Title of Invention	A SYSTEM FOR GENERATING ELECTRICAL POWER FOR SUPPLY TO A LOAD AND A METHOD FOR CONTROLLING AN ELECTRICAL GENERATOR SYSTEM
Abstract	An electrical power generating system (10) and method wherein a generator (30) is driven by an air-breathing engine (20), At any operating condition, for a given power output the engine efficiency is substantially optimized by controlling the rate of air flow through the engine in such a manner that the fuel/air ratio is controlled to maintain a high peak temperature imparted to the working fluid in the engine. The method and system of the invention eliminate the need for variable-geometry mechanisms in the engine, and also eliminate the need for variable-geometry combustors and pre-burners. The invention is applicable to various types of air-breathing engines that operate at low fuel/air ratios.

Title of Invention

A SYSTEM FOR GENERATING ELECTRICAL POWER FOR SUPPLY TO A LOAD AND A METHOD FOR CONTROLLING AN ELECTRICAL GENERATOR SYSTEM

Abstract

An electrical power generating system (10) and method wherein a generator (30) is driven by an air-breathing engine (20), At any operating condition, for a given power output the engine efficiency is substantially optimized by controlling the rate of air flow through the engine in such a manner that the fuel/air ratio is controlled to maintain a high peak temperature imparted to the working fluid in the engine. The method and system of the invention eliminate the need for variable-geometry mechanisms in the engine, and also eliminate the need for variable-geometry combustors and pre-burners. The invention is applicable to various types of air-breathing engines that operate at low fuel/air ratios.

Full Text	A SYSTEM FOR GENERATING ELECTRICAL POWER FOR SUPPLY TO A LOAD AND A METHOD FOR CONTROLLING AN ELECTRICAL GENERATOR SYSTEM FIELD OF THE INVENTION This invention relates to the generation of electrical power using an air- breathing engine to drive a generator, which produces electrical current for supply to a load. The invention in particular embodiments relates to the generation of electrical power using a generator powered by a small turbine engine. BACKGROUND OF THE INVENTION Distributed power generation is a concept that has been the subject of much discussion over the years, but to date there has not been widespread deployment of distributed generation systems. Distributed generation refers to the use of small electrical power generation systems located at the sites where the power is needed, and thus is to be distinguished from the traditional utility grid system in which a large central power plant produces power that is then transmitted over substantial distances to a plurality of users through a system of power transmission lines commonly referred to as a grid. In contrast to conventional power plants operated by utilities, which often can produce several megawatts of power, distributed generation systems are generally sized below two megawatts, and more typically in the 60 to 600 kilowatt range. The failure of distributed generation to achieve widespread deployment can be attributed primarily to cost. In most areas of the United States, and indeed in much of the world, it simply has been cheaper for most users to purchase power from the grid than to invest in and operate a distributed generation system. A major factor driving the relatively high cost of power from distributed generation systems has been the relatively low efficiency of the small engines used in such systems, particularly at part-load operation conditions. Typically, the generator in a distributed generation system is driven by a small turbine engine, often referred to as a microturbine or miniturbine depending on size. A turbine engine generally comprises a combustor for burning a fuel and air mixture to produce hot gases by converting the chemical energy of the fuel into heat energy, a turbine that expands the hot gases to rotate a shaft on which the turbine is mounted, and a compressor mounted on or coupled with the shaft and operable to compress the air that is supplied to the combustor. Because of the relatively small amount of electrical power required from a distributed generation system, the turbine engine is correspondingly small. For reasons relating to the aerodynamics that take place within the engine, and other-reasons, the-efficiency of a turbine engine tends to decrease with decreasing engine size. Accordingly, microturbines and miniturbines automatically have an efficiency disadvantage relative to larger engines. Furthermore, irrespective of size, the part-load efficiency of a turbine engine is notoriously poor, generally because of the particular manner in which the engine is operated at part-load conditions. More particularly, it is typically the case in turbine engines that the turbine inlet temperature, which essentially represents the peak temperature of the working fluid in the engine cycle, falls as the power output from the engine decreases below the "design" point. The design point is typically a 100 percent rated load condition, and the engine is usually designed so that its peak efficiency occurs substantially at the design point. It is well known that the primary variable influencing the efficiency of the thermodynamic cycle of an engine is the peak temperature of the working fluid. All other things being equal, the greater the peak temperature, the greater the efficiency; conversely, the lower the peak temperature, the lower the efficiency. Therefore, if the engine, when operating at a part-load condition, is controlled in such a manner that the peak effective temperature of the working fluid in the cycle (i.e., the turbine inlet temperature) is substantially lower than what it is at the design point, the efficiency of the engine tends to suffer to a substantial extent. In some prior-art gas turbines, particularly aircraft gas turbine engines for propulsion and large gas turbines for constant-speed electrical generator systems, variable-geometry systems have been used at part-load conditions to reduce the air flow rate so mat engine efficiency does not unduly suffer. For instance, variable inlet guide vanes (IGVs) have been used in axial-flow compressors; at part-load conditions, the IGVs are closed down to reduce the air flow rate for a given compressor speed. In the case of radial compressors, the stator vanes have sometimes been made variable for achieving a similar effect. In still other cases, variable first-stage turbine vanes or nozzles have been employed for controlling the speed of the turbine and, hence, the speed of the compressor, so as to control air flow rate. Such variable-geometry systems are expensive, and the bearings and other movable components are prone to wear, thus making these systems impractical for electrical generation systems that must be available for service for a high percentage of hours per year, must be able to operate essentially continuously if required, and must also be able to respond quickly to changes in the power required by the load being served. Furthermore, variable-geometry mechanisms are not practical to implement in microturbines and miniturbines because of the small size of the engine. Thus, a need exists for an alternative to variable- geometry methods for optimizing engine performance at part-load conditions. Emissions (including but not limited to nitrogen oxides, unburned hydrocarbons, and carbon monoxide) represent another aspect of distributed generation that has proven challenging. In general, for a given power output, NOX emissions tend to be reduced or minimized by minimizing the temperature of combustion of the fuel (also known as the flame temperature), which in general is higher than the peak thermodynamic temperature (turbine inlet temperature), thus reducing the production of oxides of nitrogen without adversely affecting efficiency. The primary method of reducing the flame temperature is to premix the fuel and air prior to the combustion zone to produce a mixture with a high relative ratio of fuel to air, i.e., a lean mixture. The premixing also assures that the temperature throughout the flame zone is very nearly uniform without hot spots that can lead to the local production of NOx. However, as the mixture is made leaner, carbon monoxide (CO), unburned hydrocarbon (UHC), and pressure fluctuations increase. These trends continue and the flame zone becomes more unstable as the mixture is made still leaner, until the lean extinction limit is reached. For mixtures any leaner than this limit, no flame can be sustained. In practice, carbon monoxide and unburned hydrocarbon emissions and/or pressure pulsations become unacceptably high before the lean extinction limit is reached. The lean extinction limit may be moved to leaner regimes by increasing the inlet temperature to the combustor and by using catalytic combustion. The use of catalytic combustion substantially increases the operating regime for lean premixed combustion, resulting in very low NOX emission, acceptable CO and UHC emissions, and essentially no pressure pulsations. Catalytic combustion does, however, introduce another constraint on operation called the lower catalytic activity limit. The inlet temperature to the catalytic combustor must be kept above this limit to sustain catalytic combustion. In many conventional microturbines, the engine control is such that at part- load conditions the combustor inlet temperature tends to fall and the fuel/air mixture becomes leaner. In the case of conventional lean pre-mixed combustion, this tends to result in increased emissions; in the case of catalytic combustion, the falling combustor inlet temperature can lead to failure to sustain catalytic combustion. In practice, lean-premixed and catalytic combustors are able to operate over only a portion of the load range of the gas turbine because of falling combustor inlet temperatures and the progressively leaner conditions that prevail as load is decreased. In some cases, pre-burners have been used before combustors for boosting the combustor inlet temperature. Additionally, variable-geometry combustors have been used in which a portion of the air is diverted around the combustor to maintain the fuel/air ratio at a level allowing operational stability. The pre-burner solution poses a reliability penalty in that over-temperature or other malfunction of the pre-bumer can damage the main burner, and also adds to the cost of the system. In addition, it imposes an operating cost penalty as a result of the pressure loss that occurs through the pre-burner; this pressure loss is experienced even when the pre- bumer is not in use. Variable geometry can be applied to eliminate the pressure loss penalty in addition to its use in maintaining fuel/air ratio. However, variable geometry solutions are costly, complicated, and prone to excessive wear, decreasing reliability and increasing maintenance costs. For many potential users, these factors have combined to make electrical power generation via distributed generation systems less attractive than purchasing power from the large utilities. SUMMARY OF THE INVENTION The present invention addresses the above needs and achieves other advantages, by providing an electrical power generating system and method wherein, at any operating condition, for a given power output the engine efficiency is substantially optimized by controlling the rate of air flow through the engine in such a manner that the fuel/air ratio is controlled to maintain a high peak femperature imparted to the working fluid in the engine. The method and system of the invention eliminate the need for variable-geometry mechanisms in the engine, eliminate the need for variable-geometry combustors, and also minimize the need for pre-burners. The invention is applicable to various types of air- breathing engines that operate at low fuel/air ratios, including but not limited to rotary engines such as turbine engines and reciprocating engines such as free piston engines. In accordance with a method aspect of the invention, a method is provided for improving part-load efficiency of an air-breathing engine in an electrical generator system. The system has a movable shaft mechanically communicating with the engine and a fuel system coupled with the engine and operable to supply fuel to the engine at a controlled fuel flow rate; the engine is designed such that peak thermodynamic efficiency of the engine substantially coincides with a 100 percent load operating condition of the engine. The system includes an electrical generator coupled to the shaft such that movement of the shaft by the engine causes the generator to operate to create an alternating electrical current, and the engine, shaft, and generator are connected such that a change in speed of the generator causes a corresponding change in speed of the engine and hence a change in rate of air flow through the engine. The method comprises the steps of operating the engine at a part-load condition, and controlling the speed of the generator at the part-load condition so as to control air flow rate through the engine while simultaneously controlling fuel flow rate to the engine so as to control fuel/air ratio in such a manner that a peak cycle temperature of the engine is substantially the same as the peak cycle temperature corresponding to the 100 percent load operating condition. In other words, the peak cycle temperature is not allowed to drop by any substantial extent when reducing load below the 100 percent load condition (although at very low load conditions the peak cycle temperature may be allowed to drop, as further described below). This is accomplished by controlling the fuel/air ratio, primarily through control of the air flow rate through the engine. Since the air flow rate is a function of the speed of the engine, the air flow rate can be controlled by controlling the generator speed. In one embodiment, the step of controlling the speed of the generator comprises controlling an electrical current level downstream of the generator. This can be accomplished by converting the alternating current from the generator into a direct current and then converting the direct current into an alternating current at a fixed frequency independent of the speed of the generator; the fixed-frequency alternating current would then be supplied to the load. Using active current control in the AC-to-DC conversion, the level of the direct current is controlled so as to control the generator speed. For example, at a substantially constant fuel flow rate, by decreasing the direct current, a reduction in load on the shaft occurs and hence the generator speeds up so that output voltage is increased to maintain an overall energy balance; conversely, increasing the direct current increases the load on the shaft such that the generator slows down. When a wound generator having an excitation system is employed, the control of generator speed may be accomplished at least in part by controlling the excitation system. Alternatively, the speed of the wound generator may be controlled by controlling the AC/DC converter as previously noted, or a combination of controlling the excitation system and controlling the AC/DC converter may be used. In another embodiment of the invention, a recuperator is used to pre-heat the air mat is mixed with the fuel, or to pre-heat the air-fuel mixture; the recuperator causes heat exchange between the air or mixture and the exhaust gases discharged from the engine. At very low part-load conditions, if the peak cycle temperature were maintained at the same level as the 100 percent load point, the temperature of the exhaust gases entering the recuperator could exceed a maximum allowable value (dictated by material limits, for example). Accordingly, in accordance with the invention, at such conditions, the generator speed is controlled so as to control air flow rate through the engine and thereby control fuel/air ratio in such a manner that the peak cycle temperature is allowed to fall below the peak cycle temperature corresponding to the 100 percent load operating condition; accordingly, the temperature of the exhaust gases entering the recuperator does not exceed the predetermined maximum allowable value. In another aspect of the invention, the fuel is combusted in a catalytic conibustor having a predetermined minimum inlet temperature required for maintenance of a catalytic reaction in the combustor. In many conventional engine control schemes, the combustor inlet temperature tends to fall as engine load is reduced below the 100 percent load condition; accordingly, it is possible for the temperature to fall below the minimum temperature required for the catalytic reaction. In accordance with the invention, the fuel/air ratio is controlled in such a manner at part-load conditions that an inlet temperature to the combustor is at least as great as the predetermined minimum inlet temperature. In one embodiment, the fuel/air ratio is controlled in such a manner that the inlet temperature to the combustor at a part-load condition is greater than the inlet temperature to the combustor at the 100 percent load condition. A system for generating electrical power for supply to a load, in accordance with one embodiment of the invention, includes an air-breathing engine mechanically communicating with a movable shaft. An electrical generator is coupled to the shaft such that movement of the shaft by the engine causes the generator to operate to create an alternating electrical current. The engine, shaft, and generator are connected such that a change in speed of the generator causes a corresponding change in speed of the engine and hence a change in rate of air flow through the engine. The system further includes a fuel system coupled with the engine and operable to supply fuel to the engine, the fuel system being responsive to a fuel control signal to vary a rate of fuel flow to the engine; and at least one engine sensor operable to measure at least one thermodynamic variable associated with the engine that is indicative of a relative thermodynamic efficiency of the engine. A power electronics unit is coupled to the generator for receiving the alternating electrical current therefrom and synthesizing an alternating output current at a predetermined frequency for supply to the load. The power electronics unit in one embodiment comprises an AC/DC module structured and arranged to operate upon the alternating electrical current from the generator so as to produce a non-alternating direct current at a non-alternating voltage, and a DC/AC module structured and arranged to operate upon the non-alternating direct current so as to synthesize an alternating output current and voltage at a predetermined frequency and relative phase for supply to the load. In one embodiment, the AC/DC module can be responsive to a current control signal to vary the level of the non-alternating direct current independently of the alternating electrical current from the generator. The system also includes a generator power sensor operable to measure power output from the system, and a load power sensor operable to measure power demanded by the load. A controller is operably connected to the fuel system, to the at least one engine sensor, to the power electronics unit, to the generator power sensor, and to the load power sensor. The controller is operable to control the fuel system so as to cause the power output from the system to substantially match the power demanded by the load, and simultaneously to control the speed of the generator so as to control engine speed (and hence air flow rate), in such a manner that fuel/air ratio of the mixture burned in the engine is controlled to substantially maximize the relative thermodynamic efficiency of the engine. Generator speed control can be accomplished by controlling the level of the non-alternating direct current from the AC/DC module of the power electronics unit, in the case of an actively controllable AC/DC module. In another embodiment wherein the generator is a wound generator having an excitation system, the control system can be operable to control the excitation system so as to control generator speed and hence air flow rate. In a system as described above, another method in accordance with the invention comprises the steps of: determining a power demanded by the load; measuring at least one thermodynamic variable associated with the engine that is indicative of a relative thermodynamic efficiency of the engine; controlling the fuel supply system to supply fuel to the engine at a controlled fuel flow rate such that the electrical power output from the system substantially matches the power demanded by the load; and controlling the air flow rate through the engine independently of the electrical power output from the system so as to control fuel/air ratio of the mixture burned in the engine in such a manner as to substantially optimize the thermodynamic efficiency of the engine while substantially matching the power demanded by the load, the air flow rate being controlled by electrically controlling the speed of the generator and hence the air flow rate through the engine. BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE ACCOMPANYING DRAWING(S) Having thus described the invention in general terms, reference will now be made to the accompanying drawings, which are not necessarily drawn to scale, and wherein: FIG. 1 is a diagrammatic view of an electrical generation system in accordance with one embodiment of the invention; FIG. 2 is a plot of temperatures at various points in the engine as functions of the relative generator load, comparing a prior-art control method (dashed lines) with a control method in accordance with one embodiment of the invention (solid lines); and FIG. 3 is a plot of fuel/air ratio versus relative generator load, comparing a prior-art control method (dashed line) with a control method in accordance with one embodiment of the invention (solid line). DETAILED DESCRIPTION OF THE INVENTION The present inventions now will be described more fully hereinafter with reference to the accompanying drawings, in which some, but not all embodiments of the invention are shown. Indeed, these inventions may be embodied in many different forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided so that this disclosure will satisfy applicable legal requirements. Like numbers refer to like elements throughout. An electrical generator system 10 in accordance with one embodiment of the invention is schematically shown in FIG. 1. The system includes an air- breathing engine 20 that burns a mixture of fuel and air to produce hot combustion gases that are then expanded to create mechanical power. In the illustrated embodiment, the engine comprises a turbine engine having a compressor 22 mounted on one end of a rotatable shaft 24, a turbine 26 mounted on the other end of the shaft, and a combustor 28 for burning the fuel/air mixture. The combustor can be of various types, including but not limited to diffusion flame, catalytic, lean pre-mixed, or others. A mixture of fuel and air is supplied to the combustor. The air is first pressurized by the compressor. The fuel/air mixture is burned in the combustor and the hot combustion gases are supplied to the turbine, which expands the gases, causing the turbine to be rotatably driven. The turbine in turn rotates the shaft, which drives the compressor. The system includes an electrical generator 30 in communication with the shaft 24 in such a manner that movement of the shaft causes the generator to be driven. In the illustrated embodiment in which the shaft is rotatable, the generator is likewise rotatable, and rotary motion of the shaft is imparted to the generator. The generator can be directly mounted on or connected to the shaft such that a one- to-one speed relationship exists between the shaft and the generator, or alternatively the generator and shaft can be connected through a gear train or the like so that a different speed relationship exists. It is also possible for the shaft to be reciprocating rather than rotary, and for the generator to be either reciprocating or rotary. In any event, the speed at which the generator operates dictates the speed of the shaft, and hence the speed at which the engine operates. The generator 30 can be of various types, including permanent magnet generators or wound generators, or combinations thereof. The generator produces an alternating electrical current and voltage. As further described below, in the illustrated embodiment the alternating electrical current from the generator is operated on by power electronics to produce an alternating output current and voltage at a predetermined fixed frequency and phase relationship for supply to a load. The system 10 also includes a fuel system for supplying fuel to the combustor 28. The fuel system generally includes a fuel pump (not shown) and a fuel metering valve 32 that is controllable by a suitable control signal 34 so as to control the fuel flow rate. A control system 40 is connected to the fuel metering valve 32 for controlling its operation. The control system also performs other functions as further described below. The system 10 can also include an optional recuperator 50 comprising a heat exchanger for transferring heat from engine exhaust gases 52 to the compressed air 54 discharged from the compressor 22 before the air is supplied to the combustor. The recuperator captures some of the waste heat that would otherwise be lost and uses it to preheat the combustion air and thereby increase the overall efficiency of the engine, as known in the art. As noted, the system 10 also includes power electronics. In the illustrated embodiment, the power electronics comprise an AC/DC converter 60 and a DC/AC module or inverter 70. The AC/DC converter 60 can comprise any suitable converter operable to convert the alternating electrical current produced by the generator, which can vary in frequency as the speed of the generator varies, into a non-alternating direct current, and further operable in a current-control mode to control the level of the direct current independently of the characteristics of the alternating input current (within certain limits). Such active current control is generally based on pulse-width modulation (PWM) schemes utilizing semiconductor switching devices that perform switching operations at a high frequency and effectively allow current to pass only during a portion of each period of the input current waveform. This "time window" during which current is allowed to pass can be varied in duration so as to vary the "average" current output from the converter. The DC/AC module or inverter 70 then processes the output from the AC/DC converter 60 so as to synthesize an alternating output current at a fixed frequency. In many countries, the standard mains frequency is 60 cycles per second, while in other countries it is 50 cycles per second. The output frequency from the inverter is selected to match the standard mains frequency used in the particular location at which the system 10 is to be operated. The system 10 also includes a number of sensors connected to the control system 40 for measuring various parameters. For instance, an output power meter 72 is arranged for measuring how much electrical power is being generated by the system. One or more engine sensors 74 monitor one or more thermodynamic variables associated with the engine cycle. The thermodynamic variables are used for determining where the engine is operating on its "map", i.e., whether the engine is running at or near its design point or is running off-design. For example, a turbine inlet temperature sensor can be used for measuring turbine inlet temperature. As previously noted, the turbine inlet temperature represents the peak temperature of the working fluid in the engine and generally correlates with overall efficiency of the engine. Hence, by measuring turbine inlet temperature along with other parameters, it is possible to deduce a relative thermodynamic efficiency of the engine. A sensor 76 measures an inlet temperature to the recuperator 50 in the exhaust-gas stream. At part-load conditions, if the engine is not properly controlled, the inlet temperature to the recuperator could exceed the maximum allowable level dictated by material limits. Accordingly, the control system advantageously is connected to the sensor 76 for monitoring the recuperator inlet temperature, and the control system adjusts the air flow rate through the engine to prevent the temperature from exceeding the material limit, while maintaining the turbine inlet temperature as high as possible within this additional constraint. It may not be necessary to actually deduce a relative thermodynamic efficiency, but merely to measure one or more parameters that are indicative of the relative efficiency or the operating condition of the engine. For example, as noted, it is known that for a given power output from the engine (and hence a given power output from the generator as measured by the power meter 72), engine efficiency generally will be optimized by maximizing the turbine inlet temperature. Accordingly, control of the fuel/air ratio, through control of the air flow rate, can be effected so as to maximize the turbine inlet temperature, within allowable limits. More particularly, the materials of the turbine inlet nozzles have a maximum allowable temperature that should not be exceeded, in order to preserve sufficient material strength and integrity to avoid failure of the parts. At the 100 percent load design point, generally the engine would be designed so that turbine inlet temperature is at or near this maximum allowable temperature. For lower load conditions, air flow can be controlled in such a manner that the turbine inlet temperature does not fall substantially below what it is at the design point. Where the system includes a recuperator 50, considerations of material limits in the recuperator may necessitate a departure from this constant turbine inlet temperature mode of operation. More particularly, at very low part-load conditions, if the turbine inlet temperature were maintained at the same level as the 100 percent load point, the temperature of the exhaust gases entering the recuperator could exceed a maximum allowable value dictated by material limits of the recuperator. Accordingly, in accordance with the invention, at such conditions, the generator speed can be controlled so as to control air flow rate through the engine (while simultaneously controlling fuel flow rate to the engine) so as to control fuel/air ratio in such a manner that the turbine inlet temperature is allowed to fall below the temperature corresponding to the 100 percent load operating condition. In this manner, the temperature of the exhaust gases entering the recuperator can be prevented from exceeding the predetermined maximum allowable value. Thus, for example, the control system 40 may have stored in memory a predetermined schedule of turbine inlet temperature versus relative generator load. The relative generator load, which is reflected by the power output measured by the power meter 72, generally indicates the relative engine load and hence gives an indication of where the engine is operating on its map. A suitable control algorithm can be used by the control system 40 to control air flow (via control of generator speed in some suitable manner, such as by controlling the DC current from the AC/DC converter 60) in such a manner that the turbine inlet temperature is caused to substantially match the value dictated by the predetermined schedule. This is merely a simplified example of one possible control scheme, and other schemes may be used in accordance with the invention. FIG. 2 shows what such a turbine inlet temperature versus relative generator load schedule might look like, and compares various temperatures at different points in the system 10 (solid lines) with corresponding temperatures that would exist if a prior-art type of control approach were taken (dashed lines). In accordance with the invention, at a relative generator load value of 100 percent (i.e., the design point for the engine), turbine inlet temperature is substantially equal to a maximum allowable turbine inlet temperature of about 1200 K. The turbine inlet temperature is maintained at this value down to a relative generator load of about 40 percent. In contrast, in the prior-art control approach, the turbine inlet temperature steadily drops as the load drops below 100 percent. Consequently, at the same relative load, the overall engine efficiency is higher for the control scheme in accordance with the invention than for the prior-art control scheme. At a relative load of 40 percent, it can be seen that the turbine exit temperature (which is essentially equal to the recuperator inlet temperature) has increased up to the maximum allowable recuperator temperature of about 900 K. At still lower loads, if the turbine inlet temperature were maintained at about 1200 K, the turbine exit temperature would exceed the maximum allowable recuperator temperature. Accordingly, in accordance with the invention, the turbine inlet temperature is allowed to drop below 1200 K. Another factor that can influence the control schedule arises when the combustor 28 is a catalytic combustor. As noted, catalytic combustors have a minimum inlet temperature that must be maintained in order to sustain the catalytic reaction. In the prior-art control approach, it can be seen in FIG. 2 that below a relative load of about 50 percent the combustor inlet temperature falls below this minimum temperature of about 800 K. In accordance with the invention, however, the combustor inlet temperature rises from about 800 K at the 100 percent load point to about 860 K at the 40 percent load point. Below 40 percent load, the combustor inlet temperature remains about constant at approximately 860 K. The invention thus enables efficiency improvements to be realized at part-load conditions while also allowing proper operation of the catalytic combustor at all operating points. FIG. 3 illustrates how the fuel/air ratio behaves in both the inventive control approach using air flow control and the prior-art control approach not using air flow control. In the case of flow control, the fuel/air ratio is generally substantially higher at part-load conditions than in the prior-art method. The higher fuel/air ratio with flow control reflects the fact that the air flow rate is lower than in the prior-art control approach. From 100 percent down to 40 percent load, the fuel/air ratio using flow control decreases at a relatively low rate; the result is that turbine inlet temperature is maintained substantially constant as already noted in FIG. 2. Below 40 percent load, the fuel/air ratio with flow control is allowed to decrease at a substantially higher rate. It will also be noted from FIG. 2 that the combustor inlet temperature is generally higher in the inventive control approach than in the prior-art approach. Advantageously, a higher fuel/air ratio and higher combustor inlet temperature generally favor lower emissions for pre-mixed low-emissions combustors. The control scheme described thus far has assumed that turbine inlet temperature is measured directly and used as a control parameter. In some cases, however, it may not be practical to measure turbine inlet temperature because of the extreme usage environment in which a turbine inlet temperature sensor would have to operate. Alternatively, therefore, it is possible to measure other thermodynamic variables in the engine cycle and deduce the turbine inlet temperature based on cycle calculations. As still another alternative, the control system could store a schedule of a suitable control parameter (e.g., engine air flow rate) versus relative generator load, and thermodynamic variables could be measured enabling the control parameter to be deduced; the control system would then drive the actual (i.e., deduced) control parameter to substantially equal the scheduled value. The particular control method that is used, and the parameters measured for effecting the method, are not critical. The basic concept of the invention entails controlling air flow rate through the engine as a means of enhancing or optimizing the overall engine efficiency for any given power output from the generator system 10. At the same time, in a load-following operational mode, the power output from the generator system 10 must be controlled to match the power demanded by the load. The power output is primarily a function of the fuel flow rate. Accordingly, in a load-following mode, the control system 40 simultaneously controls air flow as described above while also controlling the power output (as measured by power meter 72) to match the demand. Load-following control schemes are well known and hence are not further described herein. Depending on the particular application, the system 10 may also be operated in modes other than load-following. In such cases, the same type of air flow control already described would still be employed. The system 10 described above has a single-spool turbine engine 20. However, the invention is not limited to any particular type of air-breathing engine. Multiple-spool turbine engines, turbine engines having a free power turbine, rotary combustion (e.g., Wankel) engines, reciprocating piston engines, and others can be used. In each case, the air flow rate through the engine is controlled by controlling generator speed. The generator 30 can be of various types, including permanent magnet generators and wound generators. The previously described embodiment of the system 10 assumed that the generator 30 is a permanent magnet generator in which mere is no excitation system. In the case of a wound generator, on the other hand, the generator requires an excitation system 80 (FIG. 1) for supplying an excitation current to the rotor windings, as known in the art. The excitation system can comprise, for example, a small generator mounted on the same shaft as the rotor or mechanically coupled (e.g., by a drive belt) to the rotor shaft. Regardless of the generator type, the invention entails electrically controlling the generator speed so as to control the air flow rate through the engine and thereby optimize engine efficiency and possibly achieve other effects as previously noted. In the case of a permanent magnet generator, the control of the generator is accomplished by controlling the AC/DC converter or rectifier 60 as already described. In the case of a wound generator, a number of control schemes are possible. In one scheme, the control system 40 controls the excitation system 80 (via control line 82) to regulate the generator speed. The AC/DC and DC/AC conversion may not be necessary, and instead an AC/AC converter may be used to synthesize the AC output current at the desired frequency for supply to the load. Alternatively, the AC/DC and DC/AC converters may be used as previously described, in which case the AC/DC converter does not have to be current- controlled since the regulation of generator speed is performed by controlling the excitation system. In another scheme, generator speed control may be accomplished through a combination of controlling the excitation system and controlling the AC/DC converter. Yet another scheme is to control the generator speed solely through control of the AC/DC converter as already described. The particulars of how the generator speed is controlled are not critical to the invention, and various schemes for accomplishing this can be used in accordance with the invention. Advantageously, the invention allows control over the thermodynamic cycle of an engine having fixed-geometry compressor, turbine, and combustor components. Many modifications and other embodiments of the inventions set forth herein will come to mind to one skilled in the art to which these inventions pertain having the benefit of the teachings presented in the foregoing descriptions and the associated drawings. Therefore, it is to be understood that the inventions are not to be limited to the specific embodiments disclosed and that modifications and other embodiments are intended to be included within the scope of the appended claims. Although specific terms are employed herein, they are used in a generic and descriptive sense only and not for purposes of limitation. WE CLAIM : 1. A system for generating electrical power for supply to a load, comprising: an air-breathing engine (20) mechanically communicating with a movable shaft (24), the engine being structured and arranged to receive a mixture of air and fuel and burn the mixture such that the mixture expands and creates mechanical power that is used to drive the shaft; a fuel system (32) coupled with the engine and operable to supply fuel to the engine, the fuel system being responsive to a fuel control signal to vary a rate of fuel flow to the engine; at least one engine sensor (74) operable to measure at least one thermodynamic variable associated with the engine that is indicative of a relative thermodynamic efficiency of the engine; an electrical generator (30) coupled to the shaft (24) such that movement of the shaft (24) by the engine (20) causes the generator (30) to operate to create an alternating electrical current, the engine (20), shaft (24), and generator (30) being connected such that a change in speed of the generator (30) causes a corresponding change in speed of the engine (20) and hence a change in rate of air flow through the engine; a generator power sensor (72) operable to measure power output from the generator (30); a load power sensor operable to measure power demanded by the load, characterized in that: a power electronics unit (60, 70) is coupled to the generator (30) for receiving the alternating electrical current therefrom, the power electronics unit (60, 70) being operable to synthesize an alternating output current and voltage at a predetermined frequency and relative phase for supply to the load; and a controller (40) is operably connected to the fuel system (32), to the at least one engine sensor (74), to the power electronics unit (60, 70), to the generator power sensor (72), and to the load power sensor, the controller (40) being operable to control the fuel system (32) so as to cause the power output from the system to substantially match the power demanded by the load, and simultaneously to electrically control the generator (30) via regulation of the power electronics unit (60, 70) so as to regulate speed of the generator (30) and thereby control air flow rate through the engine (20) in such a manner that the fuel/air ratio of the mixture burned in the engine is controlled to substantially maximize the relative thermodynamic efficiency of the engine. 2. The system as claimed in claim 1, wherein the power electronics unit (60, 70) comprises an AC/DC module (60) structured and arranged to operate upon the alternating electrical current from the generator (30) so as to produce a non- alternating direct current at a non-alternating voltage, and a DC/AC module (70) structured and arranged to operate upon the non-alternating direct current so as to synthesize the alternating output current that is supplied to the load, the AC/DC module (60) being responsive to a current control signal to vary the level of the non-alternating direct current independently of the alternating electrical current from the generator (30), the control system (40) being operable to supply the current control signal to the AC/DC module (60) to control the level of the direct current output by the AC/DC module (60) and thereby control generator speed. 3. The system as claimed in claim 1, wherein the generator (30) and shaft (24) are rotationally movable. 4. The system as claimed in claim 3, wherein the engine (20) comprises a compression device (22) operable to compress air and a power device (26, 28) that receives the compressed air from the compression device (22) and the fuel from the fuel system (32) and burns the air and fuel mixture to produce mechanical power. 5. The system as claimed in claim 4, comprising a heat exchanger (50) arranged to receive the compressed air from the compression device (22) and exhaust gases from the power device (26, 28), the heat exchanger (50) causing heat transfer from the exhaust gases to the compressed air so as to pre-heat the compressed air prior to combustion in the power device (26, 28). 6. The system as claimed in claim 5, wherein the power device (26, 28) includes a combustor (28) in which the air and fuel mixture is burned to produce hot gases, and an expansion device (26) for expanding the hot gases so as to produce the mechanical power. 7. The system as claimed in claim 6, wherein the expansion device (26) comprises a turbine. 8. The system as claimed in claim 7, wherein the turbine (26) is a fixed- geometry turbine. 9. The system as claimed in claim 6, wherein the compression device (22) is a fixed-geometry compressor. 10. The system as claimed in claim 6, wherein the combustor (28) is a fixed- geometry combustor. 11. The system as claimed in claim 6, wherein the combustor (28) comprises a catalytic combustor. 12. The system as claimed in claim 11, comprising a sensor operable to measure a variable indicative of combustor inlet temperature, and wherein the controller (40) is connected to said sensor and is operable to control air flow through the engine (20) in such a manner as to maintain the combustor inlet temperature above a predetermined minimum temperature required for catalytic operation. 13. The system as claimed in claim 12, comprising a sensor (76) associated with the heat exchanger (50) operable to measure a variable indicative of a temperature of the exhaust gases entering the heat exchanger (50), and wherein the controller (40) is connected to said sensor (76) associated with the heat exchanger (50) and is operable to control air flow through the engine (20) to maintain the temperature of the exhaust gases entering the heat exchanger (50) below a predetermined maximum temperature. 14. The system as claimed in claim 1, wherein the generator (30) is a wound generator. 15. The system as claimed in claim 14, comprising an excitation system (80) operable to excite the generator (30). 16. The system as claimed in claim 15, wherein the control system (40) is operable to control the excitation system (80) so as to electrically control the generator speed and thereby control air flow rate. 17. A method for controlling an electrical generator system having an air- breathing engine (20) mechanically communicating with a movable shaft (24), the engine (20) being structured and arranged to receive a mixture of air and fuel and burn the mixture such that the mixture expands and creates mechanical power that is used to drive the shaft (24), the system having a fuel system (32) coupled with the engine (20) and operable to supply fuel to the engine (20), the fuel system (32) being responsive to a fuel control signal to vary a rate of fuel flow to the engine (20), the system having an electrical generator (30) coupled to the shaft (24) such that movement of the shaft (24) by the engine (20) causes the generator (30) to operate to create an alternating electrical current, wherein the engine (20), shaft (24), and generator (30) are connected such that a change in speed of the generator (30) causes a corresponding change in speed of the engine (20) and hence a change in rate of air flow through the engine (20), and wherein electrical power output from the system is substantially determined by fuel flow rate to the engine (20), the method comprising the steps of: determining a power demanded by the load; measuring at least one thermodynamic variable associated with the engine (20) that is indicative of a relative thermodynamic efficiency of the engine (20); and controlling the fuel supply system (32) to supply fuel to the engine at a controlled fuel flow rate such that the electrical power output from the system substantially matches the power demanded by the load; characterized in that: the system includes a power electronics unit (60, 70) coupled to the generator (30) for receiving the alternating electrical current therefrom and operable to synthesize an alternating output current and voltage at a predetermined frequency and relative phase for supply to the load; and the air flow rate through the engine (20) is controlled independently of the electrical power output from the system by electrically controlling the speed of the generator (30) via regulation of the power electronics unit (60,70) so as to control fuel/air ratio of the mixture burned in the engine (20) in such a manner as to substantially optimize the thermodynamic efficiency of the engine (20) while substantially matching the power demanded by the load. 18. The method as claimed in claim 17, wherein the alternating electrical current from the generator (30) is converted in an AC/DC module (60) into a non- alternating direct current at a non-alternating voltage, and the non-alternating direct current from the AC/DC module (60) is converted in a DC/AC module (70) to synthesize the alternating output current that is supplied to the load, the AC/DC module (60) being responsive to a current control signal to vary the level of the non-alternating direct current independently of the alternating electrical current from the generator (30), and wherein the step of controlling the air flow rate comprises actively controlling the non-alternating direct current from the AC/DC module (60) of the power electronics unit (60, 70) so as to alter the speed of the generator (30) and hence the air flow rate. 19. The method as claimed in claim 17, wherein the engine (20) comprises a turbine engine having a compressor (22) for compressing the air, a combustor (28) for burning the mixture of air and fuel to produce hot gases, and a turbine (26) for expanding the hot gases, and wherein optimizing the thermodynamic efficiency of the engine (20) comprises causing a turbine inlet temperature to substantially match a predetermined value. 20. The method as claimed in claim 19, wherein the combustor (28) comprises a catalytic combustor, and comprising the steps of: measuring a variable indicative of an inlet temperature to the combustor (28); and controlling air flow through the engine (20) in such a manner as to maintain the combustor inlet temperature above a predetermined minimum temperature required for catalytic operation. An electrical power generating system (10) and method wherein a generator (30) is driven by an air-breathing engine (20), At any operating condition, for a given power output the engine efficiency is substantially optimized by controlling the rate of air flow through the engine in such a manner that the fuel/air ratio is controlled to maintain a high peak temperature imparted to the working fluid in the engine. The method and system of the invention eliminate the need for variable-geometry mechanisms in the engine, and also eliminate the need for variable-geometry combustors and pre-burners. The invention is applicable to various types of air-breathing engines that operate at low fuel/air ratios.

Full Text

A SYSTEM FOR GENERATING ELECTRICAL POWER FOR
SUPPLY TO A LOAD AND A METHOD FOR CONTROLLING
AN ELECTRICAL GENERATOR SYSTEM
FIELD OF THE INVENTION
This invention relates to the generation of electrical power using an air-
breathing engine to drive a generator, which produces electrical current for supply
to a load. The invention in particular embodiments relates to the generation of
electrical power using a generator powered by a small turbine engine.
BACKGROUND OF THE INVENTION
Distributed power generation is a concept that has been the subject of much
discussion over the years, but to date there has not been widespread deployment of
distributed generation systems. Distributed generation refers to the use of small
electrical power generation systems located at the sites where the power is needed,
and thus is to be distinguished from the traditional utility grid system in which a
large central power plant produces power that is then transmitted over substantial
distances to a plurality of users through a system of power transmission lines
commonly referred to as a grid. In contrast to conventional power plants operated
by utilities, which often can produce several megawatts of power, distributed
generation systems are generally sized below two megawatts, and more typically in
the 60 to 600 kilowatt range.
The failure of distributed generation to achieve widespread deployment can
be attributed primarily to cost. In most areas of the United States, and indeed in
much of the world, it simply has been cheaper for most users to purchase power
from the grid than to invest in and operate a distributed generation system. A
major factor driving the relatively high cost of power from distributed generation
systems has been the relatively low efficiency of the small engines used in such
systems, particularly at part-load operation conditions.
Typically, the generator in a distributed generation system is driven by a
small turbine engine, often referred to as a microturbine or miniturbine depending
on size. A turbine engine generally comprises a combustor for burning a fuel and
air mixture to produce hot gases by converting the chemical energy of the fuel into
heat energy, a turbine that expands the hot gases to rotate a shaft on which the
turbine is mounted, and a compressor mounted on or coupled with the shaft and
operable to compress the air that is supplied to the combustor. Because of the
relatively small amount of electrical power required from a distributed generation
system, the turbine engine is correspondingly small. For reasons relating to the
aerodynamics that take place within the engine, and other-reasons, the-efficiency of
a turbine engine tends to decrease with decreasing engine size. Accordingly,
microturbines and miniturbines automatically have an efficiency disadvantage
relative to larger engines.
Furthermore, irrespective of size, the part-load efficiency of a turbine
engine is notoriously poor, generally because of the particular manner in which the
engine is operated at part-load conditions. More particularly, it is typically the
case in turbine engines that the turbine inlet temperature, which essentially
represents the peak temperature of the working fluid in the engine cycle, falls as
the power output from the engine decreases below the "design" point. The design
point is typically a 100 percent rated load condition, and the engine is usually
designed so that its peak efficiency occurs substantially at the design point. It is
well known that the primary variable influencing the efficiency of the
thermodynamic cycle of an engine is the peak temperature of the working fluid.
All other things being equal, the greater the peak temperature, the greater the
efficiency; conversely, the lower the peak temperature, the lower the efficiency.
Therefore, if the engine, when operating at a part-load condition, is controlled in
such a manner that the peak effective temperature of the working fluid in the cycle
(i.e., the turbine inlet temperature) is substantially lower than what it is at the
design point, the efficiency of the engine tends to suffer to a substantial extent.
In some prior-art gas turbines, particularly aircraft gas turbine engines for
propulsion and large gas turbines for constant-speed electrical generator systems,
variable-geometry systems have been used at part-load conditions to reduce the air
flow rate so mat engine efficiency does not unduly suffer. For instance, variable
inlet guide vanes (IGVs) have been used in axial-flow compressors; at part-load
conditions, the IGVs are closed down to reduce the air flow rate for a given
compressor speed. In the case of radial compressors, the stator vanes have
sometimes been made variable for achieving a similar effect. In still other cases,
variable first-stage turbine vanes or nozzles have been employed for controlling the
speed of the turbine and, hence, the speed of the compressor, so as to control air
flow rate. Such variable-geometry systems are expensive, and the bearings and
other movable components are prone to wear, thus making these systems
impractical for electrical generation systems that must be available for service for a
high percentage of hours per year, must be able to operate essentially continuously
if required, and must also be able to respond quickly to changes in the power
required by the load being served. Furthermore, variable-geometry mechanisms
are not practical to implement in microturbines and miniturbines because of the
small size of the engine. Thus, a need exists for an alternative to variable-
geometry methods for optimizing engine performance at part-load conditions.
Emissions (including but not limited to nitrogen oxides, unburned
hydrocarbons, and carbon monoxide) represent another aspect of distributed
generation that has proven challenging. In general, for a given power output, NOX
emissions tend to be reduced or minimized by minimizing the temperature of
combustion of the fuel (also known as the flame temperature), which in general is
higher than the peak thermodynamic temperature (turbine inlet temperature), thus
reducing the production of oxides of nitrogen without adversely affecting
efficiency. The primary method of reducing the flame temperature is to premix the
fuel and air prior to the combustion zone to produce a mixture with a high relative
ratio of fuel to air, i.e., a lean mixture. The premixing also assures that the
temperature throughout the flame zone is very nearly uniform without hot spots
that can lead to the local production of NOx. However, as the mixture is made
leaner, carbon monoxide (CO), unburned hydrocarbon (UHC), and pressure
fluctuations increase. These trends continue and the flame zone becomes more
unstable as the mixture is made still leaner, until the lean extinction limit is
reached. For mixtures any leaner than this limit, no flame can be sustained. In
practice, carbon monoxide and unburned hydrocarbon emissions and/or pressure
pulsations become unacceptably high before the lean extinction limit is reached.
The lean extinction limit may be moved to leaner regimes by increasing the
inlet temperature to the combustor and by using catalytic combustion. The use of
catalytic combustion substantially increases the operating regime for lean premixed
combustion, resulting in very low NOX emission, acceptable CO and UHC
emissions, and essentially no pressure pulsations. Catalytic combustion does,
however, introduce another constraint on operation called the lower catalytic
activity limit. The inlet temperature to the catalytic combustor must be kept above
this limit to sustain catalytic combustion.
In many conventional microturbines, the engine control is such that at part-
load conditions the combustor inlet temperature tends to fall and the fuel/air
mixture becomes leaner. In the case of conventional lean pre-mixed combustion,
this tends to result in increased emissions; in the case of catalytic combustion, the
falling combustor inlet temperature can lead to failure to sustain catalytic
combustion. In practice, lean-premixed and catalytic combustors are able to
operate over only a portion of the load range of the gas turbine because of falling
combustor inlet temperatures and the progressively leaner conditions that prevail
as load is decreased.
In some cases, pre-burners have been used before combustors for boosting
the combustor inlet temperature. Additionally, variable-geometry combustors have
been used in which a portion of the air is diverted around the combustor to
maintain the fuel/air ratio at a level allowing operational stability. The pre-burner
solution poses a reliability penalty in that over-temperature or other malfunction of
the pre-bumer can damage the main burner, and also adds to the cost of the system.
In addition, it imposes an operating cost penalty as a result of the pressure loss that
occurs through the pre-burner; this pressure loss is experienced even when the pre-
bumer is not in use. Variable geometry can be applied to eliminate the pressure
loss penalty in addition to its use in maintaining fuel/air ratio. However, variable
geometry solutions are costly, complicated, and prone to excessive wear,
decreasing reliability and increasing maintenance costs.
For many potential users, these factors have combined to make electrical
power generation via distributed generation systems less attractive than purchasing
power from the large utilities.
SUMMARY OF THE INVENTION
The present invention addresses the above needs and achieves other
advantages, by providing an electrical power generating system and method
wherein, at any operating condition, for a given power output the engine efficiency
is substantially optimized by controlling the rate of air flow through the engine in
such a manner that the fuel/air ratio is controlled to maintain a high peak
femperature imparted to the working fluid in the engine. The method and system
of the invention eliminate the need for variable-geometry mechanisms in the
engine, eliminate the need for variable-geometry combustors, and also minimize
the need for pre-burners. The invention is applicable to various types of air-
breathing engines that operate at low fuel/air ratios, including but not limited to
rotary engines such as turbine engines and reciprocating engines such as free
piston engines.
In accordance with a method aspect of the invention, a method is provided
for improving part-load efficiency of an air-breathing engine in an electrical
generator system. The system has a movable shaft mechanically communicating
with the engine and a fuel system coupled with the engine and operable to supply
fuel to the engine at a controlled fuel flow rate; the engine is designed such that
peak thermodynamic efficiency of the engine substantially coincides with a 100
percent load operating condition of the engine. The system includes an electrical
generator coupled to the shaft such that movement of the shaft by the engine
causes the generator to operate to create an alternating electrical current, and the
engine, shaft, and generator are connected such that a change in speed of the
generator causes a corresponding change in speed of the engine and hence a
change in rate of air flow through the engine. The method comprises the steps of
operating the engine at a part-load condition, and controlling the speed of the
generator at the part-load condition so as to control air flow rate through the engine
while simultaneously controlling fuel flow rate to the engine so as to control
fuel/air ratio in such a manner that a peak cycle temperature of the engine is
substantially the same as the peak cycle temperature corresponding to the 100
percent load operating condition. In other words, the peak cycle temperature is not
allowed to drop by any substantial extent when reducing load below the 100
percent load condition (although at very low load conditions the peak cycle
temperature may be allowed to drop, as further described below). This is
accomplished by controlling the fuel/air ratio, primarily through control of the air
flow rate through the engine. Since the air flow rate is a function of the speed of
the engine, the air flow rate can be controlled by controlling the generator speed.
In one embodiment, the step of controlling the speed of the generator
comprises controlling an electrical current level downstream of the generator. This
can be accomplished by converting the alternating current from the generator into a
direct current and then converting the direct current into an alternating current at a
fixed frequency independent of the speed of the generator; the fixed-frequency
alternating current would then be supplied to the load. Using active current control
in the AC-to-DC conversion, the level of the direct current is controlled so as to
control the generator speed. For example, at a substantially constant fuel flow rate,
by decreasing the direct current, a reduction in load on the shaft occurs and hence
the generator speeds up so that output voltage is increased to maintain an overall
energy balance; conversely, increasing the direct current increases the load on the
shaft such that the generator slows down.
When a wound generator having an excitation system is employed, the
control of generator speed may be accomplished at least in part by controlling the
excitation system. Alternatively, the speed of the wound generator may be
controlled by controlling the AC/DC converter as previously noted, or a
combination of controlling the excitation system and controlling the AC/DC
converter may be used.
In another embodiment of the invention, a recuperator is used to pre-heat
the air mat is mixed with the fuel, or to pre-heat the air-fuel mixture; the
recuperator causes heat exchange between the air or mixture and the exhaust gases
discharged from the engine. At very low part-load conditions, if the peak cycle
temperature were maintained at the same level as the 100 percent load point, the
temperature of the exhaust gases entering the recuperator could exceed a maximum
allowable value (dictated by material limits, for example). Accordingly, in
accordance with the invention, at such conditions, the generator speed is controlled
so as to control air flow rate through the engine and thereby control fuel/air ratio in
such a manner that the peak cycle temperature is allowed to fall below the peak
cycle temperature corresponding to the 100 percent load operating condition;
accordingly, the temperature of the exhaust gases entering the recuperator does not
exceed the predetermined maximum allowable value.
In another aspect of the invention, the fuel is combusted in a catalytic
conibustor having a predetermined minimum inlet temperature required for
maintenance of a catalytic reaction in the combustor. In many conventional engine
control schemes, the combustor inlet temperature tends to fall as engine load is
reduced below the 100 percent load condition; accordingly, it is possible for the
temperature to fall below the minimum temperature required for the catalytic
reaction. In accordance with the invention, the fuel/air ratio is controlled in such a
manner at part-load conditions that an inlet temperature to the combustor is at least
as great as the predetermined minimum inlet temperature. In one embodiment, the
fuel/air ratio is controlled in such a manner that the inlet temperature to the
combustor at a part-load condition is greater than the inlet temperature to the
combustor at the 100 percent load condition.
A system for generating electrical power for supply to a load, in accordance
with one embodiment of the invention, includes an air-breathing engine
mechanically communicating with a movable shaft. An electrical generator is
coupled to the shaft such that movement of the shaft by the engine causes the
generator to operate to create an alternating electrical current. The engine, shaft,
and generator are connected such that a change in speed of the generator causes a
corresponding change in speed of the engine and hence a change in rate of air flow
through the engine. The system further includes a fuel system coupled with the
engine and operable to supply fuel to the engine, the fuel system being responsive
to a fuel control signal to vary a rate of fuel flow to the engine; and at least one
engine sensor operable to measure at least one thermodynamic variable associated
with the engine that is indicative of a relative thermodynamic efficiency of the
engine.
A power electronics unit is coupled to the generator for receiving the
alternating electrical current therefrom and synthesizing an alternating output
current at a predetermined frequency for supply to the load. The power electronics

unit in one embodiment comprises an AC/DC module structured and arranged to
operate upon the alternating electrical current from the generator so as to produce a
non-alternating direct current at a non-alternating voltage, and a DC/AC module
structured and arranged to operate upon the non-alternating direct current so as to
synthesize an alternating output current and voltage at a predetermined frequency
and relative phase for supply to the load. In one embodiment, the AC/DC module
can be responsive to a current control signal to vary the level of the non-alternating
direct current independently of the alternating electrical current from the generator.
The system also includes a generator power sensor operable to measure
power output from the system, and a load power sensor operable to measure power
demanded by the load. A controller is operably connected to the fuel system, to
the at least one engine sensor, to the power electronics unit, to the generator power
sensor, and to the load power sensor. The controller is operable to control the fuel
system so as to cause the power output from the system to substantially match the
power demanded by the load, and simultaneously to control the speed of the
generator so as to control engine speed (and hence air flow rate), in such a manner
that fuel/air ratio of the mixture burned in the engine is controlled to substantially
maximize the relative thermodynamic efficiency of the engine.
Generator speed control can be accomplished by controlling the level of the
non-alternating direct current from the AC/DC module of the power electronics
unit, in the case of an actively controllable AC/DC module. In another
embodiment wherein the generator is a wound generator having an excitation
system, the control system can be operable to control the excitation system so as to
control generator speed and hence air flow rate.
In a system as described above, another method in accordance with the
invention comprises the steps of:
determining a power demanded by the load;
measuring at least one thermodynamic variable associated with the
engine that is indicative of a relative thermodynamic efficiency of the
engine;
controlling the fuel supply system to supply fuel to the engine at a
controlled fuel flow rate such that the electrical power output from the
system substantially matches the power demanded by the load; and
controlling the air flow rate through the engine independently of the
electrical power output from the system so as to control fuel/air ratio of the
mixture burned in the engine in such a manner as to substantially optimize
the thermodynamic efficiency of the engine while substantially matching
the power demanded by the load, the air flow rate being controlled by
electrically controlling the speed of the generator and hence the air flow
rate through the engine.
BRIEF DESCRIPTION OF THE SEVERAL VIEWS
OF THE ACCOMPANYING DRAWING(S)
Having thus described the invention in general terms, reference will now be
made to the accompanying drawings, which are not necessarily drawn to scale, and
wherein:
FIG. 1 is a diagrammatic view of an electrical generation system in
accordance with one embodiment of the invention;
FIG. 2 is a plot of temperatures at various points in the engine as functions
of the relative generator load, comparing a prior-art control method (dashed lines)
with a control method in accordance with one embodiment of the invention (solid
lines); and
FIG. 3 is a plot of fuel/air ratio versus relative generator load, comparing a
prior-art control method (dashed line) with a control method in accordance with
one embodiment of the invention (solid line).
DETAILED DESCRIPTION OF THE INVENTION
The present inventions now will be described more fully hereinafter with
reference to the accompanying drawings, in which some, but not all embodiments
of the invention are shown. Indeed, these inventions may be embodied in many
different forms and should not be construed as limited to the embodiments set forth
herein; rather, these embodiments are provided so that this disclosure will satisfy
applicable legal requirements. Like numbers refer to like elements throughout.
An electrical generator system 10 in accordance with one embodiment of
the invention is schematically shown in FIG. 1. The system includes an air-
breathing engine 20 that burns a mixture of fuel and air to produce hot combustion
gases that are then expanded to create mechanical power. In the illustrated
embodiment, the engine comprises a turbine engine having a compressor 22
mounted on one end of a rotatable shaft 24, a turbine 26 mounted on the other end
of the shaft, and a combustor 28 for burning the fuel/air mixture. The combustor
can be of various types, including but not limited to diffusion flame, catalytic, lean
pre-mixed, or others. A mixture of fuel and air is supplied to the combustor. The
air is first pressurized by the compressor. The fuel/air mixture is burned in the
combustor and the hot combustion gases are supplied to the turbine, which expands
the gases, causing the turbine to be rotatably driven. The turbine in turn rotates the
shaft, which drives the compressor.
The system includes an electrical generator 30 in communication with the
shaft 24 in such a manner that movement of the shaft causes the generator to be
driven. In the illustrated embodiment in which the shaft is rotatable, the generator
is likewise rotatable, and rotary motion of the shaft is imparted to the generator.
The generator can be directly mounted on or connected to the shaft such that a one-
to-one speed relationship exists between the shaft and the generator, or
alternatively the generator and shaft can be connected through a gear train or the
like so that a different speed relationship exists. It is also possible for the shaft to
be reciprocating rather than rotary, and for the generator to be either reciprocating
or rotary. In any event, the speed at which the generator operates dictates the
speed of the shaft, and hence the speed at which the engine operates.
The generator 30 can be of various types, including permanent magnet
generators or wound generators, or combinations thereof. The generator produces
an alternating electrical current and voltage. As further described below, in the
illustrated embodiment the alternating electrical current from the generator is
operated on by power electronics to produce an alternating output current and
voltage at a predetermined fixed frequency and phase relationship for supply to a
load.
The system 10 also includes a fuel system for supplying fuel to the
combustor 28. The fuel system generally includes a fuel pump (not shown) and a
fuel metering valve 32 that is controllable by a suitable control signal 34 so as to
control the fuel flow rate. A control system 40 is connected to the fuel metering
valve 32 for controlling its operation. The control system also performs other
functions as further described below.
The system 10 can also include an optional recuperator 50 comprising a
heat exchanger for transferring heat from engine exhaust gases 52 to the
compressed air 54 discharged from the compressor 22 before the air is supplied to
the combustor. The recuperator captures some of the waste heat that would
otherwise be lost and uses it to preheat the combustion air and thereby increase the
overall efficiency of the engine, as known in the art.
As noted, the system 10 also includes power electronics. In the illustrated
embodiment, the power electronics comprise an AC/DC converter 60 and a
DC/AC module or inverter 70. The AC/DC converter 60 can comprise any
suitable converter operable to convert the alternating electrical current produced by
the generator, which can vary in frequency as the speed of the generator varies,
into a non-alternating direct current, and further operable in a current-control mode
to control the level of the direct current independently of the characteristics of the
alternating input current (within certain limits). Such active current control is
generally based on pulse-width modulation (PWM) schemes utilizing
semiconductor switching devices that perform switching operations at a high
frequency and effectively allow current to pass only during a portion of each
period of the input current waveform. This "time window" during which current is
allowed to pass can be varied in duration so as to vary the "average" current output
from the converter.
The DC/AC module or inverter 70 then processes the output from the
AC/DC converter 60 so as to synthesize an alternating output current at a fixed
frequency. In many countries, the standard mains frequency is 60 cycles per
second, while in other countries it is 50 cycles per second. The output frequency
from the inverter is selected to match the standard mains frequency used in the
particular location at which the system 10 is to be operated.

The system 10 also includes a number of sensors connected to the control
system 40 for measuring various parameters. For instance, an output power meter
72 is arranged for measuring how much electrical power is being generated by the
system. One or more engine sensors 74 monitor one or more thermodynamic
variables associated with the engine cycle. The thermodynamic variables are used
for determining where the engine is operating on its "map", i.e., whether the engine
is running at or near its design point or is running off-design. For example, a
turbine inlet temperature sensor can be used for measuring turbine inlet
temperature. As previously noted, the turbine inlet temperature represents the peak
temperature of the working fluid in the engine and generally correlates with overall
efficiency of the engine. Hence, by measuring turbine inlet temperature along with
other parameters, it is possible to deduce a relative thermodynamic efficiency of
the engine.
A sensor 76 measures an inlet temperature to the recuperator 50 in the
exhaust-gas stream. At part-load conditions, if the engine is not properly
controlled, the inlet temperature to the recuperator could exceed the maximum
allowable level dictated by material limits. Accordingly, the control system
advantageously is connected to the sensor 76 for monitoring the recuperator inlet
temperature, and the control system adjusts the air flow rate through the engine to
prevent the temperature from exceeding the material limit, while maintaining the
turbine inlet temperature as high as possible within this additional constraint.
It may not be necessary to actually deduce a relative thermodynamic
efficiency, but merely to measure one or more parameters that are indicative of the
relative efficiency or the operating condition of the engine. For example, as noted,
it is known that for a given power output from the engine (and hence a given
power output from the generator as measured by the power meter 72), engine
efficiency generally will be optimized by maximizing the turbine inlet temperature.
Accordingly, control of the fuel/air ratio, through control of the air flow rate, can
be effected so as to maximize the turbine inlet temperature, within allowable
limits. More particularly, the materials of the turbine inlet nozzles have a
maximum allowable temperature that should not be exceeded, in order to preserve
sufficient material strength and integrity to avoid failure of the parts. At the 100
percent load design point, generally the engine would be designed so that turbine
inlet temperature is at or near this maximum allowable temperature. For lower
load conditions, air flow can be controlled in such a manner that the turbine inlet
temperature does not fall substantially below what it is at the design point.
Where the system includes a recuperator 50, considerations of material
limits in the recuperator may necessitate a departure from this constant turbine
inlet temperature mode of operation. More particularly, at very low part-load
conditions, if the turbine inlet temperature were maintained at the same level as the
100 percent load point, the temperature of the exhaust gases entering the
recuperator could exceed a maximum allowable value dictated by material limits of
the recuperator. Accordingly, in accordance with the invention, at such conditions,
the generator speed can be controlled so as to control air flow rate through the
engine (while simultaneously controlling fuel flow rate to the engine) so as to
control fuel/air ratio in such a manner that the turbine inlet temperature is allowed
to fall below the temperature corresponding to the 100 percent load operating
condition. In this manner, the temperature of the exhaust gases entering the
recuperator can be prevented from exceeding the predetermined maximum
allowable value.
Thus, for example, the control system 40 may have stored in memory a
predetermined schedule of turbine inlet temperature versus relative generator load.
The relative generator load, which is reflected by the power output measured by
the power meter 72, generally indicates the relative engine load and hence gives an
indication of where the engine is operating on its map. A suitable control
algorithm can be used by the control system 40 to control air flow (via control of
generator speed in some suitable manner, such as by controlling the DC current
from the AC/DC converter 60) in such a manner that the turbine inlet temperature
is caused to substantially match the value dictated by the predetermined schedule.
This is merely a simplified example of one possible control scheme, and other
schemes may be used in accordance with the invention.
FIG. 2 shows what such a turbine inlet temperature versus relative
generator load schedule might look like, and compares various temperatures at
different points in the system 10 (solid lines) with corresponding temperatures that

would exist if a prior-art type of control approach were taken (dashed lines). In
accordance with the invention, at a relative generator load value of 100 percent
(i.e., the design point for the engine), turbine inlet temperature is substantially
equal to a maximum allowable turbine inlet temperature of about 1200 K. The
turbine inlet temperature is maintained at this value down to a relative generator
load of about 40 percent. In contrast, in the prior-art control approach, the turbine
inlet temperature steadily drops as the load drops below 100 percent.
Consequently, at the same relative load, the overall engine efficiency is higher for
the control scheme in accordance with the invention than for the prior-art control
scheme.
At a relative load of 40 percent, it can be seen that the turbine exit
temperature (which is essentially equal to the recuperator inlet temperature) has
increased up to the maximum allowable recuperator temperature of about 900 K.
At still lower loads, if the turbine inlet temperature were maintained at about 1200
K, the turbine exit temperature would exceed the maximum allowable recuperator
temperature. Accordingly, in accordance with the invention, the turbine inlet
temperature is allowed to drop below 1200 K.
Another factor that can influence the control schedule arises when the
combustor 28 is a catalytic combustor. As noted, catalytic combustors have a
minimum inlet temperature that must be maintained in order to sustain the catalytic
reaction. In the prior-art control approach, it can be seen in FIG. 2 that below a
relative load of about 50 percent the combustor inlet temperature falls below this
minimum temperature of about 800 K. In accordance with the invention, however,
the combustor inlet temperature rises from about 800 K at the 100 percent load
point to about 860 K at the 40 percent load point. Below 40 percent load, the
combustor inlet temperature remains about constant at approximately 860 K. The
invention thus enables efficiency improvements to be realized at part-load
conditions while also allowing proper operation of the catalytic combustor at all
operating points.
FIG. 3 illustrates how the fuel/air ratio behaves in both the inventive
control approach using air flow control and the prior-art control approach not using
air flow control. In the case of flow control, the fuel/air ratio is generally

substantially higher at part-load conditions than in the prior-art method. The
higher fuel/air ratio with flow control reflects the fact that the air flow rate is lower
than in the prior-art control approach. From 100 percent down to 40 percent load,
the fuel/air ratio using flow control decreases at a relatively low rate; the result is
that turbine inlet temperature is maintained substantially constant as already noted
in FIG. 2. Below 40 percent load, the fuel/air ratio with flow control is allowed to
decrease at a substantially higher rate.
It will also be noted from FIG. 2 that the combustor inlet temperature is
generally higher in the inventive control approach than in the prior-art approach.
Advantageously, a higher fuel/air ratio and higher combustor inlet temperature
generally favor lower emissions for pre-mixed low-emissions combustors.
The control scheme described thus far has assumed that turbine inlet
temperature is measured directly and used as a control parameter. In some cases,
however, it may not be practical to measure turbine inlet temperature because of
the extreme usage environment in which a turbine inlet temperature sensor would
have to operate. Alternatively, therefore, it is possible to measure other
thermodynamic variables in the engine cycle and deduce the turbine inlet
temperature based on cycle calculations. As still another alternative, the control
system could store a schedule of a suitable control parameter (e.g., engine air flow
rate) versus relative generator load, and thermodynamic variables could be
measured enabling the control parameter to be deduced; the control system would
then drive the actual (i.e., deduced) control parameter to substantially equal the
scheduled value.
The particular control method that is used, and the parameters measured for
effecting the method, are not critical. The basic concept of the invention entails
controlling air flow rate through the engine as a means of enhancing or optimizing
the overall engine efficiency for any given power output from the generator system
10.
At the same time, in a load-following operational mode, the power output
from the generator system 10 must be controlled to match the power demanded by
the load. The power output is primarily a function of the fuel flow rate.

Accordingly, in a load-following mode, the control system 40 simultaneously
controls air flow as described above while also controlling the power output (as
measured by power meter 72) to match the demand. Load-following control
schemes are well known and hence are not further described herein.
Depending on the particular application, the system 10 may also be
operated in modes other than load-following. In such cases, the same type of air
flow control already described would still be employed.
The system 10 described above has a single-spool turbine engine 20.
However, the invention is not limited to any particular type of air-breathing engine.
Multiple-spool turbine engines, turbine engines having a free power turbine, rotary
combustion (e.g., Wankel) engines, reciprocating piston engines, and others can be
used. In each case, the air flow rate through the engine is controlled by controlling
generator speed.
The generator 30 can be of various types, including permanent magnet
generators and wound generators. The previously described embodiment of the
system 10 assumed that the generator 30 is a permanent magnet generator in which
mere is no excitation system. In the case of a wound generator, on the other hand,
the generator requires an excitation system 80 (FIG. 1) for supplying an excitation
current to the rotor windings, as known in the art. The excitation system can
comprise, for example, a small generator mounted on the same shaft as the rotor or
mechanically coupled (e.g., by a drive belt) to the rotor shaft.
Regardless of the generator type, the invention entails electrically
controlling the generator speed so as to control the air flow rate through the engine
and thereby optimize engine efficiency and possibly achieve other effects as
previously noted. In the case of a permanent magnet generator, the control of the
generator is accomplished by controlling the AC/DC converter or rectifier 60 as
already described. In the case of a wound generator, a number of control schemes
are possible. In one scheme, the control system 40 controls the excitation system
80 (via control line 82) to regulate the generator speed. The AC/DC and DC/AC
conversion may not be necessary, and instead an AC/AC converter may be used to
synthesize the AC output current at the desired frequency for supply to the load.

Alternatively, the AC/DC and DC/AC converters may be used as previously
described, in which case the AC/DC converter does not have to be current-
controlled since the regulation of generator speed is performed by controlling the
excitation system.
In another scheme, generator speed control may be accomplished through a
combination of controlling the excitation system and controlling the AC/DC
converter. Yet another scheme is to control the generator speed solely through
control of the AC/DC converter as already described.
The particulars of how the generator speed is controlled are not critical to
the invention, and various schemes for accomplishing this can be used in
accordance with the invention.
Advantageously, the invention allows control over the thermodynamic
cycle of an engine having fixed-geometry compressor, turbine, and combustor
components.
Many modifications and other embodiments of the inventions set forth
herein will come to mind to one skilled in the art to which these inventions pertain
having the benefit of the teachings presented in the foregoing descriptions and the
associated drawings. Therefore, it is to be understood that the inventions are not to
be limited to the specific embodiments disclosed and that modifications and other
embodiments are intended to be included within the scope of the appended claims.
Although specific terms are employed herein, they are used in a generic and
descriptive sense only and not for purposes of limitation.
WE CLAIM :
1. A system for generating electrical power for supply to a load, comprising:
an air-breathing engine (20) mechanically communicating with a movable
shaft (24), the engine being structured and arranged to receive a mixture of air
and fuel and burn the mixture such that the mixture expands and creates
mechanical power that is used to drive the shaft;
a fuel system (32) coupled with the engine and operable to supply fuel to
the engine, the fuel system being responsive to a fuel control signal to vary a
rate of fuel flow to the engine;
at least one engine sensor (74) operable to measure at least one
thermodynamic variable associated with the engine that is indicative of a relative
thermodynamic efficiency of the engine;
an electrical generator (30) coupled to the shaft (24) such that movement
of the shaft (24) by the engine (20) causes the generator (30) to operate to
create an alternating electrical current, the engine (20), shaft (24), and generator
(30) being connected such that a change in speed of the generator (30) causes
a corresponding change in speed of the engine (20) and hence a change in rate
of air flow through the engine;
a generator power sensor (72) operable to measure power output from the
generator (30);
a load power sensor operable to measure power demanded by the load,
characterized in that:
a power electronics unit (60, 70) is coupled to the generator (30) for
receiving the alternating electrical current therefrom, the power electronics unit
(60, 70) being operable to synthesize an alternating output current and voltage at
a predetermined frequency and relative phase for supply to the load; and
a controller (40) is operably connected to the fuel system (32), to the at
least one engine sensor (74), to the power electronics unit (60, 70), to the
generator power sensor (72), and to the load power sensor, the controller (40)
being operable to control the fuel system (32) so as to cause the power output

from the system to substantially match the power demanded by the load, and
simultaneously to electrically control the generator (30) via regulation of the
power electronics unit (60, 70) so as to regulate speed of the generator (30) and
thereby control air flow rate through the engine (20) in such a manner that the
fuel/air ratio of the mixture burned in the engine is controlled to substantially
maximize the relative thermodynamic efficiency of the engine.
2. The system as claimed in claim 1, wherein the power electronics unit (60,
70) comprises an AC/DC module (60) structured and arranged to operate upon
the alternating electrical current from the generator (30) so as to produce a non-
alternating direct current at a non-alternating voltage, and a DC/AC module (70)
structured and arranged to operate upon the non-alternating direct current so as
to synthesize the alternating output current that is supplied to the load, the
AC/DC module (60) being responsive to a current control signal to vary the level
of the non-alternating direct current independently of the alternating electrical
current from the generator (30), the control system (40) being operable to supply
the current control signal to the AC/DC module (60) to control the level of the
direct current output by the AC/DC module (60) and thereby control generator
speed.
3. The system as claimed in claim 1, wherein the generator (30) and shaft
(24) are rotationally movable.
4. The system as claimed in claim 3, wherein the engine (20) comprises a
compression device (22) operable to compress air and a power device (26, 28)
that receives the compressed air from the compression device (22) and the fuel
from the fuel system (32) and burns the air and fuel mixture to produce
mechanical power.
5. The system as claimed in claim 4, comprising a heat exchanger (50)
arranged to receive the compressed air from the compression device (22) and

exhaust gases from the power device (26, 28), the heat exchanger (50) causing
heat transfer from the exhaust gases to the compressed air so as to pre-heat the
compressed air prior to combustion in the power device (26, 28).
6. The system as claimed in claim 5, wherein the power device (26, 28)
includes a combustor (28) in which the air and fuel mixture is burned to produce
hot gases, and an expansion device (26) for expanding the hot gases so as to
produce the mechanical power.
7. The system as claimed in claim 6, wherein the expansion device (26)
comprises a turbine.
8. The system as claimed in claim 7, wherein the turbine (26) is a fixed-
geometry turbine.
9. The system as claimed in claim 6, wherein the compression device (22) is
a fixed-geometry compressor.
10. The system as claimed in claim 6, wherein the combustor (28) is a fixed-
geometry combustor.
11. The system as claimed in claim 6, wherein the combustor (28) comprises
a catalytic combustor.
12. The system as claimed in claim 11, comprising a sensor operable to
measure a variable indicative of combustor inlet temperature, and wherein the
controller (40) is connected to said sensor and is operable to control air flow
through the engine (20) in such a manner as to maintain the combustor inlet
temperature above a predetermined minimum temperature required for catalytic
operation.
13. The system as claimed in claim 12, comprising a sensor (76) associated
with the heat exchanger (50) operable to measure a variable indicative of a
temperature of the exhaust gases entering the heat exchanger (50), and wherein
the controller (40) is connected to said sensor (76) associated with the heat
exchanger (50) and is operable to control air flow through the engine (20) to
maintain the temperature of the exhaust gases entering the heat exchanger (50)
below a predetermined maximum temperature.
14. The system as claimed in claim 1, wherein the generator (30) is a wound
generator.
15. The system as claimed in claim 14, comprising an excitation system (80)
operable to excite the generator (30).
16. The system as claimed in claim 15, wherein the control system (40) is
operable to control the excitation system (80) so as to electrically control the
generator speed and thereby control air flow rate.
17. A method for controlling an electrical generator system having an air-
breathing engine (20) mechanically communicating with a movable shaft (24),
the engine (20) being structured and arranged to receive a mixture of air and fuel
and burn the mixture such that the mixture expands and creates mechanical
power that is used to drive the shaft (24), the system having a fuel system (32)
coupled with the engine (20) and operable to supply fuel to the engine (20), the
fuel system (32) being responsive to a fuel control signal to vary a rate of fuel
flow to the engine (20), the system having an electrical generator (30) coupled to
the shaft (24) such that movement of the shaft (24) by the engine (20) causes
the generator (30) to operate to create an alternating electrical current, wherein
the engine (20), shaft (24), and generator (30) are connected such that a change
in speed of the generator (30) causes a corresponding change in speed of the
engine (20) and hence a change in rate of air flow through the engine (20), and
wherein electrical power output from the system is substantially determined by
fuel flow rate to the engine (20), the method comprising the steps of:
determining a power demanded by the load;
measuring at least one thermodynamic variable associated with the
engine (20) that is indicative of a relative thermodynamic efficiency of the engine
(20); and
controlling the fuel supply system (32) to supply fuel to the engine at a
controlled fuel flow rate such that the electrical power output from the system
substantially matches the power demanded by the load; characterized in that:
the system includes a power electronics unit (60, 70) coupled to the
generator (30) for receiving the alternating electrical current therefrom and
operable to synthesize an alternating output current and voltage at a
predetermined frequency and relative phase for supply to the load; and
the air flow rate through the engine (20) is controlled independently of the
electrical power output from the system by electrically controlling the speed of
the generator (30) via regulation of the power electronics unit (60,70) so as to
control fuel/air ratio of the mixture burned in the engine (20) in such a manner as
to substantially optimize the thermodynamic efficiency of the engine (20) while
substantially matching the power demanded by the load.
18. The method as claimed in claim 17, wherein the alternating electrical
current from the generator (30) is converted in an AC/DC module (60) into a non-
alternating direct current at a non-alternating voltage, and the non-alternating
direct current from the AC/DC module (60) is converted in a DC/AC module (70)
to synthesize the alternating output current that is supplied to the load, the
AC/DC module (60) being responsive to a current control signal to vary the level
of the non-alternating direct current independently of the alternating electrical
current from the generator (30), and wherein the step of controlling the air flow
rate comprises actively controlling the non-alternating direct current from the
AC/DC module (60) of the power electronics unit (60, 70) so as to alter the
speed of the generator (30) and hence the air flow rate.
19. The method as claimed in claim 17, wherein the engine (20) comprises a
turbine engine having a compressor (22) for compressing the air, a combustor
(28) for burning the mixture of air and fuel to produce hot gases, and a turbine
(26) for expanding the hot gases, and wherein optimizing the thermodynamic
efficiency of the engine (20) comprises causing a turbine inlet temperature to
substantially match a predetermined value.
20. The method as claimed in claim 19, wherein the combustor (28)
comprises a catalytic combustor, and comprising the steps of:
measuring a variable indicative of an inlet temperature to the combustor
(28); and
controlling air flow through the engine (20) in such a manner as to
maintain the combustor inlet temperature above a predetermined minimum
temperature required for catalytic operation.
An electrical power generating system (10) and method wherein a generator (30) is
driven by an air-breathing engine (20), At any operating condition, for a given power
output the engine efficiency is substantially optimized by controlling the rate of air
flow through the engine in such a manner that the fuel/air ratio is controlled to
maintain a high peak temperature imparted to the working fluid in the engine. The
method and system of the invention eliminate the need for variable-geometry
mechanisms in the engine, and also eliminate the need for variable-geometry
combustors and pre-burners. The invention is applicable to various types of air-breathing
engines that operate at low fuel/air ratios.

Documents:

145-KOLNP-2006-FORM-27.pdf

145-kolnp-2006-granted-abstract.pdf

145-kolnp-2006-granted-assignment.pdf

145-kolnp-2006-granted-claims.pdf

145-kolnp-2006-granted-description (complete).pdf

145-kolnp-2006-granted-drawings.pdf

145-kolnp-2006-granted-examination report.pdf

145-kolnp-2006-granted-form 1.pdf

145-kolnp-2006-granted-form 18.pdf

145-kolnp-2006-granted-form 3.pdf

145-kolnp-2006-granted-form 5.pdf

145-kolnp-2006-granted-gpa.pdf

145-kolnp-2006-granted-reply to examination report.pdf

145-kolnp-2006-granted-specification.pdf

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Patent Number

222723

Indian Patent Application Number

145/KOLNP/2006

PG Journal Number

34/2008

Publication Date

22-Aug-2008

Grant Date

21-Aug-2008

Date of Filing

18-Jan-2006

Name of Patentee

MES INTERNATIONAL, INC.

Applicant Address

P. O. BOX 5938, ASHEVILLE, NC

Inventors:

#	Inventor's Name	Inventor's Address
1	BELOKON ALEXANDER A	15, APARTMENT 102, PAVLA KORCHAGIHA STREET, MOSCOW
2	SENKEVICH MIKHAIL V	#24/3, APARTMENT 141, BRATEEVSKAYA STREET, MOSCOW
3	TOUCHTON GEORGE L, III	35134 MILLWOOD COURT, NEWARK, CA 94560

PCT International Classification Number

F01D 15/10

PCT International Application Number

PCT/US2004/021338

PCT International Filing date

2004-07-01

PCT Conventions:

#	PCT Application Number	Date of Convention	Priority Country
1	10/612,685	2003-07-02	U.S.A.