Active noise control using noise source having adaptive resonant frequency tuning through variable ring loading
The U.S. Government has rights in this invention as provided for by the terms of contract No. NAS3-26617 awarded by the National Aeronautics and Space Administration (NASA). 
    
    
     CROSS REFERENCE TO RELATED APPLICATIONS 
     This application is related to the following copending applications: &#34;Active Noise Control Using Noise Source Having Adaptive Resonant Frequency Tuning Through Stiffness Variation,&#34; Ser. No. 08/143,602, &#34;Active Noise Control Using Noise Source Having Adaptive Resonant Frequency Tuning Through Stress Variation,&#34; Ser. No. 08/143,605, and &#34;Active Noise Control Using Noise Source Having Adaptive Resonant Frequency Tuning Through Variable Panel Loading,&#34; Ser. No. 08/143,604. All of these related copending applications are filed concurrently herewith and assigned to the same assignee as the present invention. 
     BACKGROUND OF THE INVENTION 
     This invention relates generally to reducing aircraft engine noise with a cancellation noise field which is generated by vibrational inputs to noise radiating structures and more particularly concerns changing the boundary conditions of the noise radiating structures to produce adaptive tuning of the resonant frequency of the structures. 
     Excessive noise has always been a problem confronting the aviation industry. Noise from discrete tones generated by the fans and turbines of modern aircraft engines is a major source of the noise problems. This is particularly true in communities surrounding airports which are subjected to the noise of take off and landing operations. Lately, fan and turbine noise has become an even larger issue due to the louder fan noise of the large-thrust high bypass engines and the increased enactment and enforcement of strict community anti-noise regulations. 
     Turbine and fan noise has been addressed for many years by employing passive techniques such as noise absorbing liners, tuned resonators, or a combination thereof. Such devices are usually mounted at the inlet and outlet of the engine to reduce noise radiated from the engine. Some disadvantages associated with these passive techniques include added weight and decreased thrust. Also, absorbent liners are generally ineffective against the long wavelengths of low frequency noise, and tuned resonators are only useful at the frequency to which they are tuned. 
     One possible active approach to fan and turbine noise control is to cancel the noise using secondary or cancelling noise fields generated with acoustical inputs. The cancelling noise field, which is of equal amplitude but 180° out-of-phase with the primary field, destructively interferes with and cancels the primary field. However, standard acoustical inputs, such as loudspeakers, are expensive, fragile, heavy and require a relatively large amount of power. An alternative to acoustical inputs is disclosed in the copending application entitled &#34;Active Control of Aircraft Engine Noise Using Vibrational Inputs,&#34; Ser. No. 08/051,810, filed Apr. 21, 1993 which is a File Wrapper Continuation of application Ser. No. 07/787,471, filed Nov. 4, 1991 and assigned to the same assignee as the present invention. Application Ser. No. 08/051,810 discloses using piezoceramic actuators instead of acoustical inputs to generate the cancelling noise field. The actuators are mounted either directly to an inner surface of an aircraft engine or to noise radiating elements resiliently mounted to the inner surface. When excited, the actuators produce vibrations in their supporting structure (the noise radiating elements or the engine itself) which &#34;shake&#34; the structure so that it generates the cancelling noise field. 
     The supporting structure which is shaken by the piezoceramic actuators may be made of low-damping materials because the peak vibratory response at resonance of elements fabricated with low-damping materials is very high and produces a correspondingly high acoustic output which is needed to cancel the engine noise. However, the off-resonance vibratory response of elements fabricated with low-damping materials is very low and does not result in an acoustic output sufficient to cancel engine noise. Thus, such piezoceramic-actuated noise cancellation is only effective over a narrow frequency range. Cancellation of aircraft engine noise is often required over a wider range of frequencies. 
     Accordingly, there is a need for an active noise cancellation system which is effective over a wide frequency range. 
     SUMMARY OF THE INVENTION 
     The above-mentioned needs are met by the present invention in which the cancelling sound field is generated using noise radiating structure which is vibrated by actuators mounted thereon. To accomplish noise cancellation over a wide range of frequencies, the structural resonant frequency of the noise radiating structure is tuned by adaptively changing their boundary conditions. Changing the structure&#39;s boundary conditions (such as torsional or linear stiffness, or compressive or tensile loading) will alter its resonant frequency. 
     Specifically, the present invention provides an active noise cancellation system comprising one or more actuators disposed on noise radiating structure in an aircraft engine. A plurality of drivers are arranged to contact the noise radiating structure. Excitation of the drivers causes expansion or contraction of the drivers, thereby varying the edge force applied to the noise radiating structure. The drivers are actuated by a controller which receives input of a feedback signal proportional to displacement of the noise radiating element and a signal corresponding to the blade passage frequency of the engine&#39;s fan. In response, the controller determines a control signal which is sent to the drivers, causing them to expand or contract. The noise radiating structure may be either the outer shroud of the engine or a ring mounted flush with an inner wall of the shroud or disposed in the interior of the shroud. 
     Other objects and advantages of the present invention will become apparent upon reading the following detailed description and the appended claims with reference to the accompanying drawings. 
    
    
     DESCRIPTION OF THE DRAWINGS 
     The subject matter which is regarded as the invention is particularly pointed out and distinctly claimed in the concluding part of the specification. The invention, however, may be best understood by reference to the following description taken in conjunction with the accompanying drawing figures in which: 
     FIG. 1 shows a schematic, cross-sectional view of an aircraft engine incorporating the active noise cancellation system of the present invention; 
     FIG. 2 is a cross-sectional end view showing a first embodiment .of the noise source of the present invention in detail; 
     FIG. 3 shows an alternate configuration of the present invention; 
     FIG. 4 is a perspective view of an alternate noise source of the present invention; and 
     FIG. 5 is a cross-sectional end view showing a second embodiment of the noise source of the present invention in detail. 
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     Referring to the drawings wherein identical reference numerals denote the same elements throughout the various views, FIG. 1 schematically shows the active noise cancellation system of the present invention as implemented in an aircraft engine 10. The engine 10, which in itself does not form a part of the present invention, can be any typical turbine- or fan-driven aircraft engine. The engine 10 includes an outer shroud 12 and a fan 14. For the sake of clarity, the other parts of the engine 10 are not shown. 
     In the present invention, noise sources 16 are provided to generate a secondary or cancelling noise field which destructively interferes with the primary noise field of the engine 10. FIG. 1 schematically shows a plurality of noise sources 16 mounted in the inner surface of the engine shroud 12. The size of the noise sources 16 depends on the acoustic power required to produce the secondary sound field. The number and placement of the noise sources 16 depends mainly on the modal order of the primary noise field to be cancelled. Ideally, a number of noise sources 16 will be distributed around the periphery of the engine shroud 12 in a cross-sectional plane to define a &#34;ring source.&#34; One or more ring sources may be located both upstream and downstream of the fan 14. A plurality of ring sources, each designed for a different noise bandwidth, can be used for cancellation of multiple tones. 
     The noise sources 16 are controlled by a noise cancellation controller 18 connected to each of the noise sources. The controller 18 receives input from a plurality of noise transducers 20 and a tachometer 22. The transducers 20 sense noise generated by the engine 10 and produce an error signal corresponding to the level of noise sensed. The noise transducers 20 can be microphones, piezoelectric transducers or any other type of device capable of sensing noise and producing an electrical signal output thereof. The transducers 20 are generally located near to wherever noise is believed to emanate from. Preferably, an array of noise transducers 20 is located upstream of the fan 14 and another array is located downstream of the fan 14, as shown in FIG. 1. The tachometer 22 inputs the blade passage frequency of the fan 14 into the controller 18. In response to the inputs from the noise transducers 20 and the tachometer 22, the controller 18 determines an appropriate control signal which is sent to each of the noise sources 16. The control signal causes the noise sources 16 to vibrate with the frequency and amplitude needed to create the proper secondary noise field for minimizing total noise. 
     The controller 18 can be implemented using one of a variety of standard control schemes known in the art. One preferred scheme uses a multi-input, multi-output (MI/MO) adaptive filtering approach based on the MI/MO Filtered-X LMS algorithm. Such an algorithm is described in the article &#34;A Multiple Error LMS Algorithm and its Application to the Active Control of Sound and Vibration,&#34; IEEE Transactions on Acoustic Speech and Signal Processing, Vol. ASSP-35, No. 10, October, 1987, by Stephen Elliott et al. In such a control scheme, the control signals which are sent to the noise sources 16 are adjusted in real time to minimize noise at the noise transducers 20. The controller 18 can react nearly instantly to any change in the RPM of the fan 14. Moreover, due to its adaptive nature, the controller 18 is self-configuring and can self-adapt to changes in the system such as noise source or transducer failure. 
     Turning to FIG. 2, a first preferred configuration of the present invention is shown in detail. As seen in FIG. 2, a number of the noise sources 16 are distributed evenly about the interior surface of the inner wall 24 of the shroud 12. Although six noise sources 16 are shown, this is only for purposes of illustration. More or less than six noise sources can be employed depending on the requirements of each particular application. Each noise source 16 is preferably a thin sheet actuator of piezoceramic, electrostrictive or magnetostrictive material disposed flat on the inner wall 24. The thin sheet exerts an oscillating force in the plane of the inner wall 24 when excited by the control signal sent from the controller 18. Structure-borne noise is then generated when in-plane vibrations change the shape of the inner wall 24 and produce bending motions. The highest, and thus most effective, acoustic output is achieved when the inner wall 24 is vibrated at one of its natural resonant frequencies. 
     In the present invention, the resonant frequency of the inner wall 24 is adaptively tuned by changing its boundary conditions, thereby providing effective noise cancellation over a wider frequency range. To this end, a number of drivers 26 are disposed between the inner wall 24 and the outer wall 28 of the shroud 12. Each driver 26 preferably includes a strut and an actuator supported by the strut. The actuators can comprise piezoceramic, electrostrictive or magnetostrictive materials or can even comprise an electromechanical device. Although six drivers 26 are shown, the present invention need not be limited to this particular number. Excitation of the drivers 26 with a DC voltage will cause them to expand or contract, depending on the nature of the applied voltage. The opposing ends of the drivers 26 contact the inner wall 24 and the outer wall 28, respectively, so that expansion or contraction of the drivers 26 will change the tensile or compressive edge loading on the inner wall 24, thereby changing its resonant frequency. 
     A feedback sensor 30 is optionally disposed on the inner wall 24. The feedback sensor 30 can be any type of device which produces a signal that is proportional to the displacement (as well as the velocity or acceleration) of the inner wall 24. Suitable devices include an accelerometer, a strain gauge or a patch of piezoceramic material. The feedback signal produced by the feedback sensor 30 is fed to a frequency tuning controller 32. The tuning controller 32 also receives input of the blade passage frequency from the tachometer 22. In response to these inputs, the controller 32 determines an appropriate control signal (in the form of a DC voltage) which is sent to the drivers 26. The tuning controller 32 is implemented using a control scheme in which the gain is adjusted in accordance with the inputted blade passage frequency. 
     Instead of being directly mounted to the inner wall 24, the noise sources 16 can be indirectly mounted via a noise radiating element 34 mounted in the inner wall 24. The noise sources 16 are disposed on the noise radiating element 34 and thus shake the noise radiating element 34 to generate the secondary noise field. The noise radiating element 34 is a relatively thin, cylindrical ring of a lightly damped material such as aluminum disposed in the inner wall 24 so as to be flush with its exterior surface. This arrangement assures that the noise controlling structure does not interfere with engine performance. The noise radiating element 34 is preferably attached to the inner wall 24 by resilient mounting means (not shown). The resilient mounting means allow the noise radiating element 34 to expand and contract and prevent propagation of the noise generating vibrations from the noise sources 16 to the critical parts of the engine 10. In this case, the drivers 26 will contact the noise radiating element 34 so that expansion or contraction of the drivers 26 tunes the resonant frequency of the noise radiating element 34, and the feedback sensor 30 will be disposed on the noise radiating element 34. 
     In operation, the tuning controller 32 applies the control signal to the drivers 26 causing the inner wall 24 (or the noise radiating element 34 where one is used) to either expand or contract, thereby changing its tensile or compressive loading. This tunes the resonant frequency of the inner wall 24 (or the noise radiating element 34) so that it tracks the blade passage frequency of the fan 14. The noise cancellation controller 18 then sends control signals to the noise sources 16 which cause the inner wall 24 (or the noise radiating element 34) to vibrate at resonance and generate a noise field which tends to cancel the primary field produced by the engine 10. 
     An alternative noise source 16&#39; which employs a mechanical lever arrangement instead of a thin sheet actuator is shown in FIGS. 3 and 4. This embodiment utilizes a noise radiating element 34&#39; which comprises a number of arcuate portions connected end-to-end by a number of the alternate noise sources 16&#39; so as to form a closed ring. Each noise source 16&#39; comprises a pair of lever members 36 (FIG. 4). Respective ends of the lever members 36 are connected together at a flexure point 38 so that the noise source 16&#39; forms a unitary, U-shaped assembly. The other ends of the two lever members are attached to respective arcuate portions of the noise radiating element 34&#39;. An expandable element 40, which can comprise piezoceramic, electrostrictive, magnetostrictive or electromechanical means, is disposed between the two lever members 36. When excited, the element 40 is displaced back and forth along the lateral directions shown by the arrow, thus causing the lever members 36 to essentially pivot back and forth about the flexure point 38. Consequently, the oscillating displacements of the element 40 are amplified and transferred through the lever members 36 to the noise radiating element 34&#39;, thereby shaking the noise radiating element 34&#39; to create the desired noise field. 
     Turning to FIG. 5, another embodiment of the present invention is shown. This embodiment uses a noise radiating element 34&#39; having noise sources 16&#39;, but instead of being an integral part of the inner shroud wall 24, the noise radiating element 34&#39; is disposed in the hollow interior of the shroud 12. (A noise radiating element 34 using thin sheet noise sources 16 is also applicable to this embodiment.) The noise radiating element 34&#39; is supported in the interior of the shroud 12 by a number of drivers 26 disposed between the noise radiating element 34&#39; and inner wall 24. Excitation of the drivers 26 with a DC voltage will cause them to expand or contract, depending on the nature of&#39;the applied voltage. The opposing ends of the drivers 26 contact the inner wall 24 and the noise radiating element 34&#39;, respectively, so that expansion or contraction of the drivers 26 will change the tensile or compressive loading on the noise radiating element 34&#39;, thereby changing its resonant frequency. A number of sound ports 42 are formed in the inner shroud wall 24 to permit the cancelling noise field to be transmitted into the engine interior. The sound ports 42 are preferably covered with a mesh or similar structure to prevent ingress of foreign materials. 
     The remaining elements of this embodiment are the same as those in the previously-described embodiments and function in the same manner. Thus, the feedback sensor 30 is disposed on the noise radiating element 34&#39; and sends a feedback signal to the tuning controller 32. In response to the feedback signal and the blade passage frequency input from the tachometer 22, the controller 32 determines appropriate control signals (in the form of a DC voltage) which are sent to the drivers 26. The control signals cause appropriate expansion or contraction of the drivers 26, thereby changing the tensile or compressive stresses in the noise radiating element 34&#39;. This tunes the resonant frequency of the noise radiating element 34&#39; so that it tracks the blade passage frequency of the fan 14. The noise cancellation controller 18 then sends control signals to the noise sources 16&#39; which cause the noise radiating element 34&#39; to vibrate at resonance and generate a noise field which tends to cancel the primary field produced by the engine 10. 
     The foregoing has described an active noise control system in which the cancelling noise is generated through vibrational inputs to structure which has adaptively changing boundary conditions to allow adaptive tuning of the resonant frequency of the structure for maximum efficiency. Although the present invention has been described primarily for use with an aircraft engine, the invention can be used in almost any device where high-order acoustic modes propagating down a waveguide are to be eliminated. Examples of such devices include heat, ventilation, and air conditioning (HVAC) systems and turbine devices. 
     While specific embodiments of the present invention have been described, it will be apparent to those skilled in the art that various modifications thereto can be made without departing from the spirit and scope of the invention as defined in the appended claims.