Gas turbine staged control method

Abstract

A gas turbine combustion system includes a cylindrical combustor, a plurality of combustion sections in an arrangement spaced apart in an axial direction of the combustor, a plurality of fuel supply lines independently connected to the combustion sections, respectively, premixed fuel supply sections respectively provided for the fuel supply lines for supplying a premixed fuel, a diffusion combustion fuel supply section for supplying a diffusion combustion fuel to the combustion sections, and a control switching over the fuel supply sections to selectively supply either one of the premixed fuel and the diffusion combustion fuel. The premixed fuel at a first combustion stage is burned while the premixed fuel of subsequent stage is ignited by a high-temperature gas generated from combustion of the premixed fuel of a preceding combustion stage.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

Various other objects, features and attendant advantages of the present invention will be more fully appreciated as the same becomes better understood from the following detailed description when considered in connection with the accompanying drawings in which like reference characters designate like or corresponding parts throughout the several views and wherein:

FIG. 1 illustrates an embodiment of a gas turbine combustion system according to the present invention

FIG. 2 is a cross-sectional view of part of the gas turbine combustion system of FIG. 1 ;

FIG. 3 is a view explaining the function of the embodiment shown in FIG. 1 ;

FIG. 4 is an enlarged view of the pilot burner in the embodiment shown in FIG. 1 ;

FIG. 5 illustrates a fuel system of the embodiment shown in FIG. 1 ;

FIG. 6 illustrates a combustion portion of another embodiment of the present invention;

FIG. 7 illustrates a combustion portion of still another embodiment of the present invention;

FIG. 8 illustrates a modification of a micro burner employed in the embodiment shown in FIG. 1 ;

FIG. 9 illustrates an igniter which may be replaced with the micro burner employed in the embodiment shown in FIG. 1 ;

FIG. 10 is a graphic representation showing control characteristics of a computing element of the embodiment shown in FIG. 1 ;

FIG. 11 is a flowchart illustrating the function of the embodiment shown in FIG. 1 ;

FIG. 12 illustrates NOx characteristics of the prior art;

FIG. 13 illustrates NOx characteristics of the prior art;

FIG. 14 illustrates the relation between NOx or Co and the proportion of a diffusion fuel flow rate;

FIG. 15 illustrates the relation between NOx and the combustion range premixed equivalent ratio 15 ; and

FIGS. 16A & 16B illustrate the relation between the wall surface cooling ratio and the fuel outlet equivalent ratio.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

An embodiment of a gas turbine combustion system according to the present invention will be described below with reference to the accompanying drawings.

FIG. 1 illustrates the structure of the gas turbine combustion system according to the prevent embodiment. As shown in the figure, the combustion system is provided with a combustor 1 having a cylindrical, for example, structure closed at one end by a header H and including a first combustion chamber 2 a having a three-stage combustion portion, and a second combustion chamber 2 b having a two-stage combustion portion. The first combustion chamber 2 a has a structure in which a pair of inner tubes 1 a and 1 b having small diameters are coupled to each other in the direction of a gas stream.

The small-diameter inner tube la located on an upstream side in the first combustion chamber 2 a is provided with a pilot burner 3 , premixing units 4 a and at least one micro burner 5 a (which may be a heater rod heated by an electric heater or other ignition device designed to discharge ignition energy by utilizing electric or magnetic energy). The pilot burner 3 is on the other end mounted to the header H. The small-diameter inner tube 1 b located on a downstream side in the first combustion chamber 2 a is provided with premixing units 4 b and at least one micro burner 5 b. The premixing units 4 a or 4 b , each having a configuration of a premixing duct, are arrayed in a number ranging from 4 to 8 in a peripheral direction of the inner tube 1 a or 1 b. Fuel nozzles 6 a and 6 b are disposed at air inlets of the premixing units 4 a and 4 b , respectively.

The second combustion chamber 2 b includes an inner tube 7 having a diameter larger than those of the inner tubes 1 a and 1 b, premixing units 4 c and 4 d and at least one micro burner 5 c. The premixing units 4 c or 4 d , each having a configuration of a premixing duct, are arrayed in a number ranging from 4 to 8 in a peripheral direction of the large-diameter inner tube 7 .

Fuel nozzles 6 c and 6 d are disposed at upstream sides of the premixing units 4 c and 4 d , respectively. The premixing units 4 a , 4 b , 4 c and 4 d are fixed to a dummy inner tube 9 by means of supports 8 a and 8 b (only part of which is illustrated). The axial position of the dummy inner tube 9 is set by supports 11 fixed to a casing 10 so that the dummy inner tube 9 can receive thrusts acting on the small-diameter inner tubes 1 a and 1 b and the large-diameter inner tube 7 .

An inner wall 12 of a tail pipe and an outer wall 13 of a tail pipe 13 are provided downstream of the large-diameter inner tube 7 . The tail pipe outer wall 13 is formed with a large number of cooling holes 14 . Similarly, a flow sleeve 15 , having a large number of cooling holes 16 , is provided on an outer peripheral side of the large-diameter inner tube 7 . A tie-in portion between the large-diameter inner tube 7 and the tail pipe inner wall 12 and a tie-in portion between the flow sleeve 15 and the tail pipe outer wall 13 are sealed by means of spring seals 17 , respectively.

A premixed fuel injection port 18 of the first stage is provided at the upstream end of the small-diameter inner tube 1 a. Outlets of the premixing units 4 a , 4 b , 4 c and 4 d provided in the inner tubes 1 a , 1 b and 7 serve as premixed fuel injection ports of the second, third, fourth and fifth stages 19 a , 19 b , 19 c and 19 d , respectively. The premixed fuel injection ports of the second, third, fourth and fifth stages 19 a , 19 b , 19 c and 19 d are disposed at predetermined intervals which ensure that the series combustion can be conducted adequately in the axial direction of the combustor. The premixed fuel may be injected from the injection ports 19 a , 19 b , 19 c and 19 d toward the center of the combustor. The injection ports may also be disposed in a spiral fashion so that the gas stream can have a swirling component, as shown in FIG. 2 .

The pilot burner 3 includes a diffusion fuel nozzle 20 located along a central axis of the small-diameter inner tube 1 a, a premixed fuel nozzle 21 and a swirler 22 . A peripheral wall constituting the portion of the pilot burner 3 located upstream of the swirler 22 has a large number of air holes 23 . The burning state of the pilot burner 3 is illustrated in FIG. 3 . Operation of the pilot burner 3 is described herebelow.

FIG. 4 illustrates the structure of the pilot burner 3 in greater detail. A distal end of a pilot diffusion fuel supply pipe 24 has injection holes 25 . The injection holes 25 are located close to and in opposed relation with a nozzle distal end 26 . The nozzle distal end 26 has injection holes 27 and 28 through which a diffusion fuel is injected.

The micro burners 5 a, serving as ignition sources, are provided near the central portion of the nozzle distal end 26 and an inverted flow area 29 . A flow passage 30 is formed on an outer peripheral side of the pipe 24 . A distal end of the flow passage 30 has an injection port 31 through which a premixed fuel, which is a mixture of a combustion air and a fuel, is injected into the combustion chamber.

As shown in FIG. 1 , a fuel supply system 32 has a fuel pressure adjusting valve 33 and a fuel flow rate adjusting valve 34 and is designed to supply a fuel to the fuel nozzles 6 a to 6 d through cutoff valves 35 and 36 , a fuel flow rate adjusting valve 37 , a distributing valve 38 and fuel flow rate adjusting valves, 39 a , 39 b , 39 c and 39 d.

FIG. 5 illustrates a configuration of the fuel supply system. A fuel N, which has passed through the pressure adjusting valve 33 and the flow rate adjusting valve 34 , is distributed into two systems.

One of the two systems extends through the cutoff valve 36 and is then divided into two system lines. One of these two system lines is in turn divided into a line 41 a which extends through a flow meter 40 a and the flow rate adjusting valve 39 a and a line 41 b which extends through a flow meter 40 b and the flow rate adjusting valve 39 b while the other one of the system lines extends through a flow meter 40 e and the flow rate adjusting valve 39 e and is divided into a line 41 e which extends through the flow rate adjusting valve 38 and another line 41 f.

The system line which extends through the flow rate adjusting valve 34 extends through the cutoff valve 35 and is then divided into a line 41 c which extends through a flow meter 40 c and the flow rate adjusting valve 39 c , and a line 41 d which extends through a flow meter 40 d and the flow rate adjusting valve 39 d.

Signals S 101 , S 102 , S 103 , S 104 and S 105 output from all the above-described adjusting valves, the cutoff valves, the flow meters and so on, an output signal S 106 of a generator 51 a and a load signal S 107 are supplied to a computing element 42 . The computing element 42 controls the input signals according to the load signal 107 on the basis of a schedule input in the computing element 42 . Reference numeral 51 b denotes a denitration device and reference numeral 51 c denotes a chimney.

Operation of the combustor 1 is described hereinbelow.

First, the flow of air will be explained with reference to FIGS. 3 and 5 . As shown in FIG. 5 , part of high-temperature/high-pressure air A 0 ejected from an air compressor 50 is used to cool a turbine 51 . Part of air A 0 is supplied to the combustor 1 as a combustor air A 1 . The combustor air A 1 passes through the tail pipe cooling holes 14 and 16 and flows into a gap 52 as an impinging jet A 2 to cool the tail pipe inner wall 12 and the large-diameter inner tube 7 due to a convection flow.

The impinging jet A 2 does not flow into the combustor 1 at the region of the tail pipe inner wall 12 and the large-diameter inner tube 7 so that it can flow into the premixing duct units 4 a , 4 b , 4 c and 4 d as combustion airs A 3 , A 4 , A 5 and A 6 , respectively. The impinging air A 2 also flows into the pilot burner 3 through the combustion air holes 23 as a combustion air A 7 . The impinging air A 2 also flows downstream in the gap 52 so that it can be used as a film cooling air A 8 of the small-diameter inner tubes 1 a and 1 b.

The flow of air and fuel in the pilot burner 3 will be described below.

The combustion air A 7 which has flowed from the air holes 23 shown in FIG. 4 is swirled by the swirler 22 so that it has angular momentum. The resulting swhirling air flows into the small-diameter inner tube 1 a through the injection, port 31 . The injection port 31 shown in FIG. 4 corresponds to the premixed fuel injection port 18 of the first stage shown in FIG. 2. A pilot diffusion fuel N 1 ejects, as a jet, through the holes 25 formed at the downstream side of the pipe 24 to cool the nozzle distal end 26 by the convection flow, and then flows into the small-diameter inner tube 1 a through the injection port 27 as a diffusion fuel N 2 . The diffusion fuel N 2 , is ignited by, for example, an igniter 53 provided on the peripheral wall of the small-diameter inner tube 1 a to form a pilot flame F 1 . After ignition, the diffusion fuel N 1 is gradually replaced with a premixed fuel N 3 in response to the signal S 103 from the computing element 42 .

The premixed fuel N 3 is showered through the premixed fuel nozzle 21 as a fuel N 4 . The fuel N 4 is uniformly premixed with the combustion air A 7 . A resultant premixed fuel N 5 increases its speed to a velocity twice the turbulent combustion speed or more as it swirls downstream and then flows into the small-diameter inner tube 1 a from the premixed fuel injection port 18 of the first stage, i.e. the injection port 31 . At that time, no backfire occurs from the pilot flame F 1 because the velocity of the fuel is twice the turbulent combustion speed or more. By the time the fuel replacement is completed, all the pilot flame F 1 becomes a premixed mixture flame obtained from the premixed mixture fuel N 3 , and hence generation of NOx is almost reduced to zero.

Next, the flow of fuel in the combustor inner tube and the combustion method will be described hereunder.

First, the pilot flame F 1 is formed in the small-diameter inner tube 1 a by the above-described method. The flame F 1 is stabilized because of a desired combination of the pilot diffusion fuel N 1 with the pilot premixed fuel N 3 . After the pilot flame F 1 has been formed, the fuel having a flow rate controlled on the basis of the output signal S 103 of the computing element 42 is uniformly mixed with air in the premixing unit 4 a. A resultant premixed fuel N 4 flows into the small-diameter inner tube 1 a through the premixed fuel injection ports 19 a of the second stage.

The premixed fuel N 4 is ignited and burned by the pilot flame F 1 located upstream of the premixed fuel N 4 to form a premixed flame F 2 . Next, a premixed fuel N 5 of the third stage similarly flows into the small-diameter inner tube 1 b from the premixed fuel injection ports 19 b of the third stage. The premixed fuel N 5 is ignited and burned by the total amount of combustion gas obtained by adding the pilot flame F 1 to the premixed flame F 2 located upstream of the premixed fuel N 5 thereby to form a premixed flame F 3 . Premixed fuels N 6 and N 7 of the fourth and fifth stages respectively form premixed flames F 4 and F 5 by the same process as that of the second and third stages.

The computing element 42 controls the respective fuel flow rates such that the premixed fuels N 1 , N 2 , N 3 , N 4 and N 5 have a combustion temperature, less than 1600° C., which ensures generation of no NOx. Consequently, NOx characteristics (i) (see FIG. 12 ) can be made low over the entire gas turbine load region, unlike NOx characteristics (b) (see FIG. 12 ) of a conventional low NOx combustor, and the NOx objective value (h) (see FIG. 12 ) can thus be achieved.

Flames are stabilized by the adoption of so-called “series combustion” in which the premixed fuels of the first, second, third, fourth and fifth stages are ignited and burned in series by the high-temperature gas located upstream thereof to expand a flame.

Cooling of the combustor inner tube will be discussed.

A large part of the air supplied from the air compressor 50 to the combustor 1 passes through the impinging cooling holes 14 and 16 respectively formed in the tail outer tube 13 and the flow sleeve 15 , and then collides against the tail inner tube 12 and the large-diameter inner tube 7 as the impinging jet A 2 to cool the wall surfaces thereof by the convection flow.

The impinging jet A 2 does not enter the combustor at the tail inner tube 13 but flows into the combustor as the combustion airs A 3 , A 4 , A 5 and A 6 of the premixing units 4 a , 4 b , 4 c and 4 d and as the combustion air A 7 of the pilot burner 3 .

At the small-diameter inner tubes 1 a and 1 b corresponding to the first combustion chamber 2 a, less than 20% of the combustion air A 1 flows into the combustor as a film cooling air to cool the inner surface thereof. That is, only cooling of the outer surface is conducted at the tail inner tube 12 , so that the air to be used as a film cooling air can be used as combustion airs A 3 , A 4 , A 5 , A 6 and A 7 , thus increasing the amount of combustion air. Consequently, a desired premixed fuel air ratio assuring a combustion temperature, less than 1600° C., which ensures generation of no NOx can be set, and a reduction in the NOx can thus be achieved.

The computing element 42 which performs the above-described combustion method will be discussed.

As shown in FIG. 10 , premixed fuel flow rates W 1 through W 5 of the five stages are stored beforehand as functions relative to a gas turbine load in the computing element 42 for the five stages of fuel lines. A total of the premixed fuel flow rates W 1 to W 5 is equal to a total fuel flow rate W 0 . The premixed fuel flow rates W 1 to W 5 of the five stages are obtained by the signal S 103 using the flow rate adjusting valves 37 , 39 a , 39 b , 39 c and 39 d relative to the load signal S 107 .

Referring to FIG. 11 , where a load increases, the fuel of the first stage is replaced (step 1101 ), and then the premixed fuels of the respective stages are increased in sequence (steps 1102 to 1105 ).

Where a load decreases, the fuel flow rates of the respective stages are reduced in sequence starting with the fifth stage in the manner reversed to that shown in FIG. 11 . Since an air flow rate Wa relative to the gas turbine load is substantially fixed, the combustor outlet temperature is determined by controlling the total fuel flow rate W 0 .

As shown in FIG. 4 , the micro burners 5 a for causing a small flame to issue are provided near the inverted flow regions of the inner tubes 1 a , 1 b and 7 to effectively stabilize the flames.

The above-described embodiment of the present invention is not restrictive and susceptible to various changes, modifications, variations and adaptations as will occur to those skilled in the art. FIGS. 6 through 9 illustrate such modifications of the present invention.

In the modification shown in FIG. 6 , the fuel injection ports 18 , 19 a , 19 b , 19 c and 19 d shown in FIG. 1 are modified such that they have an annular arrangement surrounded by double cylinders. That is, a combustion air A 10 is swirled by a swirler 60 so that it has an annular momentum, and then flows into the cylinder from a fuel injection port 61 a , 61 b , 61 c , 61 d or 61 e of the first, second, third, fourth or fifth stage. A fuel N 10 is supplied to the respective injection ports through separate fuel supply systems, as in the case shown in FIG. 1 . The premixed flames F 1 through F 5 are formed continuously in the axial direction of an inner tube 62 correspondingly with the fuel injection ports 61 a through 61 e of the first, second, third, fourth and fifth stages to achieve series combustion.

In the modification shown in FIG. 7 , although a pilot burner 63 is substantially the same as that of the embodiment shown in FIGS. 1 , 5 to 8 , multi-burner type cylindrical premixing units 66 fixed to a second combustion chamber 64 b (located downstream of a first combustion chamber 64 a ) are arrayed in the peripheral direction of the combustion chamber. Such an array is provided at two positions in the axial direction of the combustor. Swirlers 67 are provided in each of premixing units 66 to provide uniform premixing even in a short flow passage.

In this modification, flames are formed in series starting from the upstream side in the same manner as those of the above-described embodiment to form premixed flames F 11 , and generation of NOx can thus be effectively restricted.

FIGS. 8 and 9 illustrate modifications of the micro burner shown in FIG. 1 .

The modification shown in FIG. 8 contemplates a micro burner 5 a having a configuration which assures premixed combustion by a self-holding flame. That is, the distal end portion of the premixed fuel injection port 18 ( 19 a , - - -) is widened so that eddy currents can be generated in the distal end portion to form self-holding flames 70 . This configuration achieves further stabilization of flames. A heat-resistant coating layer 71 is formed at the distal end portion of the injection port.

In the modification shown in FIG. 9 , an igniter is structured by a heating rod 81 having a high-temperature portion 80 whose temperature is increased to a value ensuring ignition by means of electrical energy. In this modification, the premixed fuel injection port 18 is formed wide, as in the case of the modification shown in FIG. 8 , to form a staying region 82 of a fuel A.

The gas turbine combustor according to the present invention has been described above in its various embodiments and modifications. It is, however, to be emphasized that the present invention can be applied to various types of gas turbines which employ a gaseous or liquid fuel.

As will be understood from the foregoing description, in the gas turbine combustion system according to the present invention, simultaneous achievement of the super lean combustion condition, stable flame combustion and combustor wall surface cooling, which would conventionally be difficult, is made possible. As a result, NOx can be reduced to a desired aimed value or less (<10 ppm) over the entire operation range. A great reduction in NOx enables scale-down or elimination of a denitration device, reduces the operation cost including a reduction in an amount of ammonia consumed, and contributes to global environment purification.

Claims

1. A combustion control method for a gas turbine combustion system which comprises a cylindrical combustor having one end closed by a header, a plurality of combustion stages in an arrangement spaced apart in an axial direction of the combustor, a plurality of fuel supply lines independently connected to said combustion sections, respectively, a plurality of premixed fuel, a diffusion combustion fuel supply section supplying a diffusion combustion fuel to one of the combustion sections and a control unit for switching over said fuel supply sections to selectively supply either one of the premixed fuel and the diffusion combustion fuel, which comprises burning the premixed fuel at a first combustion stage while igniting the premixed fuel of the subsequent stage by a high-temperature gas generated from combustion of the premixed fuel of a preceding combustion state, said plurality of combustion stages including at least first to fifth stages and the premixed fuels of the respective stages are separately supplied and burned in series in order of the first stage fuel, second stage fuel, third stage fuel, fourth stage fuel and then the fifth stage fuel as a gas turbine load is increased, while when the gas turbine load is reduced, the premixed fuels are reduced in a reversed manner to that occurring when the load is increased in the order of the fifth stage fuel, the fourth stage fuel, the-third stage fuel, the second stage fuel and the first stage fuel, and wherein when the load is interrupted, supply of only the fourth stage fuel and the fifth stage fuel is suspended.