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H Multi-objective and Multi-Model MIMO control design for Broadband noise attenuation in a 3D enclosure Paul LOISEAU, Philippe CHEVREL, Mohamed YAGOUBI, Jean-Marc DUFFAL Mines Nantes, IRCCyN & Renault SAS March 2016 Content 1


  1. H ∞ Multi-objective and Multi-Model MIMO control design for Broadband noise attenuation in a 3D enclosure Paul LOISEAU, Philippe CHEVREL, Mohamed YAGOUBI, Jean-Marc DUFFAL Mines Nantes, IRCCyN & Renault SAS March 2016

  2. Content 1 Introduction General context PhD objective State of Art Scope of the presentation 2 System to control 3 Control Strategy 4 Results 5 Conclusions and Perspectives 2

  3. General Context Brief ANC overview Duct ◮ Propagative waves ◮ Feedforward + feedback Headphone Headrest ◮ SISO control ◮ SISO control ◮ Co-located actuator and sensor ◮ Co-located actuator and sensor 3

  4. General Context Active Noise Control (ANC) in a cavity Sensor Sensor Cavity Cavity Feedback Feedback Feedforward Feedforward Characteristics of ANC in a cavity ◮ Stationary waves ◮ Actuators and sensors co-located or not ◮ feedback or feedback + feedforward ◮ d narrow or broadband noise ◮ SISO or MIMO control 4

  5. PhD objective Active control of broadband low frequency noise in car cabin Aeroacoustic noise (Mainly in high frequency) Engine noise (Line spectrum) ROAD noise (Low frequency, Broadband spectrum) ◮ Passive treatments for low frequency noise ⇒ Addition of weight ◮ Active Noise Control (ANC) is a great opportunity to simultaneously: ◮ Reduce road noise ◮ Achieve car weight reduction 5

  6. PhD objective Active Noise Control of broadband noise Cavity Cavity Feedback Feedback ANC problem characteristics ◮ 3D enclosure Limitations involved ◮ Waterbed effect (Bode integral) ◮ Actuators and sensors not co-located ◮ No measure of w is available ◮ Non minimum phase zeros ◮ d broadband low frequency noise 6

  7. State of Art Adaptive feedforward control (FxLMS) 1 1 T. Sutton, S. J. Elliott, M. McDonald, et al. , “Active control of road noise inside vehicles”, Noise Control Engineering Journal , vol. 42, no. 4, pp. 137–147, 1994. 7

  8. State of Art Internal Model Control (feedback) 2 2 J. Cheer, “Active control of the acoustic environment in an automobile cabin”, PhD thesis, University of Southampton, Southampton, 2012, p. 346. 8

  9. Scope of the presentation Problem Cavity ◮ Attenuate broadband low frequency noise; ◮ In a closed cavity; ◮ by feedback. Feedback Goal of the presentation Compare SISO and MIMO achievable performances. 9

  10. Content 1 Introduction General context PhD objective State of Art Scope of the presentation 2 System to control Experimental Set up Identification 3 Control Strategy Control problem formulation Multi-objective optimization Controller Structure Initialization 4 Results 5 Conclusions and Perspectives 10

  11. Content 1 Introduction 2 System to control Experimental Set up Identification 3 Control Strategy 4 Results 5 Conclusions and Perspectives 11

  12. Experimental set up Top view of the cavity RC fi lter Ampli fi er Preampli fi er ADC DAC Acquisition Card Cavity characteristics NI PCIe 6259 ◮ One predominant dimension: 1D acoustic field in low frequency; ◮ One biased side: Attenuation of the first longitudinal mode; ◮ Frequency complexity: Similar to vehicle one. 12

  13. MIMO Identification Frequency Domain, Continuous time model Identification Fit indicator ◮ LS 1 LS 2 LS 3 Algorithm: Subspace; M 1 86.2326 84.1038 91.1196 ◮ Model structure: Modal; M 2 84.6231 88.8484 91.1542 ◮ Frequency range: [20-1000]Hz; ◮ Order: 80. Remark: SISO transfers contain RHP zeros. Bode Diagram N = 80 (FIT : 84.1038) From: LS 2 To: M 1 60 40 Magnitude (dB) 20 0 −20 180 Measure Model 90 Phase (deg) 0 −90 −180 200 400 600 800 1000 1200 1400 1600 1800 2000 Frequency (Hz) 13

  14. Content 1 Introduction 2 System to control 3 Control Strategy Control problem formulation Multi-objective optimization Controller Structure Initialization 4 Results 5 Conclusions and Perspectives 14

  15. Control problem formulation | W 1 | f min f max 1 | W 2 | f max G Optimization problem � �  � W 2 T w → ui < 1 � ∞    � �   � �  � W 3 T d ′ < 1 � � j → ei � min � W 1 T w → e 1 subject to i = 1 , 2 and j = 1 , 2 � ∞ K ∞   | p iK | < f e / N     Re ( p iK ) < 0 15

  16. Control problem formulation Additional robustness needed Environment conditions modify acoustic transfers Measured frequency responses from LS 2 to M 1 50 40 Magnitude (dB) 30 20 10 FRF1 0 FRF2 FRF3 (nominal plant) −10 180 90 Phase (deg) 0 −90 −180 100 200 300 400 500 600 700 800 900 1000 Frequency (Hz) A multi-model approach was used to tackle system variations 16

  17. Control problem formulation | W 1 | f min f max 1 | W 2 | f max G Optimization problem � �  max 1 ,..., N � W 2 T w → ui < 1 �  ∞   � �   max 1 ,..., N � � W 3 T d ′ � < 1  j → ei � � � min max � W 1 T w → e 1 subject to i = 1 , 2 and j = 1 , 2 � ∞ K 1 ,..., N ∞  | p iK | < f e / N      Re ( p iK ) < 0 17

  18. Multi-objective and Multi-model optimization Motivations ◮ Be able to consider various constraints without pessimism ; ◮ Clearly distinguish objective and constraints; ◮ Have the possibility to mix H 2 and H ∞ objectives, if needed; ◮ Be able to structure the controller; ◮ Be able to consider reduce order controller. Optimization tool: systune ◮ Specialized in tuning fixed-structure control systems; ◮ Based on non smooth optimization; ◮ P. Apkarian, “Tuning controllers against multiple design requirements”, in American Control Conference (ACC) , Washington, 2013, pp. 3888–3893 Drawback ◮ May lead to local optima; ◮ Necessity of ”good” initialization and controller structure. 18

  19. Controller Structure State feedback observer Model of the system ◮ No real time measure of w ◮ G p is known � ˙ x = Ax + B u u + B w w e = Cx + D u u + D w w Model of the controller � ˙ ˆ x = A ˆ x + B u u + K f ( e − ˆ e ) u = − K c ˆ x Remarks ◮ K f : observation gain ◮ K c : state feedback gain ◮ full order controller 19

  20. Initialization LQG LQ criteria � W LQ e � 2 2 + ρ � u � 2 J LQ = min 2 K c ◮ W LQ is a bandpass filter (attenuation frequency range) ◮ ρ manages trade-off between performances and control energy Kalman filter � ˙ x a = A a x a + B u a u + B w a w e = C a x a + D u a u + D w a w + v ◮ Tuning parameters are the covariances of noises v and w 20

  21. Content 1 Introduction 2 System to control 3 Control Strategy 4 Results 5 Conclusions and Perspectives 21

  22. Results Narrow attenuation: [190-220] Hz Transfer e 1 w [190-220] Hz (SIMULATION) 50 40 30 Magnitude (dB) 20 10 Open loop SISO (LS 1 ) SISO (LS 2 ) 0 MISO MIMO −10 150 160 170 180 190 200 210 220 230 240 250 Frequency (Hz) 22

  23. Results Narrow attenuation: [190-300] Hz Transfer e 1 w [190-300] Hz (SIMULATION) 45 Open loop 40 SISO (LS 1 ) SISO (LS 2 ) 35 MISO 30 MIMO Magnitude (dB) 25 20 15 10 5 0 −5 150 200 250 300 350 Frequency (Hz) 23

  24. Results Experimentation: 190-300 Hz (MIMO) Transfer e 1 w [190-300] Hz (MIMO) From: w To: e1 50 Simulation (nominal Plant) Experimentation 40 30 Magnitude (dB) 20 10 0 −10 −20 50 100 150 200 250 300 350 400 450 500 Frequency (Hz) 24

  25. Content 1 Introduction 2 System to control 3 Control Strategy 4 Results 5 Conclusions and Perspectives 25

  26. Conclusions and Perspectives Conclusions ◮ A general framework (for identification and control) was presented; ◮ It allows to quantify and compare SISO and MIMO achievable performances according to : ◮ Frequency range of attenuation ; ◮ Actuators and sensors position ; ◮ Cavity geometry ◮ . . . Ongoing work ◮ Compare feedback and feedforward control ◮ Apply methodology to the industrial problem where: ◮ G p is unknown ◮ System order and dimensions are higher 26

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