Selaa lähdekoodia

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gtheler 6 vuotta sitten
vanhempi
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61de950d2e
8 muutettua tiedostoa jossa 980 lisäystä ja 11 poistoa
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      nafems4.md
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B.pdf Näytä tiedosto


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B.svg Näytä tiedosto

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+ 44
- 11
nafems4.md Näytä tiedosto

@@ -662,7 +662,7 @@ ans =
5.767255
```

Did I convince you? More or less, right? The third eigenvalue seems to fit. Let us not throw all of our beloved linearity away and dig in further into the subject. There are still two important issues to discuss which can be easily addressed using fresh-year linear algebra (remember, do not fear maths!). First of all, even though principal stresses are not linear with respect to the sum they are linear with respect to pure multiplication. Once more, think what happens to the the eigenvalues and eigenvectors of a single stress tensor as all its elements are scaled up or down by a real scalar. They are the same! So, for example, the [Von Mises stress](https://en.wikipedia.org/wiki/Von_Mises_yield_criterion) (which is a combination of the principal stresses) of a beam loaded with a force\ $\alpha \cdot \vec{F}$ is\ $\alpha$ times the stress of the beam loaded with a force\ $\vec{F}$. Please test this hypothesis by playing with your favorite FEM solver an play. Or even better, take a look at the stress invariants $I_1$, $I_2$ and $I_3$ (you can search online or peek into the source code of [Fino](https://www.seamplex.com/fino) and grep for the routine called `fino_compute_principal_stress()`) and see (using paper and pencil!) how they scale up if the individual elements of the stress tensor are scaled by a real factor\ $\alpha$.
Did I convince you? More or less, right? The third eigenvalue seems to fit. Let us not throw all of our beloved linearity away and dig in further into the subject. There are still two important issues to discuss which can be easily addressed using fresh-year linear algebra (remember, do not fear maths!). First of all, even though principal stresses are not linear with respect to the sum they are linear with respect to pure multiplication. Once more, think what happens to the the eigenvalues and eigenvectors of a single stress tensor as all its elements are scaled up or down by a real scalar. They are the same! So, for example, the [Von\ Mises stress](https://en.wikipedia.org/wiki/Von_Mises_yield_criterion) (which is a combination of the principal stresses) of a beam loaded with a force\ $\alpha \cdot \vec{F}$ is\ $\alpha$ times the stress of the beam loaded with a force\ $\vec{F}$. Please test this hypothesis by playing with your favorite FEM solver an play. Or even better, take a look at the stress invariants $I_1$, $I_2$ and $I_3$ (you can search online or peek into the source code of [Fino](https://www.seamplex.com/fino) and grep for the routine called `fino_compute_principal_stress()`) and see (using paper and pencil!) how they scale up if the individual elements of the stress tensor are scaled by a real factor\ $\alpha$.

The other issue is that even though in general the eigenvalues of the sum of two matrices are not the same as the eigenvalues of the matrix sum, there are some cases when they are. In effect, if two matrices\ $A$ and\ $B$ commute, i.e. their product is commutative

@@ -680,7 +680,7 @@ The computation of these membrane and bending stresses are called [“stress lin

**figures**

So what about the SCLs? Well, the ASME standard says that they are lines that go through a wall of the ipe (or vessel or pump, which is what the ASME code is for) from the inside to the outside and ought to be normal to the iso-stress curves. Stop. Picture yourself a stress field, draw the iso-stress curves (those would be the lines that have the same color in your picture) and then imagine a set of lines that travel in a perpendicular direction to them. Finally, choose the one that seems the prettiest (which most of the time is the one that seems the easiest). There you go! You have an SCL. But there is a catch. So far, we have referred to a generic concept of “stress.” Which of the several stresses out there should you picture? One of the three normals, the three shear, Von Mises, Tresca? Well, actually you will have to imagine tensors instead of scalars. And there might not be such a thing as “iso-stress” curves, let alone normal directions. So pick any radial straight line through the pipe wall at a location that seems relevant and now you are done. In our case study, there will be a few different locations around the material interfaces where high stresses due to differential thermal expansion are expected to occur.
So what about the SCLs? Well, the ASME standard says that they are lines that go through a wall of the ipe (or vessel or pump, which is what the ASME code is for) from the inside to the outside and ought to be normal to the iso-stress curves. Stop. Picture yourself a stress field, draw the iso-stress curves (those would be the lines that have the same color in your picture) and then imagine a set of lines that travel in a perpendicular direction to them. Finally, choose the one that seems the prettiest (which most of the time is the one that seems the easiest). There you go! You have an SCL. But there is a catch. So far, we have referred to a generic concept of “stress.” Which of the several stresses out there should you picture? One of the three normals, the three shear, Von\ Mises, Tresca? Well, actually you will have to imagine tensors instead of scalars. And there might not be such a thing as “iso-stress” curves, let alone normal directions. So pick any radial straight line through the pipe wall at a location that seems relevant and now you are done. In our case study, there will be a few different locations around the material interfaces where high stresses due to differential thermal expansion are expected to occur.

If you cannot wait to know, the expression for computing the $i$-$j$-th element of the membrane tensor is

@@ -815,7 +815,7 @@ The main issue with fatigue in nuclear piping during operational transients is t

::::: {#fig:two-cubes}
![Surface grid showing the fixed face (magenta), the load face (green) and the shared face in the middle.](two-cubes2.png){#fig:two-cubes2 width=48%}\
![Warped displacements and Von Mises stresses.](two-cubes4.png){#fig:two-cubes4 width=48%}
![Warped displacements and Von\ Mises stresses.](two-cubes4.png){#fig:two-cubes4 width=48%}

Two cubes of different materials (the one in the left soft, the one in the right hard) share a face and a pressure is applied at the right-most face.
:::::
@@ -907,7 +907,7 @@ The boundary conditions are
* Dark green: axial $w=0$ and radial symmetry $0=vx-uy$
* Light green: internal pressure\ $p=10$\ MPa

Three radial SCLs are located at a distance of one thickness of the main line from the external wall of the branch into the main direction\ $x$.
Three radial SCLs are located at a distance of one thickness of the main line from the external wall of the branch into the main direction\ $x$. [@Fig:tee-MB] shows the results of the parametric computation, namely the linearised membrane and bending stresses computed in each of the three SCLs as a function of\ $d_b$. Note that\ $d_b$ is a continuous variable and even unreal values (such as 9-inches) were used to perform the parametric run. The thickness of such cases was interpolated using actual schedule-80 geometrical data from ASME\ B36.310M.

::::: {#fig:tee-scls}
![$y$-$z$ projection](tee-scls1.png){#fig:tee-scls1 width=29%}\
@@ -916,6 +916,35 @@ Three radial SCLs are located at a distance of one thickness of the main line fr
Location of the three radial SCLs: cyan, yellow and green.
:::::

::::: {#fig:tee-MB}
![Membrane stress](M.svg){#fig:M}

![Bending stress](B.svg){#fig:B}

Parametric membrane and bending stresses as a function of the nominal diameter\ $d_b$ of the branch.
:::::


::::: {#fig:tee-post}
![$d_b=2$\ in](tee-post-2.png){#fig:tee-post-2 width=30%}\
![$d_b=5$\ in](tee-post-5.png){#fig:tee-post-5 width=30%}\
![$d_b=10$\ in](tee-post-10.png){#fig:tee-post-10 width=30%}\

Von\ Mises stress and 400x warped displacements for three values of\ $d_b$.
:::::

[@Fig:tee-post] illustrates how the pipes deform when subject to the internal pressure. When the branch is small, the problem resembles the infinite-pipe problem where the main pipe expands radially outward and there is only traction. For large values of\ $d_b$, the pressure in the branch bends down the main pipe, generating a complex mixture of traction and compressing. The tipping point seems to be around\ $d_b\approx 5$\ in. Do you now see the added value of training throw-ins with watermelons? We might go on...

* studying how the maximum Von\ Mises stress as a function the radius\ $r_f$ of an hypothetical fillet operation on the tee’s sharp edges,
* making the branch another material and adding thermal expansion,
* adding piping supports to restrain the degrees of freedom of the pipes,
* using distributed forces from earthquakes,
* etc.

Most of the time at college we would barely do what is needed to be approved and move on to another subject. If you have the time and consider a career related to finite-element analysis, please do not.

**Clone the repository with the input files here. Feel free to ask for help in our community mailing list.**

## Bake, shake and break {#sec:break}

# Fatigue
@@ -924,6 +953,12 @@ Location of the three radial SCLs: cyan, yellow and green.

## In water

# Errors and uncertainties

errors and uncertainties: model parameters (is E what we think? is the material linear?), geometry (does the CAD represent the reality?) equations (any effect we did not have take account), discretization (how well does the mesh describe the geometry?)

do you trust your FEM program?

# Conclusions

Back in college, we all learned how to solve engineering problems. But there is a real gap between the equations written in chalk on a blackboard (now probably in the form of beamer slide presentations) and actual real-life engineering problems. This chapter introduces a real case from the nuclear industry and starts by idealising the structure such that it has a known analytical solution that can be found in textbooks. Additional realism is added in stages allowing the engineer to develop an understanding of the more complex physics and a faith in the veracity of the FE results where theoretical solutions are not available. Even more, a brief insight into the world of evaluation of low-cycle fatigue using such results further illustrates the complexities of real-life engineering analysis.
@@ -936,14 +971,12 @@ Back in college, we all learned how to solve engineering problems. But there is
* take into account that even within the finite element method, there is a wide variety of complexity in the problems that can be solved
* follow the “five whys rule” before compute anything, probably you do not need to
* use engineering judgment and make sure understand the [“wronger than wrong”](https://en.wikipedia.org/wiki/Wronger_than_wrong) concept
* play with your favourite FEM solver (mine is <https://caeplex.com>) solving simple cases, trying to predict the results and picturing the stress tensor and its eigenvectors in your imagination
* play with your favourite FEM solver (mine is [CAEplex](https://caeplex.com>)) solving simple cases, trying to predict the results and picturing the stress tensor and its eigenvectors in your imagination
* grab any stress distribution from any of your FEM projects, compute the iso-stress curves and the draw normal lines to them to get acquainted with SCLs
* first search online for “stress linearisation” (or “linearization” if you want) and then get a copy of ASME\ VIII Div\ 2 Annex 5-A
* try to show that even though the principal stresses are not linear with respect to summation, they are linear with respect to multiplication (with pencil and paper)
* measure the time needed to generate grids of different sizes and kinds with your favourite mesher
* learn this by heart: the complexity of a FEM problem is given mainly but the number of nodes, not by the number of elements
* welded materials with different thermal expansion coefficients may lead to fatigue under cyclic temperature changes



dnl errors and uncertainties: model parameters (is E what we think? is the material linear?), geometry (does the CAD represent the reality?) equations (any effect we did not have take account), discretization (how well does the mesh describe the geometry?)
* learn this by heart: the complexity of a FEM problem is given mainly by the number of _nodes_, not by the number of elements
* remember that welded materials with different thermal expansion coefficients may lead to fatigue under cyclic temperature changes
* if you have time, try to get out of your comfort zone and do more than what other expect from you (like parametric computations)
* clone the parametric tee repository, understand how the figures from\ [@sec:parametric] where built and expand them to cover “we might go on...” bullets

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