COMPRESSOR BLEED AIR CONTROL APPARATUS AND METHODS

Abstract: A turbine engine accessory power unit has a compressor (18) provided with a bleed air control system in which a surge bleed valve (58) is proportionally and integrally controlled to maintain a constant minimum compressor bleed flow rate slightly above the compressor's surge flow rate. The system control parameter is automatically reset as a function of (inter­ alia) the position of the compressor's adjustable inlet guide vanes to ensure optimum control system performance throughout the air delivery range of the compressor.

Description: The present invention relates generally to apparatus and methods for regulating the flow rate of gas discharge from a source of compressed gas which is liable to surging, for example a compressor, and more particularly although not exclusively to a novel bleed air control system adapted to ensure a constant minimum discharge flow rate in a compressor used to power pneumatically-operated aircraft accessory systems and the like. US-A-3,487,993 and 3,909,152 both show examples of an aircraft gas turbine engine with a compressed air bleed from the main engine compressor to power the aircraft accessory system. Of these, US-A-3,487,993 shows an aircraft gas turbine engine with a multi-stage compressor providing air for combustion and subsequent combustion gas expansion in the turbine section, the compressor having alternatively-operating bleeds from an intermediate-pressure stage and a high-pressure stage. Means is provided for switching the bleed from the intermediate-pressure stage to the high-pressure stage by opening a normally-closed valve controlling the high-pressure stage bleed, when a sensed pressure at e.g. the intermediate stage falls to a predetermined value. The control valve when open may be modulated to regulate the pressure of the bleed air supplied to the accessory system. US-A-3,909,152 provides only a simple accessory bleed point from the gas turbine engine compressor, and provides this bleed through a variable-area bleed port providing decreased port area when the bleed pressure is high, and vice versa, to prevent overbleeding of the engine under high power conditions. In addition to their traditional propulsion functions, gas turbine engines are often used as accessory power units (APU's) to supply mechanical and/or pneumatic power to a wide variety of aircraft accessory devices and systems. Accessory system pneumatic power is typically provided by forcing bleed air from the APU compressor section through a main bleed duct to the accessory system's supply inlet via a branch supply duct connected to and defining a terminal portion of the main duct. In order to prevent surge of the APU compressor used to power the pneumatic accessory system, it is necessary to maintain a certain minimum flow rate through the main bleed duct. However the APU-supplied accessory system normally has a widely fluctuating compressed air requirement and is automatically controlled to correspondingly regulate the amount of bleed air it receives from the compressor by modulation of an accessory valve positioned in the branch supply duct. To accommodate a decrease in accessory air demand, and maintain the compressor through flow above its surge level, a further branch passage referred to as a surge bleed duct is typically connected to the main bleed duct to provide an alternate outlet flow path for the compressor bleed air as flow through the branch supply duct is diminished by a closing of the accessory system valve. Flow through the surge bleed duct is regulated by modulating a flow control valve, referred to as the surge bleed valve positioned therein. Conventional bleed air control systems employ mechanical devices, such as diaphragm controllers, to proportionally operate the surge bleed valve in response to deviations in main duct flow rate from a desired value thereof. More specifically, as the main duct flow rate begins to deviate from a predetermined value, an error signal is generated and the control system responsively modulates the surge bleed valve to a degree directly proportional to the magnitude of the error signal. Such conventional control of the surge bleed valve requires that the valve be initially opened at a total compressor bleed air level substantially higher than the minimum flow level (i.e. a flow level exceeding the surge level by a reasonable margin of safety) required to prevent surge of the compressor. The early surge valve opening, necessitated by the stead-state droop characteristics of proportional control which cause the surge bleed valve operating characteristic line to be angled relative to the compressor surge characteristic line, results in a sizable amount of excess surge bleed air being dumped to atmosphere as the surge bleed valve is moved toward its fully open position. This heretofore unavoidable excess surge bleed air causes increased APU fuel consumption, results in increased surge bleed noise, decreases total power available from the APU, and limits the maximum supply pressure available to the pneumatically-powered accessory system. GB-A-1021797 discloses an arrangement for preventing surging in a centrifugal compressor comprising supply duct means for flowing to the gas-operated apparatus gas discharged from the source; means defining an outlet passage from the supply duct means; means for sensing the gas flow rate through the supply duct means and means for generating an error signal having a magnitude indicative of the deviation between the sensed flow rate and a desired value thereof; control means for utilising the error signal in a manner to prevent surging despite fluctuations in the flow rate of gas received by the gas-operated apparatus. A surge bleed duct control valve is controlled by a signal which is dependent on Δp 2 /p 2 , where Δp 2 is the flow rate through the compressor and p 2 is the pressure level of the compressor. The control may have a proportional action or both a proportional and an integral action. Accordingly, one object of the present invention is to provide an improved compressor system, and a bleed air control system and methods therefor, which eliminates or minimises the above-mentioned excess surge bleed air flow as well as other problems and advantages. US-A-4164035 discloses an apparatus for supplying gas discharged from a source of compressed gas as well as a control apparatus for modulating a flow controlled valve generally as set out in the precharacterising portion of claims 1 and 12. However, in this case, the gas flow rate in the supply ducts is calculated using the gas pressure before and after the compressor. This arrangement suffers a disadvantage that an accurate reflection of the true flow rate cannot be guaranteed due to changes in the gas temperature, velocity, leakage etc. It is therefore an object of the present invention to provide an arrangement in which the determination of the flow rate is not subject to these inaccuracies. This object is achieved by the apparatus defined in Claims 1 and 12, and by the method claimed in Claim 14. The invention may be carried into practice in various ways, but one specific embodiment thereof will now be described by way of example only, and with reference to the accompanying drawings, in which:- Figure 1 is a schematic diagram of a gas turbine engine accessory power unit in which is incorporated a compressor bleed air control system embodying principles of the present invention; Figure 2 is a graph of surge bleed valve position plotted against total load compressor bleed air flow which comparatively depicts the surge bleed valve control characteristics of the control system of Figure 1 and those of a conventional, proportional control system; Figure 3 is an enlarged, schematic illustration of the flow sensor portion of the control system of Figure 1; Figure 4 is an enlarged schematic diagram showing the components of the electronic controller portion of the control system of Figure 1; Figure 5 is a graph of signal strength plotted against time depicting the relationship between the electronic controller output signal and an error signal generated by the control system of Figure 1; and Figure 6 is a graph illustrating the relationship between the control system flow parameter and the position of the load compressor inlet guide vanes of the accessory power unit. The Accessory Power Unit A gas turbine engine accessory power unit (APU) 10 is schematically illustrated in Figure 1 and constitutes a preferred embodiment of the present invention. Accessory power units such as APU 10 are typically used to provide mechanical power to a driven accessory such as a generator 12, and simultaneously to supply compressed air to an accessory system such as an aircraft environmental control system 14 or to other pneumatically-operated devices such as air turbine motors or the like. APU 10 includes a power shaft 16 drivingly coupled at its left end in Figure 1 (through a gearbox not shown in Figure 1) to the generator 12. Fixedly mounted on the shaft 16 for rotation therewith are, from left to right along its length, a centrifugal load compressor 18, first and second stage centrifugal power compressors 20, 22, and first, second, and third stage axial power turbines 24, 26 and 28 positioned at the right end of the shaft 16. During operation of the APU, ambient air 30 is drawn into the inlet of the first stage power compressor 20, compressed, and then discharged through duct 32 into the inlet of the second stage power compressor 22 where it is further compressed. Compressor 22 discharges the further compressed air through a duct 34 into a combustor 36. The compressed air entering combustor 36 is mixed with fuel 38 also supplied to the combustor to form a fuel-air mixture which is continuously burned therein. Expanded gas 40 from the combustor is forced axially through the power turbines 24, 26, 28 to supply rotational power to the shaft 16 and is exhausted from the APU to atmosphere through a discharge passage 42 positioned immediately downstream of the power turbines. The rotation of the shaft 16 drives the generator 12 (or other mechanically-driven accessories) and also rotationally drives the load compressor 18 which is used to supply compressed air to the pneumatically-operated accessory system 14. Ambient air 44 is drawn through a set of adjustable inlet guide vanes (IGV) 46 into the inlet of the load compressor 18. Compressed air exiting (or "bled" from) compressor 18 is fored through a main bleed air duct 48, and then through a branch bleed air supply duct 50 connected to main duct 48, to supply compressed air to the accessory system 14. Branch bled duct 50 is sized to flow to the accessory system 14 the entire volume of compressed air discharged from the load compressor 18. The amount of compressor bleed air received by system 14 is conventionally regulated by a valve or damper 52, positioned in the branch bleed duct 50, and controlled by a volume controller 54 operatively connected between the system 14 and the valve 52. Upon sensing an increase in system compressed air demand, the controller 54 modulates valve 52 towards a fully open position. Conversely, upon sensing a decrease in system compressed air demand, the controller 54 modulates valve 52 towards a fully closed position. The bleed air-producing load compressor 18 is conventionally designed for maximum efficiency at rated load. Therefore, a certain minimum through flow of air is required to prevent compressor surge (i.e., stall on the blades of compressor 18). Because of the varying compressed air demand of accessory system 14, it is necessary to provide an alternate outlet flow path (i.e., a path in addition to branch bleed air duct 50) for the bleed air flowing through the main duct 48 in the event that the quantity of bleed air flow through branch duct 50 falls below the minimum required to prevent a surge condition in compressor 18. More specifically, when the valve 52 restricts the flow of bleed air in branch duct 50 to below the minimum surge-prevention quantity, an additional bleed air outlet passage must be provided from the main bleed duct 48. To accomplish this relief function, a surge bleed duct 56 is connected to the main bleed duct 48 and extended therefrom into the APU discharge passage 42. Like the branch bleed duct 50, the surge bleed duct 56 is sized to accommodate the entire flow of bleed air through the main duct 48 in the event that the control valve 52 closes completely, in which case all of the bleed air dischargewd from the load compressor 18 is dumped into the discharge passage 42 through the surge bleed duct 56. Compressed air flow through the surge bleed duct 56 is regulated by variable surge flow restriction means in the form of a surge bleed valve or damper 58 installed in the surge bleed duct 56. Surge bleed valve 58 is positioned by a torque motor 60 which is powered by bleed air 62 from the second stage power compressor 22. It is to the control of the surge bleed valve 58, in response to the varying compressed air demands of the accessory system 14, that the present invention is directed. The conventional method of regulating the surge bleed valve 58 is to employ a mechanical control system which senses the pressure within the main bleed duct 48 (or another parameter related to the total air flow therethrough) and generates an error signal indicative of the magnitude of the deviation of such parameter from a desired value thereof. This error signal is used to proportionally control the surge bleed valve to thereby maintain the bleed flow in duct 48 above the minimum required to prevent compressor surge. More specifically, conventional control systems modulate the surge bleed valve to a degree which is simply proportional to the strength of the mechanical error signal. The limitations and disadvantages of proportional surge bleed valve control are well known and are graphically depicted in Figure 2. In Figure 2 point A represents, for a selected inlet guide vane position, the total load compressor bleed air flow through main duct 48 with surge bleed valve 58 fully closed and accesssory valve 52 fully open. The vertical dashed line 64 to the left of point A is the surge line of the load compressor 18, a total compressor bleed flow to the left of the surge line 64 causing compressor surge. With conventional proportional control of surge bleed valve 58, its control line (dashed line 66 in Fig. 2) is inclined leftwardly relative to the vertical because of the droop characteristics inherent in proportional control. Thus, in order to ensure that the total compressor bleed air flow in slightly above its surge flow level (by a suitable safety margin of from 5 to 15 percent) when the surge valve is open to an extent necessary to cause full bleed flow through duct 56 (i.e., at point C, at which point the surge valve is somewhat less than fully open in accordance with customary design practice), it is necessary to initially open the surge valve at point B - a point well to the right of point C. This very early initial opening of the surge valve causes a rather sizeable excess of surge bleed air to be dumped to atmosphere to accommodate the proportional control droop. Such excess bleed air is graphically depicted in Figure 2 by the cross-hatched area between lines 64 and 66. The large excess surge bleed air requirement of conventional proportional control of the surge bleed valve results in increased fuel consumption of the APU, creates additional bleed air noise, limits the bleed air pressure available to the pneumatically-operated accessory system 14, and reduces the total usable power output of the APU. The present invention provides a unique electronic control system, indicated generally at 68 in Figure 1, which inexpensively solves these problems. In a novel manner described below, control system 68 operates the surge bleed valve along a control line 70 (Figure 2) which is substantially parallel to the surge line 64 and extends through point C just slightly to the right of the surge line. With the control line 70 thus shifted relative to the conventional control line 66, an initial surge valve opening point 'D' is provided which, like point 'C' is positioned slightly to the right of the surge line. Thus, as the accessory valve 52 begins to close off and the total compressor bleed air flow begins to decrease (i.e. move leftwardly from point 'A') a much later initial opening of the surge valve occurs. As can readily be seen in Figure 2, the clockwise angular displacement of the surge valve control characteristic line 70 (relative to the conventional control line 66) by the control system 68 eliminates all of the excess surge bleed flow between lines 66 and 70. The only excess surge bleed air flow remaining, represented by the cross-hatched area between lines 64 and 70, is that necessary to maintain a predetermined margin of safety during operation of the APU. The Electronic Surge Bleed Valve Control System Referring now to Figures 1, 3 and 4, the electronic control system 68 includes a flow sensor 72, connected to the main bleed air duct 48, which comprises a total pressure transducer 74 and a differential pressure transducer 76. A static pressure probe 78 extends into the main duct 48 and is coupled to the static pressure inlet of the differential transducer 76. Additionally, a total pressure probe 80 extends into the duct 48 and is coupled to the inlet of the total pressure transducer 74 and also to the total pressure inlet of the differential transducer 76. The flow sensor 72 transmits an output signal which comprises the combination of electric signals 82, 84 from the transducers 74, 76 respectively. Signal 82 is indicative of the total pressure (P t ), and signal 84 is indicative of the difference (P t - P s ) between the total and static pressures within the main duct 48. Transducer output signals 82, 84 are received by an electronic controller 86 which responsively transmits an electric control signal 88 to the valve motor 60 to vary the amount of power compressor bleed air 62 it receives, and thus vary the modulating force on the normally open surge bleed valve 58 in a manner achieving the very desirable surge valve control line 70 of Figure 2. Also received by controller 86 are electric input signals 90, 92, 94 and 96, as indicated in Figures 1 and 4, which function as subsequently described to reset the controller 86. Input signal 90 is transmitted to the controller 86 by an inlet guide vane position sensor 98 and is indicative of the actual position (i.e., opening angle) of the inlet guide vanes 46. input signal 92 is manually generated and resets controller 86 to an accessory system zero demand (or "idle") mode in which, by means not shown, the inlet guide vales are closed. input singal 94, also manually generated, resets controller 86 to an accessory system minimum demand mode and, also by means not shown, moves the inlet guide vane to a predetermined minimum opening position. input signal 96 emanates from a pressure sensor (not shown) in the load compressor 18 and is indicative of the pressure therein. Referring now to Figure 4, the electronic controller 86 includes a divider 100 which receives the pressure transducer output signals 82, 84 and responsively generates an electric output signal 102 whose magnitude represents the value of the sensed control paramater, (P t - P s )/P t of the control system 68. Reset signals 90, 94, 96 are used to combinatively define a desired value, or set point, of the main bleed flow-related control parameter (P t - P s )/P t . Signal 90, emanating from the guide vane position sensor 98, is used to adjust such set point as a function of the angular position of the inlet guide vanes 46. This guide vane-related adjustment is accomplished by a function generator 104 which receives reset signal 90 and responsively generates an output signal 106 related to signal 90 according to a predetermined, generally linearly increasing reset schedule 108 as graphically illustrated in Figure 4. As will be seen, the use of the control parameter (P t - P s )/P t , and the automatic adjustment of its set point value in response to changes in inlet guide vane position, ensure that a constant minimum load compressor bleed flow rate, between the compressor surge rate and the maximum accessory demand flow rate, is maintained by the control system 68 despite wide variations in inlet guide vane position and ambient temperatures. Signal 94, generated when the accessory system minimum demand mode is manually selected, is received by a signal generator 110 which transmits an output signal 112 whose magnitude is constant. The third control point reset signal, signal 96, which is indicative of the load compressor inlet pressure, is received by a comparator 114 which also receives an electric reference input signal 116 having a constant magnitude representative of sea level atmospheric pressure. Comparator 114 generates, through a multiplier 118, an output signal 120 which is proportional to the difference in magnitude between signals 96 and 116, thus being indicative of the actual altitude of APU 10. The three reset control signals, 106, 112, 120, and the signal 102 (which represents the actual sensed value of the flow parameter (P t - P s )/P t within the main bleed duct 48), are received by a comparator 122 which transmits, through a dynamic compensator 124, an error signal 126 whose magnitude is indicative of the difference between the actual value of the flow control parameter and the desired value thereof -namely the sum of the magnitude of signals 106, 112 and 120. Dynamic compensator 124 functions in a conventional manner to provide lead-lag dynamic compensation to error signal 126, thereby improving its transient response characteristics without affecting its steady state values. It can be seen in Figure 4 that the set point value of the main bleed flow parameter (P t - P s )/P t is increased by the control system 68 in three manners - (1) an increased opening of the inlet guide vanes, (2) a selection of the accessory system minimum demand made and/or (3) an increase in the altitude of the APU. Conversely, the set point is decreased by a reduction in the magnitude of any of the signals 106, 112, 120. Error signal 126 is supplied in parallel to a proportional controller 128 and an integral controller 130. Controller 128, 130, respectively, transmit electrical output control signals 132, 134 which are received by a summer 136. The magnitude of output signal 132 is a predetermined multiple of the magnitude of error signal 126, while the magnitude of output signal 134 is the integral, as a function of time, of the error signal 126. The summer 136 combines, or superimposes, the proportional and integral control signals 132, 134 and outputs the combined control signal 88 which is used to regulate the torque motor 60 (Figure 1), and thus modulate the surge bleed valve 58. As can be seen in Figure 5, the output signal 88 from the electronic controller 86 has a magnitude which increases linearly-relatively to the magnitude of the error signal 126 as a function of the duration of such error signal, and has, at a given time t, both an integral component I and a proportional component P. The flow rate of surge bleed air exhausted through duct 56 is thus related to the magnitude of deviation of the parameter (P t - P s )/P t , from its set point value, in both a proportional and time-integral manner. It is this unique use of proportional and integral system control, afforded by the parallel controllers 128, 130, which imparts the characteristics to the ultimate valve-controlling signal 88 that substantially eliminate the excess surge bleed problems previously described and long-associated with conventional proportional control of surge bleed valve 58. More specifically, it has been discovered that this addition to the valve-controlling signal 88 of the integral component I (i.e., the integrated output signal 134) makes possible the ideally positioned valve control line 70 (Figure 2), thereby eliminating the previously unavoidable wastage of surge bleed air represented by the area between lines 66 and 70 in Figure 2. The resulting control line 70, since it is essentially parallel to surge line 64, greatly delays the required initial opening of the surge valve (compared to conventional proportional valve control), as previously described, when the total compressor bleed air flow rat begins to diminish. In sum, the illustrated control system 68 provides a constant minimum total bleed air flow rate (line 70) instead of the wasteful varying minimum flow rate (line 66) of previous surge valve control systems. Under the greatly improved control of system 68, once the surge valve 58 is initially opened the flow through main duct 48 remains essentially constant regardless of degree to which the surge valve is further opened. Referring again to Figure 4, the error signal 126 received by the parallel controllers 128,130 is also transmitted to a "kicker" control 138. When error signal 126 reaches a predetermined maximum level (indicating a predetermined maximum deviation between the actual value of the flow parameter (P t - P s )/P t and its set point), the kicker 138 transmits a constant value output signal 140 to an OR gate 142 which also receives signal 92 (the manually selected accessory system zero demand signal). If the OR gate 142 receives either of the signals 92, 140 it immediately transmits to the integral controller 130 an electrical integrator shutoff signal 144 which interrupts current flow therethrough, thereby allowing the surge valve 58 to move, at its maximum slew rate, toward its normally open position. Thus, for example, if the total bleed flow rate in main duct 48-experiences a very rapid diminution, the kicker 138 acts as a safety mechanism to compenate for this condition by snapping the surge valve to a more open position until the error signal returns to below its predetermined maximum allowable level. Selection, via signal 92, of the zero accessory system demand mode, which closes the accessory valve 52 in a manner not shown, also de-energizes the integrator 130 and rapidly opens the surge valve to prevent compressor stall which might otherwise result from a sudden closing of the accessory valve. As previously mentioned, the selection of the flow-related main bleed air control parameter (P t - P s )/P t affords the control system certain operational advantages. Such advantages will now be described with reference to Figure 6. In Figure 6 two sets of constant temperature load compressor operating lines, 146a, 146b and 146c, and 148a, 148b and 148c, are plotted against the coordinates of load compressor outlet-to-inlet pressure ratio and corrected load compressor inlet air flow for two representative inlet guide vane angles, 70° and 35°. For the 70° inlet guide vane angle the load compressor surge line is represented by dashed line 150, while the surge line of the load compressor for the 35° inlet guide vane angle is represented by dashed line 152. To the right of, and substantially parallel to, the surge lines 150, 152 are plotted representative maximum accessory system flow rate demand lines 154, 156 which respectively correspond to the 700 and 350 wide vane angles. Finally, there are plotted on the graph of Figure 6 two control parameter lines 158, 160, each of which represents a different constant value of the main bleed duct flow parameter (P t - P s )/P t used in the preferred embodiment of the present invention. Two important characteristics of the parameter lines 158, 160 should be noted. First, each such line, as it passes through the compressor operating lines, has a constant slope, indicating that the desired parameter (P t - P s )/P t is insensitive to variations in compressor inlet (i.e., ambient) temperature. Secondly, each of the parameter lines 158, 160 extends between and is essentially parallel to a different one of the surge and demand line pairs 150,154 and 152,156. The lines 158, 160 thus respectively define ideal potential load compressor operating areas 162 (the cross-hatched area bounded by lines 146a, 156, 146c and 158) and 164 (the cross-hatched area bounded by lines 148a, 156, 148c and 160), such potential operating areas having substantially constant minimum flow rates paralleling their associated surge lines. The achievement of these optimum compressor operating areas, defined in part by the flow parameter lines 158, 160, is, of course, made possible by the previously described novel integral and proportional surge valve control built into the control system 68. Another reason why the use of this particular flow control parameter is operationally advantageous is that the optimum value of such parameter for each guide vane angle is essentially linearly related to the particular inlet guide vane angle. This generally linear relationship permits the use of the relatively simple linear function generator 104 (Figure 4) to properly reset the desired value of the flow parameter as a function of the inlet wide vane position. The bleed air control principles of the present invention are applicable to a wide variety of compressor bleed applications and are not limited to the APU load compressor application described above. For example, the proportional-plus-integral surge valve control method of the present invention is equally well adapted to the situation where partial bleed-off of the compressed air discharged from a power compressor (as distinguished from a load compressor) is used as the air source for a pneumatically-operated accessory system. Additionally, while the control parameter (P t - P s )/P t is particularly well suited to the illustrated load compressor bleed application, other flow-related parameters (such as P t - P s ) could be used if desired. Moreover, the signals used to adjust the control set point (i.e., the illustrated altitude, minimum demand mode, and inlet guide vane adjustment signals) could be varied to suit the particular bleed air application. One example of such variation would be the deletion of the guide vane adjustment of the control set point in the situation where the bled-from compressor does not have adjustable guide vanes. To summarize, the control system 68, with its integral-plus-proportional control feature, provides apparatus and methods for eliminating the large amount of wasted surge bleed air associated with previous surge valve control systems. This is accomplished by using relatively standard, rugged and reliable electronic components. The greatly improved control provided by this invention reduces fuel consumption and surge bleed air usage and noise, yet at the same time increases the maximum air pressure available to the pneumatic accessory system 14 and the maximum shaft power available to the mechanically-driven accessory 12.

Claims: Apparatus for supplying gas discharged from a source (18) of compressed gas having an inlet (46) of variable area to gas-operated apparatus (14) having a variable supply gas flow rate demand, the source being subject to surging, said apparatus comprising; (a) supply duct means (48) for flowing to the gas-operated apparatus (14) gas discharged from the source (18); (b) means (56) defining an outlet passage from the supply duct means; (c) flow regulating means (58, 60) operable to variably restrict gas flow from the duct means (48) outwardly through the outlet passage (56) ; (d) means (72) for sensing the gas flow rate through the supply duct means (48) located between the compressed gas source (18) and the outlet passage (56) and means (100, 122) for generating an error signal (126) having a magnitude indicative of the deviation between the sensed flow rate and a desired value thereof; and (e) control means (128, 130, 136) for converting the error signal (126) into a control signal (88) for operating the flow regulating means (58, 60) in a manner to maintain sufficient gas flow through the supply duct means (48) to prevent surging despite fluctuations in the flow rate of gas received by the gas-operated apparatus, the magnitude of the control signal relative to the magnitude of the error signal having both an integral component (134) and a proportional component (132), characterised in that the means for sensing the gas flow rate through the supply duct means (48) comprises a total pressure probe (80) extending into the supply duct means (48), a static pressure robe (78) extending into the supply duct means (48), a total pressure transducer (74) and a differential transducer (76), the transducers (74, 76) being connected to the pressure probes (78, 80), and the desired value of the flow rate being provided by a sensed value of a flow related parameter which has been varied in response to variation in the area of the inlet (46), the flow-related parameter being (P t - P s )/P t , P t being the total pressure in the duct means (48) and P s being the static pressure therein, and further characterised by a kicker device (138) for automatically deleting the integral component from the control signal while the error signal exceeds a predetermined magnitude; and means for generating a signal (96) indicative of the pressure at the inlet (46), means for generating a reference signal (116) having a constant value representing a reference pressure, such as sea level atmostpheric pressure, and a comparator (114) which receives the inlet presssure signal (96) and the reference signal (116) and which generates an output signal (120) which is proportional to the difference in magnitude betwwen the signal (96, 116), the output signal being selectively employed to bias the flow related parameter in dependance upon the altitude of the apparatus above the position represented by the reference pressure. Apparatus as claimed in Claim 1, in which the control means (128, 130, 136) for utilising the error signal (126) comprises a first control means (128) for receiving the error signal and transmitting a first output signal (132) having a magnitude proportional to the magnitude of the error signal, and a second control means (130) for receiving the error signal and transmitting a second output signal (134) having a magnitude representing the integral, as a function of time, of the magnitude of the error signal, and means (136) for simultaneously utilising the two output signals to modulate the flow regulating means (58) in a manner ensuring that the minimum gas flow rate through the supply duct (48) is of a substantially constant, predetermined magnitude regardless of the supply gas demand of the gas-operated apparatus. Apparatus as claimed in claim 2, wherein the error signal-generating means includes; the differential pressure transducer (76) which senses the difference between the transducer (76) which senses the difference between the total pressure and the static pressure within the supply duct means (48) and transmits a third output signal (84) indicative of the sensed pressure differential; the total pressure transducer (74) which senses the total pressure within the supply duct means (48) and transmits a fourth output signal (82) indicative of the sensed total pressure; means (100) for generating a sensed parameter signal (102) having a magnitude equal to the magnitude of said third output signal divided by the magnitude of said fourth output signal; and comparator means (122) for receiving said second parameter signal (102) and at least one reset signal (106, 112, or 120) indicative of said desired value of said parameter, and for responsively generating the error signal (126). The apparatus of Claim 3, for use with a compressor (18) of a type having adjustable inlet guide vanes, the apparatus further comprising guide vane position sensor means (98) for transmitting a reset signal (106) to the comparator means (122), the reset signal (106) varying as a function of the position of the inlet guide vanes according to a predetermined reset schedule. The apparatus of Claim 4, wherein the reset schedule is substantially linear. The apparatus of Claim 3 or Claim 4 or Claim 5, including means for transmitting a reset signal (94) to the comparator means (122), the reset signal being generated in response to the selection of a predetermined mode of operation of the gas-operated apparatus (14). Apparatus as claimed in any one of Claims 1 to 6, in combination with a source comprising an air compressor (18) subject to surging, the supply duct (48) in use delivering bleed air from the compressor to pneumatically-powered apparatus (14) having a variable supply air demand, and in which the flow regulating means comprises a surge bleed control valve (58) in a surge bleed passage constituting the outlet passage (56), and the control means (128, 130, 136) is arranged to utilise the error signal (126) to modulate the valve (58) in a manner such that, subsequent to an initial opening of the valve, the flow rate through the supply duct (48) remains substantially constant in use regardless of the degree to which the valve is further opened, whereby the valve is controlled in use along an operating characteristic line (70) substantially parallel to a surge line characteristic (64) of the compressor. Apparatus as claimed in any of Claims 2 to 7 wherein the kicker device (138) has inlet means for receiving the error signal (126) and means for deactivating the integral controller (130) when the error signal reaches a predetermined magnitude. Apparatus as claimed in any one of Claims 1 to 8, in combination with an accessory power unit for supplying compressed air to pneumatically-powered apparatus having a fluctuating compressed air supply demand, the unit comprising a power-driven compressor (18) supplying compressed air through the supply duct (48) to the pneumatically-powered apparatus, and the outlet passage (56) and its flow regulating means (58) being operable to exhaust from the supply duct a selectively-variable quantity of air to ensure at least a predetermined minimum flow rate through the supply duct sufficient to prevent surge of the compressor, the apparatus maintaining the said minimum flow rate essentially constant regardless of fluctuations in the air supply demand of the pneumatically-powered apparatus. Apparatus as claimed in claim 9, in which the accessory power unit comprises a gas turbine engine driving a compressor which supplies the compressed air to drive the pneumatically-powered apparatus. Apparatus as claimed in any one of Claims 1 to 9, incorporated in a gas turbine engine device comprising: (a) as the said source subject to surging, drivable compressor means (18, 20, 22) for receiving, compressing and discharging air; (b) combustor means (36) for receiving compressed air discharged by said compressor means, mixing the received air with fuel (38), burning the fuel-air mixture, and discharging the resultant expanded gas (40); (c) turbine means (24, 26, 28) positioned to be operated by the expanded gas (40) discharged from said combustor means (36) for driving said compressor means and creating a power output from said gas turbine device; and (d) a bleed air system including: (1) main bleed duct means (48) constituting the said surplus duct means, said main bleed duct means having a branch air supply portion (50) for flowing compressed air received from said compressor means (18) to the said gas-operated apparatus (14) to operate the latter, and further having a surge bleed outlet portion (56) constituting the said outlet passage from the supply duct means (48). Control apparatus for modulating a flow control valve (58) positioned in an outlet passage (56) connected to a main air supply passage (48) adapted to receive air discharged from a compressor subject to surging and to supply the air to pneumatically-operated apparatus (14) having a variable supply air demand, a flow sensor (72) for sensing the air flow rate through the supply passage (48) being located between the compressor and the outlet passage (56), the control apparatus comprising (a) means (122) for generating an error signal indicative of the difference between the actual magnitude of a selected flow-related parameter within the main air supply passage (48) and a desired value of the parameter; (b) first control means (128) for receiving the error signal and transmitting an output signal (132) having a magnitude proportional to the magnitude of the error signal; (c) second control means (130) for receiving the error signal and transmitting an output signal (134) having a magnitude representing the integral, as a function of time, of the magnitude of the error signal; (d) means (136, 88) for simultaneously utilising said output signals (132, 134) from said first and second control means to modulate the flow control valve (58) in a manner ensuring that the minimum air flow rate through the main air supply passage (48) is of a substantially constant, predetermined magnitude regardless of supply air demand of the pneumatically-operated apparatus; and (e) means (90, 104) for adjusting the desired value of the parameter in response to the variation of the inlet guide vane setting of the compressor, characterised in that the flow sensor (72) comprises a total pressure probe (80) extending into the supply passage (48), a static pressure probe (78) extending into the supply passage (48), a total pressure transducer (74) and a differential pressure transducer (76), the transducers (76, 76) being connected to the pressure probes (78, 80), whereby the flow-related parameter is (Pt -P s )/P t , P t being the total pressure in the duct means (48) and P s being the static pressure therein, and further characterised by a kicker device (138) for automatically deleting said integral component from the control signal while the error signal exceeds a predetermined magnitude; and means for generating a signal (96) indicative of the pressure at the inlet (46), means for generating a reference signal (116) having a constant value representing a reference pressure, such as sea level atmostpheric pressure, and a comparator (114) which receives the inlet pressure signal (96) and the reference signal (116) and which generates an output signal (120) which is proportional to the difference in magnitude between the signals (96, 116), the output signal being selectively employed to bias the flow related parameter in dependance upon the altitude of the apparatus above the position represented by the reference pressure. Control apparatus as claimed in Claim 12, in combination with a compressor (18) subject to surging supplying compressed air through the main supply passage (48) to the pneumatically-operated apparatus (14), the control apparatus serving to modulate the flow control valve (58); the flow sensor being responsive to variations in the flow rate of air received by the pneumatically-operated apparatus (14) and being arranged together with the generating means (122) to produce the said error signal (126) which has a magnitude indicative of the degree of deviation, from a desired minimum flow rate, of the actual flow rate through the main supply passage (48) , the control apparatus being arranged to utilise the error signal (126) to modulate the flow control valve (58) in such a manner that, subsequent to an initial opening of the valve (58), the flow rate through the main supply passage (48) remains substantially constant regardless of the degree to which the valve (58) is further opened, whereby in use the apparatus controls the valve along an operating charactertistic line (70) substantially parallel to a surge characteristic line (64) of the compressor. A method of controlling a flow control valve (58) positioned in an outlet branch passage (56) of a compressed air supply duct (48) interconnected between the outlet of a compressor (18) subject to surging and the inlet of pneumatically-powered apparatus (14) having a variable supply air demand, in which to ensure a predetermined, essentially constant minimum flow rate through the supply duct (48) despite fluctuations in the supply air demand of the pneumatically-powered apparatus (14), said method comprises the steps of: (a) generating an error signal indicative of the difference between the actual magnitude of a selected flow-related parameter within the supply duct (48) and a desired value of the parameter; (b) producing a first control signal (132) having a magnitude related to the magnitude of the error signal; (c) producing a second control signal (134) whose magnitude is the integral, as a function of time, of the error signal; (d) simultaneously utilising said first and second control signal (132 and 134) to modulate the flow control valve; and (e) adjusting the desired value of the parameter in response to variation of the area of the inlet to the compressor, the said control signal producing steps being performed by providing a proportional controller (128) and an integral controller (130) and transmitting said error signal to each of said controllers to produce the respective control signals, characterised in that the generating of said error signal (126) includes the steps of sensing within the supply duct (48) the value of the parameter P t - P s )/P t , P t being the total pressure within the supply duct and P s being the static pressure therein, and transmitting a signal (102) indicative of the sensed value of said parameter to an inlet of a comparator (122), and comparing the signal (102) with a set point value of the comparator to provide the error signal as the difference thereof, and further characterised by automatically deleting the integral component from the control signal while the error signal exceeds a predetermined magnitude by means of a kicker device (138) and generating a signal (8=96) indicative of the pressure at the inlet (46), generating a reference signal (116) having a constant value representing a reference pressure, such as sea level atmospheric pressure, and generating an output signal (120) which is proportional to the difference in magnitude between the signals (96, 116), the output signal being seletively employed to bias the flow related parameter in dependance upon the altitude of the apparatus above the position represented by the reference pressure. The method of Claim 14, wherein the compressor (18) has adjustable inlet guide vanes, said comparator (122) has an adjustable set point, and said method further comprises the step of adjusting said set point value in response to variations in the position of the inlet guide vanes. The method of Claim 15, wherein said point adjusting step is performed by adjusting said set point according to a schedule essentially linearly related to changes in the position of the inlet guide vanes. The method of any one of Claims 14 to 16, in which the compressed air supply duct (48) interconnects the outlet of a compressor (18) of a gas turbine engine and the pneumatically-powered apparatus (14) to drive the latter. The method of any one of Claims 14 to 16, applied to the utilisation of a compressor (18) of a gas turbine engine to power pneumatically-operated apparatus (14) having a variable inlet air flow demand, said method comprising the steps of interconnecting the said supply duct (48) between the compressor (18) and the pneumatically-operated apparatus; said method ensuring the maintenance of an essentially constant minimum supply duct flow rate, despite fluctuations in the flow rate of air received by the pneumatically-operated apparatus (14), by exhausting air from said supply duct (48) in response to variatons therein of the value of the said parameter, the flow rate of air exhausted from said supply duct being related to the magnitude of said parameter value variations in both a proportional and time-integral manner.

Inventors: ADAMS, MILTON R., LACROIX, STEPHEN R., STOKES, RICHARD F., TIMM, JAMES D.
Applicants: THE GARRETT CORPORATION
Application year: 1982
Main classification: F04D27
IPC codes: F02C9, F04D27