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1 AVC GOLLEGE OF ENGINEERING. MANNAMPANDAL. DEPARTMENT OF MECHANICAL ENGINEERING
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2 VIBRATION ANALYSIS OF DOUBLE IMPELLER MARINE PUMP USING FEA METHOD GUIDED BY PRESENTED BY Mr.S.VIJAYARAJ.M.E., P.J SENTHIL KUMAR ASST.PROFESSOR, R.NATARAJAN DEPT OF MECHANICAL ENGG T.BALAKRISHNAN K.JEGADESH
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COMPANY PROFILE COMPANY NAME : MACRO ENGINEERING PVT LTD PLACE : CHENNAI. YEAR OF ESTABLISHED: 2003 PRODUCT DESCRIPTION :DESIGN & ANALYSIS
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PUMPS On the basis of transfer of mechanical energy, the pumps can be broadly classified as, Positive displacement Pumps Roto dynamic Pumps The centrifugal pump of today is made by 250 years old evolution. It has now attained a new degree of perfection It is widely used as it can be coupled directly to electric motors, steam turbines etc.
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DOUBLE IMPELLER MARINE PUMP It is a contrivance to boost up liquids in the pipe line by creating the required pressure with the help of centrifugal action. In general it can be defined as a machine which increases the pressure energy of a fluid, as a pump may not be used to lift water at all, but just to boost the pressure in a pipe line
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MARINE PUMP
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APPLICATIONS To pump the salt water from sea to ship for process. To boost up the working fluid between two tanks To pump the back water in the seashore. To pump the water in power plant industries.
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8 PROBLEM DESCRIPTION Vibration is the major problems of all machines and rotating components. In marine pumps It affects the over all efficiency of the pump. Prevention and control of vibrations in pumps is more important point to increase the efficiency of the marine pumps. So it is necessary to find out the vibrations during its operating condition. Determination of the stress and deformation of the already designed double impeller marine pump due to vibrations in the pump if any as prevention control of vibration of machines structure is an important design consideration. For this reason, capacity, head, power consumption are the essential points in double impeller marine pump design.
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9 METHODOLOGY MODELLING – PRO-E WILD FIRE 3.0 MESHING - HYPERMESH 9.0 ANALYSIS - ANSYS 10.0
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10 HARDWARE AND SOFTWARE DESCRIPTION: The following virtual validation is carried on the following hard ware Hardware: HP xw8200 Workstation Processor-Two 64-bit Intel® Xeon™ processor(s) with Hyper-Threading Technology Memory-7 GB of ECC DDR2 400 MHz SDRAM Graphics-NVIDIA Quadro FX 1400 (PCIe)
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11 Software: Preprocessing:Hypermesh9.0 Solver :ANSYS 10.0 Post processing:ANSYS 10.0
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12 INTRODUCTION OF FEA Finite element analysis is a process, which can be used to predict deflection and stress on a structure. In finite element model, the structure is divided in to number of grids, which is called as elements. Each of the elements has a simple shape (such as square or triangle) for which the finite element program has information to write the governing equations in the form of stiffness matrix for the entire model. This stiffness matrix is solved for the unknown displacements at the nodes, the stresses in each element can be calculated.
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13 INTRODUCTION OF FEA The finite element is derived by assuming a form of the equation for the internal strains. The equilibrium equation between the external forces and the nodal displacements can be written. There will be one equation for each degree of freedom for each node of the element. The equation is [K] [U] = [F]
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14 OBJCTIVE OF THE PROJECT Build a detailed finite element model of the impeller assembly Carry out a static Analysis with a single time step Dynamic analysis with response spectrum behavior using corrugated load case.
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INPUT DATA CAD data: 3D Models of pump impeller and the assembly files of ProE wildfire3.0 Loading, boundary conditions and material properties as available in FIAT-GM Power train Italia standards.
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16 METHODOLOGY The model of marine pump was designed by using pro-E software. The designed part assembly is saved as in IGES format The IGES file was imported to hyper mesh. Now the assembled model is ready to be used with hyper mesh for meshing The IGES format meshed model is imported to ansys for taking analysis.(static & Dynamic
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PRO-E MODEL PUMP
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SIDE VIEW OF MARINE PUMP
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19 SPECIFICATIONS OF MARINE PUMP Pump size6” Pump typeRadial flow Pump speed (n)1470 rpm No. of stages (N)2 stages Discharge (Q)114 kg/s Actual head (H)105 m Motor rating200 KW Motor typeWet Voltage 415v
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20 Shaft And Impeller Assembly
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STEPS INVOLVED IN MESHING Model input Problem definition Geometry cleanup Element shape No. of nodes and elements Meshing Preview of meshing Checking of quality index
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23 Material & Loads: Material Young’s Modulus Density Poisson Ratio Yield stress σy Kgf/mm2g/ccKgf/mm2 YST310210007.850.345.0 LOAD Speed = 1470rpm Angular Velocity = 2x3.14x1470/60 = 153.86 rad/sec
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STATIC ANALYSYS
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Deformation-mm Usum - ShaftUx – Impeller and Shaft
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Deformation-mm Uz – Impeller and ShaftUy – Impeller and Shaft
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Deformation-mm Ux – ImpellerUsum – Impeller
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Deformation-mm Uz – ImpellerUy – Impeller
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Deformation-mm Usum – ShaftUx – Shaft
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Deformation-mm Uy – ShaftUz – Shaft
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Stress-Kgf/mm^2 Principle Stress – Shaft
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Stress-Kgf/mm^2 Von Mises Stress – Impeller
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PartDeformation-mm UsumUxUyUz Shaft0.068610.264e-30.068610.926e-3 Impeller3.940.12773.9393.872 Note: Usum, Ux, Uy, Uz are Resultant deformation & deformation in X, Y & Z direction.
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DYNAMIC ANALYSYS
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MODAL ANALYSIS Frequency - Hz 1 st Freq – Hz - Shaft2 nd Freq - Hz- Shaft Vertical Bend - Shaft
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2 nd Freq – Hz - Shaft3 rd Freq - Hz- Shaft Z- Bend - ShaftVertical Bend - Shaft
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4 th Freq – Hz - Shaft5 th Freq - Hz- Shaft Z- Bend - ShaftLocal Bend - Shaft
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6 th Freq – Hz - Shaft1 st Freq – Hz- Impeller & Shaft Local Bend - ShaftVertical Bend - Shaft
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4 th Freq – Hz- Impeller & Shaft 5 th Freq – Hz- Impeller & Shaft Vertical Bend - ShaftZ Bend - Impeller
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6 th Freq - Hz Twist - Impeller
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MODAL ANALYSIS RESULTS FOR 6 MODES FREQUENCY HZDeformation mm minimum Deformation mm maximum 162.7961.878 mm16.904 162.7961.878 mm16.904 435.475-11.46615.34 435.475-11.46615.34 775.888.76578.885 775.888.76578.885
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MODAL ANALYSIS RESULTS In modal analysis results the above following we find, various set of frequencies for shaft with impeller at a speed of 1470 rpm. The frequency ranges from 162.796 to775.88. It does not exceed 1KH. The deformation value is not getting increased beyond 78.885mm with higher frequencies than 775.88Hz Hence the obtained range of vibrations is lesser So that, the performance of the pump will not affected by vibrations.
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Deformation – UsumDeformation – Ux HARMONIC RESPONSE ANALYSIS Deformation Plot
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Deformation – UyDeformation – Uz HARMONIC RESPONSE ANALYSIS Deformation Plot
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Deformation – Usum - ShaftDeformation – Uy - Shaft HARMONIC RESPONSE ANALYSIS Deformation Plot
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Equivalent Stress - Shaft HARMONIC RESPONSE ANALYSIS Stress Plot
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Equivalent Stress - Impeller HARMONIC RESPONSE ANALYSIS Stress Plot
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PartStress- kgf/mm^2 Shaft0.0072 Impeller0.01712 Yield Stress45 FOS2.628 PartDeformation-mm UsumUxUyUz Impeller + Shaft0.411e-30.845e-40.411e-30.206e-5 Note: Usum, Ux, Uy, Uz are Resultant deformation & deformation in X, Y & Z direction. Note: σe – Stress Based on Energy theory (Von Misses Theory); FOS = σy / σe Design FOS 2.00< 2.628 Hence the design is safe in Dynamic load
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HARMONIC RESPONSE ANALYSIS Frequency – Hz Vs Amplitude -mm
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Conclusions: From the foregoing FE analyses & results, the following conclusions are drawn. The result of static analysis under the self weight + speed (1470rpm) are tabulated. It is seen that maximum stresses in the impeller notch. Maximum stresses are within material yield, Design FOS = 2.0, Minimum factor of safety is 2.14.
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In the dynamic analysis the frequencies ranges from 124.42Hz to 775.88Hz. It does not exceed 1 kHz. So the Obtained frequencies during the analysis are within the limit. Hence the obtained range frequency of vibrations is less. So that, the performance of the pump will not be affected by vibrations.
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52 Finally the design is found to be safe from the static and dynamic conditions are well within material yield and meet the design requirements. The analysis is carried out using ANSYS software.
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53 THANK YOU
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