Design and Optimization of Composite Base Frames & Shaft of Wind Turbine for Catamaran
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1 MEHMET SITKI MERDİVENCİ 6 th EMship cohort: October 2015 February 2017 Design and Optimization of Composite Base Frames & Shaft of Wind Turbine for Catamaran Supervisor: Reviewer: Prof. Hervé Le Sourne, L'Institut Catholique d'arts et Métiers, Nantes, France Prof. Robert Bronsart, University of Rostock, Rostock, Germany EMShip Meeting,Rostock, February 2017
2 Contents 1. History of the Boat 2. Main objectives of the study 3. Presentation of Wind Turbine and Its Finite Element Model 4. Parametric Study of Composite Fixed Shaft 5. Static and Dynamic Analysis of Entire Optimized Model 6. Investigation of a Damping Material Selection 7. Comparison between Experimental and Numerical Results 8. Conclusions 9. Future Work Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
3 Introduction Energy Observer Absorbing the Energy Solar Panels Wind Turbine Stocking the Energy Hydrogen cells Consuming the Energy Electrical Motors Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
4 1. History of The Boat Formule Tag (1983) 24 m long Jules Verne Trophy 75 days (1994) Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
5 2. Main objectives of the study Design & Structural Analyzes of Vertical Axis Wind Turbine and Its Support Investigation of damping material selection Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
6 3. Presentation of Wind Turbine and Its Finite Element Model Aerojoules Adaptation of Aerojoules to Energy Observer Designing an Appropriate Support Using composite shaft Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
7 3. Presentation of Wind Turbine and Its Finite Element Model Expected Minimum Bending Natural Frequency Maximum Rotation of Turbine : 300 RPM Frequency = n(blades) x RPM / 60 3 x 300 RPM / 60 = 5 RPS 5 x 3 = 15 Hz Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
8 3. Presentation of Wind Turbine and Its Finite Element Model (Modifications) 1st Bending Mode : 11,6 Hz 2nd Bending Mode : 11,7 Hz 1st Bending Mode : 11,9 Hz 2nd Bending Mode : 12,2 Hz 1st Bending Mode : 10,9 Hz 2nd Bending Mode : 11,3 Hz 1st Bending Mode : 12,1 Hz 2nd Bending Mode : 12,4 Hz Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
9 4. Parametric Study of Composite Fixed Shaft Carbon epoxy composite material 80 mm of external diameter Same behavior as Aerojoules Thickness (mm) 1 st Mode Frequency (Hz) 2 nd Mode Frequency (Hz) 3 rd Mode Frequency(Hz) Stacking Sequence 16 9 (180 rpm) 9,2 (184 rpm) 16 (320 rpm) ([-30,0,30,0] 4,[45,0-45,0]) s 16 9,1 (182 rpm) 9,3 (186 rpm) 16 (320 rpm) ([-30,0,30,0] 5 ) s 24 9,6 (192 rpm) 10 (200 rpm) 16,5 (330 rpm) ([-30,0,30,0] 6, -30,0,[45,0-45,0]) s 24 9,7 (194 rpm) 10 (200 rpm) 16,5 (330 rpm) ([-30,0,30,0] 7, -30,0) s Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
10 5. Static and Dynamic Analysis of Entire Optimized Model Bending Modes Flexion Modes 9.1 Hz 9.3 Hz 9 Hz (182 RPM) (186 RPM) (180 RPM) Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
11 5. Static and Dynamic Analysis of Entire Optimized Model Stresses on Composite Support Elastic limit of composite material: 603 MPa Less than 25 % of Elastic limit 144 MPa 1st Layer 121 MPa 3rd layer Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
12 6. Investigation of a Damping Material Selection Carbon composite with viscoelastic material Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
13 6. Investigation of a Damping Material Selection 3 different type of samples: 0 layer of DYAD 2 layers ofdyad 4 layers of DYAD 320 mm 40 mm Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
14 6. Investigation of a Damping Material Selection Flexion 3 points E0D = 72 GPa E2D = 1,3 GPa E4D = 0,33 GPa Shear Modulus of DYAD: τ = 0,33 Mpa (Steel = MPa) Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
15 6. Investigation of a Damping Material Selection Frequency Response Analyses Experiment Samples 0D 2D 4D 1st Natural Frequencıes 58.9 Hz 55.1 Hz 52 Hz Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
16 7. Comparison between Experimental and Numerical Results 2D Sample First Bending Mode at 53.5 Hz Samples 0D 2D 4D 1st Natural Frequencıes 58.9 Hz 55.1 Hz 52 Hz Torsion Mode at 86.3 Hz Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
17 7. Comparison between Experimental and Numerical Results Experimentally Numerically Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
18 8. Conclusions Using more composite layers or having an interior structure of a composite support does not increase sufficiently the stifness of entire system and consequently the first natural frequency. Implemented viscoelastic material increases the damping characteristics of carbon epoxy composites, however it causes a significant decrement on Young s modulus. Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
19 9. Future Work Perforation of small holes on DYAD 601 (Pan & Zhang 2009) Thank you. Mehmet Sıtkı Merdivenci, 6th EMSHIP cohort: of 19 Master Thesis, Rostock, February 2017
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