EP1436546A1

EP1436546A1 - Burner for synthesis gas

Info

Publication number: EP1436546A1
Application number: EP02765280A
Authority: EP
Inventors: Timothy Griffin; Albert Keller; Joachim Krautzig; Roland Mücke; Frank Reiss
Original assignee: Alstom Schweiz AG
Current assignee: General Electric Technology GmbH
Priority date: 2001-10-19
Filing date: 2002-10-02
Publication date: 2004-07-14
Anticipated expiration: 2022-10-02
Also published as: US7003957B2; EP1436546B1; US20040226297A1; CN1263983C; WO2003036167A1; JP2005528571A; CN1571905A

Abstract

The invention relates to a burner which essentially consists of a swirl generator (1) for a combustion air flow, and means for introducing fuel into said combustion air flow (9). Said swirl generator (1) comprises combustion air inlets for the combustion air flow (9) entering the burner, and the means for introducing fuel into the combustion air flow (9) comprise at least one first fuel admission (19) and a group of first fuel outlets (18) which are arranged in a distributed manner on an end of the burner on the side of the combustion chamber, about the burner axis (25). Said burner is characterised in that the at least one fuel admission (19) and the group of first fuel outlets (18) are mechanically decoupled from the swirl generator (1). The inventive burner enables synthesis gas to be used in a reliable and safe manner, both in a rarefied and in a non-rarefied form.

Description

Burners for synthesis gas

Technical application area

The present invention relates to a burner for operation in a combustion chamber, preferably in combustion chambers of gas turbines _/ which essentially consists 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 flow comprise one or more fuel feeds with a group of first fuel outlet openings, which is arranged distributed around the burner axis at an end of the burner on the combustion chamber side.

A preferred area of use for such a burner is in gas and steam turbine technology.

State of the art

EP 0 321 809 B1 discloses a conical burner consisting of several shells, a so-called double-cone burner, according to the preamble of claim 1. The conical swirl generator, which is composed of several shells, creates a closed swirl flow in a swirl chamber which • becomes unstable due to the swirl increasing in the direction of the combustion chamber ^• and changes into an annular swirl flow with backflow in the core. The shells of the swirl generator are of this type composed that tangential air inlet slots for combustion air are formed along the burner axis. At the leading edge of the conical shells at these air inlet slots, feeds for the premix gas, ie the gaseous fuel, are provided, 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 of the combustion air / fuel gas flow generated in the swirl chamber, leads to a good mixing of the combustion or premix gas with the combustion air. With these premix burners, thorough mixing is a prerequisite for low NO _x values during the combustion process.

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

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

A premix burner is known from EP 1 070 915 A1, in which the fuel gas supply is mechanically decoupled from the swirl generator. As a result, stresses due to thermal expansions are avoided when only slightly preheated fuel gases are used. The swirl generator is here provided with a series of openings through which fuel lines mechanically decoupled from the swirl generator for gas premixing operation protrude into the interior of the swirl generator and feed gaseous fuel to the swirled flow of the combustion air there.

These known premix burners of the prior art are so-called spin-stabilized premix burners in which a fuel mass flow is distributed as homogeneously as possible prior to combustion in a combustion air mass flow. With these types of burners, the combustion air flows in through the tangential air inlet slots in the swirl generators. The

Fuel, particularly natural gas, is typically injected along the air inlet slots. In gas turbines, in addition to natural gas and liquid fuel, mostly diesel oil or Oil # 2, synthetically produced gases, so-called Mbtu and Lbtu gases, have recently been used for combustion. These synthesis gases are produced by the gasification of coal or oil residues. They are characterized by the fact that they largely consist of H ₂ and CO. In addition, there is a smaller proportion of inerts such as N ₂ or C0 ₂ .

When synthetic gas is burned, the injection which has proven itself for natural gas in the burners of the prior art cannot be maintained due to the high risk of reignition. In contrast to the use of natural gas, there are the following special features and requirements for a burner that is to be operated with synthesis gas. Depending on a dilution of the synthesis gas known per se according to the state of the art, synthesis gas requires around four times - in the case of undiluted synthesis gas up to seven times or even more - higher fuel volume flow compared to comparable natural gas burners, so that the burner has the same gas perforation - Liege impulse relationships result. Due to the high proportion of hydrogen in the synthesis gas and the associated low ignition temperature and high flame speed of the hydrogen, there is a high tendency of the fuel to react, so that in particular the re-ignition behavior and the dwell time of ignitable fuel-air mixture near the burner must be investigated. Furthermore, a stable and safe combustion of synthesis gases for one A sufficiently large range of calorific values can be guaranteed, which, depending on the process quality of the gasification and starting product, e.g. oil residues, has a different composition of the synthesis gas. In order to achieve a premixing during combustion under these conditions and thus to achieve the typical low emissions, these synthesis gases are usually diluted with the inert N ₂ or water vapor before the combustion. This also improves the stability of the combustion and, in particular, reduces the risk of reignition due to the high H content. The burner must therefore be able to burn synthesis gases of different compositions, in particular different dilutions, safely and stably.

It is also advantageous if, in addition to the synthesis gas from the burner, a backup fuel, a so-called backup fuel, can also be burned safely. In the case of the highly complex integrated gas synthesis and power generation (IGCC, Integrated Gasification Combined Cycle) plants, this requirement results from the requirement for high availability. In such a case, the burner should also function safely and reliably in the mixed operation of synthesis gas and backup fuel, for example diesel oil, the fuel mixture spectrum usable for the burner operation in the mixed operation of a single burner being maximized. Of course, low emissions (NO _x <25 vppm, CO <5 vppm) should be guaranteed for the specified and used fuels. A double-cone burner is known from EP 0610 722 A1, in which a group of fuel outlet openings for a synthesis gas are arranged on the swirl generator at an end of the burner on the combustion chamber side around the burner axis. These outlet openings are supplied via a separate fuel line and enable the burner to be operated with undiluted synthesis gas.

Starting from this prior art, the object of the present invention is to provide a burner which 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 several types of fuel, also 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.

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

The geometry of the swirl generator as well as any swirl space that may be present can be selected in various ways in the present burner and in particular have the geometries known from the prior art. The distribution of the first fuel outlet openings exclusively at the end of the burner or swirl chamber on the combustion chamber side around the burner axis reliably prevents the synthetic gas from reigniting. Mixing with the combustion air emerging from the burner is nevertheless guaranteed. Syngas with a high water content (45 vol%) can be burned undiluted (Hu = 14000 kJ / kg). The burner thus enables safe and stable combustion of both undiluted and diluted synthesis gas. This guarantees a high degree of flexibility when using a gas turbine equipped with burners according to the invention in an IGCC process. A correspondingly cross-sectional configuration of the first fuel supply means that high volume flows, up to a factor of 7 compared to the supply of natural gas in known burners of the prior art, can be safely conducted to the injection point at the burner outlet. 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 shells which form the swirl generator and are 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 is explained in more detail in the exemplary embodiments, the injection region for the synthesis gas in the burner trays is completely cut out. The first gas channel is anchored directly in this section of the burner bowls. This means that the gas duct and burner shells are thermally and mechanically decoupled from one another, and the design problem at the connection points between the cold gas duct and the warm burner shell is solved. Earlier constructions such as that of EP 0610 722 AI showed problems, for example cracks due to the high stress concentration at these connection points, particularly when connecting a relatively cold gas duct to a hot burner bowl. With the decoupled solution and the presented

Design will achieve the required burner life.

The decoupling of individual fuel lances from the burner shells is already known from EP 1 070 915. In the present burner, however, this mechanical decoupling is realized for the first time with integral gas channels with homogeneous gas introduction. Compared to the gas injection known from EP 1 070 950 captivates the homogeneous gas injection according to the invention 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. A costly special thermal insulation of the gas channel from the hot burner bowl - as for example by the known gas channel inserts - is not necessary.

In addition to the first fuel feed (s), the burner preferably also has one or more second fuel feeds with a group of second fuel outlet openings arranged essentially along the direction of the burner axis on the swirl body. Alternatively or in combination, a fuel lance can also be provided on the burner axis for the injection of liquid fuel, which projects into the swirl chamber in the axial direction. The arrangement and configuration of these additional fuel feeds can be based, for example, on the known premix burner technology according to EP 321 809 or also other types, such as according to EP 780 629 or WO 93/17279. Such burner geometries can be designed 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 further fuel supplies results in a multifunctional burner which is able to store a wide variety of fuels safely and safely - in ¬

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 - 18000 kJ / kg, in particular 6000 to 15000 kJ / kg, preferably from 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, e.g. diesel oil, can also be used as a reserve fuel. The fuels used can differ significantly in their calorific value, for example for diesel oil with a calorific value Hu = 42000 kJ / kg and syngas 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 an additional fuel is also possible. Natural gas can be injected in the burner head either through the burner lance and / or via the second fuel feeds, which are usually formed by the gas channels which are longitudinally attached to the air inlet slots on the swirl generator or swirl body and are known to the person skilled in the art, for example, from EP 321 809 are common. In this way, the burner can be operated with three different fuels.

The synthesis gas, ie the Lbtu / Mbtu fuel, is injected radially through the first outlet openings at the burner outlet. These outlet openings are small outlet channels, the channel axis of which determines the axial injection angle α. Diameter D and injection angle α of these outlet openings or channels are special parameters which, depending on the edge Conditions, for example the special gas composition, the emissions, etc., can be appropriately selected by a person 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 optimal adaptation of the synthesis gas used to the desired emissions, the injection angle can also be selected so 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. An injection angle can also be varied in relation to the burner radius.

The design of the fuel feeds for the combustion of the synthesis gas is adapted to the fuel volume flow, which is up to 7 times greater, and in particular provides the necessary flow cross-sections. They have a multiple cross-section compared to the natural gas feeds.

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 via the burner lance. Due to various boundary conditions, such as the integration of the gas turbine in the IGCC process or fixed burner groups that are to be retained, gas turbines that burn synthesis gas have to ensure the mixed operation of pilot fuel and synthesis gas. The burner described here works is also stable and safe in the mixed operation of diesel oil and synthesis gas in various mixing ratios. It can be operated safely in mixed operation for longer periods. The gas turbine thus achieves further flexibility and can switch from one fuel to another during operation. The possible mixed operation represents a significant operational advantage.

Brief description of the drawings

The present invention is briefly explained again below without restricting the general inventive concept on the basis of exemplary embodiments in conjunction with the figures. Here show:

Figure 1 in a highly schematic representation of a premix burner, as is known from the prior art.

2 shows a sectional view of the area of a burner on the combustion chamber side according to an exemplary embodiment of the present invention,

3 shows a three-dimensional sectional view of a burner which is designed in accordance with the exemplary embodiment in FIG. 2;

4 shows an example of the assembly of a burner according to FIGS. 2 and 3;

5 is a highly schematic top view of several different injection nozzles. Geometries for synthesis gas in the burner according to the invention;

6 shows an example of a configuration of the burner with a conical inner body; 7 shows an example of a further possible one

Design of the burner.

Ways of Carrying Out the Invention

Figure 1 shows a highly schematic of a premix burner, as is known for example from EP 321 809 AI. The burner is composed of a burner head 10 and an adjoining swirl generator 1, which forms a swirl chamber 11. In such a burner, the conical swirl generator 1 consists of several 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 inlets 24 for the supply of a fuel, in particular natural gas 26, can be provided along the tangential inlet slots via the tangential air inlet slots into the swirl chamber 11. This is indicated in the figure with the short arrows. A burner lance 14 extends from the burner head 10 into the drain chamber 11, at the end of which a nozzle 16 for injecting liquid fuel 13, e.g. B. oil and / or water 12 is provided. In particular, the burner is ignited via the burner lance 14. The combustion air 9 entering the swirl generator 1 via the tangential air inlet slots mixes with the injected fuel in the swirl chamber 11. The The resulting closed swirl flow becomes unstable due to the increasing swirl at the end of the swirl chamber 11 due to the sudden cross-sectional widening when transitioning into the combustion chamber and changes 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, operation of such a burner with synthesis gas is not possible due to the high risk of reignition of this fuel.

FIG. 2 shows, in a first exemplary embodiment, in a sectional view the region of a burner according to the invention for operation with synthesis gas on the combustion chamber side. The Lbtu / Mbtu fuel is injected radially at the burner outlet by means of a gas perforation 18 which is expediently to be selected with regard to diameter D and injection angle, i. H. at the end of the swirl chamber 11. This radial injection at the burner outlet enables the hydrogen-rich synthesis gas to be burned undiluted. Diameter D and the injection angle of the radial gas injection are special parameters which are appropriately 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 enclose the swirl chamber 11. Outside of this swirl body, a gas supply element 2 is arranged, which radially surrounds the swirl body 1 and forms the first fuel supply channel or channels 19 for the supply of the synthesis gas. At the combustion chamber end of this gas supply element 2 are first Outlet openings 18 are formed for the synthesis gas. These outlet openings 18 form outlet channels which specify the injection direction of the synthesis gas. The injection angle α and the diameter D of these channels or openings 18 are selected appropriately by the person skilled in the art 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 circumferential injection of the synthesis gas is achieved.

The comparatively cold fuel supply channels 19 for injection of 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. This significantly reduces the thermal stresses. In this example, the connection between the gas supply element 2 and the swirl generator 1 takes place via tabs 3 and 4 provided on both components, which are connected to one another. In this way, minimal thermal stresses are achieved. An air flow 8, which is also shown in the figure, tends to stabilize the flames and produces a swirl cooling effect on the burner front before it emerges. In the figure, the opening or the circumferential gap 7 of the swirl generator 1 can also be seen, which is necessary in order to enable a connection between the outlet openings 18 of the gas supply element 2 and the swirl chamber 11.

Figure 3 shows a trained according to Figure 2

Burner again in three-dimensional sectional view. In this illustration, too, the swirl generator 1 and also formed from a plurality of burner shells is shown to recognize the gas supply element 2 surrounding it. This gas supply element 2 can form an annular supply slot as the fuel supply channel 19 or can also be divided into separate fuel supply channels 19. Of course, it is also possible to lead individual pipelines 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 the up to 7 times larger fuel volume flow in design, and in particular provide the necessary large flow cross sections, as can be seen from FIG. 3.

In the present example, the injection area for the fuel, i. H. the synthesis gas, completely cut out in the burner bowls. The gas supply element 2 is anchored directly in this section of the burner shells of the swirl generator 1. This solves the voltage problem at the junctures of the cold gas supply element 2 and the warm burner bowl. The decoupled solution shown in this example achieves the required burner life.

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

FIG. 4 shows an example of the assembly of a burner according to FIGS. 2 and 3 from the two subcomponents, the gas supply 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 is arranged around the burner axis 25 Outlet openings 18 are preferably produced together with the swirl generator 1 as a cast part and then separated. The

Assembly takes place by the swirl generator 1 being inserted axially into the gas supply element 2, so that the outlet openings 18 of the gas supply element 2 come to lie in corresponding openings 7 of the swirl generator 1. In the burner head area, 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 thermal expansion differences between swirl generator 1 in the gas supply element 2 in the area 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 bearing of the swirl generator 1 in the gas supply element 2. The outlet opening area of the gas supply element 2 is free in the Openings 7 of the swirl generator 1 are movable. The production of both elements from a single cast enables low manufacturing tolerances, so that a circumferential gap dimension s shown in FIG. 2 between swirl generator 1 and gas supply element 2 can be minimized. A correspondingly high accuracy of fit with a small gap dimension s in the area of the gas outlet openings 18 or the openings 7 of the swirl generator 1 minimizes an untwisted combustion air emerging through this gap, which could have potentially negative effects on the combustion stability.

FIG. 5 shows various examples of differently selected injection directions of the first outlet openings 18 at the end of the swirl chamber 11 for the synthesis gas. FIG. 5a shows in a highly simplified representation a top 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 another embodiment in the same view, in which the outlet axes of the synthesis gas injection 20 of different groups of outlet openings 18 intersect at different intersection points 21, which are distributed over the outlet cross section of the burner. It goes without saying that the distribution of these intersection points 21 can be chosen arbitrarily in order to adapt the injection to the respective conditions. On the one hand, this affects the position of the intersection points 21 and on the other hand, of course, their number. In the same way, it is possible to select the intersection points 21 at a different distance from the burner exit plane or at the same distance, as is shown schematically in FIGS. 5c and 5d.

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 pilot fuel can be supplied directly to the tip of the conical inner body 22. Here too, the outlet openings 18 for the synthesis gas are distributed around the burner axis 25 at the end of the swirl chamber 11 on the combustion chamber side. The fuel supply channels 19 are not shown in this illustration. Here, too, additional gas outlet openings for natural gas, including the supply lines 24 required for this, can additionally be provided at the tangential air inlet slots (not shown). Furthermore, in this and in the exemplary embodiments described above, a mixing tube for generating an additional mixing section can be connected to the swirl generator 1, as is known from the prior art.

FIG. 7 finally shows an example of a burner in which the swirl generator 1 is designed as a swirl grille, by means of which the combustion air 9 entering is swirled. An additional fuel for premix loading can be introduced into the combustion air 9 via the supply lines 24 leading to outlet openings in the area of the swirl generator 1. The supply of the pilot fuel 15 is via a central in the Internal volume 11 projecting nozzle 16 realized. In this burner too, the outlet openings 18 for the synthesis gas are distributed around the burner axis 25 at the end of the inner volume 11 on the combustion chamber side and are supplied with synthesis gas via the fuel supply channels 19.

Although the invention was primarily shown on a double-cone burner of the type known from EP 321 809, the person skilled in the art will readily recognize the applicability of the invention to other types of burner and swirl generator geometries, for example as described in EP 780 629 or WO 93/17279 are known. Modifications of these burner geometries are of course also possible as long as the purpose of the swirl generator to generate a swirled combustion air flow is still guaranteed.

LIST OF REFERENCE NUMBERS

1 swirl generator

2 gas supply element 3 connecting straps

4 connecting straps

5 counterpart on the burner head

6 Element of the swirl generator on the burner head

7 openings of the swirl generator 8 air flow

9 combustion air

10 burner head

11 swirl space or internal volume Water liquid fuel (oil) burner lance liquid fuel, emulsion nozzle reaction zone or combustion chamber first outlet openings first fuel supply channels synthesis gas injection / outlet channel axes intersections of the injection conical inner body cylindrical outer body second fuel supply for fuel gas (natural gas) burner axis natural gas

Claims

claims

1. Burner, essentially consisting of a swirl generator (1) for a combustion air flow and means for introducing fuel into the combustion air flow, the swirl generator (1) having one or more combustion air inlet openings for the combustion air flow entering the burner and the Means for introducing fuel into the combustion air flow comprise one or more first fuel feeds (19) with a group of first fuel outlet openings (18), which is arranged distributed around the burner axis (25) at an end of the burner on the combustion chamber side, characterized in that the one or more first fuel feeds (19) with 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 in a row distributed around the burner axis (25).

3. Burner according to claim 1 or 2, characterized in that through the first outlet openings. (18) formed outlet channels are arranged at such an angle, that the channel axes intersect at a point (21) downstream of the burner on the burner axis (25).

4. Burner according to claim 1 or 2, characterized in that through the first outlet openings (18) formed outlet channels are arranged at such angles to the burner axis (25) that the channel axes of different subgroups of the first

Cut the outlet openings (18) at different 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) with the group of first fuel outlet openings (18) made in one piece, preferably cast, and subsequently the

Manufacturing are separated.

6. Burner according to claim 5, characterized in that the one or more first fuel feeds (19) with the group of first fuel outlet openings (18) form a first component (2) which is pushed over the swirl generator (1), wherein the swirl generator (1) has openings (7) at the combustion chamber end for access by the first

Has outlet openings (18) to an inner volume (11) of the burner.

7. Burner according to claim 6, characterized in that the first component (2) via connecting straps (3, 4) with the swirl generator (1) is connected.

8. Burner according to one of claims 1 to 7, characterized in that the first fuel supply (19) is designed 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) is arranged on the burner axis (25), ie protrudes into the burner.

10. Burner according to one of claims 1 to 9, characterized in that one or more second fuel feeds (24) with a group of substantially along a direction of the burner axis (25) arranged second fuel outlet openings on the swirl generator (1) are provided.

11. Burner according to claim 10, characterized in that the one or more first fuel feeds (19) are designed with a cross section that enables a volume flow that is several times higher than that of the one or more second fuel feeds (24).

12. Burner according to one of claims 10 or 11, characterized in that an inner body (22) is arranged in an inner volume (11) of the burner, the second fuel outlet Openings of at least one second fuel feed (24) are arranged on the inner body (22) and are distributed substantially along a direction of the burner axis (25).

13. Burner according to one of claims 10 to 12, characterized in that means for independently controlling the premix fuel supply to the one or more first (19) and to the or the second fuel supply (24) are provided.

14. Burner according to one of claims 1 to 9, characterized in that the swirl generator (1) is designed as a swirl grid.

15. Burner according to one of claims 1 to 13, characterized in that the combustion air inlet openings (4) substantially in the direction of the burner axis (3) are tangential inlet slots.

16. Burner according to claim 15, characterized in that a second fuel feed (24) with a group of second fuel outlet openings is arranged along each inlet slot.

17. A method of operating a burner according to claim 10, characterized in that the first (n)

Fuel supply (s) (19) synthesis gas and natural gas via the second fuel supply (s) (24) (26) is supplied.

18. A method of operating a burner according to claim 9, characterized in that via the first (n) fuel supply (s) (19) synthesis gas and via the fuel lance (14) a liquid fuel, optionally as a fuel-water emulsion (15) becomes.