EP1199516A1 - Brenner - Google Patents
Brenner Download PDFInfo
- Publication number
- EP1199516A1 EP1199516A1 EP01123615A EP01123615A EP1199516A1 EP 1199516 A1 EP1199516 A1 EP 1199516A1 EP 01123615 A EP01123615 A EP 01123615A EP 01123615 A EP01123615 A EP 01123615A EP 1199516 A1 EP1199516 A1 EP 1199516A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- burner
- flow
- central
- swirl generator
- burner 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.)
- Granted
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN A CARRIER GAS OR AIR
- F23C7/00—Combustion apparatus characterised by arrangements for air supply
- F23C7/002—Combustion apparatus characterised by arrangements for air supply the air being submitted to a rotary or spinning motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN A CARRIER GAS OR AIR
- F23C7/00—Combustion apparatus characterised by arrangements for air supply
- F23C7/008—Flow control devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
- F23D14/02—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN A CARRIER GAS OR AIR
- F23C2900/00—Special features of, or arrangements for combustion apparatus using fluid fuels or solid fuels suspended in air; Combustion processes therefor
- F23C2900/07002—Premix burners with air inlet slots obtained between offset curved wall surfaces, e.g. double cone burners
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- 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
- F23R2900/00013—Reducing thermo-acoustic vibrations by active means
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- 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 describes a burner for a heat generator according to the Preamble of claim 1.
- the axial position of the return flow zone that is established is of crucial importance Significance for the stabilization of the flame, and in turn becomes essential determined by the axial flow in the center of the burner. Is this axial If the current is too weak, the recirculation area moves and therefore the Flame inside the burner. There is a risk of reignition Flame and successive overheating of the burner. Conversely, that is axial flow too strong, the backflow zone from the burner outlet peel off and become unstable. The result can be strong harmful Burning pulsations or even extinguishing the flame.
- the axial flow in the center of a burner is the of great importance for the stable and safe Business. It is therefore also known in such burners by a central Air injection to generate a defined axial central flow. nevertheless this burner also results in different operating states a more or less favorable location of the backflow zone. So is at full load an axial flow that is strong enough to fire the flame is desirable to keep it safely outside the burner. In contrast, at lower Burner load can be prevented that the axial flow Backflow zone drives impermissibly far from the burner mouth; the axial Central flow momentum should therefore be rather low.
- the invention seeks to remedy this.
- the invention as in the Is characterized, the task is based on a burner type mentioned above with a central injection device provided that the axial momentum of the central air flow in all Operating areas for optimal flame stabilization and positioning is customizable.
- this is achieved by said injection device adjustable elements for changing a flow cross section of the Has injection device.
- the essence of the invention is therefore the burner with a variable geometry To provide central injection.
- the axial pulse adapt the central flow to the respective operating conditions.
- This enables the position and intensity of the return flow zone to be influenced in a targeted manner.
- This makes it possible in a particularly advantageous manner, with less Burner load to reduce the centrally introduced amount of air in such a way that the backflow zone is very close to the burner mouth or partially even in the interior of the burner, making a superior one Flame stability results.
- the centrally introduced amount of air can be increased in such a way that the backflow zone reliably runs a distance downstream of the burner mouth comes to lie. This will result in thermal overloading of the burner avoided.
- a burner according to the invention is also special then advantageous if the current field due to the combustion air flow variable mass flows or temperatures varies. Such conditions are also included in the combustion chambers of gas turbines Load variations before. Through different intake air mass flows Compressor end pressures vary the conditions at the compressor outlet and the Inflow conditions at the combustion chamber inlet are considerable. This triggered Variations in the position of the backflow zone can occur in one Burner according to the invention by adjusting the geometry of the central injection device can be compensated.
- the design of the adjustable central injection device can be based on different ways can be realized; two, especially in context of gas turbine applications, preferred embodiments are in the Subclaims 2 and 3 described.
- the invention is based on premix burners, which from the above State of the art as such are well known and familiar to those skilled in the art.
- the invention can be readily used with all of the documents cited therein disclosed, and the further developed from these writings, per se Expert, swirl generator and burner types combined be, which by the specified in the subclaims Preferred variants are only partially reflected.
- control of the central air flow can be based on different criteria be carried out sensibly. It would be worth mentioning and advantageous here for example control depending on the burner load or to name a measured material temperature.
- variable central geometry in serves here Connection with the operating concepts familiar to the expert for Gas turbines with premix burners continue to be low in pollutants and to ensure stable, pulsation-free operation at the same time.
- a variation the conditions on individual burners can ultimately be used in a targeted manner be caused by acoustic resonances in the combustion chamber To prevent detuning of individual burners.
- Premix burner shown as it is known from EP 0 321 809 has become known.
- the burner consists essentially of one Swirl generator 100 for a combustion air flow, which consists of two conical partial bodies 101, 102 is formed.
- the partial body 101 and 102 with their axes 101 a and 102 a with respect to the burner axis 100a as well are mutually laterally offset. Because of this lateral Offset of the partial bodies are tangential between the partial bodies Inlet slots 121 formed. Through the tangential inlet slots 121 a combustion air flow 141 flows substantially tangentially into the Interior 122 of the swirl generator.
- the swirl generator forms in the interior
- a swirl flow 144 the axial flow component of which indicates a downstream mouth of the swirl generator.
- the partial body 101, 102 adjoin one at a downstream end of the swirl generator Front plate 108.
- the front plate 108 usually forms the front wall of one Combustion chamber 50, and is often on and not shown in the figure cooled not essential to the invention.
- the interior 122 of the Swirl generator essentially has the shape of a different one upstream to a downstream end of the swirl generator resp. Brenner's expanding truncated cone.
- the axial thus formed Flow cross-section points at a downstream end, at the mouth in the combustion chamber 50, a sudden cross-sectional expansion.
- By the cross-sectional jump causes the vortex flow 144 to burst, and to form a backflow zone 123 in the area of Burner mouth.
- the combustion air flow is opened in the swirl generator appropriately supplied a quantity of fuel.
- fuel lines 111 along the part body In the exemplary embodiment there are rows of fuel outlet bores 1111 recognizable.
- a fuel amount 142 is about Fuel lines 111 brought up, and flows over the Fuel outlet openings 1111 in the interior 122 of the swirl generator 100. This type of fuel admixture is common and preferred gaseous fuel use. Inside the swirl generator there is an intensive mixing of the fuel quantity 142 with the combustion air flowing in tangentially 141. At the outlet from the burner in the combustion chamber 50 there is a very homogeneous swirl flow 144 Mixture of air and fuel. In the area of the backflow zone 123 a flame from the premixed air-fuel mixture stabilize.
- the ratio of the is essentially determined by the swirl number Circumferential component to the axial component of the vortex flow 144, determines: If the rotational speed of the vortex flow 144 is high, it forms a wide backflow zone. One forms under these conditions robust backflow zone close to the burner opening and thus in the Operating a stable combustion zone. These are conditions like those in Interest in good flame stability at low burner loads, so high burner air numbers desired and to stabilize the comparatively low temperature burning flame also necessary are. On the other hand, with the high swirl numbers the Combustion air flow along the burner axis is an area low Pressure, which, as it were, the backflow zone and thus the flame sucks the inside of the burner. But this is at high burner loads undesirable.
- this burner operates with air figures in a range of 2, in extreme cases even with more fuel Conditions, for example with air numbers of 1.7, 1.5, or even 1.3, where but in any case air numbers in the range between 2.5 and 2, preferably about 2.3, can be achieved.
- the combustion zone therefore has significantly higher ones Temperatures higher than in the partial load area, where burner air ratios of 3 or 4 occur, and is much more stable in itself. So it becomes with high loads no such pronounced backflow zone required. On the contrary, there is Danger of hot gas from the combustion zone along the burner axis is sucked into the burner. Such reignition can on the one hand the integrity of the burner, in the extreme case of an entire one Machine set, endanger.
- the invention proposes on known way along the burner axis, respectively Swirl generator axis 100a an axial central flow 145 into the center of the Bring burner.
- the Central flow is variable.
- the injection device shown here consists of a flow body 1121.
- This is in the embodiment essentially a hollow cylinder, with an open face, and an end face that has a bottom 1124.
- the floor 1124 an opening 1125, the diameter of which is smaller than that Inner diameter of the cylinder bore.
- the flow body 1121 ends with the open side blunt on an upstream side, that is upstream end of burner or swirl generator 100 while the bottom 1124 with its opening faces the interior 122 of the burner.
- an air flow which is from the upstream side to the burner flows, mostly through the tangential inlet slots 121 as Combustion air 141 guided tangentially into the burner; a partial flow but depending on the flow cross section of the injection device, flows as axial airflow 145 along the burner axis 100a into the center of the Brenner and influences the axial by the additional axial impulse Position of the backflow zone 123.
- the flow body 1121 is coaxial adjustable central body 1122 used. This tapers on one End with a cone 1123. This cone protrudes at least in an axial Position of the central body in the opening of the bottom of the flow body into it.
- the central Fuel 146 to be introduced is passed to the fuel nozzle 113 via a Fuel line 1131 supplied.
- a fuel cone 147 for example a liquid fuel spray, which starts from the central fuel nozzle 113 in the interior 122 of the swirl generator spreads, and continues successively downstream with the Swirl flow 144 mixed.
- in gas operation as fuel quantity 142, as a so-called premix gas, fed.
- the central fuel supply can be used to on the one hand to supply the so-called pilot gas mentioned above.
- burners as a dual fuel burner, which operate with both gaseous and liquid fuels can be; in this case there is a central one in practice Liquid fuel nozzle application.
- both Liquid fuel nozzles as well as pilot gas inlets in the head area To implement Brenners.
- the burner is also located in the head area often still nozzles for water or steam injection, which are often used a further reduction in the oil or pilot gas operation of the burner to achieve nitrogen oxide emissions. In such cases, the head area the burner sometimes very tight space conditions, which the Use of a central air supply of the type preferred in the first Embodiment shown in Figure 1, make impossible.
- Fuel line 1131 with the Fuel nozzle 113 is a substantially annular flow body Arranged 1121.
- the flow body 1121 has a number of internal ones Control holes provided, and concentric in an outer body 1126 arranged.
- the outer body 1126 is a number of outer Control holes 1127 provided, each outer control hole 1127 of the outer body 1126, an inner control bore 1128 of the Flow body 1121 is assigned.
- the central flow flows through Pairs of control bores in the between the fuel line 1131 and the fuel nozzle 113 and the flow body 1121 formed annular gap and from there axially into the interior 122 of the swirl generator.
- the Outer body 1126 and flow body 1121 are relative to one another rotatably and / or axially displaceable. So that the Degree of coverage of inner control bores 1128 and outer Control bores 1127, thus the flow cross-section and Mass flow of the central flow 145 can be varied.
- the Burner 1 is on a combustion chamber 20, for example a gas turbine, arranged, and opens into a combustion chamber 50. Air does not flow from one Compressor shown in an air chamber 60, which from a housing 4th is enclosed. A burner hood 5 is located within the housing 4 arranged, which in turn encloses the burner 1. Within the Burner hood is a plenum 55 which is in fluid communication with the air chamber 60 stands. A combustion air stream 141 flows out of the Air chamber 60 in the plenum 55, and from there by tangential Inlet slots in the interior of the burner 1, where this air on the top described forms a swirl flow and mixed with fuel becomes. The burner is in the manner described above with a central one Injection device 112 provided.
- the central injection device is connected to a central air supply line 1129.
- the air chamber 60 is with a Bypass line 61 provided.
- the bypass line 61 and the central air supply line 1129 are connected to one another in such a way that a central air flow 145 from the Bypass line 61 can flow to the central air supply line 1129.
- In this Flow path is an adjustable throttle member 62 as an actuator for the Central airflow 145 arranged.
- the central air flow can also like described above varies and adapted to the load conditions of the burner become.
- Embodiments of the controllable central air injection require this here illustrated embodiment on the one hand an increased apparatus Effort because a pipe system has to be arranged; in return can the mechanically comparatively sensitive actuator on a suitable and thermally less stressed place.
- FIG. 7 A special embodiment of the central air supply with actuator is in Fig. 7 shown. Both the air bypass 61 and the central air supply line 1129 open into an overflow space 63. Inside the overflow space a throttle valve 64 is arranged inside the overflow space 63. This is rotatable about an axis, as indicated by the arrow in the drawing. By twisting the Throttle valve 64 can be the free flow cross section of the overflow space can be changed, which results in a variation of the central air flow 145.
- the burner as it is characterized in the preamble of the claims is that Expert in various training courses, which differ from those in the Figures 1, 4, 6 and 7 shown burners, which essentially consist of one conical swirl generator exist, in the concrete version differ. Nevertheless, all of these burners are after a common one Principle built: They have a swirl generator in the form of a hollow body with a longitudinal extension, which has a swirl generator interior includes. The swirl generator continues to point in the direction of the longitudinal axis of the swirl generator extended inlet slots or in the direction of the longitudinal axis arranged inlet openings, the flow cross section in the essentially specifies a tangential flow direction.
- combustion air flows with a strong tangential Speed component in the swirl generator interior, and forms there a swirl flow with a certain to the burner mouth in the Combustion chamber aligned axial component.
- At least in the area of the air inlet openings is the axial flow cross section of the swirl generator interior extended towards the mouth of the burner.
- This training is cheap, to increase in the direction of the swirl generator axis Combustion air mass flow in the swirl generator interior a constant To achieve a swirl number of the swirl flow.
- these burners have Means to introduce fuel into the combustion air flow which is in the swirl generator and in an optional downstream of the Swirl generator to be arranged mixing zone, for example a mixing tube, mixed as homogeneously as possible with the swirled combustion air.
- the actual mixing tube 230 is arranged in the transition element. By doing If necessary, the mixing tube is further homogenized Mixing combustion air and fuel. Due to the uniform provision of an ignitable mixture over the entire cross section of flow of the mixing tube there is a risk that a flame along the low-impulse wall boundary layers into the mixing tube intimidzündet.
- the mixing tube is therefore at an acute angle to the burner axis provided wall film holes 231. One flows over this Air quantity 150 into the mixing tube, and forms a wall film there. By the acceleration or reduction of the wall boundary layers on the one hand and the displacement of the ignitable mixture from the low-pulse Areas on the other hand are effectively prevented from reigniting.
- the mixing tube 230 has a at the mouth into the combustion chamber 50 Tear-off edge 232, which is also the shape and location of the Backflow zone 123 forming the burner mouth is stabilized.
- the mixing tube is on a front segment 108 which simultaneously forms a combustion chamber wall attached, which in this example via baffle cooling plates 109 and baffle cooling air 149 is chilled.
- a risk of reignition along the There is also a risk of reignition of the wall boundary layers here Flame along the burner axis 100a at high load, or the risk of swimming backflow zone 123 with flame instabilities low load.
- the one shown in FIG. 8 is also shown Burner with a controllable not shown in detail Injection device for an axial central flow 145 equipped acts as in the above-described embodiments. Of course can also be combined here with a central fuel nozzle.
- Injector 112 for axial central flow 145 is expedient in the area of the downstream End arranged this sinker.
- the inflow to the Injection device 112 can advantageously inside the Displacer are arranged; there is also space for the control means to be arranged on the burner according to the invention.
- Farther can of course have a central one here if necessary Fuel injections are arranged.
- Fig. 10 shows such an embodiment of the burner, as in the basic form is described in detail in EP 0 945 677.
- the Displacement body 105 is hollow and on its combustion chamber 50 facing end blunt.
- the injection device 112 for the axial central flow is inside the hollow and upstream On the inflow side of the burner open displacement body 105 is arranged.
- the Mass flow of the axial flow 145 can be axially displaceable Central body 1122 can be changed with a control cone 1123. It is the actual control mechanism with the cone for space reasons in the arranged upstream part of the displacement body interior.
- At the a downstream end of the displacer is a chamber arranged. This hollow chamber leads to this chamber through a fuel line 1131, through which the chamber Amount of fuel 146 is supplied.
- This fuel can be used as central Outlet openings 113 acting as fuel nozzles are centrally injected Flow fuel into the swirled combustion air stream 144.
- the position of the backflow zone 123 can be the respective Operating conditions of the burner can be adjusted.
- executions of the fuel injection and the injection of the axial central flow possible in which the fuel along the Burner axis 100a is introduced, and the injection device for the Central flow is arranged in a ring, approximately analogous to that in the figures 4 and 5 illustrated embodiments.
- the burners can also have a cylindrical swirl generator provided with a mixing section downstream of the swirl generator without deviating from the idea of the invention.
- the use of a swirl generator with a central displacement body also enables the swirl generator itself to converge towards the mouth shape, and the axial cross-section of the swirl generator interior still divergent. This, shown in Figure 11 Variant, enables a course of the transverse velocity component of the swirl flow 144.
- the central body 105 can advantageously be equipped with an injection device 112 be provided for introducing a controllable axial central flow.
- Swirl generators with tangential combustion air inlets can open be constructed differently.
- Cross-sectional structure of several partial bodies also come monolithic designs with inlet openings in question.
- Such Embodiment is shown in cross section in FIG.
- the Swirl generator is made up of a hollow cylindrical monolith.
- inlet openings 121 in the form of axially and tangentially extending Slits are incorporated through which a combustion air flow 141 tangential flows into the swirl generator interior 122.
- Fuel feeds 111 in the form of axially extending, in the area of Inlet openings arranged to recognize which Have outlet holes 1111, through which a quantity of fuel 142 in the Combustion air flow 141 can flow out.
- FIG 13 is a conical one Swirl generator 100 shown from a monolithic hollow body. This could of course also be cylindrical.
- monolithic Swirl generators are tangential openings, for example bores, incorporated, which also as tangential inlet openings 121 for one Combustion air flow 141 serve.
- the burner 14 shows a first, easy-to-use mode of operation.
- the burner 1 is operated with a fuel quantity 142.
- the mass flow of this fuel is determined at a measuring point 2.
- the resulting mass flow signal X m is processed in a control unit 3 and converted into a control signal Y for the adjustment mechanism of the axial central air injection of the burner 1.
- a second embodiment, shown in FIG. 15, relates to the use of the burner according to the invention in gas turbine systems, for which the burner according to the invention is particularly suitable.
- a compressor 10, a turbine 30, and a generator 40 are arranged on a common shaft.
- the compressor 10 is equipped with an adjustable feed line 11.
- a combustion chamber 20 is arranged in the flow path of a working medium between the compressor 10 and the turbine 30.
- the combustion chamber 20 is operated with at least one burner 1 according to the invention.
- a control signal 3 is fed from a control unit 3 to the adjustable device for injecting the axial central flow.
- the control unit 3 receives a power signal X P , signals X AMB from sensors, not shown, which determine ambient conditions - temperature, humidity, pressure and others - of the ambient air, and a signal X VLE , which represents the position of the preliminary row 11.
- a whole series of further machine-relevant data can be routed to the control unit 3; in particular, the generator power signal could be replaced by fuel mass flow signals. From these variables, the control unit 3 is able to form a burner load specific to the combustion air and to determine the control signal Y from this.
- FIG. 16 again shows a gas turbine group with a compressor 10 arranged on a common shaft, a turbine 30, and a generator 40.
- the combustion chamber 20 is shown as an annular combustion chamber, in longitudinal section, which is operated with at least one burner 1 according to the invention.
- the burner 1 is provided with a temperature measuring point for determining the material temperature, which generates a temperature signal X T.
- the combustion chamber 20 is provided with a pulsation measuring device for determining the combustion pressure fluctuations, which generates a pulsation signal X pulse .
- the signals X T and X pulse are led to a control unit 3, which generates a control signal Y for controlling the intensity of the axial central flow.
- the centrally injected mass flow is increased, so that the flame is driven a bit away from the burner mouth, which reduces the heat load on the burner. On the other hand, this can lead to an undesirable reduction in flame stability. This is determined by the pulsation measuring point. If the pulsation signal X pulse increases, the centrally injected mass flow can be reduced in order to increase the combustion stability and to counteract the increase in the combustion pressure fluctuations. In this way, the central injection can be regulated depending on the relevant data measured.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Gas Burners (AREA)
Abstract
Description
- 1
- Brenner
- 2
- Massenstrom-Messstelle
- 3
- Steuereinheit
- 4
- Gehäuse
- 5
- Brennerhaube
- 10
- Verdichter
- 11
- verstellbare Vorleitreihe
- 20
- Gasturbinen-Brennkammer
- 30
- Turbine
- 40
- Generator
- 50
- Brennraum
- 55
- Plenum
- 60
- Luftkammer
- 61
- Luftbypass
- 62
- Zentralluft-Steuerorgan
- 63
- Überströmraum
- 64
- Drosselklappe
- 100
- Drallerzeuger
- 100a
- Längsachse des Drallerzeugers, Brenners
- 102,102, 103, 104
- Drallerzeuger-Teilkörper
- 101a, 102a, 103a, 104a
- Achsen der Drallerzeuger-Teilkörper
- 105
- Drallerzeuger-Innenkörper
- 108
- Frontplatte, Frontsegment
- 109
- Prallkühlblech
- 111
- Brennstoffleitung
- 112
- Eindüsungsvorrichtung
- 113
- zentrale Brennstoffdüse
- 121
- tangentiale Einlassschlitze
- 122
- Innenraum des Drallerzeugers
- 123
- Rückströmzone
- 141
- Verbrennungsluftstrom
- 142
- Brennstoffmenge
- 144
- Drallströmung
- 145
- axiale Zentralströmung
- 146
- zentral einzudüsende Brennstoffmenge
- 147
- zentral eingedüster Brennstoff
- 148
- Kühlluft
- 149
- Prallkühlluft
- 150
- Luftmenge, Wandfilm
- 200
- Mischstrecke
- 210
- Haltering
- 220
- Übergangselement
- 221
- Übergangskanäle
- 230
- Mischrohr
- 231
- Wandfilmbohrungen
- 232
- Abrisskante
- 1051
- Kammer
- 1081
- Filmkühlöffnungen
- 1111
- Austrittsbohrung
- 1121
- Durchströmkörper
- 1122
- Zentralkörper
- 1123
- Konus
- 1124
- Boden
- 1125
- Öffnung
- 1126
- Aussenkörper
- 1127
- äussere Steuerbohrung
- 1128
- innere Steuerbohrung
- 1129
- Zentralluft-Zuführleitung
- 1131
- Brennstoffzuleitung
- X
- Messgrösse
- Y
- Stellgrösse
Claims (24)
- Brenner für einen Wärmeerzeuger, welcher im wesentlichen einen Drallerzeuger (100) zum tangentialen Einbringen eines Verbrennungsluftstroms (141) in einen Innenraum (122) des Drallerzeugers beinhaltet, sowie Mittel zum Einbringen wenigstens eines Brennstoffes (142) in den Verbrennungsluftstrom, und welcher Brenner an einem stromabwärtigen Ende eine sprunghafte Querschnittserweiterung eines axialen Brenner-Durchströmquerschnittes zu einem Brennraum (50) hin aufweist, und welcher Brenner weiterhin eine Eindüsungsvorrichtung (112) zum Einbringen einer axialen Zentralströmung (145) entlang einer zentralen Brennerachse (100a) aufweist, dadurch gekennzeichnet, dass besagte Eindüsungsvorrichtung (112) mit verstellbaren Elementen (62, 64, 1122, 1126) zur Veränderung eines Durchströmquerschnittes und zur Steuerung des Massenstromes der Zentralströmung in Wirkverbindung steht.
- Brenner nach Anspruch 1, dadurch gekennzeichnet, dass die verstellbaren Elemente (1122, 1126) unmittelbar in den Brenner integriert sind.
- Brenner nach Anspruch 1, dadurch gekennzeichnet, dass die Eindüsungsvorrichtung (112) mit einer Zentralluft-Zuleitung (1129) verbunden ist, und, dass das verstellbare Element (62,64) in Wirkverbindung mit einem der Eindüsungsvorrichtung abgewandten Ende der Zentralluft-Zuleitung (1129) angeordnet ist.
- Brenner nach Anspruch 3, dadurch gekennzeichnet, dass die Zentralluft-Zuleitung (1129) an dem der Eindüsungsvorrichtung abgewandten Ende mit einem Luftbypass (61) in Verbindung steht, und dass zwischen der Zentralluft-Zuleitung und dem Luftbypass das verstellbare Element (62) angeordnet ist.
- Brenner nach Anspruch 3, dadurch gekennzeichnet, dass die Zentralluft-Zuführung (1129) mit einem Überströmraum (63) in Fluidverbindung steht, dass ein Luftbypass (61) in den Überströmraum mündet, und dass in dem Überströmraum eine als verstellbares Element wirkende Drosselklappe (64) angeordnet ist.
- Brenner nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, dass die Eindüsungsvorrichtung ein im wesentlichen koaxial zu einer Brennerachse (100a) im Brenner angeordneter Durchströmkörper (1121) ist, der einen engsten Durchströmquerschnitt aufweist, und, dass als verstellbares Element ein in seiner axialen Position verstellbarer Zentralkörper (1122) angeordnet ist, welcher einen Steuerkonus (1123) aufweist, dergestalt, dass der engste Durchströmquerschnitt des Durchströmkörpers mit dem Steuerkonus des Zentralkörpers eine Drosselstelle mit verstellbarem Durchflussquerschnitt definiert.
- Brenner nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, dass als Eindüsungsvorrichtung ein Durchströmkörper (1121) im wesentlichen koaxial zu einer Brennerachse (100a) angeordnet ist, dass der Durchströmkörper wenigstens eine innere Steuerbohrung (1128) aufweist, dass koaxial zu dem Durchströmkörper ein den Durchströmkörper wenigstens teilweise überdeckender Aussenkörper (1126) angeordnet ist, welcher Aussenkörper wenigstens eine äussere Steuerbohrung (1127) aufweist, und, dass der Durchströmkörper (1121) und der Aussenkörper (1126) relativ zueinander verschieblich und/oder verdrehbar angeordnet sind, dergestalt, dass die Überdeckung zwischen der inneren Steuerbohrung (1128) und der äusseren Steuerbohrung (1127) variabel ist.
- Brenner nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass der axiale Brenner-Durchströmquerschnitt des Innenraums (122) im Bereich des Drallerzeugers (100) wenigstens teilweise zunimmt.
- Brenner nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass ein Innenraum (122) des Drallerzeugers (100) im Längsschnitt wenigstens näherungsweise die Form eines Kegels aufweist.
- Brenner nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass ein Innenraum (122) des Drallerzeugers (100) im Längsschnitt wenigstens näherungsweise Zylinderform aufweist.
- Brenner nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass im Innenraum (122) des Drallerzeugers (100) ein Verdrängungskörper (105) angeordnet ist.
- Brenner nach Anspruch 11, dadurch gekennzeichnet, dass der Verdrängungskörper (105) sich zur Brennermündung hin verjüngt.
- Brenner nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass zwischen dem Drallerzeuger (100) und der Brennermündung in den Brennraum (50) eine Mischstrecke (200) angeordnet ist.
- Brenner nach einem der Ansprüche 8 oder 9, wobei der Innenraum (122) des Drallerzeugers die Form eines sich zur Brennermündung hin erweiternden Kegels aufweist, dadurch gekennzeichnet, dass die Eindüsungsvorrichtung (112) an einem stromaufwärtigen, der Brennermündung abgewandten Ende des Drallerzeugers (100) angeordnet ist.
- Brenner nach einem der Ansprüche 11 oder 12, dadurch gekennzeichnet, dass die Eindüsungsvorrichtung (112) an einem stromabwärtigen, der Brennermündung zugewandten Ende des Verdrängungskörpers (105) angeordnet ist.
- Brenner nach einem der Ansprüche 1 bis 15, dadurch gekennzeichnet, dass der Drallerzeuger aus einer Anzahl lateral zueinander versetzt angeordneter Teilkörper (101, 102, 103, 104) besteht, zwischen welchen tangentiale Einlassschlitze (121) für den Verbrennungsluftstrom (141) ausgebildet sind.
- Brenner nach einem der Ansprüche 1 bis 15, dadurch gekennzeichnet, dass der Drallerzeuger als monolitischer Hohlkörper ausgebildet ist, in welchen tangentiale Eintrittsschlitze und/oder Reihen tangentialer Eintrittsöffnungen für den Verbrennungsluftstrom eingearbeitet sind.
- Brenner nach einem der Ansprüche 1 bis 17 zum Betrieb in einem Brennkammer einer Gasturbinenanlage.
- Verfahren zum Betrieb eines Brenners nach einem der Ansprüche 1 bis 18, dadurch gekennzeichnet, dass die axiale Zentralströmung (145) bei niedriger Brennerlast stark gedrosselt wird, und dass die Zentralströmung bei hoher Brennerlast gering oder nicht gedrosselt wird.
- Verfahren nach Anspruch 19, dadurch gekennzeichnet, dass die Brennerlast über ein Brennstoffmengen-Messsignal (Xm) bestimmt wird.
- Verfahren nach Anspruch 19, wobei der Brenner in einer Brennkammer (20) einer Gasturbinenanlage betrieben wird, dadurch gekennzeichnet, dass die Brennerlast in Abhängigkeit von einer Generatorleistung und/oder einer Brennstoffmenge der Gasturbinenanlage, der Stellung der Vorleitreihe eines der Gasturbinenanlage zugehörigen Verdichters, und Umgebungsbedingungen bestimmt wird.
- Verfahren zum Betrieb eines Brenners nach einem der Ansprüche 1 bis 18, dadurch gekennzeichnet, dass eine Materialtemperatur des Brenners gemessen wird, und, dass die Zentralströmung in Abhängigkeit von der gemessenen Materialtemperatur gesteuert wird.
- Verfahren zum Betrieb eines Brenners nach einem der Ansprüche 1 bis 18 in einer Brennkammer (20) einer Gasturbinenanlage, dadurch gekennzeichnet, dass Verbrennungspulsationen gemessen werden, und, dass die Zentralströmung in Abhängigkeit von den gemessenen Verbrennungspulsationen gesteuert wird.
- Verfahren zum Betrieb eines Brenners nach einem der Ansprüche 1 bis 18 in einem Mehrbrennersystem einer Brennkammer einer Gasturbine, dadurch gekennzeichnet, dass die Zentralströmung einzelner Brenner in Abhängigkeit von den gemessenen Verbrennungspulsationen gesteuert wird.
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DE10050248A DE10050248A1 (de) | 2000-10-11 | 2000-10-11 | Brenner |
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US6178752B1 (en) * | 1998-03-24 | 2001-01-30 | United Technologies Corporation | Durability flame stabilizing fuel injector with impingement and transpiration cooled tip |
-
2000
- 2000-10-11 DE DE10050248A patent/DE10050248A1/de not_active Withdrawn
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2001
- 2001-10-02 EP EP01123615A patent/EP1199516B1/de not_active Expired - Lifetime
- 2001-10-02 DE DE50108888T patent/DE50108888D1/de not_active Expired - Lifetime
- 2001-10-11 US US09/973,868 patent/US20020124549A1/en not_active Abandoned
-
2003
- 2003-09-22 US US10/665,569 patent/US6901760B2/en not_active Expired - Lifetime
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EP0309034A1 (de) * | 1987-09-15 | 1989-03-29 | Flameco-Eclipse B.V. | Gasbrenner |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102537959A (zh) * | 2012-02-28 | 2012-07-04 | 东方电气集团东方锅炉股份有限公司 | 一种旋流、直流结合型式的气体燃烧器 |
CN102537959B (zh) * | 2012-02-28 | 2014-08-27 | 东方电气集团东方锅炉股份有限公司 | 一种旋流、直流结合型式的气体燃烧器 |
Also Published As
Publication number | Publication date |
---|---|
US20040139748A1 (en) | 2004-07-22 |
US6901760B2 (en) | 2005-06-07 |
DE10050248A1 (de) | 2002-04-18 |
EP1199516B1 (de) | 2006-02-08 |
US20020124549A1 (en) | 2002-09-12 |
DE50108888D1 (de) | 2006-04-20 |
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