STOCHIOMETRICAL HYDROGEN / OXPERATE COMBUSTION TURBINE SYSTEM

Abstract

Stoichiometric hydrogen / oxygen combustion turbine system with: a high-pressure steam turbine (2); a low-pressure steam turbine (3); and a heater (5) arranged between the high-pressure steam turbine (2) and the low-pressure steam turbine (3), wherein the heater (5) has: a combustion section (53) in which stoichiometric combustion of hydrogen and oxygen is generated to form high-temperature steam; and a mixing section (55) configured such that the steam discharged from the high-pressure steam turbine (2) is mixed with the high-temperature steam from the combustion section (53) to form a mixed steam and to supply the mixed steam to the low-pressure steam turbine (3), characterized by that the combustion section (53) has: a combustion chamber in which the stoichiometric combustion of hydrogen and oxygen is produced; and a cooling chamber (61) configured to cover and cool the combustion chamber (60) from an outside; and wherein part of the live steam (S4) supplied to the high pressure steam turbine (2) is introduced into the cooling chamber (61) as cooling steam (S6).

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] The present patent application is based on and claims priority from the Paris Convention of the Japanese patent application JP 2018 - 123 811 A dated 3 February 2017, the entire disclosure of which is incorporated herein by reference as part of this application. BACKGROUND OF THE INVENTION (Field of Invention)

[0002] The present application relates to a stoichiometric hydrogen / oxygen combustion turbine system applicable in a combined cycle gas turbine power plant. (Description of the relevant state of the art)

[0003] Combined cycle power plants (CCPPs) have gained attention as a technology for CO2 reduction, potentially preventing global warming and mitigating climate change. It is proposed that a stoichiometric hydrogen / oxygen combustion turbine (often referred to as a "hydrogen turbine") or an equivalent combustion turbine be used in CCPPs. However, since the combustion temperature in a stoichiometric hydrogen / oxygen combustion turbine reaches 3000 °C, the fuel gas temperature must be reduced to a level that allows for the protection of a combustion chamber formed by a burner wall and the implementation of a turbine section using steam cooling technology.

[0004] To achieve this, a combined cycle power plant system was proposed in which an exhaust gas boiler (heat exchanger) recovers the exhaust heat from a gas turbine engine as steam, and a stoichiometric hydrogen / oxygen combustion heater (burner) is located upstream of a steam turbine (e.g., patent document 1). In this system, steam from the exhaust gas boiler is supplied to the steam turbine. A stoichiometric combustion of hydrogen and oxygen is generated in the heater, the fuel gas is diluted and cooled by means of high-temperature and high-pressure steam from the exhaust gas boiler, and the steam is then supplied to the steam turbine. [Related document][Patent document]

[0005] [Patent Document 1] JP Disclosure No. JP H07-208192A

[0006] AT 94 317 B describes a method for utilizing a highly heated gas combustion mixture.

[0007] JP H10-306 709 A describes a hydrogen combustion turbine plant.

[0008] DE 697 18 337 T2 describes a steam-cooled steam turbine with energy and water recovery.

[0009] US 4 074 708 A describes a device for the rapid superheating of steam flowing into a turbine.

[0010] JP H07- 208 192 A describes a hydrogen-oxygen combustion turbine plant. OVERVIEW OF THE INVENTION

[0011] The invention is defined by the features of claim 1.

[0012] In the combined cycle power plant disclosed in patent document 1, the gas temperature remains high even when the fuel gas produced by the stoichiometric combustion of hydrogen and oxygen (typically 2800 to 3000 °C) is diluted by exhaust steam (typically 500 to 600 °C) from the flue gas boiler. When such a high-temperature fuel gas is introduced into the steam turbine, a problem arises with the heat resistance of the turbine's metal components. To prevent this problem, the degree of stoichiometric combustion of hydrogen and oxygen must be reduced. However, reducing the degree of stoichiometric combustion of hydrogen and oxygen leads to a reduction in the power output and thermal efficiency of the power plant.

[0013] One object of the present invention is to provide a stoichiometric hydrogen / oxygen combustion turbine system that reduces CO2 production and improves performance and thermal efficiency.

[0014] To solve the above-mentioned problem, a stoichiometric hydrogen / oxygen combustion turbine system according to the invention has the following features: A high-pressure steam turbine; a low-pressure steam turbine; and a heater arranged between the high-pressure and low-pressure steam turbines. The heater comprises: a combustion section in which stoichiometric combustion of hydrogen and oxygen is generated or effected to produce high-temperature steam; and a mixing section configured such that the steam discharged from the high-pressure steam turbine is introduced into the fuel gas (high-temperature steam) of the combustion section, and the resulting product is fed to the low-pressure steam turbine.

[0015] In this configuration, the fuel gas (high-temperature steam) produced by the stoichiometric combustion of hydrogen and oxygen is quenched (rapidly cooled) by the exhaust steam, which has a relatively low temperature and is discharged from the high-pressure steam turbine. This allows the temperature of the steam supplied to the low-pressure steam turbine to be adjusted so that it does not exceed the heat resistance limit of the steam turbine's metal components, which are cooled by steam in a cooling structure similar to that of a gas turbine engine. Furthermore, the degree of stoichiometric combustion of hydrogen and oxygen does not need to be reduced, thus improving power output and thermal efficiency. The use of a hydrogen turbine also reduces CO2 emissions.

[0016] In the present invention, the combustion section comprises: a combustion chamber in which stoichiometric combustion of hydrogen and oxygen is generated; an ejector configured to expel the high-temperature vapor (fuel gas) from the combustion chamber into a mixing chamber formed in the mixing section, and to draw in the discharged vapor. The mixing section may include a diffuser configured to expand and mix the vapor from the ejector and to increase the vapor pressure. In this configuration, vapor at a suitable temperature and pressure can be obtained using a simple structure.

[0017] In the present invention, the combustion section can comprise: a combustion chamber in which stoichiometric combustion of hydrogen and oxygen is generated; and a cooling chamber configured to cover and cool the combustion chamber from the outside. A portion of the live steam supplied to the high-pressure steam turbine is introduced into the cooling chamber as cooling steam. In this case, the live steam can effectively be used as a coolant for cooling the cooling chamber without the need for a separate coolant.

[0018] In the present invention, the combustion section can have a combustion chamber wall, which forms the combustion chamber, and the combustion chamber wall can be equipped with a steam conduit hole to direct the cooling steam from the cooling chamber into the combustion chamber and to enable film cooling of an inner surface of the combustion chamber wall. Thus, film cooling is achieved for the combustion chamber wall forming the combustion chamber, and therefore, by means of a simple structure in which the steam conduit hole is formed only in the combustion chamber wall, it is possible to avoid the combustion chamber wall reaching a high temperature.

[0019] In the present invention, the stoichiometric hydrogen / oxygen combustion turbine system can further comprise: a gas turbine engine connected to the low-pressure steam turbine and the high-pressure steam turbine; and an exhaust gas boiler configured such that exhaust gas from the gas turbine engine is used as a heat source. Live steam recovered from the exhaust gas boiler can be supplied to the high-pressure steam turbine. Thus, exhaust gas from the gas turbine engine can be used effectively without generating any waste product when both steam turbines, the gas turbine engine, and the exhaust gas boiler are used in combination. This allows for the creation of a powerful and highly efficient system.

[0020] In the present invention, secondary steam obtained in an intermediate section of the exhaust gas boiler can be fed to an intermediate stage of the low-pressure steam turbine. Thus, the steam pressure can be increased in the intermediate stage of the low-pressure steam turbine and in the subsequent stages to improve performance.

[0021] In the present invention, the stoichiometric hydrogen / oxygen combustion turbine system can further comprise: a generator driven by the low-pressure steam turbine; the high-pressure steam turbine; and the gas turbine engine. In this configuration, torque obtained from the gas turbine engine and torques obtained from both steam turbines are added. Therefore, the generator can be driven with increased torque. This allows for a powerful and highly efficient system.

[0022] Any combination of at least two constructions disclosed in the attached claims and / or the description and / or the associated drawings shall be interpreted as if it were included within the scope of protection of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] The following description of preferred embodiments of the invention, in conjunction with the accompanying drawings, facilitates a better understanding of the invention. However, the embodiments and drawings serve only for illustration and explanation and are in no way to be considered as limiting the scope of protection of the present invention, the scope of which is to be determined in the appended claims. In the accompanying drawings, the same reference numerals are used to identify identical parts in the different views; and: Fig. Figure 1 schematically shows a configuration of the stoichiometric hydrogen / oxygen combustion turbine system according to a first embodiment of the present invention; Fig. Figure 2 shows a longitudinal sectional view of a heater used in the system; and Fig. Figure 3 shows an extended longitudinal section view of a main section of a combustion section of the heater. DESCRIPTION OF THE EXECUTION FORMS

[0024] A first embodiment of the present invention is described in detail below with reference to the drawings. Fig. Figure 1 shows a turbine system according to the invention comprising: a steam turbine 1, which is designed as a stoichiometric hydrogen / oxygen combustion steam turbine (often referred to as a “hydrogen turbine”); a gas turbine engine 30, an exhaust gas boiler 50; and a condenser 70.

[0025] The hydrogen turbine 1 comprises a high-pressure steam turbine 2, a low-pressure steam turbine 4, and a heater 5 arranged between the two steam turbines 2 and 3. Steam S1 discharged from the high-pressure steam turbine is fed to the low-pressure steam turbine 3 via the heater 5. A portion of the steam from the high-pressure steam turbine 2 is introduced into the low-pressure steam turbine 3 as turbine cooling steam S11.

[0026] Fig. Figure 2 shows that the heater 5 has a combustion section 53 in which stoichiometric combustion of hydrogen H2 and oxygen O2 is produced, and a mixing section 55 which allows the discharged steam S4 ( Fig. 1) the high-pressure steam turbine 2 is introduced into the combustion section 53, and this allows the discharged steam S4 to be supplied to the low-pressure steam turbine 3. The mixing section 55 has a diffuser 51 and a box-shaped body 52 that supports the diffuser 51. The diffuser 51 has a partially conical shape, in which, for example, a flow area or a cross-sectional area is substantially constant from the inlet to the intermediate section in the flow direction, and wherein the flow area gradually increases in size from the intermediate section to an outlet opening. A mixing chamber 55a is formed in the mixing section 55. The lower surface of the mixing chamber 55a forms an opening 58. The steam S1 discharged from a high-pressure steam turbine 2 is introduced into the mixing chamber 55a through the opening 58.

[0027] A mounting projection 52a is arranged on a side surface of the body 52, and a insertion hole 52b is formed in the mounting projection 52a. A stud BT is anchored in the mounting projection 52a. A flange 51b with a screw hole is arranged on the outer circumference of a proximal end section 51a of the diffuser 51. The proximal end section 51a of the diffuser 51 is inserted into the insertion hole 52b of the mounting projection 52a of the body 52. ​​The flange 51b with the screw hole on the outer circumference of the proximal end section 51a is attached to the mounting projection 52a of the body 52. ​​In this state, the stud BT of the proximal end section 51a is inserted into a insertion hole (not shown) of the flange 51b with the screw hole and tightened by means of a nut NT. Thus, the diffuser 51 and the box-shaped body 52 supporting the diffuser 51 are connected to each other.

[0028] The combustion section 53 comprises a combustion head 56 and an exhaust device 57 connected to an outlet of the combustion head 56. A boundary section 64 between the combustion head 56 and the exhaust device 57 forms an intermediate section of the combustion head 56. The combustion head 56 has, for example, a round cross-sectional shape in the transverse direction. The exhaust device 57 has, for example, a partially conical shape in which the cross-sectional area gradually increases towards the downstream side. The body 52 has a mounting hole 52c with the same axis C as the diffuser 51. The boundary section 64 of the combustion section 53 is inserted into the mounting hole 52c of the body 52 and fixed in the mounting hole 52c by means of a weld. Thus, the combustion section 53 is attached to the body 52 of the mixing section 55.

[0029] The boundary section 64 has a boundary line BL between the combustion head 56 and the exhaust device 57. The exhaust device 57 expels fuel gas (high-temperature steam) R from the combustion head 56 into the mixing chamber 55a and, by means of an exhaust effect, draws in or sucks in a portion of the steam S1 discharged through the outlet of the high-pressure steam turbine 2. The exhaust device 57 also has the same axis C.

[0030] A specific structure of combustion section 53 is described with reference to Fig. 3 described. Fig. Figure 3 shows that the combustion chamber 56 of the combustion section 53 has a combustion chamber 60 formed in its center and a cooling chamber 61 covering the combustion chamber 60 from the outside. Stoichiometric combustion of hydrogen (H2) and oxygen (O2) is generated in the combustion chamber 60. The cooling chamber 61 cools the combustion chamber 60 from the outside. The cooling chamber 61 is covered by an outer wall 54 of the combustion chamber 56. The combustion chamber 60 and the cooling chamber 61 are separated by a combustion chamber wall 63 forming the combustion chamber 60.

[0031] The ejection device 57 has an ejection passage 66 through which the fuel gas is ejected from the combustion chamber 60, and a cooling chamber 61A that covers and cools the ejection passage 66 from the outside. The cooling chamber 61A is covered by an outer wall 67 of the ejection device 57. The ejection passage 66 and the cooling chamber 61A are separated by an inner wall 68 of the ejection device 57. The two cooling chambers 61 and 61A are connected to each other. The downstream end of the cooling chamber 61A of the ejection device 57 is closed by an end wall 69. Fig. 2) connecting the two downstream end sections of the outer wall 67 and the inner wall 68 of the ejection device 57. Both outer walls 54 and 67 are formed by means of continuous wall sections. The combustion chamber 63 and the inner wall 68 of the ejection device 57 are also formed by means of continuous wall sections. This means that the combustion head 56 and the ejection device 57 are a single piece. However, both the combustion head 56 and the ejection device 57 can be designed as separate parts and connected to each other by means of an joining connection, such as a weld.

[0032] The cooling vapor S6 is introduced into the cooling chambers 61 and 61A through a cooling line 77, as described below. Several vapor line openings 65 are formed in the combustion chamber wall 63 and in the inner wall 68 of the ejection device 57. The cooling vapor S6, as described below, is introduced into the combustion chamber 60 and the ejection passage 66 through the vapor line openings 65. The cooling vapor S6 provides film cooling to the inner surfaces of the combustion chamber wall 63 and the inner wall 68 of the ejection device 57.

[0033] Fig. Figure 2 shows that hydrogen H2 and oxygen O2 are introduced into the combustion chamber 60 through a nozzle inserted into the combustion chamber 60 from a hydrogen source (not shown), such as a hydrogen cylinder, and an oxygen source (not shown), such as an oxygen cylinder.

[0034] The in Fig. The gas turbine engine shown in Figure 1 comprises a compressor 31, a turbine 32, and a burner 33. Exhaust gas G discharged from the turbine 32 is fed to the exhaust gas boiler 50, which is arranged in an outlet passage 81. The exhaust gas boiler 50 has a first boiler 50A, which is arranged on the downstream side in the direction of exhaust gas flow, and a second boiler 50B, which is also arranged on the downstream side in the direction of exhaust gas flow. The steam S3 discharged from the low-pressure steam turbine 3 is condensed by the condenser 70. The water obtained by the condenser 70 is pressurized by pumps 71 and 72 and conveyed by pumps 78 and 79 to the first boiler 50A and the second boiler 50B of the exhaust gas boiler 50. A heat exchange takes place between the exhaust gas G and the water, while the water flows into the water passage in the exhaust gas boiler 50.

[0035] Steam (superheated steam) obtained through heat exchange is collected in a first tank 74A in the first boiler 50A. The steam S4 is fed as live steam to an inlet of the high-pressure steam turbine 2 via a main line 72, which forms a main supply passage (hereinafter, "line" and "passage" have the same meaning). Steam (superheated steam) obtained from the second boiler 50B, that is, the steam S5, which has a relatively low temperature and is generated at an intermediate section 75 of the exhaust gas boiler 50, is collected in a second tank 74B. The steam S5 is fed as secondary steam to an intermediate stage 80 of the low-pressure steam turbine 3 via a secondary line 73, which forms a secondary supply passage.

[0036] The reheating steam S2, heated by the heater 5, has a temperature of approximately 900 to 1200 °C and receives enough energy to drive the low-pressure steam turbine 3.

[0037] A speed reducer 35 is arranged on the turbine 32 side of the gas turbine engine 30. A speed reducer (with a coupling) 7 is arranged on the high-pressure steam turbine side of the hydrogen turbine 1. A generator 36 is arranged as a load between the speed reducers 7 and 35. All these units 1, 7, 30, 35, and 36 are integrally connected by means of a conventional rotary shaft 6. The compressor 31 and the turbine 32 of the gas turbine engine 30 are connected by means of the conventional rotary shaft 6. However, the compressor 31 and the turbine 32 can also be connected by means of a different rotary shaft (biaxial type).

[0038] The following describes an operation carried out by the stoichiometric hydrogen / oxygen combustion turbine system with the structure described above. If the in Fig. When the gas turbine engine 30 shown in Figure 1 is operated, the exhaust gas G from the turbine 32 is fed to the exhaust gas boiler 50 via a line 76. The exhaust gas G flows into the outlet passage 81 from its upstream side to its downstream side. Meanwhile, when the hydrogen turbine 1 is operating, the steam discharged from the low-pressure steam turbine 3 is condensed by the condenser 70 into water condensate F, which is then fed to the exhaust gas boiler 50 via lines 78 and 79.

[0039] The discharged steam (live steam) S4, with the highest pressure in the cycle, is obtained from the first boiler 50A on the upstream side of the outlet passage 81. The majority of the discharged steam S4 is routed through the main line 72 to the inlet of the high-pressure steam turbine 2 of the hydrogen turbine 1. The cooling line 77 deviates from its position in the main line 72. A portion of the live steam S4 is routed as cooling steam S6 through the cooling line 77 to the cooling chamber 61 of the [unclear text]. Fig. The cooling vapor S6 is introduced into the heater 5 shown in the illustration. Thus, the cooling vapor S6 can be effectively used as a coolant for cooling the combustion chamber 60 without the need for a separate coolant.

[0040] If the internal pressure in combustion chamber 60 is set so that it is slightly below the pressure of the cooling steam S6, the film cooling described below can be carried out. If the internal pressure in combustion chamber 60 is set so that it is sufficiently higher than the pressure in the low-pressure steam turbine inlet, a high-velocity jet flow can be achieved, which is expected to produce a pressure-increasing effect at the low-pressure steam turbine inlet.

[0041] In the combustion chamber 60 of the combustion section 53, stoichiometric combustion of hydrogen H₂ and oxygen O₂ takes place to produce a fuel gas R. The combustion chamber 60 is covered from the outside by the cooling chamber 61, and several steam inlet holes 65 are formed in the combustion chamber wall 63. The cooling steam S₆, passed through the steam inlet holes 65, flows along the inner surface of the combustion chamber wall 63, thus providing film cooling for the combustion chamber wall 63. Similarly, the cooling steam passed through the steam inlet holes 65 provides film cooling for the inner wall 68 of the exhaust device 57. In this way, thermal damage to the fuel gas R on the combustion chamber wall 63 and the inner wall 68 of the exhaust device 57 is prevented.

[0042] The cooling steam S6 is not discharged to the outside as a waste product after being used for cooling, but is mixed with the fuel gas R in the combustion chamber 60 and the exhaust passage 66. This prevents a reduction in the amount of reheat steam S2 supplied from the heater 5 to the low-pressure steam turbine 3, and consequently, a reduction in the power output of the low-pressure steam turbine 3 is avoided. The outer surface of the exhaust device 57 is cooled by the discharged steam S1. Therefore, the cooling chamber 61A can be omitted, and a single duct with a simple, partially conical shape can be used.

[0043] The steam S1 discharged from the outlet of the high-pressure steam turbine 2 is introduced into the mixing chamber 55a through the opening 58 on the lower surface of the mixing section 55, as shown in Fig. Figure 2 illustrates this. The fuel gas (high-temperature vapor) R produced by the stoichiometric hydrogen / oxygen combustion is discharged through the discharge port 66 of the discharge device 57 into the mixing chamber 55a and dispersed. Due to a suction effect of the discharge device 57, the exhaust vapor S1 introduced into the mixing chamber 55a is drawn in, as indicated by arrows A, and directed into the diffuser 51 together with the fuel gas R produced by the stoichiometric hydrogen / oxygen combustion. As it flows through the diffuser 51, the high-temperature gas R produced by the stoichiometric hydrogen / oxygen combustion is mixed with the exhaust vapor S1 to form a mixed vapor. Simultaneously, the pressure of the mixed gas increases and its temperature decreases.

[0044] The fuel gas R produced by the stoichiometric hydrogen / oxygen combustion is thus sufficiently diluted by means of the discharged steam S1 (approx. 300 °C) and subsequently discharged by the diffuser 51 as intermediate superheating steam S2 (approx. 900 to 1200 °C), as in Fig. Figure 1 shows the steam supplied to the low-pressure steam turbine 3 to be used as energy to drive the low-pressure steam turbine 3. The low-pressure steam turbine 3 has an internal cooling structure similar to that of a gas turbine and uses the turbine cooling steam S11 (steam cooling) separately to be able to withstand a steam temperature of 1200 °C, unlike a conventional steam turbine.

[0045] When the reheat steam S2 is supplied to the low-pressure steam turbine 3, the steam temperature and pressure at the inlet of the low-pressure steam turbine 3 are increased to improve power output and thermal efficiency. As described above, the steam S3 discharged from the low-pressure steam turbine 3 is introduced into the condenser 70 to produce condensate, and the condensate is then converted back into steam by the exhaust gas boiler 50, and the steam is supplied to the hydrogen turbine 1. Water, the quantity of which is increased in the hydrogen turbine 1 by the stoichiometric hydrogen / oxygen combustion, is discharged to the outside via a drain 85, if necessary. In this way, the stoichiometric hydrogen / oxygen combustion turbine system can be achieved, which enables both a reduction in CO2 emissions and an improvement in power output and thermal efficiency.

[0046] In the configuration described above, the fuel gas (high-temperature steam) R produced by the stoichiometric combustion of hydrogen and oxygen in the combustion section 53 of the heater 5 is rapidly cooled (quenched) in the mixing section 55 by the steam S1 discharged from the high-pressure steam turbine 2. This allows the temperature of the steam supplied to the low-pressure steam turbine 3 to be adjusted so that it does not exceed the heat resistance limit temperature of the steam-cooled metal component. Furthermore, the degree of stoichiometric combustion of hydrogen and oxygen does not need to be reduced, leading to improved performance and thermal efficiency. Additionally, CO2 emissions can be reduced when using the hydrogen turbine.

[0047] As described above, the one from the in Fig. In the ejection device 57 shown in the illustration, the ejected steam R and the discharged steam S1 drawn in by the ejection effect are mixed in the diffuser 51 in such a way that mixed steam is produced, thereby reducing the temperature of the mixed gas. Accordingly, steam at a suitable temperature and pressure can be obtained using a simple structure.

[0048] The combustion section 53 of the heater 5 comprises the combustion chamber 60, in which stoichiometric combustion of hydrogen and oxygen is generated, and the cooling chamber 61, which covers and cools the combustion chamber 60 from the outside. A portion of the live steam S4 supplied to the high-pressure steam turbine 2 is introduced into the cooling chamber 61 as cooling steam S6. Therefore, the cooling steam S6 is effectively used as a coolant for cooling the cooling chamber 60 without the need for a separate coolant.

[0049] The steam conduit holes 65 are formed in the combustion chamber wall 63, which are located in Fig. The combustion chamber 60 shown in Figure 3 is formed, and the cooling vapor S6 in the cooling chamber 61 is introduced into the combustion chamber 60 through the vapor passages 65, and the inner surface of the combustion chamber wall 63 is cooled by means of the cooling vapor S6. In this way, it is possible to prevent the combustion chamber wall 63 from reaching a high temperature, and effective cooling to a suitable temperature can be achieved with a simple structure.

[0050] Furthermore, the in Fig. Figure 1 depicts a stoichiometric hydrogen / oxygen combustion turbine system comprising a gas turbine engine 30 and an exhaust gas boiler 50, which uses the exhaust gas G of the gas turbine engine 30 as a heat source, and the live steam S4 obtained from the exhaust gas boiler 50 is fed to the low-pressure steam turbine 2. In this way, the exhaust gas G of the gas turbine engine 30 can be used effectively without generating any waste products, and the system can be achieved with high power output and high efficiency.

[0051] Furthermore, the secondary steam S5 obtained from the intermediate section 75 of the exhaust gas boiler 50 is supplied to the intermediate stage 80 of the low-pressure steam turbine 3 via the secondary line 73. This allows the steam pressure to be increased in the intermediate stage 80 of the low-pressure steam turbine 3 and in the subsequent stages to improve performance.

[0052] Furthermore, the stoichiometric hydrogen / oxygen combustion turbine system according to the invention comprises the generator 36 driven by the high-pressure steam turbine 2, as well as the low-pressure steam turbine 3 and the gas turbine engine 30. Therefore, the torque obtained from the gas turbine engine 30 and the torques of the high-pressure steam turbine 2 and the low-pressure steam turbine 3 are added, resulting in a powerful and highly efficient generation system.

[0053] In the stoichiometric hydrogen / oxygen combustion turbine system according to the invention, an exemplary case is described in which a gas turbine engine 30 is used as a turbine, which in combination with the in Fig.The hydrogen turbine 1 shown in Figure 1 is arranged as follows. However, the turbine is not limited to the gas turbine engine 30 and, for example, a waste incineration turbine for waste incineration plants or another turbine can be arranged in combination. In any case, the stoichiometric hydrogen / oxygen combustion turbine system can be achieved, which enables a reduction in CO2 emissions and an improvement in thermal efficiency. If the gas turbine engine also uses hydrogen as fuel, a completely CO2-free generation system can be realized.

[0054] Although the present invention, in conjunction with its preferred embodiments, has been fully described with reference to the accompanying drawings, which serve only for illustrative purposes, those skilled in the art will immediately recognize numerous changes and modifications within the bounds of the obvious upon reading the description of the present invention presented here. Therefore, such changes and modifications, insofar as they do not deviate from the scope of protection of the present invention as set forth in the accompanying claims, are to be understood as being included herein. LIST OF REFERENCE MARKS 1 Steam turbine (hydrogen turbine) 2 high-pressure steam turbines 3 Low-pressure steam turbine 5 heaters 6. Rotary shaft 7 Speed ​​reducers (with clutch) 30 gas turbine engine 32 Turbine 35 Speed ​​reducers 36 Generator 50 exhaust gas boilers 51 Diffuser 53 Combustion section 55 Mixing section 55a Mixing chamber 57 Ejection device 60 combustion chamber 61 Cold storage room 63 Combustion chamber wall 65 Steam pipe hole R Fuel gas (high-temperature steam) S1 Steam from high-pressure steam turbine outlet S2 Intermediate superheating steam S4 discharged steam (fresh steam) S5 discharged steam (secondary steam) S6 Cooling steam

Claims

[1] Stoichiometric hydrogen / oxygen combustion turbine system with: a high-pressure steam turbine (2); a low-pressure steam turbine (3); and a heater (5) arranged between the high-pressure steam turbine (2) and the low-pressure steam turbine (3), wherein the heater (5) has: a combustion section (53) in which stoichiometric combustion of hydrogen and oxygen is produced to form a high-temperature steam; and a mixing section (55) configured to mix the steam discharged from the high-pressure steam turbine (2) with the high-temperature steam of the combustion section (53) to form a mixed steam and supply the mixed steam to the low-pressure steam turbine (3), characterized by , that the combustion section (53) comprises: a combustion chamber in which the stoichiometric combustion of hydrogen and oxygen is produced; and a cooling chamber (61) configured to cover and cool the combustion chamber (60) from an outside; and wherein a part of the fresh steam (S4) supplied to the high-pressure steam turbine (2) is introduced into the cooling chamber (61) as cooling steam (S6). [2] A stoichiometric hydrogen / oxygen combustion turbine system according to claim 1, wherein the combustion chamber section has a combustion chamber wall (63) which forms the combustion chamber (60); and the combustion chamber wall (63) has a steam line hole (65) to guide the cooling steam from the cooling chamber (61) into the combustion chamber (60) and to enable film cooling for an inner surface of the combustion chamber wall (63). [3] A stoichiometric hydrogen / oxygen combustion turbine system according to any one of claims 1 or 2, further comprising: a gas turbine engine (30) connected to the low-pressure steam turbine (3) and the high-pressure steam turbine (2); and an exhaust gas boiler (50) configured to use exhaust gas of the gas turbine engine (30) as a heat source, wherein the live steam obtained by the exhaust gas boiler (50) is supplied to the high-pressure steam turbine (2). [4] Stoichiometric hydrogen / oxygen combustion turbine system according to claim 3, wherein the secondary steam obtained in an intermediate section of the exhaust gas boiler (50) is supplied to an intermediate stage of the low-pressure steam turbine (3). [5] A stoichiometric hydrogen / oxygen combustion turbine system according to claim 3 or 4, further comprising a generator (36) driven by the low-pressure steam turbine (3), the high-pressure steam turbine (2) and the gas turbine engine (30).

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