STEAM COOLING TYPE GAS TURBINE COMBUSTOR

Abstract: In using a high pressure steam as a cooling medium for a gas turbine combustor, combustor walls exposed to a high temperature combustion gas is constructed such that a sheet having a strength for high temperatures is joined by brazing to those surfaces of a wall plate, on which a plurality of flow passage grooves for a cooling steam are provided, to form steam flow passages, which communicate at one side thereof with a cooling steam supply manifold and at the other side thereof with a steam recovery manifold so that a steam supplied into the steam flow passages from the supply manifold cools the combustor wall surfaces and recovery manifold combustor wall surfaces. Accordingly, it is possible to form cooling passages of adequate strength and inhibit leakage of the steam outside a system.

Description: Industrial Field This invention concerns a steam-cooled combustor for a gas turbine. More specifically, it concerns a structure for steam-cooling the exterior wall panels of the combustor, which are exposed to very hot combustion gases. Technical Background One effective way to improve the thermal efficiency of a gas turbine is to boost the temperature at the gas inlet of the turbine. It is also desirable to suppress increased emission of NO x from the combustor, which supplies combustion gases to the turbine, and to improve the heat resistance of the turbine and its cooling capacity. Since the combustor is exposed to temperatures of 1500 to 2000 °C, it must be properly cooled so that the temperature of its exterior wall panels remains in the allowable range as it experiences thermal stress. Generally, combustors in gas turbines are cooled by running the air to be used for combustion along their inner wall panels, and by forcing air inside these wall panels in order to cool the metal components so that their temperature is lower than that of the combustion gases. However, if air is used to cool the turbine, the air used for cooling and the air that leaks from the cooling channels is released into the main gas flow. This air makes it more difficult to improve the capacity of the gas turbine and decrease the emission of NO x . A method for manufacturing a combustor wall with cooling channels is disclosed in JP-A-727335. According to this method, a heat resistant metal plate is provided with channels on its side opposite to where it is exposed to combustion gas. Each channels is covered by a strip of metal welded onto the heat resistant metal plate. Thins process is difficult and expensive to carry out. As an alternative to the use of air as a cooling medium, the use of water or fuel has been proposed, see JP-A-8-261463 and JP-A-8-270950. A further alternative is the use of steam as a cooling medium for the combustor wall as disclosed in JP-A-8-338633 from which the first part of claim 1 starts out. This document discloses several alternatives for the incorporation of cooling channels in the combustor wall. In its prior art section, it describes an arrangement similar to the one disclosed in JP-A-727335: a wall plate exposed on its inner side to combustion gas is provided on its outer side with cooling channels covered by a flat plate. Incidentally, steam had been previously proposed by JP-A-62-111131 as a cooling medium for the tail cylinder of a gas burner where the combustors itself was cooled by air in a conventional way. In the past few years, combined power plants have received a great deal of publicity. These power plants make use of both gas and steam turbines in order to increase their generating efficiency (i.e., their thermal efficiency). A schematic diagram of a combined power plant is shown in Figure 6. The gas turbine generating system comprises generator 40, compressor 41, combustor 42 and gas turbine 43. A steam turbine generating system, which comprises boiler 45, steam turbine 46, on whose output shaft 46a generator 40 is mounted, and steam condenser 47, is installed on the gas turbine. The exhaust gases from the gas turbine 43 are fed into boiler 45. The boiler water supplied from steam condenser 47 is heated and vaporized, and this steam is used as the drive source for steam turbine 46. In this sort of combined power plant, there is an abundant supply of steam, which can easily be tapped, and steam has a higher thermal capacity to transmit heat than air does. Recently, engineers have been studying the use of steam instead of air as a cooling medium for the parts of the turbine that experience high temperatures. However, if the steam, which has been used to cool the hot portions of the turbine in a combined power plant, is released into the main gas flow, the temperature of the flow will drop, and the thermal efficiency of the turbine will decrease. For this reason it has been suggested that the steam used for cooling should be entirely recovered and used as high-pressure drive steam for the steam turbine. Figure 6 illustrates how this method of steam cooling would work. As indicated by the dotted lines in the drawing, the steam generated in waste heat recovery boiler 45 is extracted and conducted to the hot portions of the combustor or other areas of the turbine which need to be cooled. All the steam used for cooling is then recovered and used as drive steam for steam turbine 46. This method enables a gas turbine 43 to be realized with a temperature at its gas inlet port in excess of 1500 °C, and it also improves the overall efficiency of the combined power plant. Although the use of steam instead of air as the cooling medium in the combustor of a gas turbine has been given a great deal of consideration, it is still difficult to create steam-cooling channels in a combustor wall, which has complex forms, especially by a conventional laser or electrospark machining. For steam cooling, it is high pressure steam should be used as a cooling medium, as set forth above. This demands a strong enough stricture for forming the steam channels. Also, there must be a steam supplying means and a steam recovering means around the combustor. It is important not to allow leakage of the steam from the steam system. It is, however, not easy to fulfil all of these requirements because of structural reasons. This made it difficult to make such a steam-cooled combustor in the actual market. It is naturally not practical to use the same structure and the same concept used for an air-cooled combustor as a steam-cooled combustor, because it does not fulfil the requirements for steam-cooled combustor. Disclosure of the Invention It is therefore an object of the invention to provide a steam-cooled gas turbine combustor having a simple structure which is durable and reliably sealed against leakage of cooling steam of high pressure. This object is solved by a combustor as set forth in claim 1. The subclaims are directed to preferred embodiments of the invention. To achieve the object mentioned above, the gas turbine combustor which uses the high pressure steam as a cooling medium (steam-cooled gas turbine combustor) is provided with a gas combustor wall which includes wall-mounted cooling channels. This wall is exposed to extremely hot combustion gases, so it is configured with an exterior wall panel provided with a plurality of cooling channels and a heat-resistant and durable plate which is assembled by soldering or some other method with the exterior wall panel. One end of the cooling channels is connected to other end of the cooling channels is connected to a recovery manifold for recovering the cooling steam. With such a configuration, the supply manifold and the recovery manifold are connected through the cooling channels, and the cooling steam is introduced from the supply manifold through the cooling channels and to the recovery manifold. When the combustor wall is actually made up of metal panels it is easy to manufacture the wall by press works for any kind of complex forms. In addition to this advantage, the combustor wall can be made strong by soldering the heat-resistant thin plate on the exterior wall panel along which many cooling channels extend. This configuration makes it possible to run the high pressure cooling steam into the cooling channels. Brief Description of the Drawings Figure 1 is a cross section of a cooling channel for a gas turbine combustor, which is a preferred embodiment of this invention. Figure 2 shows a cross section of a steam-cooled wall panel in the combustor of a gas turbine taken along line A-A of Figure 1. It shows the structure for the cooling wall panel, which conducts the steam from the supply manifold to the recovery manifold through the cooling channels. Figure 3 is a perspective drawing of the cooling wall panel, which is a preferred embodiment of this invention. This drawing combines the features shown in Figures 1 and 2. Figure 4 shows a detailed drawing of the supply manifold shown in Figures 2 and 3, which is a preferred embodiment of this invention. Figure 5 shows a sketch of a gas turbine combustor, which is a preferred embodiment of this invention. Figure 6 shows how steam-cooling can be applied in a combined power plant in which a gas turbine is combined with a steam turbine. Description of Preferred Embodiments In this section a detailed explanation of several preferred embodiments of this invention will be given with reference to the drawings. To the extent that the dimensions, materials, shape and relative position of the components described in this embodiment are not definitely fixed, the scope of the invention is not limited to those specified, which are meant to serve merely as illustrative examples. In a gas turbine plant, several combustors of the sort described earlier, with a combustion nozzle 51 on the gas inlet side of combustion chamber 50, as shown in Figure 5, and a tailpipe 52 on the gas outlet side, are provided inside a cylindrical casing (not shown). The casing is pressurized using compressed air from a compressor. These combustors are arranged around the circumference of the casing. The combustion gases generated in chamber 50 are conducted to the turbine via tailpipe 52 and used to drive the turbine. As can be seen in Figure 5, the combustor, which is a preferred embodiment of this invention, has on the peripheral surface of the combustion chamber 50 an annular supply manifold 4 on the gas outlet or inlet side of the chamber. The manifold has a peripheral wall panel whose cross section is either semicircular or rectangular. There is a recovery manifold 5 of the same design on the peripheral surface of the combustion chamber 50, and it is on the gas inlet or outlet side of the chamber. In Figure 6, the steam generated by waste heat recovery boiler 45 is used as the energy that drives steam turbine 46. On the other hand, the steam extracted by said boiler 45 is then conducted via pipes 4a to supply manifolds 4. Recovery manifold 5 recovers the steam after it passes through cooling channels 2 and cools combustion chamber 50 and transports the recovered steam via recovery pipe 5a to the inlet of steam turbine 46. It is not always necessary to provide one supply manifold for each recovery manifold. There can be a plurality of pairs of supply and recovery manifolds, or one supply or recovery manifold can be associated with a plurality of recovery or supply manifolds, respectively, each of which is connected by the cooling channels depending on the combustor scale. A detailed explanation of the configuration of the cooling wall panels between the supply manifold 4 and recovery manifold 5, will next be given with reference to Figures 1 through 4. In exterior wall panel 1 of the wall of the combustor, a number of channels 2 for the cooling steam are laid out parallel to each other on the inner surface (the undersurface) of the wall panel. A separate thin heat-resistant plate 3 is soldered to the undersurface across which these channels extend. The combustion gases, represented by the white arrow, flow under plate 3. Numerous through holes 6 are provided on the surface of exterior wall panel 1 around the circumference of the chamber. These holes are in the locations where supply manifold 4 and recovery manifold 5 are mounted at both ends of channels 2. The holes 6 may be staggered to the left and right in a zigzag pattern as shown in Figure 4, or they may be arranged in a row as is shown in Figure 3. A detail view of the supply manifold 4 is shown in Figure 4. Supply manifold 4 is formed by attaching a channel-shaped piece to wall panel 1 in the location that faces the through holes 6. The steam for cooling the chamber is supplied via pipe 4a, which feeds into the channels in the appropriate place, from a source such as recovery boiler 45 inparallel with gas turbine 43. This steam passes through hole 6 in the exterior wall panel 1 and is supplied to the channels 2, which are between wall panel 1 and plate 3, as shown by the solid arrows in Figure 4. A detailed description of recovery manifold 5, which is configured identically to the supply manifold 4, will not be given. Preferably exterior wall panel 1 and plate 3, which constitute the steam-cooled wall, can be composed of Hastelloy X and Tomilloy (both are registered trademarks). Exterior wall panel 1 can be 3.0 to 5.0 mm thick, and plate 3, which is soldered to the wall panel, should be 0.8 to 1.6 mm thick. In this embodiment, then, the combustor wall comprises two panels (exterior wall panel 1 and plate 3) which have sealed channels 2 running between them. These channels 2 connect manifold 4, which supplies the cooling steam, and recovery manifold 5. As the steam supplied via manifold 4 travels through channels 2 in exterior wall panel 1, it cools the wall panel. The steam is then recovered through manifold 5. According to the embodiments, all cooling-steam supplied is recovered, and no cooling-steam leaks from the system, which is a necessary feature in the steam-cooling system. This requirement is achieved in the configuration described abode. This improves the capacity of the gas turbine 43 and reduces its emission of NO x . In the preceding, the present invention has been discussed using a preferred embodiment; however, the invention is not limited to this embodiment only. It should not be necessary to state that various modifications may be made to the actual configuration as long as it remains within the scope of the claims. Effects of the Invention According to this invention, the combustor wall is actually made of metal panels. It is, therefore, easy to manufacture the wall by press works for any kind of complex forms. In addition to this advantage, the greater heat resistance of the turbine allows the use of steam as a pressurized cooling medium. All the requirements for a steam-cooling system are achieved in this invention, and it improves the capacity of the gas turbine and reduces its emission of NO x , thereby contributing to increased efficiency of the plant as a whole.

Claims: A steam-cooled gas turbine combustor: having a combustor wall (1, 3) to be exposed to combustion gas and cooled by steam, the combustor wall comprising an exterior wall panel (1), a heat resistant plate (3) to be exposed to combustion gas, a plurality of cooling channels (2) for guiding cooling steam between the exterior wall panel (1) and the heat resistant plate (3), a supply manifold (4) provided on one end of the cooling channels (2) for supplying the cooling steam to the cooling channels (2), and a recovery manifold (5) provided on another end of the cooling channels (2) for recovering the cooling steam from the cooling channels (2), characterised in that the cooling channels (2) are provided in the exterior wall panel (1) and are sealed by the heat resistant plate (3) which is assembled with the exterior wall panel (1) by soldering to form a sealed structure for use with high pressure steam as said cooling steam. A combustor according to claim 1, wherein the supply manifold (4) is provided on a gas inlet side of the combustor, the recovery manifold (5) is provided on a gas outlet side of the combustor, and the cooling channels (2) are laid out in parallel to each other.

Inventors: AKAGI KOUICHI, IGARASHI KIRYO, INADA MITSURU, OGOSE AKIO, AKAGI, KOUICHI, IGARASHI, KIRYO, INADA, MITSURU, OGOSE, AKIO, AKAGI, Kouichi, Mitsubishi Heavy Industries, Ltd., Igarashi, Kiryo, Tohoku Electric Power Co., Inc, INADA, MITSURU, Mitsubishi Heavy Industries, Ltd., OGOSE, Akio, Tohoku Electric Power Co., Inc.
Applicants: MITSUBISHI HEAVY IND LTD, TOHOKU ELECTRIC POWER CO, MITSUBISHI HEAVY INDUSTRIES, LTD., TOHOKU ELECTRIC POWER CO., INC.
Application year: 1998
Main classification: F23R3
IPC codes: F02C7, F23M5, F23R3