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internship exam ppt.pptx on embedded system and IOT
internship exam ppt.pptx on embedded system and IOT
RM&IPR M5 notes.pdfResearch Methodolgy & Intellectual Property Rights Series 5
RM&IPR M5 notes.pdfResearch Methodolgy & Intellectual Property Rights Series 5
Lecture17
1.
Lecture 17:Axisymmetric Problems APL705 Finite Element Method v18
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Axisymmetric Solids • The solids with an axis of symmetry or solids of revoluDon with axisymmetric loading (and support) are modeled as simple 2D elements. As seen from the figures below all stresses are independent of rotaDonal angle. Eg. Flywheel, bearing, thick-walled pressure vessels
3.
CondiDon for Axisymmetric Problems 1. The problem domain must have an axis of symmetry. It is customary to align this symmetry axis with the z-axis of the cylindrical (r,θ,z) coordinate system. 2. The boundary condiDons are symmetric about the axis. Therefore all BCs are independent of θ 3.
All loading condiDons are symmetric about z hence these are also independent of circumferenDal direcDon θ 4. Also, the material properDes must be homogeneous or symmetric. This condiDon always saDsfied for isotropic materials 5. Lastly, the soluDons are independent of θ
4.
Axisymmetric as Special 2D Problems • Where there is symmetry in geometry and loads we can model such problems as special two-dimensional problems. •
5.
Axisymmetric FormulaDon • Consider the elemental volume shown here. Now we write the potenDal energy in axisymmetric form • Here we note that all integrals are independent of θ •
where π = 1 2 σ T ε A ∫ rdAdθ 0 2π ∫ − uT f A ∫ rdAdθ 0 2π ∫ − uT Tr L ∫ dl dθ 0 2π ∫ − ui T i ∑ Pi π = 2π 1 2 σ T ε A ∫ rdA − uT f A ∫ rdA − uT Tr L ∫ dl ⎛ ⎝ ⎜ ⎞ ⎠ ⎟ − ui T i ∑ Pi u =[u,w]T ; f =[ fr, fz ]T ; T =[Tr,Tz ]T
6.
Stress Strain RelaDons • We can write strains for this case as • Using derivaDves of displacements this can be wrien as •
The stress vector for this case is • Now the stress-strain relaDon is given as where D is ε =[εr,εz,γrz,εθ ] ε = ∂u ∂r , ∂w ∂z , ∂u ∂z + ∂w ∂r , u r ⎡ ⎣⎢ ⎤ ⎦⎥ σ =[σr,σz,τrz,σθ ] σ = Dε D = E(1−ν) (1+ν)(1− 2ν) 1 k 0 k k 1 0 k 0 0 s 0 k k 0 1 ⎡ ⎣ ⎢ ⎢ ⎢ ⎢ ⎤ ⎦ ⎥ ⎥ ⎥ ⎥ ;k = ν 1−ν ;s = 1− 2ν 2(1−ν)
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Axisymmetric Galerkin FormulaDon • The Galerkin formulaDon for an axisymmetric modeling can be given as • Here the strain vector is given as 2π
σ T ε(φ) A ∫ rdA −(2π φT f A ∫ rdA + 2π φT Tr L ∫ dl + φi T i ∑ Pi ) = 0 φ =[φr,φz ]T ε(φ) = ∂φr ∂r , ∂φz ∂z , ∂φr ∂z + ∂φz ∂r , φr r ⎡ ⎣ ⎢ ⎤ ⎦ ⎥ T
8.
Axisymmetric Modeling using Triangular Elements • The area of axisymmetry is now divided into triangular finite elements. By revolving these elements we actually get the discreDzed solid object. Therefore though each element is a triangle, it actually represents a solid ring of triangular secDon about the axis of symmetry. • Following the discussion on CST and replacing x, y coordinates with r,z we have a similar formulaDon now. Using 3 shape funcDon N1, N2 and N3 we write
{u}=[N]{q} where N = N1 0 N2 0 N3 0 0 N1 0 N2 0 N3 ⎡ ⎣ ⎢ ⎢ ⎤ ⎦ ⎥ ⎥ q =[q1 ,q2,q3,q4,q5,q6 ]T
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Axisymmetric - Isoparametric FormulaDon • We can write the displacements in r and z direcDons as • The same funcDons are used to interpolate the r, z coordinates also in the isoparametric formulaDon u=(q1
−q5)ξ +(q3 −q5)η+q5 v =(q2 −q6 )ξ +(q4 −q6 )η+q6 r =(r1 −r3)ξ +(r2 −r3)η+r3 z =(z1 −z3)ξ +(z2 −z3)η+z3
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CalculaDng Strains • The strain relaDon is converted to a matrix form • Here the (2x2) matrix is the Jacobian of transformaDon, J •
On taking the derivaDves we have ∂u ∂ξ ∂u ∂η ⎧ ⎨ ⎪ ⎪ ⎩ ⎪ ⎪ ⎫ ⎬ ⎪ ⎪ ⎭ ⎪ ⎪ = ∂r ∂ξ ∂z ∂ξ ∂r ∂η ∂z ∂η ⎡ ⎣ ⎢ ⎢ ⎢ ⎢ ⎢ ⎤ ⎦ ⎥ ⎥ ⎥ ⎥ ⎥ ∂u ∂r ∂u ∂z ⎧ ⎨ ⎪ ⎪ ⎩ ⎪ ⎪ ⎫ ⎬ ⎪ ⎪ ⎭ ⎪ ⎪ J = ∂r ∂ξ ∂z ∂ξ ∂r ∂η ∂z ∂η ⎡ ⎣ ⎢ ⎢ ⎢ ⎢ ⎢ ⎤ ⎦ ⎥ ⎥ ⎥ ⎥ ⎥ J = r13 z13 r23 z23 ⎡ ⎣ ⎢ ⎢ ⎤ ⎦ ⎥ ⎥
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Element Strains • Using the definiDon of J we have • The inverse transformaDon of the above is •
where J-1 is the inverse of J given by ∂u ∂r ∂u ∂z ⎡ ⎣ ⎢ ⎢ ⎢ ⎢ ⎤ ⎦ ⎥ ⎥ ⎥ ⎥ = J−1 ∂u ∂ξ ∂u ∂η ⎡ ⎣ ⎢ ⎢ ⎢ ⎢ ⎢ ⎤ ⎦ ⎥ ⎥ ⎥ ⎥ ⎥ ∂u ∂ξ ∂u ∂η ⎧ ⎨ ⎪ ⎪ ⎩ ⎪ ⎪ ⎫ ⎬ ⎪ ⎪ ⎭ ⎪ ⎪ = J ∂u ∂r ∂u ∂z ⎧ ⎨ ⎪ ⎪ ⎩ ⎪ ⎪ ⎫ ⎬ ⎪ ⎪ ⎭ ⎪ ⎪ ∂w ∂r ∂w ∂z ⎡ ⎣ ⎢ ⎢ ⎢ ⎢ ⎤ ⎦ ⎥ ⎥ ⎥ ⎥ = J−1 ∂w ∂ξ ∂w ∂η ⎡ ⎣ ⎢ ⎢ ⎢ ⎢ ⎢ ⎤ ⎦ ⎥ ⎥ ⎥ ⎥ ⎥ J−1 = 1 detJ r13 −z13 −r23 z23 ⎡ ⎣ ⎢ ⎢ ⎤ ⎦ ⎥ ⎥
12.
Strain Displacement RelaDon • From strain-displacement relaDon • This will lead to
{ε}=[B]{q} ε = ∂u ∂r ∂v ∂z ∂u ∂z + ∂v ∂r u r ⎡ ⎣ ⎢ ⎢ ⎢ ⎢ ⎢ ⎢ ⎢ ⎢ ⎢ ⎢ ⎤ ⎦ ⎥ ⎥ ⎥ ⎥ ⎥ ⎥ ⎥ ⎥ ⎥ ⎥ = z23(q1 −q5)−z13(q3 −q5)( )/detJ −r23(q2 −q6 )−r13(q4 −q6 )( )/detJ −r23(q1 −q5)−r13(q3 −q5)+z23(q2 −q6 )−z13(q4 −q6 )( )/detJ N1q1 + N2q3 + N1q5( )/r ⎡ ⎣ ⎢ ⎢ ⎢ ⎢ ⎢ ⎢ ⎤ ⎦ ⎥ ⎥ ⎥ ⎥ ⎥ ⎥
13.
Strain Displacement RelaDon • The strain-displacement relaDon is • Where B is the element strain-displacement matrix given as ε
= Bq B = z23 detJ 0 z31 detJ 0 z12 detJ 0 0 r32 detJ 0 r13 detJ 0 r21 detJ r32 detJ z23 detJ r13 detJ z31 detJ r21 detJ z12 detJ N1 /r 0 N2 /r 0 N3 /r 0 ⎡ ⎣ ⎢ ⎢ ⎢ ⎢ ⎢ ⎢ ⎢ ⎤ ⎦ ⎥ ⎥ ⎥ ⎥ ⎥ ⎥ ⎥
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