Method of controlling fuel injection in a reheat combustor for a combustor unit of a gas turbine

Abstract

A method is disclosed for controlling fuel injection in a reheat combustor of a gas turbine combustor assembly including a combustor casing defining a gas flow channel and a plurality of injection nozzles distributed in or around the gas flow channel; the method includes the step of distributing fuel among the injection nozzles according to a non-uniform distribution pattern.

Claims

1. A method of controlling fuel injection in a reheat combustor of a combustor assembly of a gas turbine, the reheat combustor having a combustor casing defining a gas flow channel and a combustion chamber, wherein the reheat combustor includes a plurality of injection units, each injection unit having a body extending across the gas flow channel along a first direction orthogonal to a gas flow direction and having a streamlined shape along the gas flow direction with a leading edge and a trailing edge and a plurality of fuel injection nozzles spaced along the first direction; the plurality of injection units being spaced along a second direction orthogonal to the first direction and including at least one central injection unit and two lateral injection units disposed at opposite sides of the at least one central injection unit along the second direction, wherein the method comprises: receiving a fuel flow; and distributing fuel among the injection nozzles according to a non-uniform distribution pattern, wherein said distributing according to said non-uniform distribution pattern comprises: applying different fuel supply rates between the two lateral injection units injecting fuel towards a propagation-stabilized flame region and the at least one central injection unit injecting fuel towards an auto-ignition stabilized flame region of the combustion chamber, wherein the fuel supply rate to each of the lateral injection units is greater than the fuel supply rate to the at least one central injection unit.

2. The method according to claim 1, wherein said distributing according to said non-uniform distribution pattern comprises: applying different individual fuel supply rates among the injection nozzles in at least one of the injection units.

3. The method according to claim 1, wherein the at least one central injection unit includes at least two central injection units.

4. A reheat combustor, comprising: a combustor casing defining a gas flow channel and a combustion chamber; a plurality of side-by-side injection units, each injection unit having: a body extending across the gas flow channel along a first direction orthogonal to a gas flow direction and having a streamlined shape along the gas flow direction with a leading edge and a trailing edge; a plurality of fuel injection nozzles spaced along the first direction, the injection units being spaced along a second direction orthogonal to the first direction and including at least one central injection unit and two lateral injection units disposed at opposite sides of the at least one central injection unit along the second direction; and a controller for controlling fuel supply rates to said injection nozzles, wherein said controller is configured to distribute fuel among the injection nozzles according to a non-uniform distribution pattern, wherein said non-uniform distribution pattern includes applying different fuel supply rates between the two lateral injection units injecting fuel towards a propagation-stabilized flame region and the at least one central injection unit injecting fuel towards an auto-ignition stabilized flame region of the combustion chamber, wherein said non-uniform distribution pattern includes applying a fuel supply rate to each of the lateral injection units which is greater than a fuel supply rate to the at least one central injection unit.

5. The reheat combustor according to claim 4, wherein said non-uniform distribution pattern includes applying different individual fuel supply rates among the fuel nozzles in at least one of the injection units.

6. The reheat combustor according to claim 4, wherein said injection units comprises: integrated mixing devices configured for mixing an injected fuel with passing hot gas flow.

7. The reheat combustor according to claim 6, wherein the mixing devices are vortex generators formed as lateral appendices extending from sides of the injection units upstream from each injection nozzle.

8. The reheat combustor according to claim 6, wherein the mixing devices are lobes of a trailing edge of each injection unit forming an undulated profile thereof.

9. The reheat combustor according to claim 4, wherein the at least one central injection unit includes at least two central injection units.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) For a better comprehension of the present invention and its advantages, an exemplary embodiment of the invention is described below in conjunction with the accompanying drawings, in which:

(2) FIG. 1 is a schematic view of a gas turbine for power plants provided with a reheat combustor according to the present invention;

(3) FIG. 2 is a schematic view of a can combustor including a premix combustor and a reheat combustor according to the invention;

(4) FIG. 3 is a schematic downstream view of the reheat combustor of the can combustor of FIG. 2;

(5) FIG. 4 is a schematic side view of an injection unit of the reheat combustor of FIG. 3;

(6) FIG. 5 is a schematic plan view of the injection unit of FIG. 4;

(7) FIG. 6 is a schematic downstream view of an alternative embodiment of the injection unit;

(8) FIG. 7 is a block diagram of a fuel injection control system of the reheat combustor;

(9) FIG. 8 is a schematic longitudinal cross sections of the reheat combustor of FIG. 3, in uniform fuel distribution conditions;

(10) FIG. 9 is a schematic longitudinal cross sections of the reheat combustor of FIG. 3, in accordance with a first non-uniform distribution pattern;

(11) FIG. 10 is a diagram showing pulsation amplitude and NOx emission against fuel rate distribution; and

(12) FIG. 11 is a schematic longitudinal cross sections of the reheat combustor of FIG. 3, in accordance with a second non-uniform distribution pattern.

DETAILED DESCRIPTION OF EMBODIMENTS

(13) FIG. 1 is a schematic view of a gas turbine 1 for power plants that can be provided with a reheat combustor according to the present invention.

(14) Gas turbine 1 comprises a compressor 2, a combustor assembly 3 and a turbine 4. Compressor 2 and turbine 4 have a common axis A and form respective sections of a rotor 5 rotatable about axis A.

(15) As is known, ambient air 6 enters compressor 2 and is compressed. Compressed air 7 leaves compressor 2 and enters a plenum 8, i.e. a volume defined by an outer casing 9. From plenum 8, compressed air 7 enters combustor assembly 3 that comprises a plurality of can combustors 10 annularly arranged around axis A. Here at least a fuel is injected, and the air/fuel mixture is ignited, producing hot gas 11 that is conveyed to turbine 4.

(16) As is better shown in FIG. 2, each can combustor 10 is housed in a respective portal hole 12 of the outer casing 9 and has an axis B. Can combustor 10 comprises, in series along gas flow M, a first or premix combustor 15 and a second or reheat combustor 16.

(17) In particular, premix combustor 15 comprises a premix burner 17 and a first combustion chamber 18. Reheat combustor 16 comprises a housing 20 defining a channel 21 (better shown in FIGS. 3 and 7), a reheat burner 22 housed within the channel 21 and a second combustion chamber 23.

(18) Reheat burner 22 comprises a plurality of, e.g. four, injection units collectively referenced 26, and individually referenced 261, 262, 263, 264. Injection units 26 are arranged across channel 21 for injecting fuel into the hot gas flow.

(19) According to a variant not illustrated the injection units can be arranged around channel for injecting fuel into the hot gas flow.

(20) FIG. 3 is a downstream schematic view of reheat burner 22 of the can combustor 10, i.e. reheat burner 22 is seen along axis B, counter to the hot gas flow direction.

(21) Channel 21 has a square/rectangular cross section and a convergent shape.

(22) Injection units 26 have a body 27 of substantially rectangular shape in side view (FIG. 4) with longer sides extending in a first direction parallel to one side of the channel 21 and orthogonal to the flow direction and shorter sides extending in the air flow direction. When seen along the first direction (FIG. 5), body 27 has a streamlined shape with a broader, rounded leading edge 28 defining one of the longer sides of body 27 and a narrower, pointed trailing edge 29 defining the other longer side of body 27.

(23) Injection units 26 are arranged side-by-side across channel 21 (FIGS. 3 and 8) so as to extend substantially parallel to the first direction between opposite sides thereof, and are spaced between one another in a second direction orthogonal to the first direction. Injection units 26 are preferably slightly converging with respect to one another when seen along the first direction (FIG. 7), in order to follow the stream lines of the air passing through convergent channel 21.

(24) Each of the injection units 26 includes a plurality of fuel injection nozzles 30 configured to inject fuel in the flow direction downstream of the trailing edge 29 and extend and are spaced with one another along the first direction. Injection nozzles 30, in a downstream view (FIG. 3), form a rectangular matrix of injection points across a section of channel 21, which are spaced along the first and the second directions.

(25) Injection units 26 preferably comprise mixing devices configured to improve the fuel/air mixing.

(26) According to a first embodiment (FIGS. 3-5), mixing devices are constituted by vortex generators 31 extending laterally from body 27, upstream of each fuel injection nozzle 30.

(27) Preferably, a vortex generator 31 is associated to each injection nozzle 30. Vortex generators 31 project alternately on opposite lateral directions from body 27; according to the embodiment shown in FIG. 3, vortex generators 31 associated to the first, third and fifth fuel injection nozzle 30 project on one side, while vortex generators 31 associated to the second, fourth and sixth injection nozzle (30) project on the opposite side.

(28) Vortex generators 31 have a substantially tetrahedral shape with one side resting against a lateral side of body 27.

(29) More particularly, with reference to FIGS. 4 and 5, each vortex generator 31 is delimited in the first direction by two triangular side surfaces 32, 33 having respective upstream vertexes 34 at a side surface of body 27 and converge towards a common downstream base 35 that is perpendicular to the first direction and substantially perpendicular to the flow direction; each vortex generator is delimited in the second direction by a triangular surface 36 having an upstream base 37 at a side surface of body 27 and a downstream vertex 38 at a free end of common downstream base 35 of side surface 32, 33.

(30) As an alternative, mixing devices can be constituted by an undulated shape of trailing edge 29 (FIG. 6) formed by lobes 40 extending in opposed lateral directions.

(31) Lobes 40 can be rounded, so as to form a substantially sinusoidal profile as shown in FIG. 6, or rectangular in shape, so as to form a substantially “square-wave” profile.

(32) FIG. 8 is a schematic view of a conventional operational condition in which all injection nozzles 30 are supplied with the same fuel supply rate (uniform supply). As can be seen from the fuel streamlines schematically shown, the two central injection units 262, 263 mainly inject the fuel into a central, auto-ignition stabilized flame zone 40 of the combustion chamber 23, while the two external injection units 261, 264 mainly inject the fuel into a recirculation or propagation stabilized flame zone 41 of the combustion chamber 23.

(33) According to the present invention, fuel supply is distributed non-uniformly among injection units 261-264 and/or individual injection nozzles 30 according to a predetermined pattern.

(34) The predetermined pattern can either be fixed, i.e. determined once for all and maintained during operation of the gas turbine, or variable.

(35) In the latter case, fuel supply to injection nozzles 30 may be adjusted by a valve unit controlled by a programmable control unit 39 according to one or more predetermined patterns as a function of operational conditions, e.g. load (FIG. 7).

(36) The valve unit may comprise one valve 42 for each of the injection units 26, in which case all of injection nozzles 30 of a given injection unit 26 receive the same fuel supply rate (FIG. 7), or even one valve 42 for each injection nozzle 30 (not shown), in which case fuel supply rate can be controlled individually for each point of the injection matrix.

(37) According to one embodiment of the present invention, fuel is distributed non-uniformly between the auto-ignition stabilized flame region 40 and the propagation-stabilized flame region 41 so as to reduce thermo-acoustic pulsation. In particular, the distribution pattern comprises a greater fuel supply rate to the external injection units 261, 264 and a lower fuel supply rate to the central injection units 262, 263. The result is a richer air/fluid mixture in the propagation-stabilized region than in the auto-ignition region, as schematically shown in FIG. 9.

(38) FIG. 10 is a diagram where pulsation amplitude and NOx emissions are plotted against fuel rate distribution, expressed as the percentage ratio between fuel rate to outer injection units 261, 264 and the total fuel supply rate.

(39) As can be seen, pulsations decrease as distribution percentage increases.

(40) FIG. 11 is a scheme showing an inverted fuel distribution, where a richer mixture is created in the auto-ignition stabilized flame region. Other distributions are possible, and individual control of injection nozzles 30 may allow 2-D distribution patterns.

(41) Although the invention has been explained in relation to its preferred embodiment(s) as mentioned above, it is to be understood that many other possible modifications and variations can be made without departing from the scope of the appended claims.