Abstract:
A land based gas turbine apparatus includes an integral compressor; a turbine component having a combustor to which air from the integral compressor and fuel are supplied; and a generator operatively connected to the turbine for generating electricity; wherein hot gas path component parts in the turbine component are cooled entirely or at least partially by cooling air or other cooling media supplied by an external compressor. A method is also provided which includes the steps of supplying compressed air to the combustor from the integral compressor; and supplying at least a portion of the cooling air or other cooling media to the hot gas path parts in the turbine component from an external compressor.

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
       [0001]    This application is a Division of application Ser. No. 11/892,354, filed Aug. 22, 2007, the entire contents of which are hereby incorporated by reference into this application. 
     
    
       [0002]    This invention relates to supplying augmenting compressed air and/or cooling media to a combustion turbine via a separate compressor. 
       BACKGROUND OF THE INVENTION 
       [0003]    Most combustion turbines use air bled from one or more locations of the integral compressor to provide for cooling and sealing in the turbine component. Air bled from the compressor for this purpose may be routed internally through the bore of the compressor-turbine rotor or other suitable internal passages to the locations that require cooling and sealing in the turbine section. Alternatively, air may be routed externally through the compressor casing and through external (to the casing) piping to the locations that require cooling and sealing. Many combustion turbines utilize a combination of the internal and external routing of cooling and sealing air to the turbine component. Some combustion turbines use heat exchangers to cool the cooling and sealing air routed through the external piping before introduction into the turbine component. 
         [0004]    The output or capacity of a combustion turbine usually falls off with increasing temperature at the inlet to the compressor component. Specifically, the capacity of the compressor component to supply air to the combustion process and subsequent expansion through the turbine is reduced as the compressor inlet temperature is increased (usually due to increased ambient temperature). Thus, the turbine component and combustion component of the combustion turbine usually have the capability to accept more compressed air than the compressor component can supply when operating above a certain inlet temperature. 
       BRIEF DESCRIPTION OF THE INVENTION 
       [0005]    The invention augments the compressed air and/or cooling media supplied by the integral compressor using a separate compressor. Thus, the invention may be embodied in a land based combustion gas turbine apparatus comprising: an integral compressor; a turbine component; a combustor to which air from the integral compressor and fuel are supplied, said combustor arranged to supply hot combustion gases to the turbine component; a generator operatively connected to the turbine for generating electricity; and an external compressor arranged and connected to supply cooling air or other cooling media to hot gas path component parts in said turbine component, said external compressor also being arranged and connected to selectively supply atomizing air to atomize said fuel supplied to said combustor. 
         [0006]    The invention may also be embodied in a land based combustion gas turbine apparatus comprising: an integral compressor; a turbine component; a combustor to which air from the integral compressor and fuel are supplied, said combustor arranged to supply hot combustion gases to the turbine component; a generator operatively connected to the turbine for generating electricity; an external compressor arranged and connected to supply compressed air to a storage chamber for selectively storing said compressed air, an outlet of said storage chamber being connected to supply said compressed air as cooling media from the storage tank to hot gas path component parts in said turbine component. 
         [0007]    The invention may also be embodied in a land based combustion gas turbine apparatus comprising: an integral compressor; a turbine component; a combustor to which air from the integral compressor and fuel are supplied, said combustor arranged to supply hot combustion gases to the turbine component; a generator operatively connected to the turbine for generating electricity; an external compressor arranged and connected to supply cooling air or other cooling media to hot gas path component parts in said turbine component; and an external turbine for producing at least some of the work required to compress the cooling air in the external compressor, wherein said integral compressor is operatively coupled to said external turbine for selectively supplying compressed air from said integral compressor to said external turbine. 
         [0008]    The invention may also be embodied in a method of insuring peak power capability for a land based gas turbine power plant including an integral compressor, a turbine component, a combustor and a generator, wherein hot gas path parts in the turbine component are cooled by cooling air, the method comprising: a) supplying compressed air to said combustor from said integral compressor; b) supplying cooling air or other cooling media to said hot gas path parts in the turbine component from an external compressor; and c) supplying compressed air from said external compressor to atomize fuel supplied to the combustor. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0009]    These and other objects and advantages of this invention, will be more completely understood and appreciated by careful study of the following more detailed description of the presently preferred example embodiments of the invention taken in conjunction with the accompanying drawings, in which: 
           [0010]      FIG. 1  is a schematic diagram of a prior art cooling arrangement for a combustion turbine; 
           [0011]      FIG. 2  is a schematic diagram of another prior art cooling arrangement for a combustion turbine; 
           [0012]      FIG. 3  is a schematic diagram of yet another prior art cooling arrangement, for a combustion turbine; 
           [0013]      FIG. 4  is a schematic diagram of a further prior art cooling arrangement for a combustion turbine; 
           [0014]      FIG. 5  is a schematic diagram of a cooling arrangement for a combustion turbine in accordance with an example embodiment of the invention; 
           [0015]      FIG. 6  is a schematic diagram of a cooling arrangement for a combustion turbine in accordance with another example embodiment of the invention; and 
           [0016]      FIG. 7  is a schematic diagram of a cooling arrangement for a combustion turbine in accordance with yet another example embodiment of the invention. 
       
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
       [0017]      FIG. 1  represents a conventional cooled combustion turbine system including an integral compressor  10 , combustor  12  and turbine component  14 . The compressor  10 , turbine section  14  and generator  32  are shown in a single shaft configuration with the single shaft  34  also driving the generator  32 . 
         [0018]    Inlet air is supplied to the compressor via stream  16 . Compressor air is extracted from various locations in the compressor and supplied to the locations in the turbine component  14  that require cooling and sealing. The extraction locations are chosen to supply air at required pressures. Flow streams  26 ,  28  and  30  represent cooling air extractions from the integral compressor that are routed to the turbine section of the machine for cooling and sealing hot gas path component parts. Streams  26  and  28 , which supply the low and intermediate pressure coolant, respectively, may be routed via piping external to the compressor casing, and reintroduced through the turbine casing into the parts that need cooling. Stream  30  supplies the highest pressure coolant and is typically routed internally of the machine, for example, through the bore of the compressor-turbine rotor. The remaining compressed air is supplied at high pressure to the combustor via stream  18  where it mixes with fuel supplied by stream  20 . 
         [0019]    The hot combustion gas is supplied to the turbine component  14  via stream  22 . Some compressor air may be diverted to bypass the combustor via stream  24 , entering the hot combustion gases before they enter the turbine. 
         [0020]      FIG. 2  illustrates an example of a prior art cooled combustion turbine system wherein the supply of pressurized cooling air to the turbine components is through use of an external compressor. The  FIG. 2  cooled combustion turbine system is disclosed in U.S. Pat. No. 6,389,793, the entire disclosure of which is incorporated herein by this reference. 
         [0021]    For the sake of convenience and ease of understanding, reference numerals similar to those used in  FIG. 1  are applied to corresponding components in  FIG. 2 , but with the prefix “1” added. As in the conventional system described above, inlet air is supplied to the compressor  110  via stream  116 . Compressed air is supplied to the combustor  112  via stream  118  where it mixes with fuel supplied to the combustor via stream  120 . Bypass air may be supplied to the hot combustion gases via stream  124 . Here, however, the respective low, intermediate and high pressure cooling air streams  126 , 128  and  130  (or other cooling media) are generated by a separate external compressor  136  driven by a motor  138 . In this embodiment, all of the air or other cooling media is supplied by the external compressor  136 , thus allowing more of the combustion turbine compressor air to be used in the combustion process. Because the compressor  136  can be dedicated for supplying only cooling air or other cooling media, the cooling requirements of the turbine component  114  can be met regardless of compressor capability variations due to increased ambient temperatures. In other words, because the integral compressor  110  is freed from cooling duty requirements, sufficient air is available to satisfy the capability of the combustor and turbine component, thereby increasing output. 
         [0022]      FIG. 3  illustrates a prior art variation where cooling air is supplied by both the integral turbine compressor  210  and by an external compressor  236  (this could be an intercooled compressor) in a pure augmentation technique. In other words, the external compressor  236  is utilized to augment the supply of compressed air from the integral compressor  210  to the turbine component for cooling and sealing purposes. Here, the low, intermediate and high pressure cooling air is supplied by integral compressor  210  via respective streams  226 ,  228  and  230 , but supplemented as necessary by cooling air supplied by external compressor  236  via respective low, intermediate and high pressure streams  242 ,  244  and  246 . Because the cooling duty requirements are augmented by the external compressor  236 , the supply of compressed air to the combustor  212  from the compressor  210  is increased, resulting in increased output. 
         [0023]    As shown in  FIG. 4 , in another prior art variation, compressed air from stream  246  can be supplied to the combustor via line  218  (rather than to the turbine section via stream  230 ) to augment the supply of air from the integral compressor  210 . Otherwise, the arrangement in  FIG. 4  is identical to the arrangement in  FIG. 3 . Moreover, the augmented supply of cooling media to the turbine section  214  via streams  242  and  244  can be shut off, so that the external compressor augments the air supply only to the combustor. 
         [0024]    It is known that humidification of the cooling media can be added to the separate air cooling media supply system. One suitable means of humidification employs a saturator and hot water heated by waste or primary energy. Moisture introduction is shown in  FIGS. 2 ,  3 , and  4  via streams  140 , and  240 , respectively. It is also known that waste heat is readily available from the turbine exhaust in single cycle systems for evaporation of water that can then be introduced into any of the discharge air streams of compressor  136  or  236 , as appropriate. The coolant supply system can modulate the flow, pressure, temperature and composition of the supplied cooling media. 
         [0025]    The above described systems thus provide increased power capability for a gas turbine, particularly when ambient temperature rises to a level that causes reduced flow to the integral turbine compressor, resulting in reduced output. In other words, as ambient temperature rises and air flow into the turbine compressor decreases, the external compressor  136  or  236  may be employed to maintain or increase output by supplying all, or additional, cooling air (or other cooling media) in an amount necessary to optimize the flow of cooling air to the hot gas path parts of the turbine sections and/or to augment the flow of air or other cooling media to the combustion process. Further in this regard, by using an external compressor, greater cooling air flow can be provided than that available from the integral turbine compressor since only a small percentage of air from the turbine compressor is available for cooling duty. In other words, in conventional systems the amount of cooling air is limited by the capacity of the integral compressor. By supplying cooling air from an external compressor, where all of the air or other cooling media may be used for cooling duty, the turbine compressor can supply more air to the combustion process, thereby increasing turbine output. This is true whether the external compressor  136 ,  236  is used alone or in conjunction with the integral turbine compressor  110 ,  210 . 
         [0026]    That is not to say, however, that further improvement to the above described systems cannot be made. Indeed, the invention disclosed herein relates to further system improvements relating to supplying augmenting compressed air and/or cooling media via a separate compressor. 
         [0027]    Typically a gas turbine is configured as a dual fuel unit. In this regard, provision is made for the combustor to burn either natural gas or oil fuel. For adequate operation on oil fuel, conventionally the unit is equipped with an atomizing air (AA) skid. This conventional skid comprises high pressure compressors that provide air to the liquid fuel tip to atomize the fuel spray. In most cases, the oil fuel (and AA skid) are rarely used, e.g., during required maintenance or during temporary disruption in gas fuel supply, or as determined by fuel costs tradeoffs. In accordance with an embodiment of the invention, as illustrated in FIG.  5 , the external compressor provides not only cooling air, independently or to augment the integral combustor and possibly power augmentation air (as described above, with reference to  FIGS. 2-4 ), but the compressed air  248  from the external compressor  236  can be selectively used as the atomizing air, thereby eliminating the atomizing air skid. In view of the limited use of oil fuel and thus atomizing air therefor, significant capital costs savings will be seen by selectively conducting compressed cooling air  248  from the external compressor  236  for use as atomizing air. 
         [0028]    According to a further feature of the invention, an external compressor may be used as a means to increase the gas turbine turndown. Turndown is defined as the lowest load at which the gas turbine can operate in emissions compliance. For Dry Low NOx (DLN) combustors, this is dependent on the combustor exit temperature. Below a certain temperature premixed combustion is no longer possible and the combustor is transferred to other modes (diffusion combustion for example). These not fully premixed modes result in much higher emissions and prevent the unit from operating because of enforced emissions regulations. Consequently it would be desirable to maintain the combustor exit temperature above a certain limit, at lowest load possible (desirable up to Full Speed No Load or even spinning reserve). If this would be possible the operator of a gas turbine would have the greatest operability flexibility. In the prior art extended turndown is accomplished for example by reducing the inlet guide vanes. In this way the airflow to the combustor is reduced and higher temperatures can be maintained at low loads. The limit to which the airflow can be reduced (below which the compressor cannot operate—there are also mechanical limits) limits the turndown. Now consider a gas turbine according to the present invention in which the cooling air can be supplied by either the external compressor or the integral compressor. At the minimum (integral) compressor airflow, the external compressor is turned off and required cooling flow is now supplied by the integral compressor (by energizing a control valve). This results in further decreasing the combustor air flow, at constant compressor flow. As a consequence, elevated combustor exit temperature can be maintained at lower loads, and the turndown is increased. 
         [0029]    Another, prior art method to increase turndown is to use OBB (over board bleed). In this case, at the minimum compressor airflow, turndown is increased by discharging some of the compressed air into atmosphere, in order to reduce the airflow to the combustor and allow high combustor exit temperatures. Obviously this is done at a considerable loss for the customer because compressed air is lost for the cycle. Assuming that using the extra air for cooling could lead to increased complexity, according to another embodiment of the present invention, illustrated in  FIG. 6 , the compressed OBB air  250  (otherwise lost to the ambient) is expanded in a turbine  252  (similar to the automobile superchargers) to produce some (or all) of the work required to compress the cooling air in the external compressor  236 . An electric motor  238  could be used in parallel to cover any power deficit. 
         [0030]    As yet a further alternative to the above, the external compressor is used at low loads only to increase turndown. Thus, during normal operation a prior art configuration as in  FIGS. 2-4  is used. Then, at low loads OBB is used to drive a small external compressor to provide the cooling air as in  FIG. 6 . 
         [0031]    According to a further feature of the invention, the external air (for all purposes: cooling, atomizing air, power augmentation etc) is delivered through a reservoir. This would allow tremendous flexibility and optimization possibilities. For example any type of compressor (including reciprocating compressors or mixed combinations) could be used while maintaining the required parameters (flow, pressure, temperature, steadiness) at the engine ports. In addition economicity of the power plant could be substantially improved. There are many instances where the engines are operated cyclically. Output is valued during peak demand (usually day time) but customers may have excess capacity during night. During reduced demand the electricity price is low or the customers could be forced off grid. In order to better take advantage of the peak hours and swings in demand, most customers choose to keep the units running at a loss during night at some parking mode (at lowest load possible—biggest turndown). Using an external compressor with a storage tank would allow the customer to use the extra capacity to generate the air required during the day and minimize the power consumption in the external compressor during peak hours. 
         [0032]    Thus, according to a further feature of the invention, a compressed air storage and retrieval system is provided and, in the embodiment illustrated in  FIG. 7 , includes an external compressor  236  driven by an electric motor  238  to supply compressed air to compressed air storage  254  via charging structure  256  in the form of piping. 
         [0033]    As schematically illustrated, an outlet of the compressed air storage  254  is fluidly coupled to the cooling air supply lines  226 , 228 , 230  extending from the integral compressor  210  to the turbine  214 . In the illustrated embodiment, a valve  258  is provided between an outlet of the compressed air storage and the supply lines. 
         [0034]    The compressed air storage may be an underground geological formation such as a salt dome, a salt deposition, an aquifier, or may be made from hard rock. Alternatively, the air storage  254  may be a man-made pressure vessel which can be provided above-ground. 
         [0035]    As illustrated in  FIG. 7 , a heat exchanger  260  may be provided between the external compressor  236  (or tank  254  as the case might be) and the turbine to control the temperature of the cooling media. The cooling effectiveness depends on flow and temperature. For the same flow, cooling effectiveness could be increased for lower temperature. This allows for optimization and tradeoffs between power consumption, size of the compressor, and variable (actual cycle conditions) cooling requirements. The heat exchanger could be closed or open loop. 
         [0036]    Although only one combustion turbine assembly is shown in the embodiments described herein it can be appreciated that numerous combustion turbine assemblies may be provided and coupled with a common external compressor and/or with a common compressed air storage to provide the desired cooling air flow, augmented air flow and/or power augmentation. 
         [0037]    While the invention has been described in connection with what is presently considered to be the most practical and preferred embodiment, it is to be understood that the invention is not to be limited to the disclosed embodiment, but on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.