Semi Automatic Shrub Cutting Machine

Transcription

1 Semi Automatic Shrub Cutting Machine Prof. Suraj R. Gavali 1, Professor, Department of Mechanical Engineering Dr. D. Y. Patil School Of Engineering, Lohegaon, Charholi (Bk.) Pune Aditya R. Patil 2, U.G Students, Department of Mechanical Engineering Dr. D. Y. Patil School Of Engineering, Lohegaon, Charholi (Bk.) Pune Mahesh D. Karpe 3, U.G Students, Department of Mechanical Engineering Dr. D. Y. Patil School Of Engineering, Lohegaon, Charholi (Bk.) Pune Akshay S. Khedekar 4, U.G Students, Department of Mechanical Engineering Dr. D. Y. Patil School Of Engineering, Lohegaon, Charholi (Bk.) Pune Swapnil D. Bhujbal 5, U.G Students, Department of Mechanical Engineering Dr. D. Y. Patil School Of Engineering, Lohegaon, Charholi (Bk.) Pune ABSTRACT - This paper aims at developing a non-conventional and user friendly mechanism as an alternative to conventional method of shrub cutting. The construction of this mechanism is much easier and its functioning requires less operational efforts as compared to the conventional methods of shrub cutting. This innovation would definitely prove to be a boon in the field of agriculture and in the field of gardening as well. It is well suited when the need for accuracy and maximum work output is to be considered. Also safety of operator can be considered as an added advantage of this innovation. Four wheel driving mechanism has been used for better directional stability and the whole system is actuated with the help of wired remote control system. KEYWORDS Frames, Sliding Mechanism, Motors, Cutter, Remote Control System INTRODUCTION Semi Automatic Shrub Cutting Machine is an innovative and efficient mechanism in today s modern agriculture and gardening fields. The shrubs mainly in gardens can easily be cut to desired height with the help of this machine. Conventional method of shrub cutting takes a lot of time and requires more human effort. The main motto of this project is to increase the work output, reduce the worker fatigue and introduce partial automation. Introducing automation indirectly means, more time saving, better cutting accuracy and better work efficiency. Our aim was to make the system that is easily portable and to make it much lighter in weight so as to get sufficient speed and motion for proper functioning. A Remote control system helps in assisting the system in desired pathway and also helps in providing motion to the motors as well as cutter mechanism. The base supports the vertical structure and the sliding mechanism mounted on it. The driving mechanism under the base also plays a vital role in giving direction to the system and to steer the system to desired position. Motors are easily available and economical to buy. Also they are easy to operate. Thus, the whole system proves to be economical and cost effective when the benefits from it are considered. 1838

2 PROBLEM STATEMENT In many gardens and nurseries small trees are planted on either sides of the road. These plants or shrubs keep on growing in any direction and thus spoils the visual appearance of the garden. These shrubs needs to be cut properly from time to time. But conventional cutting process becomes more tedious and time consuming and also causes worker fatigue. Work output obtained is much lesser as compared to mechanical or automated cutting. Also, lesser accuracy is obtained which indirectly affects the overall work satisfaction. To overcome these problems and to ensure proper growth of the shrubs Semi Automatic shrub cutting machine has been introduced. OBJECTIVES - The objective of this paper is to introduce modern and innovative method for shrub cutting used in gardening and agricultural fields. Following are some objective listed below :- To produce a system with better dimensional accuracy in terms of various cutting and trimming parameters. Mass cutting of shrubs to be possible. Faster in operation. Increase the overall work output and efficiency. Increase worker safety and reduce fatigue. COMPONENTS : A. FRAME : The material used for frame is partly wooden and partly white foam sheet. As we know foam sheets are much lighter in weight it provides an added advantage of reduced weight. The Base on which the whole system is mounted is a wooden ply. The foam sheet constitute of the lifting mechanism (the vertical member) mounted on the wooden base. Fig 1. Frame B. LIFTING MECHANISM : It consists of a rectangular wooden block fitted in the vertical foam member. A metallic wire or string is tied to this block and the other end of this string is attached to the motor. Once the switch in the remote control system switches on the motor shaft rotates and lifts the wooden block and supporting arrangements. 1839

3 Fig 2. Lifting Mechanism C. SLIDING MECHANISM : The horizontal sliding mechanism has the simplified structure consisting of the stainless steel made sliding mechanism usually used in drawers and trolleys. It has much smoother motion and requires minimal force for sliding. Fig 3. Sliding Mechanism. D. MOTORS : We used 4 DC motors with metallic gearbox for driving the system. Each having a speed of 1000 rpm.1 big DC motor with speed of 8000rpm for cutter mechanism. Two small DC motors with plastic gearbox. And 1 big DC motor with metallic gearbox having 500rpm speed used for lifting mechanism. All motors are working on a battery of 12V and 35 amperes. E. Cutter : Type of cutter used is a standard wood cutter. Having diameter of about 200 mm or 20 cm. The material used for cutter is carbide which is heavy duty material and hence possess longer life. 1840

4 Fig 4. Cutter F. DPDT Switch (Remote Control System) : DPDT stands for Double Pole, Double Throw switch. DPDT Switches can control two separate circuits, but are always switched together by a single actuator. Five DPDT Switches has been used in our remote control system. Fig 5.Remote Control System G. WHEELS : Four wheels with driving mechanism are attached to the wooden base. The rotary motion of the wheels is controlled by the remote control system. Fig 6. Wheel 1841

5 H. BATTERY : An automotive battery with rating of 12V and 35 amperes has been used. Pb battery used in four wheelers has been employed for the purpose. Fig 6. Battery DESIGN CALCULATIONS : Fig. Static Structural Fig. Total Deformation Fig. Equivalent Stress Fig. Equivalent Elastic Strain 1842

6 Fig. Life Fig. Safety Factor Project First Saved Last Saved Product Version Save Project Before Solution Save Project After Solution Wednesday, March 14, 2018 Wednesday, March 14, Release 1843

7 Contents o o o o Units Units Model (A4) Geometry upper body-1 o Coordinate Systems o Connections Contacts Mesh Static Structural (A5) Analysis Settings Loads Solution (A6) Solution Information Results Fatigue Tool Results Material Data Structural Steel Unit System TABLE 1 Metric (mm, kg, N, s, mv, ma) Degrees rad/s Celsius Model (A4) Geometry Angle Rotational Velocity Object Name Temperature State Degrees rad/s Celsius TABLE 2 Model (A4) > Geometry Geometry Fully Defined Definition Source Type Length Unit Element Control C:\Users\Dell\AppData\Local\Temp\WB_DELL- PC_Dell_4296_2\unsaved_project_files\dp0\SYS-1\DM\SYS-1.agdb Design Modeler Meters Program Controlled 1844

8 Display Style Length X Length Y Body Color Bounding Box mm mm Length Z Volume mm Properties e+006 mm³ Mass kg Scale Factor Value 1. Statistics Bodies 1 Active Bodies 1 des 9155 Elements 4250 Mesh Metric Parameters ne Basic Geometry Options Parameter Key DS Attributes Named Selections Material Properties Use Associativity Advanced Geometry Options 1845 Coordinate Systems Reader Mode Saves Updated File

9 Use Instances Smart CAD Update Compare Parts On Update Attach File Via Temp File Temporary Directory C:\Users\Dell\AppData\Local\Temp Analysis Type 3-D Decompose Disjoint Geometry Enclosure and Symmetry Processing Object Name TABLE 3 Model (A4) > Geometry > Parts State Graphics Properties Visible upper body-1 Meshed Transparency 1 Definition Suppressed Stiffness Behavior Coordinate System Reference Temperature Material Flexible Default Coordinate System By Environment 1846

10 Assignment Structural Steel nlinear Effects Thermal Strain Effects Bounding Box Length X mm Length Y mm Length Z mm Properties Volume e+006 mm³ Mass kg Centroid X mm Centroid Y mm Centroid Z mm Moment of Inertia Ip1 1.08e+006 kg mm² Moment of Inertia Ip e+005 kg mm² Moment of Inertia Ip e+005 kg mm² Statistics des 9155 Elements Mesh Metric 4250 ne Coordinate Systems TABLE 4 Model (A4) > Coordinate Systems > Coordinate System Object Name Global Coordinate System State Definition Type Fully Defined Cartesian Coordinate System ID 0. Origin Origin X 0. mm Origin Y Origin Z 0. mm 0. mm 1847

11 Directional Vectors X Axis Data [ ] Y Axis Data [ ] Z Axis Data [ ] Connections TABLE 5 Model (A4) > Connections Object NameConnections Auto Detection Fully StateDefined Generate Automatic Connection On Refresh Transparency Enabled TABLE 6 Model (A4) > Connections > Contacts Object Name Contacts State Fully Defined Definition Connection Type Contact Scope Scoping Method Geometry Selection Geometry All Bodies Auto Detection Tolerance Type Slider 1848

12 Tolerance Slider 0. Tolerance Value mm Use Range Face/Face Face/Edge Edge/Edge Priority Include All Group By Bodies Search Across Bodies Mesh 1849 TABLE 7 Model (A4) > Mesh Object Name Mesh State Solved Defaults Physics Preference Mechanical Relevance 0 Sizing Use Advanced Size Function Off Relevance Center Coarse Element Size Default Initial Size Seed Active Assembly Smoothing Medium Transition Fast Span Angle Center Coarse Minimum Edge Length mm Inflation Use Automatic Inflation ne Inflation Option Smooth Transition Transition Ratio Maximum Layers 5 Growth Rate 1.2

13 Inflation Algorithm Pre View Advanced Options Patch Conforming Options Triangle Surface Mesher Program Controlled Patch Independent Options Topology Checking Advanced Number of CPUs for Parallel Part Meshing Program Controlled Shape Checking Standard Mechanical Element Midside des Program Controlled Straight Sided Elements Number of Retries Default (4) Extra Retries For Assembly Dimensionally Rigid Body Behavior Reduced Mesh Morphing Disabled Defeaturing Pinch Tolerance Please Define Generate Pinch on Refresh Automatic Mesh Based Defeaturing On Defeaturing Tolerance Default Statistics des 9155 Elements 4250 Mesh Metric ne Static Structural (A5) Object Name State Definition Physics Type Analysis Type TABLE 8 Model (A4) > Analysis Static Structural (A5) Solved Structural Static Structural Solver Target Mechanical APDL Options Environment Temperature 22. C Generate Input Only 1850

14 Object Name TABLE 9 Model (A4) > Static Structural (A5) > Analysis Settings Analysis Settings State Step Controls Number Of Steps 1. Current Step Number 1. Fully Defined Step End Time 1. s Auto Time Stepping Solver Type Program Controlled Solver Controls Program Controlled Weak Springs Program Controlled Large Deflection Off Inertia Relief Generate Restart Points Retain Files After Full Solve Newton-Raphson Option Restart Controls Program Controlled nlinear Controls Program Controlled Off Force Convergence Program Controlled Moment Convergence Program Controlled 1851

15 Displacement Convergence Program Controlled Rotation Convergence Program Controlled Line Search Program Controlled Stabilization Output Controls Off Stress Strain dal Forces Contact Miscellaneous General Miscellaneous Store Results At Solver Files Directory Future Analysis All Time Points Analysis Data Management C:\Users\Dell\AppData\Local\Temp\WB_DELL- PC_Dell_4296_2\unsaved_project_files\dp0\SYS-1\MECH\ ne Scratch Solver Files Directory Save MAPDL db Delete Unneeded Files nlinear Solution 1852

16 Solver Units Solver Unit System Active System nmm TABLE 10 Model (A4) > Static Structural (A5) > Loads Fixed Object Name Support Force State Fully Defined Scope Scoping Method Geometry Selection Geometry 1 Face Definition Fixed TypeSupport Force Suppressed Define By Components Coordinate Global Coordinate System System X Component 0. N (ramped) Y Component 10. N (ramped) Z Component 0. N (ramped) FIGURE 1 Model (A4) > Static Structural (A5) > Force 1853

17 Solution (A6) TABLE 11 Model (A4) > Static Structural (A5) > Solution Object Name Solution (A6) State Solved Adaptive Mesh Refinement Max Refinement Loops 1. Refinement Depth 2. Information Status Done TABLE 12 Model (A4) > Static Structural (A5) > Solution (A6) > Solution Information Object Name Solution Information State Solved Solution Information Solution Output Solver Output Newton-Raphson Residuals 0 Update Interval Display Points 2.5 s All FE Connection Visibility Activate Visibility Display Draw Connections Attached To Line Color Visible on Results Line Thickness Display Type All FE Connectors All des Connection Type Single Lines 1854

18 TABLE 13 Model (A4) > Static Structural (A5) > Solution (A6) > Results Object Name Total Deformation Equivalent Stress Equivalent Elastic Strain State Scoping Method Solved Scope Geometry Selection Geometry Type Total Deformation All Bodies Definition Equivalent (von-mises) Stress Equivalent Elastic Strain By Time Display Time Calculate Time History Last Identifier Suppressed Results Minimum 0. mm e-011 MPa e-016 mm/mm Maximum mm MPa e-005 mm/mm Minimum Value Over Time Minimum 0. mm e-011 MPa e-016 mm/mm Maximum 0. mm e-011 MPa e-016 mm/mm Maximum Value Over Time Minimum mm MPa e-005 mm/mm Maximum Time mm MPa e-005 mm/mm Information 1. s Load Step 1 Substep 1 Iteration Number 1 Integration Point Results Display Option Averaged Average Across Bodies 1855

19 TABLE 14 Model (A4) > Static Structural (A5) > Solution (A6) > Fatigue Tools Object Name Fatigue Tool State Solved Materials Fatigue Strength Factor (Kf) 1. Loading Type Fully Reversed Scale Factor 1. Definition Display Time End Time Options Analysis Type Stress Life Mean Stress Theory ne Equivalent (Von Stress Component Mises) Life Units Units Name cycles 1 cycle is equal to 1. cycles FIGURE 2 Model (A4) > Static Structural (A5) > Solution (A6) > Fatigue Tool 1856

20 FIGURE 3 Model (A4) > Static Structural (A5) > Solution (A6) > Fatigue Tool TABLE 15 Model (A4) > Static Structural (A5) > Solution (A6) > Fatigue Tool > Results Object Name Life Safety Factor 1857 State Scoping Method Geometry Definition Scope Solved Geometry Selection All Bodies Type Life Safety Factor Identifier Suppressed Design Life Integration Point Results Average Across Bodies Minimum Results 1.e+009 cycles 1.e+006 cycles > 15

21 Material Data Structural Steel TABLE 16 Structural Steel > Constants Density Coefficient of Thermal Expansion 7.85e-006 kg mm^-3 1.2e-005 C^-1 Specific Heat 4.34e+005 mj kg^-1 C^-1 Thermal Conductivity 6.05e-002 W mm^-1 C^-1 Resistivity 1.7e-004 ohm mm TABLE 17 Structural Steel > Compressive Ultimate Strength Compressive Ultimate Strength MPa 0 TABLE 18 Structural Steel > Compressive Yield Strength Compressive Yield Strength MPa 250 TABLE 19 Structural Steel > Tensile Yield Strength Tensile Yield Strength MPa 250 TABLE 20 Structural Steel > Tensile Ultimate Strength Tensile Ultimate Strength MPa 460 TABLE 21 Structural Steel > Isotropic Secant Coefficient of Thermal Expansion Reference Temperature C 22 TABLE 22 Structural Steel > Alternating Stress Mean Stress 1858 Alternating Stress MPa Cycles Mean Stress MPa

22 e e e TABLE 23 Structural Steel > Strain-Life Parameters Strength Strength Ductility Ductility Cyclic Strength Coefficient MPa Exponent Coefficient Exponent Coefficient MPa Cyclic Strain Hardening Exponent TABLE 24 Structural Steel > Isotropic Elasticity Temperature C Young's Modulus MPa Poisson's Ratio Bulk Modulus MPa Shear Modulus MPa 2.e e TABLE 25 Structural Steel > Isotropic Relative Permeability Relative Permeability

23 CALCULATION OF ACTUAL FORCE AND OTHER RELATIVE PARAMETERS : A) CUTTER CALCULATION: Maximum force acting on shrub for cutting the leaves = maximum load sustained by the leaves Gravitational force F= mg=2 9.81= N, Hence strength of the shrub is N. B) DESIGN OF UPPER MOTOR: Let the torque on cutter motor = 2kg approx Ta, Nm We are using 8000 rpm motor for cutting mechanism. Total Torque, T = 2 Ta = = Nm P = KW Cutter motor Of 8000rpm. = C) WHEELS: Assume total Weight of the body = 10kg Weight on each wheel = 2.5 kg We selected wheel diameter = 100 mm These wheels is capable for 2.5 kg so we selected rubber wheel. = 10 4 = 2.5 WORKING : Fig. WORKING PRINCIPLE OF MOTOR 1860

24 Fig. Designed CAD Model The system consists of total eight motors as discussed above. Function of each motor differs according to their role ie. Whether it is used to achieve speed or to work under the given payload. (Example. Lifting and driving mechanism). When the connections are connected to the battery and when the switch on the remote control system is pressed, the current start to flow from battery to the motors. Further controls of the remote control system allow the user to run the desired motion as per his needs. For example a switch corresponding to the cutter mechanism is pressed, it rotates the cutter and so on. Simultaneously, the switches for steering mechanism will allow steering of the system as required by the user. The user may adjust the height of the cutter as per the cutting height of shrubs is required. Fig. Actual Fabricated Setup CONCLUSION : Thus, a system featuring complete/partial automation in the field of shrub cutting has been developed. There are numerous challenges being faced in conventional shrub cutting methods. But the one using automation seems to be more efficient and cost effective. Hence, this paper focussed on development of automation in shrub cutting techniques and we hope that future modifications and innovations related to this idea would prove to be a blessing to the society and help mankind to a greater extent. 1861

25 FUTURE SCOPE : This system can be effectively applied in the field of gardening and on domestic level easily. Also, the space required for this machine is much lesser as compared to other equipments. Further modifications in the system may increase the level of automation by use of wireless remote control systems. ACKNOWLEDGMENT: We would like to thank Mr. Suraj Ramesh Gavali, Professor of department of Mechanical Engineering, Dr. D. Y. Patil School Of Engineering College, Charholi (bk.), Pune, Maharashtra for his valuable support and guidance to develop this paper. REFERENCES 1. Chaitanya Tambe, Ganesh Malle, Utkarsha Deore, Akshay Parandkar, Automatic Road Divider Shrub Leaf Cutting Machine, IJARIIE-ISSN(O) , Vol-3 Issue Kriti Shrivastava, Prof M.D Pawar, A Review on Types of DC Motors and the Necessity of Starter for Its Speed Regulation, International Journal of Advanced Research in Computer and Communication Engineering Vol. 5, Issue 4, April K. V. Muralidhar sharma and Vishal Yadav, Comparison of batteries in automotives, International Journal of Advanced Research (2016), Volume 4, Issue 4, Bansode S. P., Gaikwad A. A., Salgude P. S., Tiwari T. D., Prof. Avhad N.V., Prof. BhaneA.B., "Zero Turn Vehicle" International Journal Of Emerging Technology And Advanced Engineering, March-2015,Page Design Of Machine Elements by V.B.Bhandari. 6. Jovan Vladić* - Petar Malešev Rastislav Šostakov - Nikola Brkljač, University Of vi Sad, Faculty Of Technical Sciences, Serbia, Dynamic Analysis Of The Load Lifting Mechanisms, Strojniški Vestnik - Journal Of Mechanical Engineering, July-2008,Page Shirsath Sachin, Jadhav Kiran, Patil Rahul, Mohite Abhilash,D.D. Patil, "Study Of Zero Turn Vehicle", International Journal Of Advanced Technology In Engineering And Science,March-2016,Page Er. Amitesh Kumar, Dr.Dinesh.N.Kamble," Zero Turn Four Wheel Stearing System",International Journal Of Scientific & Engineering Research, Issue 12, December-2014.Page