Untitled e ISSN 2582 5208 International Research Journal of Modernization in Engineering Technology and Science Volume 03/Issue 05/May 2021 Impact Factor 5 354 www irjmets com www irjmets com @Interna[.]
e-ISSN: 2582-5208 International Research Journal of Modernization in Engineering Technology and Science Volume:03/Issue:05/May-2021 Impact Factor- 5.354 www.irjmets.com OPTIMIZED RESEARCH ON THE DESIGN OF PARTS TO IMPROVE THE SAFETY OF 2-FLOOR PASSENGER CARS Huy - Nguyen Huu*1, Thanh – Pham Van*2, Khai – Chu Thanh*3, Song – Ngo Duy*4, Nam – Tran Duy*5 *1,2,3,4,5Dong Nai Technology University, Dong Nai, Vietnam ABSTRACT Flatbed passenger car is a new trend in passenger transport today because of the convenience and comfort it brings when transporting long-distance passengers However, there have been tragic accidents of passenger buses in recent times, especially in complicated traffic conditions, partly because there are no specific standards and regulations for passenger buses that are still in use Use standard passenger car seats for car beds In this paper, the suspended part design (the position of the passenger bed) will be optimized to match the passenger car seat standards Considering the durability and stability of the car after changing the design Modeling and centering of cars with Inventor & Lapview simulation software I INTRODUCTION Changing the structure of the vehicle body will directly affect the working conditions as well as the controls, [14] many different influencing factors and depending on the different working conditions of the vehicle Therefore, the thesis does not re-study the suspension, but uses those results to calculate [5-7] The focus will be on design analysis and redeployment of the suspended mass to lower the center of gravity of the vehicle compared to the present, while still ensuring motion safety and comfort for passengers[7-10] II THE PART IS SUSPENDED AFTER A DESIGN CHANGE Determine the mass of the car itself after a design change Figure The layout of the upper bunk bed before changed Figure Layout of upper bunk bed after changing www.irjmets.com @International Research Journal of Modernization in Engineering, Technology and Science [2466] e-ISSN: 2582-5208 International Research Journal of Modernization in Engineering Technology and Science Volume:03/Issue:05/May-2021 Impact Factor- 5.354 www.irjmets.com Figure The layout of the lower bunk bed before changed Figure Layout of a lower bunk bed after changing Figure Cross section A-A before change, B-B after change GTS GDC GK GKX GGN GKV GBX GML GNT CAÀ U SAU GTT GTNL CẦ U TRƯỚ C 725 1335 Z02 3232 3295 3495 3691 4005 6150 Z01 1215 8847 Figure Mass distribution of vehicle clusters Write the equation for the balance of moment at the front center of the sphere, we have: Z02*6150=(GDC*8847+GTS*6150+GK*4005+GKX*3691+GGN*3495+GKV*3295+ GBX*3232+GML*1335+GNT*725+GTT*0+GTNL*(-1215)).g www.irjmets.com @International Research Journal of Modernization in Engineering, Technology and Science [2467] e-ISSN: 2582-5208 International Research Journal of Modernization in Engineering Technology and Science Volume:03/Issue:05/May-2021 Impact Factor- 5.354 www.irjmets.com Solving the equation we get: - The self-mass jet acts on the rear axle: Z02 = 81430 (N) - Self-mass counterforce acts on the front axle: Z01 = G0.g - Z02 = 46470 (N) Determine the total volume of the car Assume that the mass components are distributed symmetrically across the car's longitudinal axis of symmetry [9-1] Draw a diagram of calculation of the distribution of the volume of passengers and luggage: GG8 GG14 GG7 GG13 GG6 GG12 GG5 GHL GG11 GG4 GG10 GG3 CAÀ U TRƯỚ C CẦ U SAU Zt2 GG9 GG2 GG1 1300 1370 2700 2770 2970 4100 4170 5500 5570 6150 6900 6970 8300 30 Zt1 100 1640 Figure Diagram of calculation of distribution of passenger and baggage volumes Writing the equilibrium moment at the front center, we have: Zt2*6150 = (GG8*8300+GG14*6970+GG7*6900+GG13*5570+GG6*5500+GG12*4170+GG5*4100 +GHL*2970+GG11*2770+GG4*2700+GG10*1370+GG3*1300+GG9*(-30)+GG2*(-100)+GG1*(-1640)).g Solving the above equation we get: - Jet due to the amount of passengers and luggage distributed on the rear axle: Zt2 = 18100 (N) - Doing the same for the front axle, we calculate the jet due to the amount of passengers and luggage distributed on the front wheels: Zt1 = 12000 (N) - So, the total jet due to the passenger and baggage weight is allowed to be distributed over bridges: Zt = Zt1+Zt2 = 30100 (N) - Weight of car itself: G0 = 12790 (kg) Total weight: - Total jet due to the mass distributed to the front axle: Z1 = Z01 + Zt1 = 44670 + 12000 = 58470(N) - Total jet due to the mass distributed to the following bridge: Z2 = Z02 + Zt2 = 81430 + 18100 = 99530(N) - Total total mass jet of cars: Z = Z1 + Z2 = G0.g + Zt = 158000 (N) Recalculate the focus after a design change HEIGHT CALCULATION MEASUREMENT TABLE Mass composition Symbol Coordinates hi (mm) Mass (kg) Volume of engine-gearbox (clutch, water tank, intercooler) GDC 960 1527 The mass of the car chassis - the steering system GKX 1018 3100 The mass of the front axle - suspension GTT 515 365 The mass of the rear axle assembly - suspension GTS 515 1098 Weight of car wheels (including spare wheels) GBX 524 560 Fuel tank volume GTNL 635 400 www.irjmets.com @International Research Journal of Modernization in Engineering, Technology and Science [2468] e-ISSN: 2582-5208 International Research Journal of Modernization in Engineering Technology and Science Volume:03/Issue:05/May-2021 Impact Factor- 5.354 www.irjmets.com Frame weight GTH 1402 5540 Volume of passengers GHK 1830 2795 The weight of the baggage GHL 1830 215 Weight of automobile chassis GCH hCH 7050 The volume of the car itself G0 hg0 12790 Whole car volume G hg 15800 Center coordinates by height: Based on the weight of the components and the height of the center of gravity, we can determine the height of the center of gravity of the car as follows: hg = ( Gi * hgi) / G Inside hg- Car center height; Gi - Volume of components (chassis, luggage, ); hgi - Center height of mass components; G - Whole car volume From there we can calculate: The height of the center of the car frame: hCH = 0,790 (m) The height of the center of gravity of the car when the car is not loaded: hg0 = 1,079 (m) The height of the center of gravity of the car when the car is full load: hg = 1,115 (m) Compare the recalculation results of some criteria after changing the design Parameter Value Limits apply The biggest dynamic factor Dmax 0,253 No specified Smallest dynamic factor Dmin 0,018 No specified Calculated Vmax velocity (km/h) 112,7 60 Actual Vmax velocity according to the drag coefficient of the road surface (km/h) 112,7 No specified The greatest ability to cross the slope imax (%) 23,5 Maximum permissible slope capability according to grip conditions (%) 50,7 ≥20% No specified Acceleration time (full load) ends 200m 25,5 ≤ 26,4 Comment: The above mentioned dynamic parameters all satisfy Vietnamese standards 09:2011/BGTVT ensuring passenger cars (with bed), after changing the design, can operate well on the road Modeling When the car moves, the entire skeleton is subjected to loads such as the self-weight of the skeleton passenger weight, baggage, the car's inertia brakes suddenly and the inertia force when the car turns around Consider the bearing case of the following components Figure 3D rendering of the rear chassis structure changed www.irjmets.com @International Research Journal of Modernization in Engineering, Technology and Science [2469] e-ISSN: 2582-5208 International Research Journal of Modernization in Engineering Technology and Science Volume:03/Issue:05/May-2021 Impact Factor- 5.354 www.irjmets.com Load exerted on the car floor skeleton Mass of the entire side, roof of passenger car acts on the horizontal beam at the end of the horizontal beams The passenger volume, seats and weight of the horizontal beams are evenly spread across the car floor Figure Results of simulation of deformation caused by load on the chassis Largest displacement: xmax = 1,044 (mm), ymax = 0,374 (mm) Maximum bending stress: max = 41,89 (MPa) < [] = 160 (MPa) Specifications are consistent with Vietnamese regulations 09:2011/BGTVT of the Ministry of Transport, These parameters allow cars to operate well on Vietnam's roads Conclude: Almost with the layout of changing the seat position inside the trunk, it almost does not distort or change the old structure of the car, so there is no need to reinforce the wall frame as well as the ceiling structure III CONCLUSION Improved design of SAMCO PRIMAS KFE6 suspension parts (change of structure, layout of the passenger bed) reduces the vehicle's center of gravity while ensuring the quantity and space of individual passengers safe and comfortable space according to Vietnamese and international passenger car standards Based on the theory of automobile structure, and the process of car movement on the road to calculate and simulate the force exerted on the vehicle's skeleton structure after changing the design with ANSYS tool on the part Inventor soft Comparing the results after optimizing the design has significant improvements over the original design, increasing the static stability coefficient of the passenger car when traveling on the road IV [1] [2] [3] [4] [5] [6] [7] [8] [9] [10] [11] REFERENCES Nguyen Van Phung Automotive theory Industrial University of Ho Chi Minh City Lam Mai Long Textbook of Automotive Motion Mechanics Ho Chi Minh City University of Science and Technology Year 2003 Nguyen Huu Can - Du Quoc Thinh - Pham Minh Thai - Nguyen Van Tai - Le Thi Vang The theory of automobile tractor Hanoi Science and Technology Publishing House In 1998 Nguyen Huu Can - Phan Dinh Kien Design and calculation of automobile tractors episode III Hanoi Professional College and Secondary Publishing In 1985 QCVN9 / 2011- Ministry of Transport's design and improvement of passenger cars Circular 85/2014 / TT-BGTVT issued by the Ministry of BGTVT on December 31, 2014 Nguyen Van Phung The control and motion trajectory of the car Ho Chi Minh City University of Science and Technology BJORN ANDERSSON PATRIC GILLBERG High speed Braking Stability Master’s thesis in Applied Mechanics 2013 VEHICLE DYNAMICS and CONTROL Rajesh Rajamani Mechanical Engineering Series, University of Mechaniacal Engineering 2012 National transportation research center, Incorporated Univesity Transportation center Vehicle Stablity and Dinamics Electronic Stability Control Final Report 2011 Determination of Safety Distance by Simulation and Collision Avoidance on a Road’s Danger Zones by Schreiber Peter, Bartunek Marian and Moravcik Oliver, Slovak University of Technology Bratislava, Trnava SK 917 24, Slovakia www.irjmets.com @International Research Journal of Modernization in Engineering, Technology and Science [2470] ... Impact Factor- 5.354 www.irjmets.com Load exerted on the car floor skeleton Mass of the entire side, roof of passenger car acts on the horizontal beam at the end of the horizontal beams The passenger. .. car movement on the road to calculate and simulate the force exerted on the vehicle''s skeleton structure after changing the design with ANSYS tool on the part Inventor soft Comparing the results... III CONCLUSION Improved design of SAMCO PRIMAS KFE6 suspension parts (change of structure, layout of the passenger bed) reduces the vehicle''s center of gravity while ensuring the quantity and