EP1292795A1

EP1292795A1 - Method for operating a burner and burner with stepped premix gas injection

Info

Publication number: EP1292795A1
Application number: EP01951833A
Authority: EP
Inventors: Adnan Eroglu; Jaan Hellat; Peter Stuber
Original assignee: Alstom Technology AG; Alstom Schweiz AG
Current assignee: General Electric Technology GmbH
Priority date: 2000-06-15
Filing date: 2001-06-13
Publication date: 2003-03-19
Anticipated expiration: 2021-06-13
Also published as: AU2001272682A1; US6769903B2; WO2001096785A1; JP2004507701A; US20030152880A1; JP4625609B2; EP1292795B1

Abstract

The invention relates to a method for operating a burner comprising at least one first fuel supply (5) with a first group of fuel outlets (6) for a first amount of premix fuel, said first group of fuel outlets being essentially arranged in the direction of a burner axis (3); and at least one second fuel supply (7) with a second group of fuel outlets for a second amount of premix fuel, said second group of fuel outlets (8) being essentially arranged in the direction of the burner axis (3). Fuel can be fed to the second fuel supply or supplies (7) independently from the first fuel supply (5). Both fuel supplies (5, 7) are operated using the same fuel. The inventive method for operating a burner enables optimum mixing conditions to be adjusted even in cases of varying loads, quality of gas or gas pre-heating temperatures.

Description

Process for operating a burner and burner with staged premix gas injection

Technical application area

The present invention relates to a method for operating a burner, the at least one first fuel supply with a first group of fuel outlet openings arranged essentially in the direction of the burner axis for introducing a first quantity of premixed fuel into a swirl space and one or more second fuel supplies with a second group of fuel outlet openings arranged essentially in the direction of the burner axis, the second fuel feeds being able to be acted upon with fuel independently of the first fuel feed. The invention further relates to a burner that can be operated advantageously with the method. A preferred area of application for such burners is the combustion chambers of gas turbines; Such burners are also used, for example, in atmospheric boiler furnaces.

State of the art

EP 0 321 809 discloses a conical burner consisting of several shells, a so-called double-cone burner, according to the preamble of claim 1. Due to the conical shape of several A swirl flow is generated in shells composed of swirl generators in the cone interior enclosed by the partial cone shells. Due to a cross-sectional jump at an end of the burner on the combustion chamber side, the swirl flow becomes unstable and changes into an annular swirl flow with a backflow in the core. This backflow enables the stabilization of a flame front at the burner outlet. The shells of the swirl generator are composed in such a way that tangential air inlet slots for combustion air are formed along the burner axis. On the inflow edge of the conical shells formed in this way, feeds for a gaseous premix fuel are provided, which have outlet openings for the premix gas which are distributed in 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 thorough mixing of the combustion or

Premix gas with the combustion air. With such premix burners, thorough mixing is the 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, 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 into which the flow emerging from the swirl generator has no significant te flow losses is transferred. With this additional mixing section, the degree of mixing can be increased further and the pollutant emissions reduced.

WO 93/17279 shows another known premix burner in which a cylindrical swirl generator with an additional conical inner body is used. 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. This burner also has a central feed for fuel gas in the conical inner body, which is close to the outlet opening of the

Brenners can be injected into the swirl room for piloting. This additional pilot stage is used to start the burner. However, the supply of the pilot gas in the outlet area of the burner leads to increased NO _x emissions, since in this area only insufficient mixing with the combustion air can take place.

EP 0918191 AI shows a generic burner for operating a heat generator which, in addition to a first supply for fuel, also has a second supply for another type of fuel, which is matched to the other type of fuel. Both feeders are independent of each other. controllable. With this configuration, the burner can be operated with different types of fuel without having to be modified. In all the burners shown, the premix gas is injected into the air inlet gap by means of feeds with outlet openings arranged essentially in the direction of the burner axis. So the characteristics of the injection are regarding

Depth of penetration and mixing of the gas jets as well as the fuel distribution along the air inlet slots or the burner axis are specified. The arrangement of the outlet openings thus already defines the mixing quality of the gas and the combustion air as well as the fuel distribution at the burner outlet. These variables are in turn decisive for the NO _x emissions, for the extinguishing and flashback limits as well as for the stability of the burner with regard to combustion pulsations.

With different loads, gas qualities or gas preheating temperatures, however, different gas admission pressures occur at the outlet openings, which in turn lead to different premixing conditions and mixture qualities at the fuel outlet. The different premixing conditions then result in different emission values and stability conditions, which depend on the load, the gas quality and the gas preheating. The known burners can therefore only be operated optimally for very specific value ranges of these parameters.

The problem with the operation of premix burners, particularly in gas turbines, is the partial load range, since only comparatively small amounts of fuel are mixed into the combustion air. When the fuel is completely mixed with all the air, however, a mixture is created, which is precisely in the lower one Partial load range is no longer ignitable, or is only able to form a very unstable flame. This can lead to harmful combustion pulsations or to the complete extinguishing of the flame.

For an adaptation of the known burners to specific emission values or to a specific stability window with different loads, ambient conditions, gas qualities and preheating temperatures, there is currently the possibility, on the one hand, of using pre-mixed or premix gas supply to individual burner groups when using multiple burner arrangements. However, this is only possible with multi-row burner arrangements. For single-row, annular combustion chambers, this technology has the disadvantage that a non-uniform temperature profile occurs in the combustion chamber outlet in the circumferential direction.

Another possibility is to equip burners with a pilot fuel supply, as briefly outlined above. The burners are then operated as diffusion burners at very high air ratios. On the one hand, this results in superior flame stability, but on the other hand in high emission values and other operational disadvantages.

The object of the present invention is to provide a method for operating a burner and a burner with which the burner with approximately constant NO _x even when the load, the gas quality or the gas preheating temperature changes. Emission values can be operated stably in premix mode if possible.

Presentation of the invention

The object is achieved with the method according to claims 1 and 7 and the burner according to claim 8. Advantageous refinements and developments of the burner and the method are the subject of the dependent claims.

In the present method, a burner with swirl body and the swirl chamber is used, which at least stanchions a first fuel supply with a first group of substantially in the direction of a burner axis arranged fuel outlet orifices for introducing a first Vormischbrennstoffmenge in ^'the swirl space and one or more second Brennstoffzufüh- with a second group of essentially in

Has fuel outlet openings arranged in the direction of the burner axis, wherein the second fuel supply is / can be acted upon independently of the first fuel supply. To operate the burner, the supply of the fuel via the first fuel feeds is controlled or regulated separately from the supply of the fuel via the second fuel feeds, the same fuel being fed to the first and second fuel feeds. By controlling the mass flow ratio of the first quantity of fuel supplied via the first fuel supply to a second quantity supplied via the second fuel supply Amount of fuel while the burner is in operation, the burner can be operated stably even with changes in the load, gas quality or gas preheating temperature with approximately constant NO _x emission values.

In the preferred embodiment, the fuel is used as a premixed fuel and is divided into a variable mass flow ratio between the first and second feeds. The feed of pre-mixed fuel differs from the feed of pilot fuel, i.e. of fuel for the implementation of a pilot stage, in that premixed fuel is introduced into the swirl chamber with a higher momentum, preferably transversely to the flow of the combustion air. In contrast, when fuel is introduced as a pilot fuel, the burner is operated in a diffusion mode.

The fuel is preferably introduced into the burner in a distributed manner as a function of the load on the first and second fuel feeds.

In a further preferred mode of operation of the burner, in a first operating state essentially the entire fuel quantity is supplied via the first fuel supply or feeds and introduced into the combustion air flow via the first group of fuel outlet openings, and in a further operating state at least part of the total fuel quantity introduced into the combustion air flow via at least one of the second fuel feeds with the second group of fuel outlet openings. I o

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Combustion air flow entering swirl space, the means for introducing fuel into the combustion air flow comprise one or more first fuel feeds with a first group of fuel outlet openings arranged essentially in the direction of the burner axis for a first quantity of premixed fuel, and the burner one or more second fuel feeds with a second Group of fuel outlet openings arranged essentially in the direction of the burner axis for a second fuel quantity, preferably a pre-mixed fuel quantity, which second fuel feeds can be / are acted on independently of the first fuel feed or feeds. In the preferred variant described, the burner is characterized in that an inner body is arranged in the swirl chamber, the fuel outlet openings of at least one second fuel feed being arranged on the inner body essentially in the direction of the burner axis. In which

In a preferred embodiment, the inner body is a fuel lance which is arranged in the swirl chamber on the burner axis.

One or more of the first groups of fuel outlet openings are preferably in the region. at least one of the combustion air inlet openings arranged.

In the present application, an arrangement essentially in the direction of the burner axis is understood to mean an arrangement on axes which run parallel or at an angle <45 ° to the burner axis. In one possible embodiment of the present burner, some of the second fuel feeds are also arranged directly next to the first fuel feeds, preferably parallel to these. In this case, at least one second fuel feed should be provided next to each first fuel feed.

However, it goes without saying that the second fuel feeds can also be provided in a symmetrical arrangement on the swirl generator independently of the first fuel feeds. The geometry of the swirl generator is irrelevant here. Thus, cone-shaped swirl generators, as are known from the prior art documents mentioned at the outset, can be used, for example with two, four or more air inlet slots. Other geometries, such as cylindrical swirl generators or cylindrical swirl generators with conical or cylindrical inner bodies, can also be used.

In one embodiment of the burner, some of the second fuel feeds are arranged on the outer shell of the swirl body and in this case in particular on the air inlet slots along this. It is essential in the present burner that the second fuel feeds have a plurality of fuel outlet openings essentially distributed in the direction of the burner axis in order to be able to achieve a sufficient premixing. The outlet openings are generally on axes running parallel or at an angle to the burner axis that is predetermined by a cone shape of the swirl generator or inner body. Depending on the desired influence on the premixing, the second fuel outlet openings of the second fuel feeds can have different mutual distances or flow cross-sections compared to the first fuel outlet openings. Particularly in the case of an arrangement in which at least one second fuel supply is also provided in addition to a first fuel supply, the respective fuel

Outlet openings also have the same mutual distances, but be arranged offset to one another. This leads to a more even injection of the premixed fuel into the swirl chamber. Furthermore, for example, the first fuel outlet openings can be arranged over the entire axial extent of the combustion air inlet openings, but the second fuel outlet openings can only be arranged in a specific axial partial area. In the same way, it is also possible to provide the first fuel outlet openings only in a first axial section and the second fuel outlet openings only in a second axial section adjoining the first section - or vice versa. Different possibilities to influence the operation of the burner due to these different possible configurations, the combination of no practical limits, ^'can be found in the embodiments.

In order to act independently of one another on the first and second fuel feeds with the premixed fuel, these are of different types Connections equipped. In addition, means for independent regulation or control of the premix fuel supply to the first and second fuel supplies are preferably provided. The different supply can be controlled, for example, by a suitable control valve.

The burner according to the invention and the burner with which the method according to the invention can be carried out are explained in more detail below on the basis of exemplary embodiments in conjunction with the drawings without restricting the general inventive concept. Here show:

Figure 1 schematically shows an embodiment of a burner that can be operated with the inventive method, in longitudinal and cross section;

FIG. 2 shows an example of the gas outlet from the outlet openings in a possible mode of operation of the burner shown in FIG. 1;

FIG. 3 schematically shows an example of the arrangement of the fuel feeds and the fuel outlet openings of a burner which can be operated using the method according to the invention;

Figures 5 to 7 examples of the arrangement of the

Fuel feeds and the fuel outlet openings of a burner connected to the the inventive method can be operated;

FIG. 8 schematically shows an example of a burner with a cylindrical swirl generator that can be operated with the method according to the invention;

FIG. 9 shows an example of a burner design with a cylindrical swirl body and a conical inner body, as can be operated using the method according to the invention;

Figure 10 shows a first example of the design of a burner according to the invention;

FIGS. 11 to 14 schematically show examples of further swirl generator geometries with which the present invention can be implemented;

FIGS. 15 and 16 swirl generator geometries with a downstream premixing tube, in which the invention can be implemented;

Figures 17 and 18 schematically show two examples of the structure of the swirl body in cross section, as it can be used in the burner according to the invention;

Figures 19 to 21 further examples of the

Design of a burner according to the invention;

Figure 22 shows an example of the operation of a burner of Figures 20 and 21; and FIGS. 23 and 24 schematically show two examples of the configuration of the fuel feeds for carrying out the method according to the invention.

Ways of Carrying Out the Invention

In the following figures, the burners are shown in a highly schematic design, so that the features essential for the respective explanation are only highlighted at one position. The skilled worker is familiar with the further design of the burners shown, inter alia, from the documents cited as prior art, which form an integral part of the present description. Furthermore, reference is made in part to the injection of gaseous fuel in the exemplary embodiments. However, it goes without saying that liquid fuel can also be introduced into the combustion air stream via the fuel outlet openings. The fuel is still referred to as a premix fuel; it goes without saying that part of the total fuel quantity can also be introduced as a pilot fuel in certain load ranges to further increase flame stability. Feeds for pilot fuel are not shown in any of the figures, since they are not essential to the invention; With knowledge of the prior art, the person skilled in the art will readily know how to implement this in the exemplary illustrated burners if he considers this necessary. FIG. 1 shows a first example of a burner that can be operated using the method according to the invention. FIG. 1 a shows an arrangement of the first 5 and second fuel feeds 7 in a burner with a conical swirl body 1 a second feed 7 for a second premix fuel quantity P2 is arranged for a first premix fuel quantity PI. These two feeds can be supplied with premix fuel independently of one another, ie that, for example, the mass flow of the second premix fuel P2 flowing through the second feed 7 can be set independently of the mass flow of the first premix fuel PI through the first feed 5. This is indicated by the different supply lines with the arrows. It goes without saying that preferably several of these feed pairs 5, 7 are arranged symmetrically about the burner axis. The fuel supply to the two supply channels can be set independently of one another via control valves that are not explicitly described here. The arrangement of the control valves is not shown in the example, but is readily familiar to the person skilled in the art.

In Figure lb the burner is shown in vertical section through the burner axis 3. The two shells la, lb of the swirl body can be seen in this illustration. These are arranged with axes of symmetry 3a, 3b offset from the actual burner axis 3, in such a way that air inlets between them step slots 4 are formed for the combustion air 11. The first supply duct 5 with the corresponding outlet openings 6 for the premixed fuel can be recognized at such an air inlet slot 4 in a manner known from the prior art.

Immediately next to this first feed channel 5, the second feed channel 7 with the corresponding second outlet openings 8 is arranged. Both feed channels point with their outlet openings 6, 8 to the incoming combustion air flow.

The gradation of the premixed fuel quantities via feed channels which can be acted on separately from one another allows the depth of penetration of the premixed fuel quantities PI, P2 into the combustion air flow via one

Feed channel large and set small via the other feed channel. This is shown schematically in FIG. 2, which figure shows the arrangement according to FIG. 1 in one possible operating mode. In this case, the amount of fuel in the first feed channel 5 is set higher than in the second feed channel 7, so that the pressure and thus the outlet speed of the fuel at the outlet openings 6 increase in comparison to the outlet openings 8. The first premix fuel PI from the first feed channel 5 thus penetrates deeper into the combustion air flow than the premix fuel P2 from the second feed channel 7, as is indicated in the figure. The same effect can also be achieved by different opening diameters or flow cross-sections of the respective

Exit openings are reached, then the amount of fuel flowing through the two channels ω t ro H o cπ o cπ O cπ

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Pi P- Φ P μ- P Φ a Φ P 3 a 0 μ- P 0 a

Φ aaa ti ^ ^• N a 0 CQ P LQ a ti Ω td rt rt P Φ ra a

P. li Φ 0 = • <: Φ <! ti Φ Φ öd Φ μ- tr fi φ Φ P tύ μ- σ> NP fi CQ 0 P a Cπ ra φ fi φ Φ rt tj P d μ- α Φ - ai £> CQ t5 μ- fi a φ μ- CQ 3 P • a μ- LQ ti CQ Hi φ P td SD Φ oo rr CQ μ- P a öd H

SD a φ oo

• a = tsi μ- fi P H P rt tSJ ti μ- Hi rt CQ td Φ fi P 0 fi tr φ CQ fi φ CQ rt μ- a a = rt Φ tr Φ rr

N ti μ- rt CD μ- a Φ CQ 0 = 3 • Φ ü PO μ- 3 PP tr> wa tö ^ CQ ^• »CQ a tr Φ a μ- ra Φ Hi Φ P μ- fi

0 = Hl φ SD rt tr Ω Φ Φ μ- a rt ö rt P ü Hi p CQ Φ Φ P ti a = μ- P φ Hi tr fi P P Φ μ- $, SD μ- <i 0 p. rt ra

P a SD

TJ tr SD tr μ- a = Φ ra a P φ μ- fi φ IS- Φ Φ 0 φ φ ti P μ- CQ a ti ti P • φ Φ fi ^ -3 fi fi Hl 3 CQ LQ li p φ φ ti P ^ μ- P tr P. Φ rt Hi rt φ

CQ SD 3 -0 fi μ- P μ- μ- a Φ a μ- Φ SD tr ¹ rd 0 1

P tr φ μ- a Φ μ- Φ CQ rt μ- CQ SD μ- SD Hl μ> SD = 3 Φ Φ P μ- 1 Φ 1 rt ra P Hi μ- μ- 1 φ

Φ rt a P rt P

Good to H μ>

O cπ o cπ o cπ

SD CQ <! Hl a O 0 O Q 3 ti fi

Φ 0 SD 3 o tr P fi CQ P *

P Φ Φ μ- a μ- CQ Q CQ

SD 3 SD a rt P φ fi α CQ fi

CQ fi Φ Hi μ> φ SD P μ- o μ- Φ P a P P N p a φ

0 = Öd P μ- fi Φ CQ CQ ti μ- CQ rt

Φ ra CQ φ fi ti φ Φ a μ- 3 μ-

H Φ SD = a tr W μ- $, φ Φ ö φ μ- P P φ ti φ μ- t

P. öd ra Q SD μ- ti ti

Φ a φ φ μ-

N Ω P φ

Φ tr N P μ- Z Φ Q μ- φ fi Hi rt 3 μ- CQ a =

Φ rt _^ fi

P H φ

P a tr φ

Ω P Φ μ-

Φ Φ N μ- a

0 P a Φ

3 pr Hi P φ 0 = a = φ rt fi tr 3 a fi ts fi ra μ- Φ a P Hi

Φ ü a φ a =

P CQ fi tr

CD Φ fi μ- PN a ra za rt φ CQ μ- CQ rt 1 Φ

o t to μ> o cπ o cπ o cπ

can be formed, for example, as milled air inlet slots or as rows of air inlet bores.

The combinations of the feed channels and the arrangement or configuration of the outlet openings in the feed channels mentioned in the preceding and subsequent examples can be changed or combined with one another as desired. Thus, all variants of the outlet opening arrangements shown in FIGS. 4 to 7 can also be used in the embodiments of FIGS. 8 to 16. This applies both to the distribution, the number and the arrangement of the individual outlet openings. Furthermore, different hole diameters can be used in all of the variants shown in the two feed channels. In this way, a certain admission pressure and a desired exit speed can be set in the stage which is to take up a smaller amount of fuel. There are no limits to the possible combinations of the individual design variants. The person skilled in the art will choose the appropriate arrangement depending on the desired application condition and desired effects. In particular, it is in no way imperative to arrange the outlet openings equidistantly in the axial direction, as is implied in all drawings. On the contrary, it can be extremely advantageous to arrange the outlet openings for the premixed fuel in an arbitrary • axial distribution, or others

Implement distribution rules, such as a geometric grading of the axial distances. The same applies to the use of different burner geometries or the combination of swirl generators with inner bodies or premix pipes. It is apparent to the person skilled in the art that the present invention can be implemented with a wide variety of burner types and combinations of swirl bodies, inner bodies, pre-mixing tubes and other known burner features.

Further very advantageous embodiments of a burner can be seen in FIGS. 19 to 21. The burners shown comprise the conical swirl body 1, in the outer formwork of which a first group of outlet openings 6 for premixing gas are arranged on the inflow edges of the air inlet slots. The burners are also equipped with a central fuel lance 12, which can have a nozzle at its end on the combustion chamber side, ie at its tip, as in the present example, which can be used for a liquid fuel 13 or for a pilot fuel. Outlet openings for shielding air 14 can be provided around this nozzle in a known manner. In addition to the fuel feeds to the first group of outlet openings 6 and a fuel feed for the injection of liquid fuel 13 at the tip of the fuel lance 12, the burners shown have a further fuel feed to a second group of outlet openings 8 in the fuel lance 12. The outlet openings 8 of the second group are arranged essentially in the direction of the burner axis in the lateral surface of the fuel lance 12, as can be seen in FIGS. 19 to 21, and are preferably radially symmetrical about the axis of the fuel lance

SD tö tsi Si tr ¹ P CQ Pi td <a td <! tu

P fi μ- Φ SD Φ fi Φ μ- Φ a μ- 0 ti

CQ φ Ω φ P Φ

Φ a tr μ- a P P Φ P Ω ti P.

Ω a a r rt Pi P t) a rt rt ö Φ ö N _l- et Φ Ω & P. P

SD Φ Φ fi fi Φ Φ a μ- fi ra φ CQ

CQ fi Φ SD td SD Ö a s: a 0 = a fi rt

CQ ra μ- Ω μ * <μ- Φ Q a I) a O rt P fi h- ¹ Φ μ- a φ CQ öd Hi φ 0 φ a fi öd fi ^ a CQ fi Hi

P ti SD fi SD öd a μ- a P- <! Φ tö φ D ti a φ a fi Q P. D μ- 0 P SD φ fi a Φ 3 P 3 φ CQ φ a φ rt a P P

P a SD P Hl CQ ra N ti Pi Pi <fi Φ Φ a rt 3 φ öd rt Φ μ- Φ μ- O SD fi fi CQ μ- to Hl Pi fi fi 0

Φ fi φ a CQ CQ rt o P SD Φ φ Hl μ> tr Φ rt O a Hi a a fi a Hl t r P. -_1. a fi Hi Φ 0 CQ a a

S Φ φ a 0 Φ Hi a fi ra bd ra CQ SD <! φ a: ^> CQ, - - P Ω P fi fi rt rt P φ μ- Φ rt> τ- φ Pt SD a Φ μ- φ fi 0 tsi fi ra tö μ- ti μ- fi Φ aa fi Ω a μ - Hi φ rt φ fi μ- CQ a tsi P. a tr a rt Hi Φ

_* φ μ- rt • SD φ

_^ - _^ a rt ra rt μ> μ- a CQ rt a tö CQ a rt ra μ- to α P Φ CQ to Ω <μ> a = Φ 0 0

Φ a = a rt

Φ a 0 = H tr CQ t Ω a CQ Hi Hi c

P • ti fi Hl - tr Hi Hl P SD c tö Hi • a • ra P 1 a Φ Ω to tsi P Φ a a SD Ω Φ SD a a tr μ-

R a rt a μ. ti tϋ a tr ra ϊ ^> aa Φ φ rt fi aa μ- a H "μ- NQ Ü SD μ- N μ- CQ Φ CQ SD td fi Φ Φ fi a φ rt Φ Φ Φ tr μ- CQ CQ fi Pi a SD a fi φ P tr a Φ a μ- CQ φ> Φ 3

PP CQ μ- μ> Ω fi μ- to oo i co tr a - ¹ a 0 = φ tr oo. p. pr Φ aa fi CQ

Ω a Φ φ a P Φ 1 ra SD CQ fi P P i a fi N fi s 0 a Φ μ- a> μ- 0 tsi a Φ Φ CQ μ- £, 3 fi Ω

O ti a ti r φ P P tr a μ- μ- tr ti H CQ tsi SD = CQ SD 3 SD = Φ Ω Φ

Φ SD a a rt CQ μ- P SD ö tr P

CQ a CQ to o μ- Φ φ LQ X P μ- rt

<! φ CQ races * .. <! Ξ μ- μ- φ φ Φ P

O Φ ä, P a = i ¹ CQ D fi rt μ- a 0 a φ Ω r ^ tr 0 = Φ Φ Φ ti μ- μ- tr tr ¹ φ CQ φ φ rt μ- rt Ω μ- aa

P m CQ 0 fi N fi μ- Φ φ rt μ- ra a rt • tr rt SD SD

3 P CQ 1 tr Pi

SD μ- P. μ- <μ-

H 3 μ- a 0 SD φ ti

u co t H μ> o cπ o cπ o cπ

t

During the operation of these burners, both groups of outlet openings 6, 8 are charged with premix gas. The burner is ignited and started in an operating mode in which the premix gas is introduced into the swirl chamber mainly via the outlet openings 8 on the fuel lance 12, also referred to below as stage 1. As the load increases, the supply of the premix gas to stage 1 is reduced and the supply of premix gas via the first group of outlet openings 6, hereinafter referred to as stage 2, is increased. Such a distribution of the premixed fuel to stages 1 and 2 depending on the operating state of the burner can be seen in FIG. 22 as an example. In this way, for example, a gas turbine with such a burner can be operated from the ignition to the base load without a pilot stage.

The supply of fuel to stages 1 and 2 is independently controlled or regulated by suitable valves.

FIGS. 23 and 24 show examples of the supply of a fuel quantity PO to the burner. In both examples, the fuel line branches in order to divide the total fuel quantity PO into a fuel quantity PI for the first group of outlet openings 6 and a fuel quantity P2 for the second group of outlet openings 8.

In FIG. 23, the division or mass flow ratio is set via one valve each

15 and 16 in each of the branches. Figure 24 shows an embodiment in which a valve 16 before the branch to adjust the total amount of fuel PO and another valve 15 is arranged in the branch to the first group of outlet openings 6. By controlling the valve 15, the mass flow ratio between PI and P2 can also be changed here. Of course, in this example the valve 15 can also be arranged in the branching to the second group of outlet openings 8.

Furthermore, several burners can be supplied with fuel in the set mass flow ratio at the same time via such an arrangement, as is indicated by the dashed lines in the figures.

In both exemplary embodiments, the mass flow ratio P1 / P2 is controlled by actuating the valves depending on the operating state of the

Brenners changed. The change in the mass flow ratio can be controlled or regulated as a function of various measurement and operating parameters, as has already been stated in a previous part of the present description. The configurations shown are independent of the burner geometry and can be used with all burners of the previous exemplary embodiments.

LIST OF REFERENCE NUMBERS

1 swirl generator la swirl generator body lb swirl generator body lc swirl generator body ld swirl generator body

2 swirl rooms 3 burner axis

3a axis of a swirl generator part body

3b axis of a swirl generator part body

3c axis of a swirl generator body 3d axis of a swirl generator body

4 entry openings / louvers

5 first fuel feeds

6 first fuel outlet openings

7 second fuel feeds 8 second fuel outlet openings

9 inner body

10 premix tube

11 combustion air

12 fuel lance 13 liquid fuel

14 shielding air

15 control valve

16 control valve

PO total fuel quantity PI first premixed fuel

P2 second premix fuel nl first number of holes n2 second number of holes

Claims

claims

1. Method for operating a burner, which has at least one first fuel feed (5) with a first group arranged essentially in the direction of a burner axis (3)

Has fuel outlet openings (6) for introducing a first amount of premixed fuel into a swirl chamber and one or more second fuel feeds (7) with a second group of fuel outlet openings (8) arranged essentially in the direction of the burner axis (3), the second Fuel supplies (7) can be acted upon independently of the first fuel supply (5), in which the supply of the fuel via the first fuel supply lines (5) is controlled or regulated separately from the supply of the fuel via the second fuel supply lines (7) , characterized in that the first and second fuel feeds (5, 7) are fed the same fuel.

2. The method according to claim 1, characterized in that the / the first and second fuel feeds (5, 7) premixed fuel is supplied.

3. The method according to claim 1 or 2, characterized in that the first and second fuel feeds (5, 7) supply gaseous fuel. ω co to μ »o cπ o ι-π cπ

φ S! CQ <fi a = φ D. μ- Φ Hi rart P <tr N a tr P <CQ CQ SD P <CQ fi): φ a Φ aa tr μ- SD P fi a = rt fi SD φ ti a Φ SD: SD Φ Φ rt tr SD Φ Φ m fi pr m ti ra a P ra ra tr 0 μ- P. fi D Hl fi a Pi fi tr 0 tr P ü Hi rt 3 Φ ti Hl rt CQ ü CQ P. rt fi Hi φ a Hi Ω a = ra CQ a Hi li Hl SD = a Hi

Φ Φ a = a ü SD fi Φ t-3 φ φ a Hi tr fi SD tr P "μ- fi SD SD Hi P fi SD tr a Φ aa = tr μ- as: φ μ- P a 3 ra Ω tr rt fi SD CQ Ω tr Ω ISl CQ Ω tr fi ti tsi Ω ti rt Φ μ- P Ω CQ φ N tr fi aa tr tr fi tr a μ- tr ü rt öd tsi φ tr Φ rt. -, a t- ¹ <fi Φ aa Φ £.

Φ μ- Φ a -j μ- Φ φ a Hi φ Φ rt Hi CQ Φ ü P r a a CQ ra CQ P μ- CQ μ- CQ P a = CQ p

Φ -sa Ω a 0 = CQ D- μ- ti ts Φ rt φ fi Φ P. rt Φ -2 tr SD Φ μ- a LQ tr tsi Hi ra φ P tr ti _^ - _^ SD pr PP a μ- P ^ p μ- ti a pr p fi

P φ P a Hl 3 rt fi Φ fi φ LΠ a = a Φ SD φ <Φ D fi a Hi Φ D ra fi Φ 3 a μ- φ 3 φ - ^ tr a Ω _-- _^ . o P Ω P p P Ω rt CQ rt tr a rt a CQ P <Φ a tr O φ ω 3 P tr LQ P p tr

0 _^ μ- a CQ Φ 3 P 0 P fi μ- tsi fi N Φ μ- N

Hi ü CQ Φ CQ P- ra φ a a Φ 3 Φ Φ ra f Φ Φ P Φ Φ Φ

Hi φ P rt Φ Φ φ SD μ- P 3 P μ- μ- <rt a μ- μ- μ- μ-

N fi SD ω fi a ti μ- 3 rt CQ tö Φ s; Ω P φ Φ Hl Ω P _^ -. Φ Ω P a CQ μ- a rt Φ CQ fi tö a Φ tr Φ ti a rt tr φ Sl fi tr Φ

Hi CQ ra μ- Φ _^ ---. N Φ Φ fi μ- ¹ φ fi CQ P 3 rt 1 P 3 _^ - ^ CQ p 3 a = Φ a tr 03 2 P Φ aa Φ tr φ Φ Φ, - -. tö Φ rt Φ tr CQ μ- - - Φ P. P Hi aa N a rt P. μ- c-π μ, rt P <Φ rt Pi fi SD P Φ Φ μ- Φ Öd rt ra as: rt - φ - Φ ~ Φ φ a ~ Φ a 3 μ- μ- N rt fi fi tö ra rt Φ ti rt a fi fi fi

P rt φ aaa Φ Φ Φ rt 0 μ μ- P. aa P rt _^ -. P.

CQ Φ μ- φ Φ CQ P N P rt ii Hl Pi Ω SD! μ- a CQ SD Φ cπ SD

Φ P 3 ra Φ 3 P fi 0 Hi tsi μ- tr ra a a P rt ra P μ- - CQ P

P öd φ Hl Ω Φ ra μ- φ ra CQ 0 rt φ 3 1 a Φ CQ ra ra CQ fi 3 s! öd a = fi μ- LQ P ti P N Hl ti rt a ti

_^ -. Φ S: fi tr £ rt 0 tr φ a Φ Φ μ- fi Φ s; Hi CL- fi cπ a t-3 ü φ ti ti a P fi

Φ Hi ra μ- ra Hl fi P P

* - a = a Φ <Φ a Φ a = μ- P. Φ a =

3 a rt t ⁾ a Hi tsi P rt a = CQ μ- Ω μ- φ fi Ω P fi Ω

CQ μ- Φ a Φ 3 a CQ fi tr rt φ φ tr tö rt fi tr N tr

N rt Φ g td Φ ra φ μ- fi Φ μ- Φ ü Φ tr tö Φ a P. $, tö Φ

O fi ti μ- <! fi P rt tr rt rt a CQ P φ a (D: fi φ Φ μ,

CQ Hl SD tsi ra fi 0 φ CQ SD fi rt Φ φ φ i CQ φ ra φ HP μ- Φ μ ¹

H P a P Φ a SD a a öd CQ 3 a tö rt P rt p

Hi rt a CQ • PP Ω 0 = a fi SD tr Φ fi a P tr td Φ pa = N CQ φ tr a = tö CQ D. tr Hl P φ 3 Φ μ- fi φ μ- ra μ- fi aa CQ μ- tr tr a Φ 3 ti rt Φ s rt Hl a rt fi ra ra rr r Φ rt CQ ü Φ CQ fi P): φ 0 3 Φ t Hi aa = a Φ CQ Φ 0 P tö r fi rt * - ot Ö aa $. a tr ra rt CO μ- a CQ S- Hi ω P fi Hi.

SD a Hl cd μ- μ- a Φ rt tö Φ a rt Φ Hl -. Φ Φ Holy ».

3 P a Pi P ra N fi CQ fi CQ fi 0 fi P CQ - Hl o CQ fi μ- μ rt a Φ ra P Φ Φ φ Hl μ- a

D. SD Φ fi φ a

P. a 0 Hi P rt - a P Hi P ö 1 Hi tö p Φ 1 SD

Di a Hl a = P Φ μ- N a Φ 1 fi μ- CQ

- Φ fi Hl tr Φ P a .— -. φ a 1 1 φ P rt ra Ω I 1 fi ma σ \ I & 1 1 tr P ^ a 1 1

and that, at least in full load operation of the heat generator, the fuel is divided between the first fuel feeds (5) and at least one second fuel feed (7).

8. Burner, consisting essentially of one

Swirl generator (1) for a combustion air flow (11), a swirl chamber (2) and means for introducing fuel into the combustion air flow, the swirl generator (1) combustion air inlet openings (4) for the combustion air flow tangentially entering the swirl chamber (2) The means for introducing fuel into the combustion air flow have at least one first fuel feed (5) with a first one

Group of fuel outlet openings (6) arranged essentially in the direction of a burner axis (3) for a first premixed fuel quantity (PI) and the burner has one or more second fuel feeds (7) with a second group essentially in the direction of the burner axis (3) arranged fuel outlet openings (8) for a second fuel quantity (P2), which second fuel feeds (7) can be acted upon independently of the first fuel feeds (5), characterized in that in the swirl space (2) an inner body (9) is arranged, the fuel outlet openings (8) of at least one second fuel feed (7) being distributed essentially in the direction of the burner axis (3) on the inner body (9) are arranged.

9. Burner according to claim 8, characterized in that the inner body (9) is a fuel lance (12) which has at least one outlet nozzle for liquid fuel (13) and / or pilot fuel at its combustion chamber end.

10. Burner according to claim 8 or 9, characterized in that the fuel outlet openings (8) which are distributed on the inner body (9) in the direction of the burner axis (3) are arranged in an axial partial area of the inner body (9) remote from the end on the combustion chamber side. are arranged.

11. Burner according to one of claims 8 to 10, characterized in that the second group of fuel

Outlet openings (8) is designed for the supply of premix fuel.

12. Burner according to one of claims 8 to 11, characterized in that at least one of the groups of fuel outlet openings is arranged in the region of at least one of the combustion air inlet openings (4).

13. Burner according to one of claims 8 to 12, characterized in that a plurality of first fuel feeds (5) and a plurality of second fuel feeds (7) are provided, each of the first Fuel supply lines (5) is assigned to at least one second fuel supply line (7).

14. Burner according to one of claims 8 to 13, characterized in that second fuel feeds (7) are arranged immediately adjacent to first fuel feeds (5).

15. Burner according to one of claims 8 to 14, characterized in that the combustion air inlet openings (4) are tangential inlet slots running essentially in the direction of the burner axis (3).

16. Burner according to claim 15, characterized in that a first fuel feed (5) with a first group of fuel outlet openings (6) is arranged along each inlet slot.

17. Burner according to claim 15 or 16, characterized in that at least one second fuel feed (7) with a second group of fuel outlet openings (8) is arranged along each inlet slot.

18. Burner according to one of claims 8 to 17, characterized in that the fuel outlet openings (8) of one or more second fuel inlets (7) at axial positions between the fuel outlet openings (6) of one or more first fuel inlets (5) are arranged. ω co co ¹ o cπ o cπ o cπ to co to to H ω co μ> o CO

N Öd t) P. td td rt> td φ CQ td a SD fi Φ SD fi μ- Φ a μ- μ- Φ ü

3 CQ Φ p ra φ P ü CQ a P PC φ μ- ra P ra a rt Φ rt rt Φ Φ a a P P fi a fi fi 3 a a

P. CQ Φ P. φ μ- μ- μ- a Φ φ μ- fi μ- fi rt SD rt rt φ N ü ra Ω φ rt X rt rt fi Φ rt tr P P m μ- CQ ra ra μ-

SD SD SD a

0 = SD 0 = 0 = rt Ω SD rt, Ω X Ω Hi Hi Hl Φ tr Ω

Φ Φ tr μ- P ^J Hi Φ Hi Hi PP tr μ- P SD P aa P Φ μ- ¹ μ- - ¹ aaa SD rt Φ

= ^» CQ Φ & a H aa X ~ μ- φ ra CQ a CQ CQ Φ CQ CQ μ- P μ- rt ti t) Φ μ- Φ Φ SD P φ ra φ fi μ. ti a ^j aa SD 3 φ P a φ a tr Φ CQ ra Ω μ- Ω -— - φ - _^ . , - ^ P ra P. a = tr t hü. fi σ>. Φ tr tsi tr ~ - ^ Φ ~ - 'm Pi ü

Φ 3 to Φ co μ- Φ μ- ι fi φ μ> fi μ><Ω 00 a μ- Φ> μ- ^• «Φ - Φ tr PP

SD μ- ti Φ P. tr öd ra i P Pi Ω (X rt P SD Φ ü ti i φ SD tr SD Φ a P. fi φ ti

Φ fi P φ P μ- P P μ- φ P a = a • a a Φ Φ φ μ- P Ω

SD H ar fi rt fi fi Ω CQ tr

X Ω μ- Ω Φ td t rt Φ μ- tr Ω t CQ td fi fi 0

SD tr μ- fi φ Pi Hl oo

CQ LQ a Φ Ω P Φ Hl

Φ Φ P Φ P P fi P ti 1 tr

P PC μ- pc • P a m to μ-

Φ Ω Φ μ ^j ti et öd a CQ μ] P tr aat) o ti ra φ P rt P Hl φ Hl Φ et μ> μ- NN rt a Hi P 00

Φ a = Φ 1 1 P μ- tr μ- tr μ- SD ct

Φ Ω Φ Ω aa rt P- fi tri tr Hi Hi ra SD φ PH ¹ P rt 1 P μ- Φ SD Φ $, 1

Ω rt ti rt Φ a

H tr - 1 * "μ- Ω

Φ ι tr

24. Burner according to one of claims 8 to 23, characterized in that the fuel outlet openings (6, 8) of two or more groups have different flow cross-sections.

25. Burner according to one of claims 8 to 24, characterized in that means are provided for independently controlling the premix fuel supply to the one or more (5) and to the or the second fuel supply (7).

26. Burner according to claim 25, characterized in that the means for independently controlling the premix fuel supply have a common fuel line, which leads into a first supply line to the first or the first (5) and in a second supply line to the or the second fuel supply ( 7) branches, a valve (15, 16) for adjusting the flow rate of fuel being arranged in at least one of the supply lines.

27. Burner according to one of claims 8 to 26, characterized in that several of the second fuel feeds (7) can be supplied with fuel independently of one another.