Improved Design And Simulation Research On The Conveyor Of Billet Harvester

Sugarcane is not only an important economic crop in the south of China,but also is one of the main raw materials of sugar production in C hina,which occupies more than 90% of the total sugar in the country.The planting area of sugarcane was about 1.795 million hectares,ranking third in the world.At present,the ratio of sugarcane mechanized harvesting mechanization in C hina was only about 0.7%.It is an urgent problem to be solved in the development of sugar industry in china.Because the technology of sugarcane billet harvesters was more matured,it got more and more attention and recognition from farmers and scientific research units and also gets great development.The function of the elevator of billet harvester was to carry billets to field transporter timely.In view of the existing problems that the end of the blanking position is not accurate and the harvest structural stiffne ss problem in the process of carrying billets,the paper improved design a folded elivator based on the study of literature.Virtual and real prototy tests were conducted.The main contents and conclusions were as follows:(1)Based on the study of literature,a folded elevator was designed and improved.(2)Virtual prototype of elevator was created by the software of ADAMS.Three-dimensional assembly model was created by SolidWorks.Unnecessary parts was removed from the assembly model.Interference detect ion were conducted.The well done assembly model was imported to Adams to get the virtual prototype of elevator.(3)Kinematic model of the elevator was created,simulation and analysis on it were conducted.The kinematic model was created with D-H method.The positive and inverse kinematics solution of the model was solved with theoretical analysis to prove the kinematics solution.(4)The space motion range of the elevator was solved by the combined simulation of Adams and MATLAB.Results was that: the highest point was 6.367 meters,the lowest end of the conveyor was 1.824 meters,the side of which it could reach was 5.991 meters and the close quarters it could reach was 3.557 meters.(5)The static analysis and modal analysis of the elevator were conduc ted based on FEM to get its deformation image,modal shape and modal resonance frequency.The rationality and weak point of its analyzed to provide guidance for the design.Simulation results showed that:The largest stress area of the small arm structure was located on the connection point between the large and small arm.The maximum stress of small arm was 113 MPa,its safety coefficient was 3.14;The maximum stress of the large arm was 225 MPa,its safety coefficient was 1.58;The safety factor is 1.2~1.4,all value met the requirements of structural strength.The location of the maximum deformation amount of the small arm structure was at the end center position.C loser to the end position,the value was larger.The maximum value was 4.24 mm.The maximum deformation of the large arm was at the end of the end of the connection with the small arm.C loser to the end,position,the value was larger.The maximum deformation was 5.3 mm.All deformation was within its tolerance range and satisfied design requirements.The maximum stress position of intermediate connection axis was located in the shoulder.The maximum value was 232 MPa.Its safety coefficient was 1.53.The safety factor is 1.2~1.4,the maximum deformation was at the end of the axis.Its the maximum value was 0.88 mm.All values met its design requirements within tolerance range.(6)Real prototype tests were conducted to verify results of simulation.Results showed that: the stress of the small arm near the intermediate connection axis was maximum and the stress values of other two test positions have little difference.The mean value of overall maximum stress was 104.484 MPa.It was less than 113 MPa,the value of simulation.The minimum stress in the middle of the test point of the three cross sections of the large arm,the maximum stress was in the connection position,it was at the point between the other two test points.The mean value of the maximum test stress was 212.47 MPa.It was less than the simulated value 225 MPa.Compared results of real p rototype tests and virtual tests,the conclusion was as follows: although they were difference,their variation tendency was similar.All the test values of real prototyipe was within the tolerance range of the value of virtual tests.That is,the simulation results were reliable.