Patent Application
20150369125
This application claims priority to European application 14172982.2 filed Jun. 18, 2014, the contents of which are hereby incorporated in its entirety.
The present invention relates to combined-cycle power plants. It refers to a method for temporary increasing the power of a gas turbine, which is part of a combined-cycle power plant according to the preamble of claim 1.
It further refers to a combined-cycle power plant for conducting such method.
In combined-cycle power plants (CCPPs) the hot exhaust gas of one or more gas turbines (GTs) is used to generate steam for a separate water/steam cycle in a subsequent heat recovery steam generator (HRSG). The steam generated in the HRSG is used to drive a steam turbine, which often comprises a high pressure turbine (HP turbine), an intermediate pressure turbine (IP turbine) and a low pressure turbine (LP turbine). All turbines are connected with the HRSG to receive from and feed back to the HRSG steam at various pressures and temperatures.
According to the current State of the Art, the GT in a CCPP uses steam injection for temporary power increase, peak demands, etc.. For this purpose, steam is injected into the combustor or into the cooling system of the GT, which steam is extracted from the water/steam cycle.
In the case of the applicant's well-known gas turbines of type GT26/GT24 steam is extracted from the high pressure live steam line, which supplies the HP turbine of the steam turbine, or the once through cooler (OTC) feed line.
However, this kind of GT steam injection reduces the overall efficiency of the power plant.
It is an object of the present invention to provide a method for GT steam injection, which results in an improved efficiency.
It is a further object of the invention to disclose a combined-cycle power plant for conducting such a method.
These and other objects are obtained by a method according to claim 1 and a combined-cycle power plant according to claim 8.
The inventive method for temporary increasing the power of a gas turbine, which is part of a combined-cycle power plant, wherein the exhaust gas of said gas turbine is used in a heat recovery steam generator to generate steam for a water/steam cycle including a steam turbine with a high pressure steam turbine, an intermediate pressure steam turbine and a low pressure steam turbine, comprises the step of injecting steam from said water/steam cycle at a predetermined injection pressure into said gas turbine.
It is characterized in that steam of a lower pressure than said predetermined injection pressure is taken from said water/steam cycle, that the pressure of said steam taken from said water/steam cycle is increased to said predetermined injection pressure by subjecting it in separate compressing means to a compression step, and that said compressed steam is injected into said gas turbine.
An embodiment of the method according to the invention is characterized in that said separate compressing means comprises at least one steam-driven ejector.
Another embodiment of the method according to the invention is characterized in that said separate compressing means comprises at least two steam-driven ejectors with different fixed steam nozzles or with a fixed steam nozzle and a variable steam nozzle.
Just Another embodiment of the method according to the invention is characterized in that said at least one steam-driven ejector is driven by high pressure live steam, which is generated in said heat recovery steam generator and used to drive said high pressure steam turbine, that said steam of a lower pressure, which is compressed by means of said at least one steam-driven ejector, is cold reheat steam taken at the outlet of said high pressure steam turbine, and by mixing the high and lower pressure flow in said at least one steam-driven ejector an intermediate pressure flow is generated.
More specifically, the mass flow ratio between high pressure live steam and cold reheat steam is in the order of 2:1.
Another embodiment of the method according to the invention is characterized in that said at least one steam-driven ejector is driven by high pressure steam, which is on a lower temperature level than a high pressure live steam, which is generated in said heat recovery steam generator and used to drive said high pressure steam turbine, and that said high pressure steam is taken from said heat recovery steam generator upstream of a superheater section. The high pressure steam for driving the ejector can for example be taken from a high pressure drum or high pressure evaporator of the steam generator.
In a further embodiment a de-superheater can be arranged in the suction steam line before the ejector or other compression means to reduce its superheating degree. The stem to the ejector or other compression means is de-superheated to reduce the compression work needed to boost it to the pressure level required for injection into the gas turbine. Thus the amount of high pressure steam to increase the pressure level of the suction steam is reduced. The heat from de-superheating can be used for example for fuel preheating, for feedwater preheating or as heat source for other process steps.
A further embodiment of the method according to the invention is characterized in that the engagement of said at least one steam-driven ejector is controlled and/or switched on/off during operation, depending on available pressure differences or levels.
Furthermore, said gas turbine may be equipped with a turbine cooling air system, and said steam from said water/steam cycle is injected at a predetermined injection pressure into said turbine cooling air system of said gas turbine.
When said gas turbine is a gas turbine with sequential combustion comprising a first and second combustor and a first and second turbine, said steam from said water/steam cycle is preferably injected at a predetermined injection pressure into said gas turbine upstream of said second combustor, especially into said first turbine.
When said gas turbine is equipped with at least one combustor, said steam from said water/steam cycle is preferably injected at a predetermined injection pressure directly into said at least one combustor, especially together with a fuel for said combustor.
Usually, said gas turbine is equipped with at least one compressor, which supplies compressed air to a compressor plenum. Said steam from said water/steam cycle is preferably injected at a predetermined injection pressure into said the compressor plenum.
The inventive combined-cycle power plant for conducting the method according to the invention comprises a gas turbine the exhaust gas of which passes through a heat recovery steam generator, which is part of a water/steam cycle and supplies a steam turbine with steam at various pressures and temperatures.
It is characterized in that a steam line is provided between the water/steam cycle and said gas turbine for injecting steam from said water/steam cycle at a predetermined injection pressure into said gas turbine, and that a separate compressing means is inserted into said steam line for increasing the pressure of the steam flowing through said steam line.
An embodiment of the inventive combined-cycle power plant is characterized in that said separate compressing means comprises at least one steam-driven ejector with a fixed or variable steam nozzle.
Another embodiment of the inventive combined-cycle power plant is characterized in that said separate compressing means comprises at least two steam-driven ejectors with different fixed steam nozzles or with a fixed steam nozzle and a variable steam nozzle.
Just another embodiment of the inventive combined-cycle power plant is characterized in that said steam turbine comprises a high pressure steam turbine, which is connected with its inlet by a first HRSG connection to said heat recovery steam generator to receive high pressure live steam from said heat recovery steam generator, and that said at least one steam-driven ejector is driven by said high pressure (HP) live steam, which is supplied via a high pressure live steam line from said first HRSG connection.
Specifically, said high pressure steam turbine is connected with its outlet by a second HRSG connection to said heat recovery steam generator to feed cold reheat steam to said heat recovery steam generator, and that said at least one steam-driven ejector receives cold reheat steam, which is supplied via a cold reheat line from said second HRSG connection.
Another embodiment of the inventive combined-cycle power plant is characterized in that a switchable bypass line is provided for bypassing that said separate compressing means.
When said gas turbine is equipped with a turbine cooling air system, said steam line may be connected to said turbine cooling air system of said gas turbine.
A further embodiment of the inventive combined-cycle power plant is characterized in that said gas turbine is a gas turbine with sequential combustion comprising a first and second combustor and a first and second turbine, and that said steam line is connected to said gas turbine upstream of said second combustor, especially to said first turbine.
Another embodiment of the inventive combined-cycle power plant is characterized in that said gas turbine is equipped with at least one combustor, and that said steam line is connected to said at least one combustor.
Besides the combined cycle power plant a method for operating such a plant is object of the invention. The combined-cycle power plant comprises a gas turbine the exhaust gas of which passes through a heat recovery steam generator, which is part of a water/steam cycle and supplies a steam turbine with steam at various pressures and temperatures. A steam line is provided between the water/steam cycle and said gas turbine for injecting steam from said water/steam cycle at a predetermined injection pressure into said gas turbine, and that a separate compressing means is inserted into said steam line for increasing the pressure of the steam flowing through said steam line.
According to a first embodiment of the method loading of the combined-cycle power plant comprises the following steps:
Base load is the maximum continuous load which can be derived by the gas turbine, respectively steam turbine at given operating conditions. A high part load operating point in this context is a load point with at least 80% of the base load power output preferably more than 90% of the base load power output of the gas turbine, respectively steam turbine.
The above described method can advantageously be used for fast loading of the plant to a high load with steam injection. The “booster” (steam injection with compressing means) can start before the steam turbine reaches base load or a high part load operating point or after the team turbine reaches base load or a high part load operating point.
The present invention is now to be explained more closely by means of different embodiments and with reference to the attached drawings.
The gas turbine 11 receives air at an air inlet 15, which is compressed by compressor 16 and used in combustor 17 to burn a (gaseous and/or liquid) fuel 18. The hot gases from combustor 17 drive turbine 19 and afterwards flow through an exhaust gas line 25 to heat recovery steam generator 13 to generate and/or reheat steam, and finally into a stack 26.
Steam turbines 20 and 21 are connected via various HRSG connections h1, h4 and h2, h5 to heat recovery steam generator 13 (four exemplary HRSG accesses H1-H4 are shown in
High pressure steam turbine 20 receives high pressure live steam via HRSG connection h1 and feeds back to heat recovery steam generator 13 cold reheat steam via HRSG connection h4.
The HRSG can have a superheater section for example between accesses H1 and H2 (not shown). Further, a drum can be arranged for the different pressure levels (not shown).
According to the embodiment shown in
Thus, cold reheat steam pressure is increased by compressing means, in particular an ejector. The ejector is “driven” by HP live steam. The engagement of the ejector can be controlled, switched on/off during operation, depending on available pressure differences or levels. Instead of HP live steam HP steam can be used to drive the ejector from a lower HP temperature level e.g. upstream of a superheater section in the HRSG instead of HP live steam (via pre-superheater steam line 28 in
The consideration is that it is more efficient to take steam from the intermediate pressure line (i.e. cold reheat steam), where it has already done work in the HP steam turbine 20. However, the pressure level is not sufficiently high, although close to the desired value.
The efficiency and power advantage to use only cold reheat steam instead of HP steam in a combined-cycle can be significant. Since the cold reheat pressure is not far from the desired pressure level, the cold reheat steam can easily be compressed to bring it to the desired level.
The compression is favourably done with an ejector, which has been disclosed in a different application in document DE 197 02 830 C1. However, the ejector needs a higher pressure source. By mixing the high and low pressure flow in such an ejector an intermediate pressure flow is generated. The high pressure source is the HP live steam (HRSG connection h1). The low pressure source is the cold reheat steam (HRSG connection h4). The necessary mass flow ratio should be in the order of 2:1 (HP:IP).
The ejector of the compressing means 14 can be in operation under all steam injection load points, or it can be in operation just at load points where the cold reheat steam pressure is not sufficient. These can be cases where the water/steam cycle is not at base load yet.
A variation of the invention is to use HP steam to (a) drive the ejector or (b) directly inject into the GT from a lower temperature source, e.g. before entering the superheater section in the HRSG 13.
Since there is HP steam required to drive the ejector, the potential benefit for the combined cycle (CC) is in the order of 0.2%-points and 1 MW.
There are various configurations possible for the ejector-equipped compressing means 14. Some of these configurations are shown in
a) shows a compressing means 14a with an ejector E1, which is a fixed nozzle steam ejector (the driving steam nozzle has a fixed cross section).
In this configuration, the design of fixed nozzle steam ejector E1 may be optimized according to the motive and suction steam pressures, and the targeted discharge steam pressure and mass flow at the mostly operated condition (design point).
b) shows a compressing means 14b with an ejector E2, which has a variable nozzle (indicated by the additional arrow). The variable nozzle steam ejector E2, which can be controlled by a control unit 30, may be designed in addition to the fixed nozzle ejector E1 to cover the entire or part of the off design operation range, and may be optimized for selected part load operations.
c) shows a compressing means 14c with a plurality of fixed nozzle steam ejectors E3, E4, E5. They are designed to improve the efficiencies at the mostly operated condition (design point) and over the entire operation range and can be controlled by a control unit 30. Similar to
d) shows a combination of fixed nozzle steam ejectors E3 and E4 with a variable nozzle steam ejector E6.
Thus, depending on the operation range (discharge steam mass flow, suction to discharge pressure ratio etc.), efficiency, cost of requirements, fixed and/or variable nozzle ejectors can be considered.
The fix nozzle steam ejector must be designed for a part-load case based on lowest available motive steam pressure, targeted discharge steam pressure and mass flow, while the efficiency at full load is lower. To improve efficiencies at design point and over the operation range, multiple fix nozzle ejectors may need to be combined (see above).
The variable nozzle ejector has relatively high efficiencies over larger range of operation (in terms of motive steam pressure/discharge mass flow), which is comparably more expensive than fix nozzle ejector. Depending on the range of operation, multiple variable nozzle ejectors may also needed sometime.
Furthermore, as shown in
Furthermore, a de-superheater may be arranged in the suction steam line 29 before the ejector to reduce its superheating degree. The suction steam temperature at the ejector after de-superheating is then at a saturation temperature of +3˜50 K.
The suction steam can also be hot reheat steam to the steam turbine or from the HRSG.
An optional de-superheater 31 is shown in
In general, the steam can be injected into the turbine cooling air system.
The steam can also be injected directly into the combustor 17b (or burner)
Finally, the steam can be injected into the compressor plenum.
As has already been mentioned above, the low pressure steam can be de-superheated to improve the ejector efficiency (mass flow rate of boosted steam to high pressure steam). De-superheating can be done by heat exchange using the heat for example for feed water preheating. De-superheating can also be done by water injection into the steam thereby increasing the steam flow.
The bypass line 27 described above can be used for fast loading of the system. This allows start of the steam injection before the steam pressures reach base load level.
| Number | Date | Country | Kind |
|---|---|---|---|
| 14172982.2 | Jun 2014 | EP | regional |
