according to the invention for the combustion of synthesis gases, in particular for the combustion of Mbtu and Lbtu fuels.

The preferred embodiment of the present burner with one or more other fuel feeds a multifunctional burner is obtained, the most diverse fuels safely and burns stably. The burner ensures in particular the stable and safe combustion of Mbtu synthesis gases with heating values (lower heating value Hu or Lower Heating Value LHV) of 3500 to 18000 kJ / kg, in particular 6000 to 15000 kJ / kg, preferably 6500 to 14500 kJ / kg or from 7000 to 14000 kg / kJ. In addition to the safe and stable combustion of undiluted and diluted synthesis gas, liquid fuel, for example diesel oil, can also be used as reserve fuel. The fuels used here can differ significantly in the calorific value, for example in the case of diesel oil with a calorific value Hu = 42000 kJ / kg and synthesis gas with a calorific value of 3500 - 18000 kJ / kg, in particular 6000 to 15000 kJ / kg, preferably from 6500 to 14500 kJ / kg or from 7000 to 14000 kg / kJ.

The use of natural gas as additional fuel is also possible. The injection of natural gas can optionally be carried out in the burner head through the burner lance and / or via the second fuel feeds, which are usually formed by the longitudinally attached to the air inlet slots on the swirl generator or swirl body gas channels, which, for example EP 321 809 are common. In this way, the burner can be operated with three different fuels.

The injection of the synthesis gas, ie the Lbtu / Mbtu fuel takes place via the first outlet openings radially at the burner outlet. These outlet openings are small outlet channels whose channel axis α determines the axial injection angle. Diameter D and injection angle α of these outlet openings or channels are special parameters which, depending on the boundary conditions, For example, the specific gas composition, emissions, etc., may be suitably selected by those skilled in the art. The injection angle can be selected so that the channel axes of all outlet openings intersect at a point on the burner axis downstream of the burner or swirl space. In order to achieve an optimum adaptation of the synthesis gas used to the desired emissions, the injection angles can also be selected such that the channel axes of subgroups of the outlet openings intersect at different points. In this way, any distribution of the injected fuel at the burner outlet can be achieved. In this case, an injection angle relative to the burner radius can be varied.

The fuel feeds for the combustion of the synthesis gas are adapted to the up to 7 times larger fuel volume flow in the design and provide in particular the necessary flow cross sections available. In this case, they have a multiple cross-section compared to the feeds for natural gas.

When using oil as fuel, the design known from the prior art is maintained with the injection of the oil or the oil-water emulsion over the burner lance. Due to various boundary conditions, such as integration of the gas turbine in the IGCC process or fixed burner groupings that are to be maintained, gas turbines burning syngas must ensure the mixed operation of pilot fuel and synthesis gas. The burner described here works stable and safe even in mixed operation of diesel oil and syngas in different mixing ratios. It can be operated safely for longer periods in mixed operation. The gas turbine thus achieves further flexibility and can change from one fuel to another during operation. The possible mixing operation represents a significant operational advantage.

Brief description of the drawings

Fig. 1

in stark schematisierter Darstellung einen Vormischbrenner, wie er aus dem Stand der Technik bekannt ist;

Fig. 2

eine Schnittansicht des brennraumseitigen Bereiches eines Brenners gemäß einem Ausführungsbeispiel der vorliegenden Erfindung;

Fig. 3

eine dreidimensionale Schnittansicht eines Brenners, der gemäß dem Ausführungsbeispiel der Figur 2 ausgestaltet ist;

Fig. 4

ein Beispiel für die Montage eines Brenners gemäß den Figuren 2 und 3;

Fig. 5

in Draufsicht stark schematisiert mehrere unterschiedliche Eindüsungsgeometrien für Synthesegas beim erfindungsgemäßen Brenner;

Fig. 6

ein Beispiel für eine Ausgestaltung des Brenners mit konischem Innenkörper; und

Fig. 7

ein Beispiel für eine weitere mögliche Ausgestaltung des Brenners.

The present invention will be briefly explained again below without limiting the general inventive idea using exemplary embodiments in conjunction with the figures. Hereby show:

Fig. 1

in a highly schematic representation of a premix burner, as it is known from the prior art;

Fig. 2

a sectional view of the combustion chamber side portion of a burner according to an embodiment of the present invention;

Fig. 3

a three-dimensional sectional view of a burner, according to the embodiment of the FIG. 2 is designed;

Fig. 4

an example of the installation of a burner according to the Figures 2 and 3 ;

Fig. 5

in plan view, highly schematic several different injection geometries for synthesis gas in the burner according to the invention;

Fig. 6

an example of an embodiment of the burner with conical inner body; and

Fig. 7

an example of another possible embodiment of the burner.

Ways to carry out the invention

FIG. 1 shows very schematically a premix burner, as he, for example, from the EP 321 809 A1 is known. The burner is composed of a burner head 10 and an adjoining swirl generator 1 which forms a swirl space 11. The conical swirl generator 1 in such a burner consists of a plurality of burner shells, between which tangential inlet slots for combustion air 9 are formed. The incoming combustion air 9 is indicated in the figure by the long arrows. Furthermore, gas feeds 24 for the supply of a fuel, in particular natural gas 26, can be provided via the tangential inlet slots into the swirl space 11 along the tangential entry slots. This is indicated in the figure by the short arrows. From the burner head 10, a burner lance 14 extends into the swirl chamber 11, at the end of a nozzle 16 for injecting liquid fuel 13, for. As oil and / or water 12 is provided. About the burner lance 14 in particular the ignition of the burner is made. The combustion air 9 entering via the tangential air inlet slots at the swirl generator 1 mixes in the swirl chamber 11 with the injected fuel. The The closed swirl flow produced in this case becomes unstable due to the increasing swirl at the end of the swirl space 11 due to the sudden cross-sectional widening during the transition into the combustion chamber and merges into an annular swirl flow with backflow in the core. This area forms the beginning of the reaction zone 17 in the combustion chamber.

However, an operation of such a burner with synthesis gas is not possible due to the high Rückzündgefahr this fuel.

FIG. 2 shows in a first embodiment in a sectional view of the combustion chamber side region of a burner according to the invention for operation with synthesis gas. The injection of the Lbtu / Mbtu fuel is carried out by a diameter D and Eindüsungswinkel α expediently to be selected Gasbelaufung 18 radially at the burner outlet, ie at the end of the swirl chamber 11. By this radial injection at the burner outlet, the combustion of the hydrogen-rich synthesis gas is also undiluted possible. Diameter D and injection angle α of the radial gas injection are special parameters that are suitably selected by the person skilled in the art depending on the boundary conditions (special gas composition, emissions,...).

The figure shows the burner shells of the swirl body 1, which surround the swirl space 11. Outside this swirl body, a gas supply element 2 is arranged, which surrounds the swirl body 1 radially and forms the first or the first fuel supply channels 19 for the supply of the synthesis gas. At the combustion chamber end of this Gaszuführelements 2 are first Outlets 18 formed for the synthesis gas. These outlet openings 18 form outlet channels which predetermine the injection direction of the synthesis gas. The injection angle α and the diameter D of these channels or openings 18 are suitably selected by the skilled person depending on the requirements. In the present example, the outlet openings 18 are arranged in a row around the burner axis 25, so that a homogeneous homogeneous injection of the synthesis gas is achieved.

The comparatively cold fuel supply channels 19 for injecting the synthesis gas and the burner shells of the swirl generator 1, which in principle are significantly warmer, are thermally and mechanically decoupled from one another. As a result, the thermal stresses are significantly reduced. The connection between the Gaszuführelement 2 and the swirl generator 1 takes place in this example via provided on both components tabs 3 and 4, which are interconnected. In this way, minimal thermal stresses are achieved. An air flow 8, which is furthermore shown in the figure, tends to stabilize the flames and, before exiting, produces a swirl-cooling effect at the burner front. In the figure, the opening or the circumferential gap 7 of the swirl generator 1 can still be seen, which is necessary to allow a connection between the outlet openings 18 of the gas supply element 2 and the swirl space 11.

FIG. 3 shows one according to FIG. 2 trained burner again in three-dimensional sectional view. Again, in this illustration, the swirl generator 1 formed from a plurality of burner bowls is also to recognize this enclosing Gaszuführelement 2. This Gaszuführelement 2 may form an annular feed slot as a fuel supply channel 19 or be divided into separate fuel supply channels 19. Of course, it is also possible to lead individual pipes as fuel supply channels 19 to the outlet openings 18.

The fuel supply channels 19 for the synthesis gas are adapted for the combustion of the synthesis gas to up to 7 times larger fuel flow in the design, and in particular the necessary large flow cross-sections available, as from FIG. 3 can be seen.

In the present example, the injection range for the fuel, i. H. the synthesis gas, completely cut out in the burner bowls. In this case, the gas supply element 2 is anchored directly in this section of the burner shells of the swirl generator 1. Thus, the voltage problem at the joints of cold Gaszuführelement 2 and hot burner cup is solved. With the decoupled solution shown in this example, the required life of the burner is achieved.

The injection of the synthesis gas is indicated in the figure by the reference numeral 20. Of course, in such a burner and additional gas injection channels 24 may be provided along the swirl generator 1, in the same manner as in, for example, in FIG. 1 can be seen, for example, with which natural gas 26 upstream of the injection point of the synthesis gas into the swirl chamber 11 can be initiated. The injection of oil or an oil-water emulsion is schematically indicated at the combustion head end of the swirl chamber 11, as well as the inflow of combustion air 9 via the tangential inlet slots.

FIG. 4 shows an example of the installation of a burner according to the Figures 2 and 3 from the two subcomponents, the gas feed element 2 and the swirl generator 1.

The gas supply element 2 with the integrated one or more fuel supply channels 19 for synthesis gas and the combustion chamber side around the burner axis, 25 arranged outlet openings 18 is preferably prepared together with the swirl generator 1 as a casting and then separated. The assembly is carried out by the swirl generator 1 is axially inserted into the gas supply element 2, so that the outlet openings 18 of the Gaszuführelementes 2 come to rest in corresponding openings 7 of the swirl generator 1. In the burner head region, an element 6 of the swirl generator 1 is held in the sliding seat in a counterpart 5 of the gas supply element 2, so that differential thermal expansion between swirl generator 1 in the gas supply element 2 in the region of the burner head can be freely compensated. In the area of the burner front, the connecting straps 3 of the gas supply element 2 and the connecting straps 4 of the swirl generator 1 are connected to one another in a suitable manner, for example welded, and form the only fixed support of the swirl generator 1 in the gas supply element 2. The outlet opening region of the gas supply element 2 is free in the Openings 7 of the swirl generator 1 movable. The production of both elements made possible in one piece low manufacturing tolerances, so a in FIG. 2 represented circumferential gap s between swirler 1 and gas supply element 2 can be minimized. A correspondingly high accuracy of fit with a small gap dimension s in the region of the gas outlet openings 18 or the openings 7 of the swirl generator 1 minimizes an untreated combustion air emerging through this gap, which could potentially have negative effects on combustion stability.

FIG. 5 shows various examples of differently selected injection directions of the first outlet openings 18 at the end of the swirl space 11 for the synthesis gas. FIG. 5a shows a highly simplified representation of a plan view of the burner outlet and the injection axes of the synthesis gas injection 20 of the individual outlet openings 18, which intersect at an intersection point 21 on the burner axis.

FIG. 5b shows a further embodiment in the same view, in which the exit axes of the synthesis gas injection 20 different groups of outlet openings 18 intersect at different points of intersection 21, which are distributed over the outlet cross-section of the burner. It goes without saying that the distribution of these points of intersection 21 can be chosen arbitrarily in order to adapt the injection to the respective conditions. On the one hand, this concerns the position of the points of intersection 21 and, of course, also their number.

In the same way, it is possible to choose the intersections 21 at different distances from the exit plane of the burner, or at the same distance, as in the FIGS. 5c and 5d is shown schematically.

FIG. 6 shows an example of a swirl generator 1 with a purely cylindrical swirl body 23 in which a conical inner body 22 is inserted. The supply of the pilot fuel can in this case take place directly up to the tip of the conical inner body 22. Again, the outlet openings 18 for the synthesis gas are distributed around the burner axis 25 at the combustion chamber end of the swirl chamber 11. The fuel supply channels 19 are not shown in this illustration. Again, in addition to the tangential air inlet slots, not shown, further gas outlet openings for natural gas, including the necessary supply lines 24 may be provided. Furthermore, in this embodiment as well as in the embodiments described above, a mixing tube can be connected to the swirl generator 1 to produce an additional mixing section, as is known from the prior art.

FIG. 7 Finally, shows an example of a burner in which the swirl generator 1 is formed as a swirl lattice, is offset by the incoming combustion air 9 in spin. An additional fuel for premix loading into the combustion air 9 can be introduced via the feed lines 24 leading to outlet openings in the region of the swirl generator 1. The supply of the pilot fuel 15 is centrally via a in the Inner volume 11 projecting nozzle 16 realized. Also in this burner, the outlet openings 18 for the synthesis gas are arranged distributed around the burner axis 25 at the combustion chamber end of the inner volume 11 and are acted upon via the fuel supply channels 19 with synthesis gas.

Although the invention primarily to a double-cone burner of the EP 321 809 the skilled artisan readily recognizes the applicability of the invention to other types of burner and vortex generator geometries, for example, as shown in the EP 780,629 or the WO 93/17279 are known. Modifications of these burner geometries are of course possible, as long as the purpose of the swirl generator to produce a twisted combustion air flow, is still guaranteed.

LIST OF REFERENCE NUMBERS

1

swirl generator

2

Gaszuführelement

3

connecting straps

4

connecting straps

5

Counterpart at the burner head

6

Element of the swirl generator at the burner head

7

Openings of the swirl generator

8th

airflow

9

combustion air

10

burner head

11

Swirl space or inner volume

12

water

13

Liquid fuel (oil)

14

burnerlance

15

Liquid fuel, emulsion

16

jet

17

Reaction zone or combustion chamber

18

first outlets

19

first fuel supply channels

20

Synthesegaseindüsung / outlet channel axes

21

Intersections of the injection

22

conical inner body

23

cylindrical outer body

24

second fuel supply for fuel gas (natural gas)

25

Brenner

26

natural gas

Claims (18)

1. Burner, substantially comprising a swirl generator (1) for a combustion air stream and means for introducing fuel into the combustion air stream, the swirl generator (1) having one or more combustion-air inlet openings for the combustion air stream which enters the burner, and the means for introducing fuel into the combustion air stream comprising one or more first fuel feeds (19) having a group of first fuel outlet openings (18), which is arranged distributed around the burner axis (25) at a combustion chamber-side end of the burner, characterized in that, outside this swirl body, there is arranged a gas feed element (2) which radially surrounds the swirl generator (1) and forms the first fuel feed(s) (19), and in that the one or more first fuel feeds (19) having the group of first fuel outlet openings (18) are mechanically decoupled from the swirl generator (1).
2. Burner according to Claim 1, characterized in that the group of first fuel outlet openings (18) is arranged distributed in a row around the burner axis (25).
3. Burner according to Claim 1 or 2, characterized in that outlet passages formed by the first outlet openings (18) are arranged at an angle which is such that the passage axes intersect at one point (21) on the burner axis (25) downstream of the burner.
4. Burner according to Claim 1 or 2, characterized in that outlet passages formed by the first outlet openings (18) are arranged at angles with respect to the burner axis (25) which are such that the passage axes of different subgroups of the first outlet openings (18) intersect at various points (21) downstream of the burner.
5. Burner according to one of Claims 1 to 4, characterized in that the swirl generator (1) and the one or more first fuel feeds (19) having the group of first fuel outlet openings (18) are produced integrally as a single component, preferably by casting, and are separated after they have been produced.
6. Burner according to Claim 5, characterized in that the one or more first fuel feeds (19) having the group of first fuel outlet openings (18) form a first component (2), which is pushed over the swirl generator (1), the swirl generator (1) having, at the combustion chamber-side end, openings (7) for providing the first outlet openings (18) with access to an internal volume (11) of the burner.
7. Burner according to Claim 6, characterized in that the first component (2) is connected to the swirl generator (1) via connecting lugs (3, 4).
8. Burner according to one of Claims 1 to 7, characterized in that the first fuel feed (19) is formed as an annular slot around the swirl generator (1).
9. Burner according to one of Claims 1 to 8, characterized in that a fuel lance (14) which projects into the burner is arranged on the burner axis (25).
10. Burner according to one of Claims 1 to 9, characterized in that one or more second fuel feeds (24) having a group of second fuel outlet openings, arranged substantially along a direction of the burner axis (25), are provided at the swirl generator (1).
11. Burner according to Claim 10, characterized in that the one or more first fuel feeds (19) are configured with a cross section which allows the volumetric flow to be several times higher than in the one or more second fuel feeds (24).
12. Burner according to Claim 10 or 11, characterized in that an inner body (22) is arranged in an internal volume (11) of the burner, the second fuel outlet openings of at least one second fuel feed (24) being arranged distributed on the inner body (22), substantially along a direction of the burner axis (25).
13. Burner according to one of Claims 10 to 12, characterized in that there are means for independently controlling the premix fuel feed to the first (19) and second (24) fuel feeds.
14. Burner according to one of Claims 1 to 9, characterized in that the swirl generator (1) is designed as a swirl grating.
15. Burner according to one of Claims 1 to 13, characterized in that the combustion-air inlet openings (4) are tangential inlet slots running substantially in the direction of the burner axis (3).
16. Burner according to Claim 15, characterized in that a second fuel feed (24) having a group of second fuel outlet openings is arranged along each inlet slot.
17. Method for operating the burner according to Claim 10, characterized in that synthesis gas is supplied via the first fuel feed(s) (19) and natural gas (26) is supplied via the second fuel feed(s) (24).
18. Method for operating the burner according to Claim 9, characterized in that synthesis gas is supplied via the first fuel feed(s) (19), and a liquid fuel, if appropriate in the form of a fuel-water emulsion (15), is supplied via the fuel lance (14).

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