ORNL-1771 - Oak Ridge National Laboratory
ORNL-1771 - Oak Ridge National Laboratory
ORNL-1771 - Oak Ridge National Laboratory
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AMP QUARTERLY PROGRESS REPORT<br />
studied include sodium silicate, silica, silicon<br />
nitride, and boric oxide.<br />
The fluoride-to-sodium intermediate heat ex-<br />
changer, which failed in a life test after 1680 hr of<br />
cyclic service in the temperature range 1080 to<br />
15OO0F, was examined, It is probable that the<br />
failures in the tube-to-header welds were caused<br />
by unequal thermal expansion, which caused stress<br />
concentration at the roots of the tube-to-header<br />
welds. These stresses, combined with expansion<br />
and contraction of the tubes, would tend to propa-<br />
gate cracks through the walls. These failures<br />
emphasize the extreme desirability of using back-<br />
brazing as a means of rniriirnizing the notch effect<br />
in tu be-to-header welds.<br />
STRESS-RUPTURE TESTS OF INCONEL<br />
R. B. Oliver<br />
D. A. Douglas<br />
J. H. DeVan<br />
J. W. Woods<br />
Metallurgy Division<br />
The tube-burst test for obtaining information on<br />
the stress-rupture properties of lnconel has been<br />
studied intensively. The stress pattern introduced<br />
into the specimen in this test simulates to some<br />
extent the stress pattern that will be present in<br />
circulating-fuel reactors. The test consists of<br />
stressing a closed-end tube with internal gas pres-<br />
sure. In tests of this type reported previously,' it<br />
WQS observed that lnconel specimens stressed in<br />
this manner showed less ductility and much shorter<br />
rupture life than the uniaxially stressed specimens,<br />
and therefore an intensive study of the multiaxial<br />
stress system was initiated. W. Jordan of the<br />
Mechanics Department of the University of Alabama<br />
is investigating this problem.<br />
Part of the investigation consists of a study of<br />
the theory of stresses in cylindrical pressure ves-<br />
sels, with particular attention to the variations in<br />
stresses calculated by the thin-wall formula vs the<br />
stresses determined by the niore exact Lame' theory.<br />
The stresses under discussion are those in the<br />
walls only, with no consideration given to the end<br />
closure shape, except that the ends are assumed to<br />
be completely closed. The three principal stresses<br />
at a given point are the radial stress (G), the tan-<br />
gential (hoop) stress (ut), and the longitudinal<br />
(axial) stress (uj. The theory of elasticity yields<br />
'R, €3. Oliver, B. A. Douglas, and J. W. Woods, ANP<br />
Qrtnr. Prog. Rep. ]me 10, 1954, <strong>ORNL</strong>-1729, p 89.<br />
112<br />
the following equations:<br />
(1 ) =<br />
2 2<br />
PIT2 - P OTO<br />
2 2<br />
to - r .<br />
2 2<br />
Tire ( p, *.. p )<br />
2 2<br />
r0 - r . '<br />
where r is the radial distance to the point at which<br />
the stress is desired, rz and ro are the internal and<br />
external radii, and pi and p, are the internal and<br />
external pressures. For the special case of the<br />
cylinder subjected to internal pressure only (p, =O),<br />
the equations reduce to:<br />
(4) u . = p . u - 0 ,<br />
YZ 70<br />
u . = u<br />
UZ<br />
r. 2<br />
a* = PI ___ I<br />
r2 - r2<br />
0 1<br />
where the additional subscripts i and o an the<br />
stress terms indicate stresses at the inner and<br />
outer surfaces, To simplify these equations for<br />
application to cylinders with thin walls, it is fre-<br />
quently assumed that the tangential stress does<br />
not vary across the wall of the vessel. This simpli-<br />
fication results in the following equations for in-<br />
ternal pressures only:<br />
(7)<br />
where the letter s is used to denote stress and I<br />
is the thickness of the wall (t = ro - r.). A simpli-<br />
fied expression for radial stress in thin-walled<br />
cylinders is not commonly used.