Rev. Téc. Ing. Univ. Zulia. Vol. 39, Nº 5, 95-100, 016 doi:10.1311/001.39.5.14 Dynamic Analysis a Simulation on Planetary Gear Transmission of Corn Harvester TFuxiang Xie T School of Mechanical-electronic a Vehicle Engineering, Weifang University, Weifang61061,Shaong, China Jian Song School of Mechanical-electronic a Vehicle Engineering, Weifang University, Weifang61061,Shaong, China Haoyu Jiang 1, 1. School of Mechanical-electronic a Vehicle Engineering, Weifang University, Weifang61061,Shaong,China. College of Engineering, Heilongjiang Bayi Agricultural University, Daqing 163319, Heilongjiang,China Abstract At the beginning, overall structure of corn combine harvester planetary gear transmission is designed optimization by Pro/E software, a makes the calculation of sun gear a a planetary gear a a planetary gear a the inner between meshing force theory, a by using ADMAS of corn combine harvester planetary gear transmission movement process simulation analysis, to sum up the laws of motion. Sun gear, a planetary gear one between the meshing force is 140.38N; the sun gear, a planetary gear two between the meshing force is 1359.51N; the sun gear, a planetary gear between the meshing force is 191.10N. Simulation test results show that the force is 1034.6N meshing planetary gear one a between the inner rings; the planet gear between two a inner meshing force is 981.09N; planetary gear three a the inner ring between the meshing force is 904.3N. Key words:corn Harvester; Planetary Gear; Pro/E. 1. INTRODUCTION Corn is an important crop, the current domestic corn production mechanization level is relatively backward, the urgent need for the development of agronomic corn combine harvester technology to further enhance the entire corn harvest mechanization technology(gosselin,1990;gosselin a Merelet,1994). However, corn combine harvester transmission of this key technology to become one of the main factors that limit the development of China's corn harvest mechanization(fang Yong-long a Zhang Boying,000;Li a Wu,015;Jiao a Yang,015). Mostly foreign corn harvester transmission is the more mature technology for the use of self-propelled agricultural machinery a engineering machinery(senthil Kumar a Muni,008; Tong a Walton,1987), while China corn combine harvester transmission focused on the technical aspects of the hydraulic continuously variable transmission studies. Through the above literature analysis, the planetary gear transmission on the corn harvester application is not much literature. Planetary gear mechanism of corn harvester transmission was studied the kinetic analysis in this paper. Through virtual prototyping software focus on studying engagement force a movement of the gear between each pair, a providing a theoretical basis for the optimization design of the whole corn combine harvester.. STRUCTURE AND WORKING PRINCIPLE OF THE TRANSMISSION Transmission of corn harvester was mainly composed of two parts of the planetary gear transmission mechanism a control components(xi a Zhou,015;Liu a Liu,010;Liao a Ma,015;Xu a Liu,015). Structure on planetary gear mechanism was composed of three main parts of the input shaft, the planetary gear mechanism a the output shaft. Each parts on planetary gear transmission of corn combine harvester was designed a focused on parametric in the paper, established modeling by Pro/E software based on the determined size parameters for each component, assembled for the use the way to self- inside to out, a finally the model self-test, to ensure proper engagement between the various components, as shown in Figure 1. Structural principle of corn combine harvestertransmission is based on the existing planetary gear transmission mechanism, the use of alternating of double clutch, thereby completing the work. Each clutch are connected to the odd gears, the biggest difference was that a hollow shaft was connected with the clutch, a 95
Rev. Téc. Ing. Univ. Zulia. Vol. 39, Nº 5, 95-100, 016 otherclutch wasconnected withsolid shaft.whenever one of the gear was in working coition, the other clutch was a clutch state, a achieved uninterrupted power transmission conversion. The power transmission performance optimization a upgrading. Figure1. Structure on corn combine harvester transmission(1. input shaft;. the planetary gear mechanism; 3. output shaft). In order to switch between different stalls on the planetary gear transmission of corn harvester, the transmission gear needs to be designed. In this paper, dynamic analysis of the planetary gear mechanism was mainly composed of the planetary gear one, the inner ring gear, sun gear, the planetary gear two a the planetary gear three a so on, as shown in Figure. Working principle of the planetary gear transmission is that planetary gear was driven by the sun gear, a engagement between planet gears a the inner ring gear, to achieve motion transmission. Sun gear teeth number designed on the planetary gear transmission of corn combine harvester was 37 in this paper, the number of teeth of the planetary gear was 19, a the number of teeth of the inner ring gear was 75. At the same time meshing force of each pair of gears was studied kinetic analysis, the analysis was mainly two parts for engaging force between the sun gear a three planetary gear a engaging force between three planetary gear a the inner ring. A the meshing of gears in both cases were compared, one for theoretical models, that is, between the gears meshing theory model of computing; the other is the dynamic simulation analysis, that is in each of the gear add contact force, which each gear results was compared with the theoretical value for the engaging force. Figure. Planetary gear mechanism(1. the planetary gear one;. inner ring gear; 3. sun gear; 4. the planetary gear two; 5. the planetary gear three). 3. KEY TECHNOLOGIES OF TRANSMISSION 3.1. Degrees of Freedom Degrees of freedom on the planetary gear transmission of corn combine harvester was calculated by according to the following formula: w 3n p p (1) l h 96
Rev. Téc. Ing. Univ. Zulia. Vol. 39, Nº 5, 95-100, 016 Formula (1): n was the motion member of corn harvester transmission, pl was the number on low motion deputy of corn harvester transmission, p was the number on high motion deputy of corn harvester transmission. h h p = K in the planetary transmission of corn combine harvester, was substituted into the formula (1) obtained: Formula (): n0 was the number of basic components, a planetary line number was k. w n k () 3..Number of control elements Suppose that the number of degrees of freedom in the use of the planetary gear transmission corn combine harvester was W(Zhou Bing a Jiang Qinghua,011). Corn harvester planetary gear transmission was engaged to obtain a degree of freedom of the planetary gear, therefore, the need to eliminate the number of degrees of freedom was W-1. Control element number m in corn harvester transmissions are calculated a according to the following formula: o Formula (3): M was the number of the brake; L was the number of the clutch. m ZL(3) 3.3.Number of transmission gear Transmission gear number of the transmission corn combine harvester was n d, the number of combinations while being controlled transmission element number m was selected (W-1), according to the following inequality to determine the transmission gear number: (1) when m = W, from expression (4) can be obtained: () when m> W, from expression (4) can be obtained: In this case W = 3 or In this case W = 4. When W = 5,6,7..... when, a so on. Thus, in general, the control element number M: W -1 m C (4) ( n-w 1)( w-1 ) w-1 m! C m (5) m ( m-1 )! mm ( 1) C >m (6) m 3 ((m-1) )(m-)) C >m (7) m 3! M W (8) 3.4.Transmission ratio K-H (A) was Used in the row as part in the planetary gear transmission of corn combine harvester(zhaohan a FengYongkai,015). Each member of planetary line on speed equation was: na 1 p1nb 1 (1 p1 ) nh1 0 n a pnb (1 p ) nh 0 (9) n (1 ) 0 ak pknbk pk nhk Formula (9): na, nb, nh was speed of each planetary gear. p was coefficients for the various planetary line, that is: p =ZBb B/ZBa B(10) formula (10):the number of the center gear teeth was Za, the number of teeth of the inner gear was Zb. 97
was Rev. Téc. Ing. Univ. Zulia. Vol. 39, Nº 5, 95-100, 016 3.5.Engaging Force Planetary gear mechanism meshing force between the gears in the planetary gear transmission of corn harvester was primarily the planet gear a sun gear, a meshing force planetary gear a the inner ring gear(chen Yuxiang a Zang Mengyan,01). Engaging force between the sun gear a three planetary gear were calculated according to the following formula: 95.5 10 Fs n d F ' s 5 F tan Fs Fs " cos s 1 1 1 P (11) Formula (11): P was the input power, Kw; n was the input rotational speed, r/min; d B B1 the diameter of the pitch circle of the driving gear, mm; engagement angle of the sun gear a the planetary gear was α1. Three planetary gear engaging force with the inner ring gear in the planetary gear transmission of corn combine harvester was F p 95.5 10 N n d 5 F ' F tan p p Fp Fp " cos P (1) In the formula (1), P was the input power, Kw; n was the input rotational speed, r/min; the number of planetary gear in the planetary gear transmission of corn combine harvester was N; d BB was the diameter of the pitch circle of the driving gear; engagement angle between planetary gear a the ring gear was αb B. 4. SIMULATION TEST 4.1.Pre-treatment Simulation After making sure to working principle on the planetary gear transmission of corn combine harvester, in order to further verify the above design planetary gear mechanism whether to complete the design goals, simulate its motion state, a the movement of summary. ADAMS simulation software was used in this paper. Firstly, save the model into ADAMS / View, a then click Add rotating pair to each part, then for each rotation vice to add drivers, set the simulated input speed was 6000 / s. The virtual prototype model was established by ADAMS software about the planetary gear transmission of corn harvester, as shown in Figure 3. Figure3. virtual prototype 4.. Simulation Method (1) In order to study movement on planetary gear mechanism of corn harvester planetary gear transmission, the following assumptions: each member is a rigid body; during movement, without considering the impact was brought about by deformation of each member. 98
Rev. Téc. Ing. Univ. Zulia. Vol. 39, Nº 5, 95-100, 016 () Virtual prototype model was simulated by performing in the ADAMS software, the entire movement focuses on the process of the planetary gear mechanism, engaging force mainly studied the sun gear a three planetary gears a inner ring gear a three planetary gears. 4.3.Simulation results a analysis Between the sun gear a three planet gears a three planetary gears a inner ring gear to add contact definition, simulated to add pair gears a gear to add the contact force during the movement on magnitude of the force. After adding the rotating pair a add the contact force, engaging dynamics simulation between sun gear a the three planetary gears was shown in Figure 4. Engaging dynamics simulation results was shown in Figure 5 between the three planetary gears a the inner ring gear. Figure4. Dynamic Analysis between sun gear a the three planetary gears According to Figure 4 a Figure 5 can be drawn between the kinetic changes of engaging the sun gear a three planetary gears a three planetary gears a the inner ring gear. according to the test results analysis in Figure 4, engaging force between the sun gear a three planetary gears at the beginning of contact with the largest maximum value was 3548.67N. Calculated according to the formula engaging force on planetary gear transmission of corn harvester gears between the theoretical value a simulation value. Dynamics simulation results show that sun gear a three planetary gears, the engaging force between the sun gear a a planetary gear was 140.38N; engagement force between the sun gear a the planetary gear two was 1359.51N; a engaging force between the sun gear a the planet wheel three was 191.10N. Figure 5 shows the maximum value of the planetary gear a inner ring gear maximum value was 3851.13N. Dynamics simulation results show that three planetary gears meshing with the inner gear, engaging force between planetary gear one a the inner ring gear was 1034.6N; engaging force between the planetary gear two a the inner ring gear was 981.09N ; engaging force between planetary gear wheel three a the inner ring gear was 904.3N. The tre of engagement force of the sun gear a three planetary gear a three planetary gears a the inner ring gear was getting smaller a smaller. Engaging force between the sun gear a the planetary gear meshing force is larger than the planet gear a the inner ring gear. 5. CONCLUSIONS Figure5. Kinetic analysis between the inner ring gear a the three planetary gears (1) Structural on the planetary gear transmission of corn harvester was designed by the use of Pro/E threedimensional design software, through ADAMS software movement planetary dynamics were analyzed, a two 99
Rev. Téc. Ing. Univ. Zulia. Vol. 39, Nº 5, 95-100, 016 types of engaging force between the sun gear a the three planet gears a three planetary gears amd the ring gear were analyzed. () for the engagement force of state theory a simulation state, analysis a comparison, the meshing of gears are basically the same, the error range is small. Virtual prototype model to meet the requirements of practical application for the next whole corn harvester was designed to provide research basis for analysis. (3) The simulation results show that the engagement force between the sun gear a planetary gear one was 140.38N; engagement force between the sun gear a the planetary gear two was 1359.51N; engaging force between the sun gear a the planet gear three was 191.10N. Engaging force between the planet gear one a the inner ring gear was 1034.6N; engaging force between the planet gear a the inner ring gear two was 981.09N; engaging force between the inner ring gear a the planet gear three was 904.3N. Acknowledgements This work was supported by Project of National NaturalScience Fouation(No.51505337) a Project of Natural Science Fouation of Shaong Province(No.ZR014EEP013). REFERENCES Gosselin C.M., Angeles J.(1990) Singularity analysis of close-loop kinematics chains,transaction on Robotics a Automation, 6(3),pp.81-90. Gosselin C.M.,Merelet J P. (1994) On the direct kinematics of planar parallel manipulators: special a chitectures a number of solutions,mechanism a Machine Theory, 9(8),pp.1083-1097. Fang Yong-long, Zhang Boying, Dong Xiuguo, et.al.(000) Analysis of the Hydraulic Control System for Metal Type CVT,Natural Science Journal of Jilin University of Technology,30(3),pp.14-19. Li Di, Wu Guangqiang,Wu Huwei(015) Multi-body Dynamics Modeling a Analysis of Transmission Gear Rattle,Journal of Mechanical Transmission,39(1),pp.64-68. Jiao Wanming,Yang Jue,Ma Fei(015) Equal Strength Optimal Design of Planetary Gear Transmission. Transactions of the Chinese Society of Agricultural Machinery,46(1),pp.359-364. V.Senthil Kumar, D.V.Muni, G.Muthuveerappan(008) Optimization of asymmetric spur gear drives to improve the being load capacity, Mechanism a Machine Theory, 43(7),pp.89-858. B.S.Tong, D.Walton(1987) The optimization of internal gears,international Journal of Machine Tools a Manufacture, 7(4),pp.491-504. Xi Zhiqiang, Zhou Zhili.(015) Application Status a Technical Analysis of Automatic Transmission on Tractor,Journal of Mechanical Transmission,39 (06),pp.187-195. Liu Zhenjun,Liu Fei(010) Three-Dimensional Modeling a Simulation of the Dual Clutch Transmission, Journal of Mechanical Transmission, 34(6),pp.6-30. Liao Linqing,Ma Anpeng,Zhang Jun, et.al.(015) Analysis of Key Techniques a Application Prospect of Dual Clutch Transmission,Journal of Mechanical Transmission, 39(6),pp.196-199. Xu Liyou,Liu Hailiang,Wei Mingliang(015) Modeling a Simulation of Dual Clutch Automatic Transmission Triving System for Tractor,Journal of Agricultural Mechanization Research, 37(11),pp.36-4. Zhou Bing,Jiang Qinghua,Yang Yi(011) Transmission Ratio Optimization with Dual Objectives of Power Performance a Economy for a Two-speed Electric Vehicle,Automotive Engineering,33(9),pp.79-797 ZhaoHan,FengYongkai,HuangKang(015) TransmissionRatioIntervalOptimizationforElectricVehicle, China Mechanical Engineering,6(5),pp.698~703. Chen Yuxiang,Zang Mengyan,Chen Yong, et.al.(01) Shift force analysis of manual transmission based on virtual prototyping technology,chinamechanicalengineering, 3(8),pp.996-1000. 100