EP1137899B1 - Verbrennungsvorrichtung und verfahren zur verbrennung eines brennstoffs - Google Patents
Verbrennungsvorrichtung und verfahren zur verbrennung eines brennstoffs Download PDFInfo
- Publication number
- EP1137899B1 EP1137899B1 EP99964516A EP99964516A EP1137899B1 EP 1137899 B1 EP1137899 B1 EP 1137899B1 EP 99964516 A EP99964516 A EP 99964516A EP 99964516 A EP99964516 A EP 99964516A EP 1137899 B1 EP1137899 B1 EP 1137899B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- combustion
- fuel
- flow
- combustion device
- region
- 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.)
- Revoked
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 100
- 239000000446 fuel Substances 0.000 title claims abstract description 36
- 238000000034 method Methods 0.000 title claims description 12
- 239000012530 fluid Substances 0.000 claims abstract description 51
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 claims description 16
- 239000007789 gas Substances 0.000 claims description 9
- 239000003345 natural gas Substances 0.000 claims description 8
- 230000015572 biosynthetic process Effects 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000002737 fuel gas Substances 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
Classifications
-
- G—PHYSICS
- G10—MUSICAL INSTRUMENTS; ACOUSTICS
- G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
- G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
- G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
- G10K11/161—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general in systems with fluid flow
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
- F23M20/00—Details of combustion chambers, not otherwise provided for, e.g. means for storing heat from flames
- F23M20/005—Noise absorbing means
-
- 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
-
- 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
- F23R2900/00014—Reducing thermo-acoustic vibrations by passive means, e.g. by Helmholtz resonators
Definitions
- the invention relates to a combustion device for combustion a fuel, the fuel being a Fluid flow can be fed to the combustion via a feed channel is.
- the invention also relates to a corresponding method.
- outflow processes are described in chapter 5.6.
- Outflow processes of a fluid from a container in which the fluid is stored at pressure p i and density ⁇ i are shown in more detail.
- the fluid exits the container as a jet, the jet pressure p a prevailing in the jet.
- the pressure ratio at which the given container state - i.e. given container pressure ⁇ i and given fluid density ⁇ i and given container opening from which the fluid exits - the mass flow of the fluid no longer changes as the critical pressure ratio (p a / p i ) (k) .
- p a / p i Depending on the size of the pressure ratio p a / p i, a distinction is made between two types of outflow processes: 1. Subcritical outflow; 2. Supercritical outflow.
- a Laval nozzle is described in section 5.6.2 of the same book.
- the Laval nozzle serves the outflowing fluid to expand beyond the critical pressure ratio and thus the flow velocity over the speed of sound increase beyond.
- the fluid is first of all compresses a narrowing channel, the Flow rate increased to the speed of sound.
- An expanding channel section follows in which the fluid expands and the flow rate Supersonic range reached.
- Such a Laval nozzle serves e.g. to achieve maximum outflow speeds for shear gases of rocket engines.
- the Laval nozzle is behaving here like a venturi tube. For the definition of a Venturi tube follow further details below.
- Section 5.7 of the same book contains compression flows described.
- Section 5.7.1 explains how a Subsonic diffuser.
- Subsonic diffusers are in the direction of flow extended channels, one in the subsonic area current is delayed. Through the Delay there is an increase in pressure.
- Subsonic diffusers can be found, for example, in jet devices, venturi tubes and in the idlers and outlet housings of turbocompressors.
- Section 5.7.2 describes a supersonic diffuser where the channel cross-section changes in the direction of flow narrows.
- the European standard EN ESO 5167-1 concerns flow measurements of fluids with throttling devices.
- part 1 are bezels, Nozzles and Venturi tubes in fully flowed lines with Circular cross section described.
- Figure 10 shows a classic one Venturi tube.
- the Venturi tube flows along a flow direction a fluid.
- the venturi tube consists of one narrowing in the flow direction inlet cone and a adjoining the inlet cone in the direction of flow, widening outlet cone.
- A is created in the inlet cone large pressure loss. This is through the outlet cone Pressure loss made up for the most part, so that the overall through the Venturi tube compared to a tube with unchangeable Cross section and the same length Pressure loss remains small.
- EP-A-122 526 discloses a fuel lance that operates simultaneously both the decoupling of the fuel line to avoid of combustion vibrations as well as the possibility fuel regulation.
- the fuel lance carries an adjustable, with fuel passage openings provided throttle body, the penetration depth compared to that solid body a measure of the amount of fuel flowing through is.
- the object of the invention is to provide a combustion device, those in terms of control and influence the spread and formation of a burn induced sound waves has favorable properties.
- Another object of the invention is to provide a corresponding Process.
- this object is achieved by specifying a Combustion device for burning fuel with a supply channel for supplying the fuel to one Combustion zone, with the fuel as a fluid stream a flow direction and one in a nominal operating interval nominal speed through the feed channel is feasible and wherein the supply channel in a decoupling area is narrowed, the decoupling area as one continuous narrowing of the feed channel along the flow direction is designed so that from the combustion zone Sound waves running in the fluid flow against the direction of flow at least at the nominal speed in the decoupling area partially reflected.
- combustion vibrations can result arise that with a fluctuation in a power release a pressure pulse occurs in the fluid flow during combustion.
- a pressure pulse in the fluid stream in turn has one Non-uniformity in the mass flow into the combustion zone resulting fluid flow. This leads to again a fluctuating release of power during combustion.
- the geometric designs of the feed channel it can help build positive feedback between pressure pulses in the fluid flow and the fluctuating Power release when combustion comes. It forms a combustion oscillation.
- Such a combustion vibration can e.g. as a significant noise pollution disruptive.
- the Invention is based on the knowledge that the spread of sound waves in the fuel via the feed channel into further, acoustically coupled areas the tendency to training such combustion vibrations favored.
- a acoustic decoupling of the feed channel or several This mechanism prevents fuel supply channels.
- Such an acoustic decoupling is by a Narrowing of the feed channel or feed channels reached.
- narrowing in the direction of flow increases Flow velocity of the fluid.
- the flow rate can be increased so far that contrary to the Direction of flow against the narrowing sound waves be reflected.
- the constriction is designed so that at a nominal velocity of the fluid flow in the supply channel at the constriction such a high acceleration of the Fluids reveals that a high proportion of those against the narrowing current sound waves is reflected.
- the nominal speed lies e.g. within a speed interval, such operating conditions of the combustion device corresponds to those with a high tendency to training of combustion vibrations.
- the decoupling area is considered a continuous one Narrowing of the feed channel along the flow direction educated. Result from such a continuous narrowing less than a discontinuous narrowing Flow and pressure losses due to turbulence.
- a such continuous narrowing could e.g. B. something like that be trained, such as that in the above-mentioned book by Willi Bohl described supersonic diffuser.
- a pressure increase area the one Expansion of the feed channel corresponds.
- the Passage from the decoupling area and pressure increase area corresponds to e.g. that in the European given above Standard Venturi tube or a Laval nozzle.
- Such a configuration is particularly advantageous if when a high fluid mass flow has to be provided.
- the fuel is preferably natural gas or oil.
- the combustion zone is preferably located in a combustion chamber.
- the combustion chamber can have any shape, special meaning but comes a tubular or an annular Combustion chamber too.
- Combustion vibrations can occur in a combustion chamber through an interaction of a fluctuation in performance in the combustion and acoustic modes of the Form the combustion chamber.
- Such combustion chamber vibrations can spread out in fluidically coupled rooms, e.g. into the supply lines of fuel or air and possibly up to a supply pump, which makes it mechanically strong can be loaded.
- An acoustic decoupling by means of the tapering of the feed channel prevents such Propagation of combustion chamber vibrations.
- the Tendency to develop combustion chamber vibrations at all reduced, because the available for the combustion chamber vibrations standing acoustic resonance space by decoupling the feed channel is reduced.
- the combustion device is preferably a gas turbine, especially with an annular combustion chamber.
- a gas turbine With a gas turbine there is a particularly high level of power release the combustion.
- Combustion vibrations can be here to particularly large noise pollution and damaging vibrations to lead.
- There are acoustic modes in an annular combustion chamber due to the complicated geometry practically unpredictable, so that the formation of combustion chamber vibrations is particularly difficult to prevent here.
- the acoustic decoupling between the ring combustion chamber and the feed channels the combustion media is of particular importance here.
- the object is also achieved according to the invention by giving a method of burning fuel, the Fuel as a fluid flow with a flow direction a flow direction and one in a nominal operating interval nominal speed fed to a combustion zone is and wherein the fluid flow in a decoupling area is tapered, the fluid flow in the flow direction is continuously narrowed so that from the combustion zone running in the fluid flow against the direction of flow Sound waves at the nominal speed in the decoupling area be at least partially reflected.
- the fluid flow is preferably continuous in the flow direction narrows.
- the pressure in the Fluid flow through one following the constriction Expansion of the fluid flow increases. It is further preferred as Natural gas or oil used as fuel.
- FIG. 1 shows a combustion device 1.
- a Cross-section circular air duct 3 is also in the Cross section of circular fuel channel 5, which is a supply channel 5, arranged concentrically.
- air 6 in the form of an air stream 7 with a Flow direction 8 out.
- fuel channel 5 is as Fluid flow 9 along a flow direction 10 fuel 14, e.g. Oil, led out of a fuel tank 12.
- the Air 6 and the fuel 14 are in a combustion zone 11 burned in a flame 13.
- a fluctuation in the power release during the combustion a sound wave calls 15 in the fluid flow 9 of the fuel 14. This sound wave 15 migrates against the direction of flow 10 in Fluid stream 9 upstream.
- the sound wave 15 could enforce the entire feed channel 5 and approximately to one Fuel pump, not shown, and wander if necessary damage.
- the combustion zone 11 by means of the feed channel 5 considerably extended rooms acoustically coupled, due to the combustion vibrations in the combustion device 1 could spread and also the resonance rooms represent the formation of combustion vibrations can favor.
- the decoupling area 17 is due to a narrowing of the feed channel 5 is formed along the flow direction 10.
- the flow velocity is thus in the decoupling area 17 of the fluid flow 9 increased.
- the decoupling area 17 is designed so that at a nominal speed of Fluid flow 9 in the feed channel 5 this flow rate is greatly increased in the decoupling area 17, preferably to a value close to the speed of sound in the fluid flow.
- the remaining one Part continues as the residual sound wave 21 the feed channel 5 upstream.
- the nominal speed is in one Nominal operating interval, which is an interval of operating states close to a full load and a full load state.
- the full load state of the combustion device 1 is the maximum value for a power release during combustion. In operating conditions of the combustion device 1, the less power release than a full load correspond, there is less reflection of the Sound wave 15. Combustion vibrations can be special be disturbing and harmful near full load, because there is a high level of power release here. With less Load conditions is therefore less reflection of the Sound wave 15 and thus a higher spread of the sound wave 15 acceptable.
- Connects to the decoupling area 17 a pressure increase area 23.
- the decoupling area 17 forms a reflection section together with the pressure increasing area 23 24 with a length 24 of the feed channel 5.
- the pressure increase area 23 corresponds to an expansion of the Feed channel 5, in this case on the cross section of the feed channel 5, which is also in the flow direction 10 before the decoupling area 17 is present.
- the reflection section 24 is a venturi tube.
- the pressure increasing area 23 is preferred designed so that at the nominal speed maximum pressure increase in the fluid flow 9 results.
- the decoupling area 17 has an entry area 25 and one End area 27 on. The end region 27 is on at the same time Entry area 29 of the pressure increase area 23.
- the pressure increase area 23 ends at an exit area 31 schematic representation of the pressure curve in the decoupling area 17 and in the pressure increase area 23 is also in the figure 1 added.
- FIG. 2 shows schematically a gas turbine Combustion device 1.
- a Compressor 45 and a turbine 47 are arranged.
- a combustion chamber 49 is connected, which is designed as an annular combustion chamber.
- the burner 51 has an air duct 3, which is fluidically connected the compressor 45 is connected.
- the burner 51 continues to point a supply channel 5 for supplying natural gas 14.
- combustion media So here are air 6 from the compressor 45 and Natural gas 14. These burn in the combustion chamber 49.
- Hot fuel gases 53 generated drive the turbine 47 on. Due to the great power release in such Gas turbine 1 can with special combustion vibrations large amplitudes arise.
- Such combustion vibrations can occur as combustion chamber vibrations in the combustion chamber 49 form.
- a decoupling area 17 is provided in the feed channel 5. On this a pressure increase area closes in the direction of flow 23 on.
- the effects and advantages of the decoupling area 17 and the pressure increasing area 23 correspond to the to Figure 1 explained.
- the natural gas supply system, not shown is therefore effective acoustically from the combustion chamber 49 decoupled.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Aviation & Aerospace Engineering (AREA)
- Fluid Mechanics (AREA)
- Acoustics & Sound (AREA)
- Multimedia (AREA)
- Fluidized-Bed Combustion And Resonant Combustion (AREA)
- Feeding And Controlling Fuel (AREA)
Abstract
Description
- Figur 1
- eine Verbrennungsvorrichtung und
- Figur 2
- eine Gasturbine.
Claims (14)
- Verbrennungsvorrichtung (1) zur Verbrennung von Brennstoff (14) mit einem Zufuhrkanal (5) zur Zuführung von Brennstoff (14) zu einer Verbrennungszone (11), wobei der Brennstoff (14) in einem Fluidstrom (9) mit einer Strömungsrichtung (10) und einer in einem Nennbetriebsintervall liegenden Nenngeschwindigkeit durch den Zufuhrkanal (5) führbar ist, wobei der Zufuhrkanal (5) in einem Entkopplungsbereich (17) verengt ist, dadurch gekennzeichnet, daß der Entkopplungsbereich (17) als eine kontinuierliche Verengung des Zufuhrkanales (5) entlang der Strömungsrichtung (10) so ausgebildet ist, daß von der Verbrennungszone (11) im Fluidstrom (9) gegen die Strbmungsrichtung (10) laufende Schallwellen (15) bei der Nenngeschwindigkeit im Entkopplungsbereich (17) zumindest teilweise reflektiert werden.
- Verbrennungsvorrichtung (1) nach Anspruch 1,
dadurch gekennzeichnet, daß der Zufuhrkanal (5) einen kreis- oder ringförmigen Querschnitt aufweist. - Verbrennungsvorrichtung (1) nach Anspruch 1 oder 2,
dadurch gekennzeichnet, daß sich in Strömungsrichtung (10) an den Entkopplungsbereich (17) ein Druckerhöhungsbereich (23) anschließt, in dem sich der Zufuhrkanal (5) erweitert. - Verbrennungsvorrichtung (1) nach Anspruch 3,
dadurch gekennzeichnet, daß der Entkopplungsbereich (17) zusammen mit dem Druckerhöhungsbereich (23)einen Reflexionsabschnitt (22) bilden, der in Form einer Lavaldüse ausgebildet ist. - Verbrennungsvorrichtung (1) nach Anspruch 3,
dadurch gekennzeichnet, daß der Entkopplungsbereich (17) zusammen mit dem Druckerhöhungsbereich (23) einen Reflexionsabschnitt (22) bilden, der in Form eines Venturirohres ausgebildet ist. - Verbrennungsvorrichtung (1) nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, daß der Brennstoff Erdgas oder Öl ist. - Verbrennungsvorrichtung (1) nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, daß die Verbrennungszone (11) in einer Brennkammer (49) liegt. - Verbrennungsvorrichtung (1) nach Anspruch 7,
gekennzeichnet durch eine Ausführung als Gasturbine . - Verbrennungsvorrichtung (1) nach Anspruch 7 oder 8,
d a durch gekennzeichnet; daß die Brennkammer (49) als Ringbrennkammer ausgeführt ist. - Verbrennungsvorrichtung (1) nach einem der vorhergehenden Ansprüche,
bei der das Nennbetriebsintervall ein Vollastintervall ist, das die Betriebszustände umfaßt, bei denen eine bei der Verbrennung umsetzbare Energie zumindest nahezu maximal ist, dadurch gekennzeichnet, daß der Entkopplungsbereich (17) so verengt ist, daß im Vollastintervall ein gegenüber anderen Zuständen größerer Anteil an Schallwellen (15) reflektiert wird. - Verfahren zur Verbrennung eines Brennstoffs (14) bei dem ein Fluidstrom (9) mit einer Strömungsrichtung (10) und einer in einem Nennbetriebsintervall liegenden Nenngeschwindigkeit einer Verbrennungszone (11) zugeführt wird, wobei der Fluidstrom (9) in einem Entkopplungsbereich (17) verengt wird, dadurch gekennzeichnet, daß der Fluidstrom (9) in Strömungsrichtung (8, 10) kontinuierlich so verengt wird, daß von der Verbrennungszone (11) im Fluidstrom (9) gegen die Strömungsrichtung (8, 10) laufende Schallwellen (15) bei der Nenngeschwindigkeit im Entkopplungsbereich (17) reflektiert werden.
- Verfahren nach Anspruch 11,
dadurch gekennzeichnet, daß der Fluidstrom (9) im Anschluß an die Verengung aufgeweitet und damit der Druck im Fluidstrom (9) erhöht wird. - Verfahren nach einem der Ansprüche 11 oder 12,
dadurch gekennzeichnet, daß als Brennstoff (14) Erdgas oder Öl verwendet wird. - Verfahren nach Anspruche 11, 12 oder 13,
dadurch gekennzeichnet, daß der Brennstoff (14) in einer Brennkammer (49), insbesondere einer Ringbrennkammer, einer Gasturbine (1) verbrannt wird.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP99964516A EP1137899B1 (de) | 1998-12-08 | 1999-12-01 | Verbrennungsvorrichtung und verfahren zur verbrennung eines brennstoffs |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP98123359 | 1998-12-08 | ||
EP98123359 | 1998-12-08 | ||
PCT/EP1999/009401 WO2000034714A1 (de) | 1998-12-08 | 1999-12-01 | Verbrennungsvorrichtung und verfahren zur verbrennung eines brennstoffs |
EP99964516A EP1137899B1 (de) | 1998-12-08 | 1999-12-01 | Verbrennungsvorrichtung und verfahren zur verbrennung eines brennstoffs |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1137899A1 EP1137899A1 (de) | 2001-10-04 |
EP1137899B1 true EP1137899B1 (de) | 2003-11-12 |
Family
ID=8233108
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99964516A Revoked EP1137899B1 (de) | 1998-12-08 | 1999-12-01 | Verbrennungsvorrichtung und verfahren zur verbrennung eines brennstoffs |
Country Status (5)
Country | Link |
---|---|
US (1) | US6615587B1 (de) |
EP (1) | EP1137899B1 (de) |
JP (1) | JP2002531805A (de) |
DE (1) | DE59907751D1 (de) |
WO (1) | WO2000034714A1 (de) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1096201A1 (de) * | 1999-10-29 | 2001-05-02 | Siemens Aktiengesellschaft | Brenner |
US6820431B2 (en) * | 2002-10-31 | 2004-11-23 | General Electric Company | Acoustic impedance-matched fuel nozzle device and tunable fuel injection resonator assembly |
EP2110602A1 (de) * | 2008-04-16 | 2009-10-21 | Siemens Aktiengesellschaft | Akustiche Teilentkopplung zur Verringerung von selbstinduzierten Flammenschwingungen |
US20100089065A1 (en) * | 2008-10-15 | 2010-04-15 | Tuthill Richard S | Fuel delivery system for a turbine engine |
JP5448762B2 (ja) * | 2009-12-02 | 2014-03-19 | 三菱重工業株式会社 | ガスタービン用燃焼バーナ |
US8322140B2 (en) * | 2010-01-04 | 2012-12-04 | General Electric Company | Fuel system acoustic feature to mitigate combustion dynamics for multi-nozzle dry low NOx combustion system and method |
WO2013172777A1 (en) * | 2012-05-15 | 2013-11-21 | Andritz Technology And Asset Management Gmbh | Cellulose pulp dryer having blow boxes, and a method of drying a web of cellulose pulp |
JP5762481B2 (ja) * | 2013-07-16 | 2015-08-12 | 三菱日立パワーシステムズ株式会社 | 燃料ノズル、これを備えた燃焼器及びガスタービン |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3958413A (en) * | 1974-09-03 | 1976-05-25 | General Motors Corporation | Combustion method and apparatus |
EP0122526B1 (de) | 1983-04-13 | 1987-05-20 | BBC Aktiengesellschaft Brown, Boveri & Cie. | Brennstofflanze für die Brennkammer einer Gasturbine |
US4835962A (en) * | 1986-07-11 | 1989-06-06 | Avco Corporation | Fuel atomization apparatus for gas turbine engine |
GB2224315B (en) | 1988-08-10 | 1992-09-02 | Fawcett Christie Hydraulics Li | Hydraulic noise attenuators |
WO1993010401A1 (de) | 1991-11-15 | 1993-05-27 | Siemens Aktiengesellschaft | Einrichtung zur unterdrückung von verbrennungsschwingungen in einer brennkammer einer gasturbinenanlage |
US5211004A (en) * | 1992-05-27 | 1993-05-18 | General Electric Company | Apparatus for reducing fuel/air concentration oscillations in gas turbine combustors |
US5319931A (en) * | 1992-12-30 | 1994-06-14 | General Electric Company | Fuel trim method for a multiple chamber gas turbine combustion system |
DE4430697C1 (de) * | 1994-08-30 | 1995-09-14 | Freudenberg Carl Fa | Zuluftschalldämpfer |
NL1000492C1 (nl) | 1995-06-02 | 1996-12-03 | Q E International Bv | Geluidsdemper, een hiermee uitgeruste cokesovengasinstallatie, en een schot voor de geluidsdemper. |
-
1999
- 1999-12-01 WO PCT/EP1999/009401 patent/WO2000034714A1/de not_active Application Discontinuation
- 1999-12-01 JP JP2000587129A patent/JP2002531805A/ja active Pending
- 1999-12-01 US US09/857,939 patent/US6615587B1/en not_active Expired - Lifetime
- 1999-12-01 DE DE59907751T patent/DE59907751D1/de not_active Revoked
- 1999-12-01 EP EP99964516A patent/EP1137899B1/de not_active Revoked
Also Published As
Publication number | Publication date |
---|---|
EP1137899A1 (de) | 2001-10-04 |
US6615587B1 (en) | 2003-09-09 |
JP2002531805A (ja) | 2002-09-24 |
WO2000034714A1 (de) | 2000-06-15 |
DE59907751D1 (de) | 2003-12-18 |
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