EP0781967B1 - Gasturbinenringbrennkammer - Google Patents
Gasturbinenringbrennkammer Download PDFInfo
- Publication number
- EP0781967B1 EP0781967B1 EP96810777A EP96810777A EP0781967B1 EP 0781967 B1 EP0781967 B1 EP 0781967B1 EP 96810777 A EP96810777 A EP 96810777A EP 96810777 A EP96810777 A EP 96810777A EP 0781967 B1 EP0781967 B1 EP 0781967B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- combustion chamber
- gas
- air
- turbine
- chamber according
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
- F23R3/00—Continuous combustion chambers using liquid or gaseous fuel
- F23R3/02—Continuous combustion chambers using liquid or gaseous fuel characterised by the air-flow or gas-flow configuration
- F23R3/04—Air inlet arrangements
- F23R3/10—Air inlet arrangements for primary air
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
- F23R3/00—Continuous combustion chambers using liquid or gaseous fuel
- F23R3/02—Continuous combustion chambers using liquid or gaseous fuel characterised by the air-flow or gas-flow configuration
- F23R3/04—Air inlet arrangements
- F23R3/045—Air inlet arrangements using pipes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
- F23R3/00—Continuous combustion chambers using liquid or gaseous fuel
- F23R3/28—Continuous combustion chambers using liquid or gaseous fuel characterised by the fuel supply
- F23R3/286—Continuous combustion chambers using liquid or gaseous fuel characterised by the fuel supply having fuel-air premixing devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
- F23R3/00—Continuous combustion chambers using liquid or gaseous fuel
- F23R3/42—Continuous combustion chambers using liquid or gaseous fuel characterised by the arrangement or form of the flame tubes or combustion chambers
- F23R3/50—Combustion chambers comprising an annular flame tube within an annular casing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
- F23R2900/00—Special features of, or arrangements for continuous combustion chambers; Combustion processes therefor
- F23R2900/03041—Effusion cooled combustion chamber walls or domes
Definitions
- the invention relates to the field of combustion technology. It relates to a gas turbine ring combustion chamber, which is operated with premix burners, and a method for Operation of this device.
- Gas turbines essentially consist of the components compressor, Combustion chamber and turbine. For environmental reasons is increased instead of diffusion combustion worked with a low-pollutant premix combustion.
- the air coming out of the compressor is very high Speed (approx. 200 m / s) and is to the contained in it Recover kinetic energy, as lossless as possible delayed in a deflection diffuser.
- the speed in the combustion chamber strong at least locally downstream of the burner lowered. Usually a local recirculation zone with negative Speeds generated. In the combustion chamber the speed then about 50 m / s to a sufficient Preservation time and the heat transfer between hot gas and to keep the combustion chamber wall small. At the exit of the The combustion chamber accelerates again, so that on Entry of the turbine speeds up to close to the gas the speed of sound can be reached.
- the invention tries to avoid all these disadvantages. you is based on the task of a gas turbine ring combustion chamber, which is equipped with special premix burners develop, which is characterized by a small size and simplified compared to the known prior art is, with improved premixing of fuel and Air occurs with a lower total pressure drop.
- this is done in a gas turbine ring combustion chamber, which is arranged downstream of a compressor and on it Front plate with at least one arranged in a ring Premix burner row is equipped, achieved by direct downstream of the compressor outlet from the guide vanes of the last compressor series for each burner one as Diffuser-trained burner air duct leads to the latter downstream end there is at least one longitudinal vortex generator is located, at least in or downstream of the longitudinal vortex generator a fuel injection is provided and downstream the fuel injection ends in the combustion chamber Mixing channel of constant channel height and with a length that is approximately corresponds to twice the hydraulic duct height, is arranged.
- the combustion air is released immediately after it leaves the compressor into individual air flows for the burners and for the Cooling of the combustion chamber and turbine split, after that the speed of the air for the burners to about that delayed half the value of the compressor outlet speed, then at least one longitudinal vortex per combustion air duct generated in the air, during or downstream of the Longitudinal vortex generation fuel is added to the mixture now flows along in a mixing channel and with a total swirl contaminated flows into the combustion chamber and there finally burns.
- the advantages of the invention include that the combustion chamber compared to the prior art has smaller dimensions and the area to be cooled in the Combustion chamber is reduced. The pressure loss between the compressor outlet and turbine entry is smaller. Furthermore there is a very good and robust uniform distribution of the air on the burners and the premixing of fuel and combustion air will be improved.
- the ratio of the number the blades of the last row of compressors to the number of premix burners is an integer, especially 1 or 2, because then a combustion air duct directly to one or two blade ducts the last row of compressors can be coupled.
- the mixing channel is approximately rounded Cross-section, because then a good mixing of air and fuel is achieved. But also mixed channels with a rectangular cross section are conceivable. Likewise can if there is only one burner row, the mixing channel be designed as a segmented annular gap.
- combustion air channels are spiral are arranged around the axis of the gas turbine. In this way axial length can be saved.
- the axes of the mixing channels are advantageous (i.e. the direction of flow of the entering the combustion chamber Mixture), arranged so that it coincides with the axis of the Gas turbine an angle, preferably an angle of 45 °, form. This will allow the mixture and flame stabilization further improved.
- FIG. 1 shows a partial longitudinal section of a gas turbine system with an annular combustion chamber according to the prior art.
- an annular combustion chamber 4 Between a compressor 1 and a turbine 2, of which only one guide vane 3 of the first row of guide vanes is shown is an annular combustion chamber 4, which with premix burners 5 of the double cone design is equipped, arranged.
- the supply of fuel 6 to each premix burner 5 is realized over fuel lances 7.
- the annular combustion chamber 4 is cooled convectively or by means of impingement cooling.
- the compressor 1 essentially consists of the blade carrier 8, in which the guide vanes 9 are hooked in and out of the rotor 10, which receives the blades 11. In Fig. 1 are each only the last compressor stages are shown.
- a deflection diffuser 12 At the exit of the Compressor 1, a deflection diffuser 12 is arranged. It ends in a arranged between the compressor 1 and the annular combustion chamber 4 Plenary 13.
- the air 14 emerging from the compressor 1 has a very high high speed. It is delayed in the deflection diffuser 12, to recover the kinetic energy it contains so that in the adjoining the deflection diffuser 12 Plenary 13 only very low air speeds to rule. This can result in a uniform distribution of the air 14 the burner 5 can be reached and there can be cooling air without any problems for the combustion chamber 4 and the turbine 2 are removed. There but on the other hand for the reliable design of the premixing process of air 14 and fuel 6 at the mixing point the fuel 6 the speed in order to avoid must be high from flashback, the air 14 in the premixing zone be accelerated again strongly before again downstream of the burner 5 in the combustion chamber 4 for reasons of flame stability the speed is reduced.
- Air 14 is no longer delayed to plenary conditions, but instead the delay in the air 14 is only limited to that Speed level of the premix section. This allows the multiple redirection of the total air mass flow is eliminated and the size of the combustion chamber is significantly reduced become.
- each burner 5 of the annular combustion chamber 4 each designed as a diffuser Burner air duct 15 leads.
- At least one fuel injection 17 is provided and downstream of the fuel injection 17 is in the combustion chamber 4 ending mixing channel 19 of constant height H and with a length L, which is about twice the value of the hydraulic channel diameter D corresponds to arranged.
- the deflection diffuser 12 and 12 is therefore omitted plenary session 13.
- the air from the compressor 1 is immediately after the outlet from the compressor 1 into a large number of individual channels divided, namely into the combustion air channels 15 and in annular Channels 20 arranged on the hub side or housing side for the cooling air 21 of the combustion chamber 4 and the turbine 2, the is provided here at a high pressure level. Furthermore can air 22 from the channels 20 for flushing out the Mixing channel 19 forming boundary layer can be removed. This is only an example for the innermost mixing channel 19 shown.
- the combustion air channels 15 are designed as diffusers and delay the air speed to about half the value the compressor outlet speed, with a maximum of 75% of the dynamic energy can be converted into pressure gain.
- the longitudinal vortex generator 16 After the combustion air 14 to an appropriate speed level was delayed at the longitudinal vortex generator 16 generates one or more longitudinal vortices per combustion air duct 15.
- the longitudinal vortex generator 16 is an integrated Fuel injection 17 fuel 6, which for example is supplied by fuel lances 7, mixed with the air 14.
- the fuel injection 17 also downstream of the longitudinal vortex generator 16 may be arranged.
- the longitudinal vortices generated guarantee a good mixture of fuel 6 and combustion air 14 in the subsequent mixing channels 19. These have a constant height H and are approximately double as long as two hydraulic channel diameters D.
- the mixing channels 19 have a circular shape Cross section, are therefore a mixing tube.
- the mixing tube axes 24 are arranged parallel to the axis 25 of the gas turbine.
- the mixing channels 19 not shown here in the drawing can the mixing channels 19 a right or have polygonal cross-section or they can also be a segmented annular gap.
- FIGS. 1 and 2 the reduction in the area of the combustion chamber wall to be cooled can be clearly seen according to the invention.
- a gas turbine from the 170 MWel class, eg GT13E2 should serve as an example. While according to the prior art (FIG. 1) the outer diameter in the area of the combustion chamber is approximately 4.5 m, this value is only 3.5 m when using the invention, so that the size is reduced by approx. 20% is reached. Due to the greatly reduced area to be cooled in the new combustion chamber and the extremely low NOx emissions that can be achieved with good premix burner technology at relatively high flame temperatures (theoretically approx. 5 ppm NOx at 15% O 2 and 1850 K flame temperature), the combustion chamber can be cooled via film or effusion cooling.
- FIG. 3 is a partial cross section of a two-row annular combustion chamber corresponding to a section in the plane III-III of the in Fig. 2 shown four-row combustion chamber.
- the annular combustion chamber 4 according to FIG. 3 is thus with two rows Premix burners 5 equipped.
- the arrows in Fig. 3 are intended an opposite angle of attack of the burner 5 in the side by side Clarify rows. By this opposite Angle of attack is achieved in the combustion chamber 4 no total swirl is generated.
- the cross section of the mixing channels 19 is not round in this embodiment, but elliptical.
- the mixing tube axes 24 are opposite the shaft in the circumferential direction, i.e. the mixing tube axis 24 forms an angle of ⁇ with the machine axis 25 approx. 45 °. This will allow the mixture and flame stabilization improved in the combustion chamber 4.
- combustion air channels 15 spiral about the axis 25 of the Gas turbine arranged to the axial length of the machine to keep it as small as possible.
- the invention is particularly suitable for the use of MBtu as fuel, i.e. fuel with a medium calorific value, for example in the gasification of heavy oil, coal and Tar arises.
- the fuel admixture can be used in this case very easily into a higher speed range (> 100 m / s) to be relocated to these fuels, too are characterized by a high flame speed, to avoid backfire to the fuel injector.
- the high-frequency generated by the last row of compressor runs (> 1000 Hz) pressure pulsations (wake of the blades) particularly support the fuel-air mixing process, because between the end of the compressor 1 and the fuel injection 17 only a short delay section, i.e. a short burner air duct 15 designed as a diffuser, is required
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Description
- Fig. 1
- einen Teillängsschnitt einer Gasturbinenanlage mit einer mit Vormischbrennern bestückten Ringbrennkammer nach dem Stand der Technik;
- Fig. 2
- einen Teillängsschnitt einer Gasturbinenanlage mit einer erfindungsgemässen vierreihigen Ringbrennkammer;
- Fig. 3
- einen Teilquerschnitt einer zweireihigen Brennkammer entsprechend einem Schnitt in der Ebene III-III der in Fig. 2 dargestellten vierreihigen Brennkammer;
- Fig. 4
- eine Abwicklung der Vormischstrecke (entlang IV-IV in Fig. 3) zwischen Verdichteraustritt und Brennkammerfrontplatte .
- 1
- Verdichter
- 2
- Turbine
- 3
- Leitschaufel von Pos. 2
- 4
- Ringbrennkammer
- 5
- Vormischbrenner
- 5a
- äussere Brennerreihe
- 5b
- innere Brennerreihe
- 6
- Brennstoff
- 7
- Brennstofflanze
- 8
- Schaufelträger
- 9
- Leitschaufel von Pos. 1
- 10
- Rotor
- 11
- Laufschaufel von Pos. 1
- 12
- Umlenkdiffusor
- 13
- Plenum
- 14
- Luft
- 15
- als Diffusor ausgebildeter Brennluftkanal
- 16
- Längswirbelerzeuger
- 17
- Brennstoffeindüsung
- 18
- Frontplatte
- 19
- Mischkanal
- 20
- Kanal für Pos. 21
- 21
- Kühlluft
- 22
- Luft zur Ausspülung der Grenzschicht in Pos. 19
- 23
- Brennstoff/Luft-Gemisch
- 24
- Achse von Pos. 19
- 25
- Maschinenachse
- H
- Höhe von Pos. 19
- L
- Länge von Pos. 19
- D
- hydraulischer Kanaldurchmesser
- α
- Winkel zwischen Pos. 24 und 25
Claims (15)
- Gasturbinenringbrennkammer (4), welche stromab eines Verdichters (1) angeordnet und auf ihrer Frontplatte (18) mit mindestens einer ringförmig angeordneten Reihe von Vormischbrennern (5) bestückt ist, dadurch gekennzeichnet, dass direkt stromab des Verdichteraustritts von den Leitschaufeln (9) der letzten Verdichterreihe zu jedem Brenner (5) jeweils ein als Diffusor ausgebildeter Brennluftkanal (15) führt, an dessem stromabwärtigen Ende sich mindestens ein Längswirbelerzeuger (16) befindet, wobei im oder stromab des Längswirbelerzeugers (16) mindestens eine Brennstoffeindüsung (17) vorgesehen ist und stromab der Brennstoffeindüsung (17) ein in die Brennkammer (4) endender Mischkanal (19) konstanter Höhe (H) und mit einer Länge (L), die etwa dem zweifachen Wert des hydraulischen Kanaldurchmessers (D) entspricht, angeordnet ist.
- Gasturbinenringbrennkammer nach Anspruch 1, dadurch gekennzeichnet, dass das Verhältnis der Anzahl der Schaufeln (9) der letzten Verdichterreihe zur Anzahl der Vormischbrenner (5) ganzzahlig ist.
- Gasturbinenringbrennkammer nach Anspruch 2, dadurch gekennzeichnet, dass das Verhältnis der Anzahl der Schaufeln (9) der letzten Verdichterreihe zur Anzahl der Vormischbrenner (5) Eins ist.
- Gasturbinenringbrennkammer nach Anspruch 2, dadurch gekennzeichnet, dass das Verhältnis der Anzahl der Schaufeln (9) der letzten Verdichterreihe zur Anzahl der Vormischbrenner (5) Zwei ist.
- Gasturbinenringbrennkammer nach Anspruch 1, dadurch gekennzeichnet, dass die Brennluftkanäle (15) spiralig um die Achse (25) der Gasturbine angeordnet sind.
- Gasturbinenringbrennkammer nach Anspruch 1, dadurch gekennzeichnet, dass der Mischkanal (19) einen runden Querschnitt aufweist.
- Gasturbinenringbrennkammer nach Anspruch 1, dadurch gekennzeichnet, dass der Mischkanal (19) einen rechteckigen Querschnitt aufweist.
- Gasturbinenringbrennkammer nach Anspruch 1, dadurch gekennzeichnet, dass der Mischkanal (19) ein segmentierter Ringspalt ist.
- Gasturbinenringbrennkammer nach Anspruch 1, dadurch gekennzeichnet, dass die Achsen (24) der Mischkanäle (19) und die Achse (25) der Gasturbine parallel sind.
- Gasturbinenringbrennkammer nach Anspruch 1, dadurch gekennzeichnet, dass die Achsen (24) der Mischkanäle (19) mit der Achse (25) der Gasturbine einen Winkel (α) bilden.
- Gasturbinenringbrennkammer nach Anspruch 10, dadurch gekennzeichnet, dass der Winkel (α) etwa 45° beträgt.
- Gasturbinenringbrennkammer nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass bei mehr als einer ringförmigen Vormischbrennerreihe die Brenner (5) von Reihe (5a) zu Reihe (5b) gegensinnig in Umfangsrichtung angestellt sind.
- Verfahren zum Betrieb einer Gasturbinenringbrennkammer nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass die Verbrennungsluft (14) direkt nach Austritt aus dem Verdichter (1) in einzelne Luftströme für die Brenner und für die Kühlung der Brennkammer und Turbine aufgeteilt wird, dass danach die Geschwindigkeit der Luft (14) für die Brenner (5) in den Brennluftkanälen (15) auf etwa den halben Wert der Verdichteraustrittsgeschwindigkeit verzögert wird, dass anschliessend pro Brennluftkanal (15) mindestens ein Längswirbel in der Luft (14) erzeugt wird, wobei während oder stromab der Längswirbelerzeugung Brennstoff (6) beigemischt wird, das Gemisch in einem Mischkanal (19) entlangströmt und mit einem Gesamtdrall behaftet in die Brennkammer (4) strömt und dort verbrennt.
- Verfahren nach Anspruch 13, dadurch gekennzeichnet, dass zusätzlich Luft (22) in die Grenzschicht des Mischkanales (19) eingedüst wird.
- Verfahren nach Anspruch 13, dadurch gekennzeichnet, dass bei Verwendung von Brennstoff (6) mit mittlerem Heizwert (MBtu) dieser in einen Bereich hoher Luftgeschwindigkeit von grösser 100 m/s eingemischt wird.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19549143 | 1995-12-29 | ||
DE19549143A DE19549143A1 (de) | 1995-12-29 | 1995-12-29 | Gasturbinenringbrennkammer |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0781967A2 EP0781967A2 (de) | 1997-07-02 |
EP0781967A3 EP0781967A3 (de) | 1999-04-07 |
EP0781967B1 true EP0781967B1 (de) | 2003-04-02 |
Family
ID=7781645
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96810777A Expired - Lifetime EP0781967B1 (de) | 1995-12-29 | 1996-11-12 | Gasturbinenringbrennkammer |
Country Status (5)
Country | Link |
---|---|
US (1) | US5839283A (de) |
EP (1) | EP0781967B1 (de) |
JP (1) | JPH09196379A (de) |
CN (1) | CN1088151C (de) |
DE (2) | DE19549143A1 (de) |
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-
1995
- 1995-12-29 DE DE19549143A patent/DE19549143A1/de not_active Withdrawn
-
1996
- 1996-11-12 EP EP96810777A patent/EP0781967B1/de not_active Expired - Lifetime
- 1996-11-12 DE DE59610298T patent/DE59610298D1/de not_active Expired - Fee Related
- 1996-11-18 US US08/751,721 patent/US5839283A/en not_active Expired - Fee Related
- 1996-12-25 JP JP8345880A patent/JPH09196379A/ja not_active Abandoned
- 1996-12-27 CN CN96123618A patent/CN1088151C/zh not_active Expired - Fee Related
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Publication number | Publication date |
---|---|
CN1158383A (zh) | 1997-09-03 |
EP0781967A2 (de) | 1997-07-02 |
EP0781967A3 (de) | 1999-04-07 |
DE19549143A1 (de) | 1997-07-03 |
US5839283A (en) | 1998-11-24 |
DE59610298D1 (de) | 2003-05-08 |
JPH09196379A (ja) | 1997-07-29 |
CN1088151C (zh) | 2002-07-24 |
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