Method for operating a combustion device including injecting a fluid together with diluent fuel to address combustion pulsations

This application claims benefit under 35 USC §119 to European Patent Application No. 11179344.4 filed Aug. 30, 2011, the entire contents of which are incorporated by reference herein as if fully set forth.

The present invention relates to a method for operating a combustion device. In particular, the method according to the invention allows operation of a combustion device with reduced pulsations. Preferably the combustion device is a part of a gas turbine.

In the following particular reference to combustion devices that are part of a gas turbine is made; it is anyhow clear that the method can also be implemented in combustion devices for different applications. Thus, before the combustion device a compressor and after the combustion device a turbine are typically provided.

Combustion devices are known to include a body with a fuel supply for either a liquid fuel (for example oil) or a gaseous fuel (for example natural gas) and an oxidizer supply (usually air).

During operation, the fuel and the oxidizer react within the combustion device and generate high pressure and temperature flue gases that are expanded in a turbine.

During transient operation, such as for example when the gas turbine is started up, switched off, during fuel switch over or also during other transient operations, problems can occur.

In fact, during transient operations pressure waves can generate within the combustion device.

FIG. 1 shows an example of a possible circumferential pressure wave (it can be a static or a rotating pressure wave). FIG. 1 shows the pressure P as a function of the angular position φ over the combustion device at a period in time t=t 0 (solid line) and t=t 1 (dashed line). From this figure it is apparent that an injector located at a position φ 1 :

at the period in time t=t 0 faces an environment at a low pressure P 1 ; this promotes fuel supply through the injector; and

at the period in time t=t 1 faces an environment at a high pressure P 2 ; this hinders fuel supply through the injector.

Likewise, FIG. 2 shows an example of a possible axial pressure wave. FIG. 2 shows the pressure P as a function of the axial position x (L indicates the combustion device length) at a period in time t=t 0 (solid line) and t=t 1 (dashed line).

Also in this case, an injector will face a combustion device having a pressure that fluctuates with time; as explained above, this fluctuating pressure adversely influences fuel injection.

FIG. 3 shows the effect of the fluctuating pressure within the combustion device on the fuel injection. In particular FIG. 3 shows an example in which the fuel mass flow is reduced; this could be an example of a switch off, nevertheless the same conditions are also present at the beginning of a start up or at the beginning and end of a switch over and in general each time the fuel mass flow supplied decreases and falls below a given mass flow.

FIG. 3 shows the fuel mass flow M injected through an injector as a function of time t. From FIG. 3 at least the following phases can be recognized:

before t=t 3 : steady operation with substantially constant fuel mass flow through the injector (curve 1 ),

between t=t 3 and t=t 4 (the fuel mass flow stays above a critical fuel mass flow Mc): the amount of fuel injected decreases, but the fluctuating pressure within the combustion device does not noticeably affect fuel injection (curve 2 ),

after t=t 4 (i.e. when the fuel mass flow falls below the critical fuel mass flow Mc): in these conditions, since the amount of fuel is low, the fluctuating pressure within the combustion device alternatively promotes and hinders fuel injection, causing a fluctuating fuel injection. In particular in FIG. 3 , curve 2 shows a theoretical run of the reducing fuel mass flow and curve 3 an example of a possible real run of the reducing fuel mass flow.

Fluctuating fuel supply into the combustion device generates large combustion pulsations.

Combustion pulsations, largely mechanically and thermally, stress the combustion device and the turbine downstream of it, therefore they must be counteracted.

An aspect of the present invention thus includes providing a method by which combustion pulsations generated during transient operation are counteracted.

This and further aspects are attained by providing a method in accordance with the accompanying claims.

Further characteristics and advantages of the invention will be more apparent from the description of a preferred but non-exclusive embodiment of the method, illustrated by way of non-limiting example with reference to the accompanying drawings, in which:

FIGS. 1 and 2 schematically show the pressure waves P within the combustion device as a function of the circumferential angle φ or axial position x at two different periods in time t 0 and t 1 ;

FIG. 3 schematically shows the mass flow injected into the combustion device as a function of the time t;

FIGS. 4 through 9 show different combustion devices that can implement the method; and

FIGS. 10 through 17 show different embodiments of the method.

The method can be implemented with any kind of combustion device, for example adapted to generate a premixed flame, a diffusion flame, a mixed flame, etc.

For example the combustion device can be a premixed combustion device 5 ( FIG. 4 ), with conical swirl chamber 6 and combustion chamber 7 extending downstream of the swirl chamber 6 ; a front plate 8 is provided between them. This combustion device further includes fuel supply (for example a lance 9 that typically injects a liquid fuel) and tangential slits 10 at the swirl chamber 6 for oxidizer supply (typically air). Additional fuel supply includes injectors 11 ( FIG. 5 ) provided on lines 12 that are connected to the wall of the swirl chamber 6 , at positions close to the slits 10 , for fuel injection (typically gaseous fuel). This kind of combustion device 5 is well known and is schematically shown in FIGS. 4, 5 and 9 .

A different kind of premixed combustion devices 15 is for example schematically shown in FIG. 6 . This combustion device 15 includes a body 16 (for example a tubular body with square or trapezoidal cross section) with an inlet 17 and outlet. Within the body 16 , vortex generators 19 (for example tetrahedral vortex generators but also different shapes and concepts are possible) and fuel supply including a lance 20 with fuel injectors 21 are housed. Downstream of the body 16 , a combustion chamber 22 is provided.

FIGS. 7 and 8 show further examples of combustion devices that are arranged to generate a diffusion flame.

These combustion devices 25 have a body 26 with fuel supply including fuel injectors 27 (liquid or gaseous fuel) and oxidizer supply including oxidizer injectors 28 .

In all the figures, reference 30 indicates the flame and reference G indicates the hot gases generated in the combustion device and directed toward the turbine.

In the following, particular reference to the embodiment of FIG. 3 is made; it is anyhow clear that the same method can be implemented in all kind of combustion devices (i.e. those described or others).

The method for operating a combustion device 5 comprises supplying a fuel 35 and an oxidizer 36 into the combustion device 5 and burning them.

In addition, during at least a part of a transient operation such as for example a start up, a switch off or a switch over, an additional fluid 37 is supplied into the combustion device 5 together with the fuel 35 .

The additional fluid 37 is advantageously supplied through the same injectors as the fuel 35 and it is typically at least partly mixed with the fuel 35 .

The amount of the additional fluid 37 is thus regulated to counteract combustion pulsations.

With reference to FIG. 14 , a first parameter FP indicative of the fuel feed is chosen and the additional fluid supply starts only when the first parameter reaches a critical value FPc. The critical value FPc can be chosen such that when the first parameter reaches or passes it, pulsations start to generate or to substantially generate. In this respect FIG. 14 shows the first parameter FP and its critical value FPc; supply of the additional fuel starts only at t 5 , when the first parameter reaches its critical value FPc.

In different examples, the first parameter can be the fuel mass flow M or the differential pressure ΔP between a fuel supply and the inside of the combustion device 5 ; in these cases additional fluid supply starts when the fuel amount supplied into the combustion device or the differential pressure falls below the critical value Mc or ΔPc.

In addition, a second parameter SP indicative of the fuel and additional fluid feed is also chosen; the regulation includes maintaining the second parameter above or below a given value ( FIG. 15 ) or preferably maintaining the second parameter SP within a prefixed range R ( FIG. 16 ).

The given value can be a critical value SPc of the second parameter SP. Also in this case, the critical value can be chosen such that when the second parameter reaches or passes it, pulsations start to generate or to substantially generate.

In different examples the second parameter range R corresponds to the critical value SPc of the second parameter ±10% or preferably to the critical value SPc of the second parameter ±1% or more preferably to the critical value SPc of the second parameter.

Preferably, the bottom or the top of the range corresponds to the critical value SPc of the second parameter.

The second parameter SP can be the fuel and additional fluid mass flow M or the differential pressure ΔP between a fuel and additional fluid supply and the inside of the combustion device 5 . In these cases the regulation includes maintaining the total mass flow of fuel 35 and additional fluid 37 or differential pressure AP above the critical value or maintaining them within the prefixed range R.

FIG. 17 shows an example in which the first and the second parameter are the same physical entity (for example mass flow M or differential pressure AP as indicated above). In this case the first parameter and the second parameter can be measured through the same sensors. In particular FIG. 17 shows that before t=t 6 (i.e. when the fuel mass flow M or differential pressure ΔP between the fuel supply and the inside of the combustion device) are above the critical value Mc or ΔPc the sensors measure the first parameter and only fuel is injected and when the first parameter (i.e. M or ΔP) reaches the critical value Mc or ΔPc also the additional fluid 37 starts to be fed and the sensors measure the second parameter SP; in this example the second parameter is kept at the critical value Mc or ΔPc but as already described it can be kept above or below it or within a range R.

To measure the differential pressure ΔP the control device shown in FIG. 9 can be used.

FIG. 9 shows a control device 45 connected to sensors 46 for measuring the pressure in a line supplying the fuel (or fuel and additional fluid) to the combustion device 5 and sensors 47 for measuring the pressure within the combustion device; the control device 45 elaborates the signals from the sensors 46 , 47 and provides a control signal (to a valve 48 or different component) to regulate the amount of the additional fluid 37 .

The fuel 35 is supplied into the combustion device 5 via a fuel supply (for example the lance 9 or the lines 11 but, in the other examples of combustion devices 15 , 25 , also lance 20 ); the additional fluid 37 is preferably also supplied into the same fuel supply (i.e. into the lance 9 or the lines 11 or lance 20 ).

Advantageously, the additional fluid 37 is at least partly mixed with the fuel 35 and in this respect a mixer 49 can be provided.

The additional fluid 37 is preferably an inert fluid; inert fluid is a fluid that does not react during burning, i.e. it is neither a fuel nor an oxidizer.

In addition, when the fuel is a liquid fuel, the inert fluid is preferably a liquid fluid (for example the fuel can be oil and the additional fluid water) and when the fuel is a gaseous fuel the additional fluid is preferably a gaseous fluid (for example the fuel can be natural gas or methane and the additional fluid nitrogen).

Advantageously, since when the amount of fuel becomes low the additional flow is injected with it, no fluctuating amounts of fuel are injected into the combustion device; this prevents or hinders thermal and mechanical pulsations.

In the following some embodiments of the invention are described in detail.

1 fuel mass flow at steady operation

2 theoretical fuel mass flow during transient operation

3 real fuel mass flow during transient operation

5 combustion device

6 swirl chamber

7 combustion chamber

8 front plate

9 lance

10 tangential slits

11 injectors

12 line

15 combustion device

16 body

17 inlet

19 vortex generators

20 lance

21 injectors

22 combustion chambers

25 combustion device

26 body

27 injectors

28 oxidizer injectors

30 flame

35 fuel

36 oxidizer

37 additional fluid

45 control device

46 sensor

47 sensor

48 valve

49 mixer

50 premix gas

51 premix oil

52 water

53 differential pressure

54 nitrogen

t, t 0 , t 1 , t 3 , t 4 , t 5 , t 6 time

x axial position

φ, φ 1 angular position

ΔP differential pressure

ΔPc critical value of ΔP

FP first parameter

FPc critical value of FP

G hot gases

L combustion device length

M mass flow

Mc critical value of M

P, P 1 , P 2 pressure

R range

SP second parameter

SPc critical value of SP