DE10124494A1 - Operating combination power plant for different demands involves no additional exhaust gas heating or induction air cooling for low loads, one or both for medium loads, both for peak loads - Google Patents

Abstract

The invention relates to a method for operating a combined cycle power plant, in which combined cycle power plant air is compressed in a compressor (2), then fed as combustion air (10) to a combustion chamber (3), and the hot gas (12) that is produced there is fed to a gas turbine (4 ) is passed and the exhaust gas (6) of the gas turbine (4) is used in a waste heat boiler (7) to generate steam for a steam turbine system (13). For additional heating of the exhaust gas (6) of the gas turbine (4), an additional firing (44) is arranged, and in addition means (46) are provided which allow the intake air (9) of the gas turbine system to be cooled to increase performance. A targeted performance-dependent use of additional firing (44) and intake air cooling (46) enables a driving style that is adapted to the electricity tariffs, in that the combined cycle power plant is operated without additional firing (44) and without intake air cooling (46) in times of low load, and that the combined cycle power plant is operated in times of medium load is operated with additional firing (44) and / or intake air cooling (46) and that the combined cycle power plant is operated with additional firing (44) and intake air cooling (46) during peak load times.

Description

TECHNICAL AREA

The present invention relates to a method for operating a combined cycle power plant at un different network requirements. In particular, it relates to a process which is carried out via the targeted use of additional firing and intake air cooling a the electricity tariffs adapted driving style of the combined cycle power plant.

STATE OF THE ART

With the liberalization of the energy markets, competition in the area of Power supply significantly tightened. On the one hand, this leads to the rapid realization of mo their energy conversion process, in particular with very high efficiency. But also in the area of the power flexibility of a power plant or the provision of cold and hot reserve power is sought, for cheaper options to search. Gas turbine plants and combined cycle power plants in ho hem fair.

Gas turbine plants are able to comparatively very large power gradients realize and be operated in different performance ranges. Furthermore modern gas turbine systems designed so that they have a wide upper performance range can be operated with very high partial load efficiencies.  

As a result of the liberalization, the power grid operators are demanding from the power plants of the Electricity generators increasingly have "primary response" properties. The expression "primary re sponse "refers to an increase in performance over the registered or current actual performance of a respective energy producer with a defined performance gradient. For example, the increase in performance from the actual performance to a ge required about 10% higher performance to be done within 10 seconds. That is, the power plants In the event of a drop in the mains frequency (e.g. 0.5 Hz), they must be able to a certain time unit (e.g. 10 sec.) an increase in performance (e.g. 10% of the actual performance). This increase in performance should then be in the sense of "se condary response "over a range of, for example, 30 minutes or longer can be. "Secondary response" means holding an additional service over a Actual performance defined, i. H. for example, the operation with an additional service of z. B. 10% for a period of e.g. B. 30 minutes.

For questions of "primary response" and "secondary response" are the maximum Fahrba re power gradient, the amount of the additional service depending on the currently driven Actual power and the maximum duration of driving the additional service of interest. The An additional service should, with the exception of the limit service, come from every load point be possible out. An increase in performance places particularly high demands beyond the nominal power.

The term nominal power is identical to the term continuous power, so an upper output for which the system is designed for continuous operation. Under part load becomes a power below the continuous limit power and a lei under overload understood above the continuous limit power. For the time-limited maximum driving In the following, the term limit power is used.

The nominal power or the continuous limit power is the power that the combined cycle power plant with a performance of the gas turbine system of 100% without other performance-enhancing Measures. The power of the combined cycle power plant is based on the power the gas turbine plant and the steam turbine plant together.

Increases in performance are particularly critical during network peak loads, during which the respective energy producers already with their limit continuous output (Rated power) are operated, and at the same time an unplanned event occurs, which a short-term increase in power beyond the limit continuous power requires.

As already mentioned, gas turbine plants are capable of comparatively very large lei driving gradient. For this reason, gas turbine systems are principally available for tasks of covering network-side demand peaks, for example for "primary respon se "purposes.  

However, modern gas turbine systems are today for reasons of high part load performance levels designed so that they are in a wide upper performance range in the range of for continuous operation at rated power maximum permissible design temperatures (upper Process temperature) d. H. at their temperature side for continuous operation limit.

In this upper power range, the power is adjusted by means of the mass flow adjustable guide vanes at the compressor inlet. Performance improvements in this area therefore, when leaving the driving regime of normal operation lead to exceeding the Design temperatures, which has a negative impact on the lifespan in particular of those affected components of the hot gas path.

However, it also follows that an increase in output beyond the nominal output at current design can only be achieved by overfiring the gas turbine system can. The disadvantage here is that the gas turbine system deviates from the normal regime soft driving style very many equivalent operating hours (EOH - Equivalent Operating Hours, OH - Operating Hours) loses (e.g. 1.3 EOH / OH for steam injection or 1.5 EOH / OH for frequency re sponse). This is especially the case if the overload has to be endured for a long time.

Basically, a distinction is made after use d. H. the number of hours of use three Areas of application of the power plants: In the base load range d. H. for hours of use above 4000 h / a (with a low network load and thus low electricity remuneration) mainly power plants with low variable costs or with higher efficiency (and thus high fixed costs), such as B. Nuclear power plants and modern coal-fired power plants operated. In the medium load range d. H. for hours of use between 2000 and 4000 h / a (at a medium network load and thus an increased electricity tariff), power plants are included mean variable costs or mean efficiencies (and thus mean fixed costs) such as B. operated older coal-fired power plants and combined cycle power plants. In the peak load range d. H. for hours of use below 2000 h / a (with a high network load and thus the highest Electricity remuneration) the variable costs and thus the efficiency only play a minor role ordered role. Rather, for economic reasons, one strives for this application Power plants with the lowest possible fixed costs such as B. gas turbine plants hold and operate. The thermal power plants must also be able to peak loads and the above mentioned reserve benefits in the form of "primary" and to provide "secondary response".

The variable costs are primarily due to the fuel prices, but also by the Fuel consumption (and thus the efficiency) and the other operating resources Right. The fixed costs are primarily required to build the facilities investments, but also the use of personnel and Like. Determined.  

As a result of the liberalization of the electricity markets, more and more countries are no longer using land nopole for power supply and other long-term purchase guarantees for electricity. The The electricity price or the electricity tariff then depend on the electricity demand. As a result, larger Fluctuations in electricity demand over the year, the week and the day are also the Electricity price and electricity remuneration are subject to very large fluctuations. So that be there is great interest on the part of the power plant operators in power plant systems which meet new requirements in the most economical way possible.

PRESENTATION OF THE INVENTION

The following power plant procedures are of interest to power plant operators under the conditions of liberalized electricity markets:

• - During times of a weak load on the network side with low electricity tariffs it is important, the lowest possible electricity generation costs and thus the highest possible To realize efficiency.
• - It is during times of a medium load on the network side with increased electricity tariffs important to achieve a balanced relationship between performance and efficiency. The Power plants are operated in the upper performance range. In this top performance In general, the power plants also have the upper efficiency range on.
• - During times of a high load on the network side, especially during off-peak periods Taking situations with high and even extremely high electricity tariffs is the effect Degree of electricity generation of minor importance. It depends now ne to achieve the highest possible output as close as possible to the limit output.

The invention is therefore based on the object of a method for operating a comm bi-power plant, consisting of at least one gas turbine plant, at least one Abhit to provide zekessel and at least one steam turbine plant, the Gas turbine system comprising at least one compressor, at least one combustion chamber and there is at least one gas turbine, the waste heat boiler has at least one pressure stage and the steam turbine system consists of at least one steam turbine. With such a Towards a combined cycle power plant, air is compressed in a compressor, then as combustion air Combustion chamber supplied, the hot gas generated there is passed to a gas turbine, and the exhaust gas from the gas turbine in a waste heat boiler to generate steam for one Steam turbine plant used. The procedure is supposed to be based on electricity tariffs enable the combined mode of operation of the combined cycle power plant.

This object is achieved according to the invention by additionally heating the exhaust gas ses the gas turbine an additional firing is arranged, and in addition means are provided  are, which allow the cooling of the intake air of the gas turbine system. In last The combined cycle power plant is now experiencing weak times without additional firing and without intake air cooling driven. In times of medium load, the combined cycle power plant with additional firing and / or intake air cooling. Also in exceptional cases during peak load periods situations, the combined cycle power plant is operated with additional firing and intake air cooling.

The essence of the invention is to form a combined cycle power plant with additional means an additional firing and an intake air cooling and by the targeted on set of these additives to implement modes of operation to the power plant among the various most network conditions d. H. under the conditions of different electricity tariffs to operate optimally (i.e. maximized profit).

In this context is also due to the mutual positive influence of the two especially in the case of peak load times, the additional fire and the intake air cooling. The intake air cooling increases the masses flow of the exhaust gases from the turbine and thus also the efficiency of the heat transfer in the consequent more powerful waste heat boiler. With the additional firing you usually increase constant pressure and temperature conditions the mass flows in the water / steam Circulation. With simultaneous use of intake air cooling and additional firing, the improved heat transfer efficiency in the waste heat caused by the intake air cooling As a result, the boiler also increases the efficiency of the additional firing.

Preference is given to the above driving styles in low-load times with low power consumption the combined cycle power plant without additional firing and without intake air cooling in the Lei range up to the maximum rated power or maximum continuous power. Continue to be The combined cycle power plant can also be preferred in times of medium load with increased electricity tariffs Additional firing and / or intake air cooling in the power range between nominal power or maximum continuous power and maximum power are driven, and / or during peak load times the combined cycle power plant with additional firing and intake can operate with the highest electricity tariffs air cooling in the range of the maximum power.

According to a further embodiment of the invention, the Zu becomes in times of medium load set firing or the intake air cooling operated and thereby an increase in Lei power of the combined cycle power plant up to about 20% in the case of additional firing or 5% in the case of Intake air cooling, particularly preferably up to 10% in the case of additional firing or 2.5% in the case of intake air cooling based on the nominal output. But it is also possible Additional times and intake air cooling, both at medium times, are required in times of medium load Performance to operate, and thereby an increase in the performance of the combined cycle power plant about 12.5%, particularly preferably up to 6%, based on the nominal power. However, it is particularly preferred to operate only the auxiliary firing at medium load.  

According to a further embodiment of the invention, the peaks become during peak load times set firing and the intake air cooling operated, increasing the performance of the Combined power plant up to about 25%, particularly preferably up to 12.5% based on the nominal performance is effected.

Another embodiment of the invention is characterized in that the addition Firing in the direction of flow of the exhaust gas of the gas turbine system in front of the waste heat boiler and / or inside the waste heat boiler, particularly preferably in the direction of flow the medium pressure evaporator is arranged. The intake air is cooled by means of a Intake air line arranged cooling device. The cooling of the intake air can by means of a cooling medium via a heat exchanger, directly or indirectly, d. H. about one Secondary cooling circuit. On the other hand, cooling by means of injection is cool lumbar / evaporating medium in the intake air possible (evaporative cooler).

Further preferred embodiments of the invention are in the dependent claims described.

BRIEF EXPLANATION OF THE FIGURES

The invention is intended to be explained below using exemplary embodiments in connection with the figures are explained in more detail. Show it:

Figure 1 is a schematic of a combined cycle power plant. and

Fig. 2 is a diagram of a combined cycle power plant with additional firing and intake air cooling.

WAYS OF CARRYING OUT THE INVENTION

Fig. 1 shows an exemplary embodiment of the inventive method, a schematic representation of a combined cycle power plant with a single-shaft system. The water / steam circuit with waste heat boiler 7 and steam turbine system 13 is designed, for example, as a three-pressure process with reheating 17 .

The combination of a gas and a steam pro understood in the form of a gas turbine system and a steam turbine system. The Heat of the exhaust gases from the gas turbine of the gas turbine system is used to generate steam in a waste heat boiler. The steam generated is used to drive the steam turbine system uses.

According to FIG. 1, the combined cycle power plant has a gas turbine system 1 , the exhaust gas 6 of which is fed to a waste heat boiler 7 . The gas turbine system 1 consists of a compressor 2 , a combustion chamber 3 and a gas turbine 4 . The gas turbine 4 , the compressor 2 and the generator 5 are arranged on a common shaft 8 . The gas turbine 4 drives both the compressor 2 and the generator 5 via this common shaft 8 . The Ga sturbinenanlage 1 and the generator 5 are referred to as a gas turbine set. The air supplied to the compressor 2 via an intake air line 9 arrives after compression in the compressor 2 as combustion air 10 in the combustion chamber 3 . In the combustion chamber 3 , fuel supplied via the fuel line 11 is burned. The hot gas 12 generated in the combustion chamber 3 reaches the gas turbine 4 and is expanded there in a work-performing manner.

A gas turbine system can also have multiple combustion chambers and multiple gas turbines point. For example, in gas turbine plants with sequential combustion are one High pressure combustion chamber with high pressure turbine a low pressure combustion chamber with low downstream of the pressure turbine. A gas turbine system can also have several compressors sen.

The steam generated in the waste heat boiler 7 in a plurality of pressure stages is fed to a steam turbine system 13 via the respective live steam lines 30 , 37 , 42 . The high pressure steam is after its processing in the high pressure steam turbine 14 of the steam turbine system 13 via the cold reheater steam line 16 to the reheater 17 of the waste heat boiler 7 , where it overheats and via the hot reheater steam line 18 together with the medium pressure steam of the medium pressure / low pressure steam turbine 13 of the steam turbine 15 fed.

This steam turbine system 13 consists of a high-pressure steam turbine 14 and a medium-pressure / low-pressure steam turbine 15 . In the present case, the steam turbine system 13 also drives the generator 5 via a clutch 19 . In cases in which the gas turbine system 1 and the steam turbine system 13 with the generator 5 are on the shaft 8 , one also speaks of single-shaft systems. If the gas turbine system, consisting of compressor 2 , combustion chamber 3 and gas turbine 4 , and the steam turbine system 13 each have their own generator 5 , this is referred to as a multi-shaft system. In analogy to the gas turbine set (gas turbine system and generator), one also speaks of a steam turbine set with a steam turbine system. In multi-shaft systems, more than one gas turbine set with associated waste heat boiler can be combined with, for example, a steam turbo set.

The steam processed in the steam turbine plant 13 flows into a condenser 20 . After the condensation of the exhaust steam in the condenser 20 , the condensate is conveyed from the condensate pump 21 to the feed water tank / degasser 22 , degassed there and stored ge.

From the feed water tank / degasser 22 , feed water is conveyed to a high pressure economizer I 24 by means of the high pressure feed water pump 23 , then flows to the high pressure economizer II 25 , to the high pressure economizer III 26 and from there to the high pressure steam drum 27 . The high-pressure steam drum 27 communicates with the high-pressure evaporator 28 in connection Ver. The high-pressure steam drum 27 is followed by a high-pressure superheater 29 , to which the high-pressure fresh steam line 30 connects, which leads to the high-pressure steam turbine 14 of the steam turbine system 13 .

From the feed water tank / degasser 22 , feed water is conveyed to a medium pressure economizer I 32 by means of the medium pressure feed water pump 31 , then flows to the medium pressure keconomizer 11 33 and from there to the medium pressure steam drum 34 . The medium pressure steam drum 34 is connected to the medium pressure evaporator 35 . Next follows the medium pressure steam drum 34, a medium pressure superheater 36 , to which the medium pressure fresh steam line 37 connects, which leads to the medium pressure / low pressure steam turbine 15 of the steam turbine system 13 .

From the feed water tank / degasser 22 , feed water is conveyed to a low pressure economizer 39 by means of the low pressure feed water pump 38 and flows from the latter to the low pressure steam drum 40 . The low pressure steam drum 40 is connected to the Niederdruckver steamer 41 . The low-pressure fresh steam line 42 connects to the low-pressure steam drum 40 and also leads to the steam turbine system 13 . The low pressure steam also serves to degas the condensate in the feed water tank / degasser 22 .

The high pressure economizer I 24, the high pressure economizer II 25 , the high pressure economizer III 26 , the high pressure steam drum 27 , the high pressure evaporator 28 and the high pressure superheater 29 together form a high pressure steam system working at a first pressure stage.

The medium-pressure economizer I 32, the medium-pressure economizer II 33 , the medium-pressure steam drum 34 , the medium-pressure evaporator 35 and the medium-pressure superheater 36 together form a medium-pressure steam system working at a second pressure stage.

The low pressure economizer 39 , the low pressure steam drum 40 and the Niederdruckver steamer 41 together form a low pressure steam system working at a third pressure level.

In the present case, a waste heat boiler consisting of drum circulation evaporators described. Therefore, the economizer of the respective pressure level is preheated Feed water conveyed into the steam drum. The drum water becomes steam in the system drum evaporator circulated and partially evaporated. In the steam drum the separation of water and steam. The water is fed back to the evaporator, while the steam is supplied directly or via a possibly existing superheater Steam turbine plant arrives.  

After flowing through the waste heat boiler 7 , the exhaust gas 6 finally reaches the outside via a chimney 43 .

To the water / steam cycle essentially include the waste heat boiler 7 , the Dampfturbi nenanlage 13 , the condenser 20 , the feed water tank / degasser 22 and the Pum pen, connecting pipes, etc. In the present case is located directly in the exhaust pipe 6 between gas turbine 4th and waste heat boiler 7 an additional firing 44 with the corresponding fuel line 45 . By means of this additional firing 44 , the exhaust gas 6 of the gas turbine 4 can be reheated if necessary, the residual oxygen present in the exhaust gas 6 being used for the combustion. Since the additional firing 44 is only in operation when the gas turbine system 1 is in operation, it initially does not require a fresh fan. Of course, the additional firing 44 can also be equipped with its own fresh fan if this is advantageous for structural, economic or operational reasons.

In addition to the illustrated embodiment of FIG. 1 with an additional firing 44 between the gas turbine 4 and waste heat boiler 7 , the additional firing 44 can also be arranged within the waste heat boiler 7 preferably in the flow direction upstream of a respective pressure stage, as shown in FIG. 2 using the example of the additional firing 44 a can be seen. Also, several additional firing devices can be arranged before the respective pressure levels.

As already mentioned, modern gas turbine systems are for good partial load reasons shafts, d. H. a high partial efficiency, designed so that this in a wide upper performance range can be operated at design temperature. Within that lei performance range takes place by regulating the mass flow of Intake air using adjustable guide vanes at the compressor inlet in connection with the Re regulation of the fuel heat output. At rated power, the options are above the air mass flow exhausted.

Modern combined cycle power plants are the power plants with the highest efficiency today. in the In the area of conventional power plants, they guarantee an extremely economical Stromer generation. The combined cycle power plants are therefore preferably operated at nominal power.

From the described designs and modes of operation of a gas turbine plant or a combined cycle power plant it follows:

• 1. With an increase in performance in the range below the upper process temperatures can it only for control and accuracy reasons and when leaving the Driving regime of normal operation to exceed the maximum for a limited time casual upper process temperatures.  
• 2. When there is an increase in output in the area of the upper process temperature that has already been driven Ren is inevitable when leaving the driving regime of normal operation violations of the maximum permissible upper process temperatures.
• 3. An increase in output beyond the nominal output or starting with the nominal output only possible by overfiring the gas turbine system. By ver tied enormous overload especially of the hot gas path is the operation of a Ga turbine system above the nominal power is only possible for a limited time or makes sense.

For these reasons, it is not sensible to operate a combined cycle power plant above the nominal power or the limit continuous power without further modifications and special driving styles. There are therefore at least one additional firing 44 and means for intake air cooling 46 are also provided for the method to be described here. Fig. 2 shows on one side an additional firing 44 a, which is arranged in the waste heat boiler 7 in front of the medium pressure evaporator 35 . In addition, the system in the intake air line 9 includes means for intake air cooling 46 of the gas turbine system 1 .

With an increase in performance by means of additional firing 44 , the exhaust gas 6 of the gas turbine system 1 is additionally heated by means of the heat introduced via the additional firing 44 . The se temperature increase of the exhaust gas 6 can now be used either to increase the parameters or the mass flow of the live steam generated in the waste heat boiler 7 . The output of the steam turbine plant 13 and thus of the combined cycle power plant can be increased in both ways. The increase in performance by means of additional firing 44 is theoretically not limited. Since the combined efficiency of a combined cycle power plant is greater than the efficiency of the steam process, an increase in output using additional firing, with a few exceptions, usually leads to a reduction in the combined efficiency. Furthermore, the increase in output by means of additional firing 44 due to the design, in particular of the water / steam cycle, but also, for example, of the electrical systems starting with the generator, has technical and economic limits. The increase in output by means of additional firing 44 is therefore limited to values up to approximately 20%, preferably to values up to 10% based on the nominal output.

With an improvement in performance by 46 Intake air of the intake air 9 and the associated increase in the density of the intake air is 9 increases their Mas senstrom by cooling. The output of the gas turbine system 1 increases by increasing the mass flow of the working fluid. The increase in performance by means of intake air cooling 46 is limited by the design of the gas turbine system 1 . Depending on the ambient conditions, an increase in performance by means of intake air cooling usually does not lead to a significant change in the combined efficiency, with a few exceptions. Furthermore, the increase in performance by means of intake air cooling is subject to technical and economic limits not only through the design of the gas turbine system but also, for example, also of the electrical systems starting with the generator. The increase in performance by means of intake air cooling is therefore limited to values of up to about 5%, preferably to values of up to 2.5% based on the nominal output.

If appropriate measures are implemented, in particular regarding the design, the measures of the additional firing and the intake air cooling are used to to preferably increase the output of the combined cycle power plant by up to about 25% if necessary to achieve up to 12.5% based on nominal power.

An increase in output beyond the nominal output is, for example, due to overload, through the use of existing reserves or, for example, through an enlarged outage individual components or systems can be laid. The possibilities can be seen in Ab dependency of the respective component or system can be very different.

First of all, the gas turbine system must be as wide as possible in terms of its design In the area of the ambient conditions, a performance-increasing intake air cooling is possible chen.

Steam turbines often fail to swallow at rated power. That is, The steam turbines can process steam mass flows that are in part significantly higher than the nominal steam mass flow at the expense of a lower efficiency and thus deliver more power. One can design the high-pressure and medium-pressure / low-pressure steam turbine 14 , 15 , as with the enlarged design 47 , 48 , but also for larger steam mass flows. Analogous relationships also apply to many other components. For example, in the case of a condenser, an increased exhaust mass flow would only be at the expense of the vacuum. Other components are manufactured in specific output sizes regardless of specific power plants. This applies, for example, to the generator. Either the generator has reserves anyway, you can improve its cooling to increase performance, or you can install a more powerful version.

The waste heat boiler is logically equipped with additional firing. The heat sink sel and the additional firing are advantageously designed, designed and to operate that for the purpose of increasing performance an increased steam mass flow ge can be driven. This concept offers an increase in steam parameters the advantage of waste heat boilers, steam turbines, pipes, etc. not for higher parameters to have to interpret.

The water / steam cycle also has to cope with the increased mass flows during operation of the Zu Take into account the set firing. For example, this may be the case with the pipes Possible only through higher flow velocities, for example the deflection the changing conditions.  

He for increasing the output of a combined cycle power plant beyond the nominal output required additional investments for the additional firing and the intake air cooling as well as all However, further adjustments are significantly less than the additional investments for one on the corresponding increased output designed power plant. A performance increase of the com The bi-power plant using additional firing and intake air cooling is then economically special advantageous, the more often and the shorter the overload modes to be expected. Investitio Additional services to cover peak loads are becoming less and less economical useful, the lower the hours of use for these additional services.

The increased operating costs when operating the auxiliary firing and intake air cooling result from the increased use of fuel and, in the case of intake air cooling, from operation of cooling systems and / or the need for cooling medium.

The structure of the water / steam circuit described, the waste heat boiler 7 , the Ga sturbinenanlage 1 and the steam turbine system 13 is only to be considered as an example, since, as is generally known, such components or systems can be designed very differently. For the idea of the invention it is only essential that

• - Between gas turbine 4 and waste heat boiler 7 , ie in the exhaust pipe 6 ,
• - Inside the waste heat boiler 7 or
• - Provided the waste heat boiler 7

an additional firing

44

and that means are provided which allow the intake air of the gas turbine system

1

to cool.

The power plant is now operated as follows:

• 1. In low-load times with low electricity tariffs, the combined cycle power plant in a performance range with maximum efficiency, d. H. with lowest variables Costs (without additional firing and without intake air cooling).
• 2. In times of medium load with increased electricity tariffs, the combined cycle power plant is included Additional firing and / or intake air cooling, d. H. in a performance range above the nominal output and thus increased variable costs.
• 3. During peak load times and for the purpose of "primary" and "secondary response" with The combined-cycle power plant with the additional firing and intake runs the highest electricity tariffs air cooling in the range of the maximum capacity and thus with high variable costs.

Additional firing and / or intake air cooling can be used depending on the specific edge conditions in different order but also in combination to "low rem power level "are used. Additional combustion and / or intake air cooling can also be used, for example, in times of very low fuel prices, to drive the gas turbine plant gently at reduced process temperatures.  

In addition to the means mentioned above, the combined cycle power plant can also use steam Have injection, which similar to the intake air cooling, the mass flow in the Ga turbine system and thus the performance of the gas turbine system increased. The steam injection Tongue can be in the compressor, in the combustion chamber, in the gas turbine or in between arranged paths are done. This steam injection can ins especially with medium load or peak load, if the Design of the facility allows this.  

LIST OF REFERENCE NUMBERS

1

Gas turbine plant (consisting of

2

.

3

.

4

)

2

compressor

3

combustion chamber

4

gas turbine

5

generator

6

Exhaust gas, exhaust pipe

7

waste heat boiler

8th

(common) wave

9

Intake air, intake air line

10

combustion air

11

Fuel line (for combustion chamber

3

)

12

hot gas

13

Steam turbine plant (consisting of

14

.

15

)

14

High pressure steam turbine

15

Medium-pressure / low-pressure steam turbine

16

Cold reheater steam line

17

Reheater

18

Hot reheater steam line

19

clutch

20

capacitor

21

condensate pump

22

Feedwater vessel / degassing

23

High-pressure feed water pump

24

High pressure economizer I

25

High pressure economizer II

26

High pressure economizer III

27

High-pressure steam drum

28

High pressure evaporator

29

High-pressure superheater

30

High-pressure steam line

31

Medium pressure feed water pump

32

Medium pressure economizer I

33

Medium pressure economizer II

34

Medium pressure steam drum

35

Medium-pressure evaporator

36

Medium pressure superheater

37

Medium pressure steam line

38

Low-pressure feed water pump

39

Niederdruckeconomizer

40

Low-pressure steam drum

41

Low-pressure evaporator

42

Low-pressure steam line

43

stack

44

supplementary firing

45

Fuel line (for additional firing

44

)

46

Intake air cooling

47

Enlarged interpretation of

14

48

Enlarged interpretation of

15

Claims (15)

1. Method for operating a combined cycle power plant, comprising at least one gas turbine system ( 1 ), at least one waste heat boiler ( 7 ) and at least one steam turbine system ( 13 ), the gas turbine system ( 1 ) comprising at least one compressor ( 2 ), at least one combustion chamber ( 3 ) and at least one gas turbine ( 4 ), the Abhit boiler ( 7 ) has at least one pressure stage and the steam turbine system ( 13 ) consists of at least one steam turbine ( 14 , 15 ), in which combined power plant compresses air in a compressor ( 2 ) and as combustion air ( 10 ) is fed to a combustion chamber ( 3 ), the hot gas ( 12 ) formed there is passed to a gas turbine ( 4 ), and the gas ( 6 ) from the gas turbine ( 4 ) in a waste heat boiler ( 7 ) to generate Steam is used for a steam turbine system ( 13 ), characterized in that an additional firing ( 44 ) is arranged for the additional heating of the exhaust gas ( 6 ) of the gas turbine ( 4 ) is t, that further means (46) are provided which permit a performance enhancing cooling of the intake air (9) of the gas turbine plant (1), that in low load Zei th with low power compensation the combined cycle power plant with no supplemental firing (44) and without Intake air cooling (46) driven is that at times intermediate load with increased Stromver remunerations the combined cycle power plant with supplemental firing (44) and / or Intake air cooling (46) will drive ge, and that the combined cycle power generation during peak load periods with the highest current compensation plant with supplementary firing (44) and Intake air cooling (46) driven becomes. 2. The method according to claim 1, characterized in that the combined cycle power plant is operated without additional firing ( 44 ) and without intake air cooling ( 46 ) in the power range up to the maximum rated power or limit continuous power in low-load times with low power payments. 3. The method according to any one of the preceding claims, characterized in that the combined cycle power plant with additional firing ( 44 ) and / or intake air cooling ( 46 ) is operated in the power range between nominal power or limit continuous power and limit power in times of medium load with increased electricity remuneration. 4. The method according to any one of the preceding claims, characterized in that the combined cycle power plant with additional firing ( 44 ) and intake air cooling ( 46 ) is operated in the area of the maximum power during peak load times with the highest power remuneration. 5. The method according to any one of the preceding claims, characterized in that the auxiliary firing ( 44 ) or the intake air cooling ( 46 ) are operated in times of medium load and thereby an increase in the output of the combined cycle power plant up to approximately 20% in the case of the auxiliary firing ( 44 ) or 5% in the case of intake air cooling ( 46 ), particularly preferably up to 10% in the case of additional firing ( 44 ) or 2.5% in the case of intake air cooling ( 46 ) in relation to the nominal output. 6. The method according to any one of the preceding claims, characterized in that the auxiliary firing ( 44 ) and the intake air cooling ( 46 ), both at medium power, are operated at times of medium load, and thereby an increase in the power of the com bi-power plant to about 12, 5th %, particularly preferably up to 6% based on the nominal power is effected. 7. The method according to any one of the preceding claims, characterized in that only the auxiliary firing ( 44 ) is operated at times of medium load. 8. The method according to any one of the preceding claims, characterized in that only the intake air cooling ( 46 ) is operated at times of medium load. 9. The method according to any one of the preceding claims, characterized in that the additional firing ( 44 ) and the intake air cooling ( 46 ) are operated during peak load times and thereby an increase in the output of the combined cycle power station is up to about 25%, particularly preferably up to 12.5% to the nominal power. 10. The method according to any one of the above claims, characterized in that the gas turbine system ( 1 ) drives a power-generating generator ( 5 ), and that the com bikraftwerk a steam turbine system ( 13 ) with several steam turbines ( 14 , 15 ), in particular re preferably with one High-pressure steam turbine ( 14 ) and a medium-pressure / low-pressure steam turbine ( 15 ). 11. The method according to any one of the above claims, characterized in that a gas turbine system ( 1 ) and a steam turbine system ( 13 ) are arranged on a shaft ( 8 ), and that the gas turbine system ( 1 ) and the steam turbine system ( 13 ) ge over this Drive shaft ( 8 ) an electricity generating generator ( 5 ). 12. The method according to claim 11, characterized in that the generator ( 5 ) between the gas turbine system ( 1 ) and the steam turbine system ( 13 ) is arranged, and that between the steam turbine system ( 13 ) and the generator ( 5 ), a clutch ( 19 ) is arranged. 13. The method according to any one of the above claims, characterized in that the additional firing ( 44 ) in the flow direction of the exhaust gas ( 6 ) of the gas turbine system ( 1 ) in front of the waste heat boiler ( 7 ) and / or within the waste heat boiler ( 7 ), particularly preferably in the flow direction is arranged in front of the high pressure evaporator ( 28 ). 14. The method according to any one of the above claims, characterized in that the intake air cooling ( 46 ) takes place by means of a cooling medium via a heat exchanger. 15. The method according to any one of the above claims, characterized in that the intake air cooling ( 46 ) takes place by means of injection of a cooling / evaporating medium into the intake air ( 9 ).