ML20207S077
| ML20207S077 | |
| Person / Time | |
|---|---|
| Site: | 07106601 |
| Issue date: | 02/28/1987 |
| From: | CHEM-NUCLEAR SYSTEMS, INC. |
| To: | |
| Shared Package | |
| ML20207S070 | List: |
| References | |
| NUDOCS 8703180498 | |
| Download: ML20207S077 (28) | |
Text
.
'O APPENDIX A DESCRIPTION AND SAFETY ANALYSES FOR AN OPTIONAL TIE-DOWN ARRANGEMENT FOR THE 8-120A SHIPPING PACKAGE NRC DOCKET 71-6601 0
)
FEBRUARY 1987 i
l i
i i
Chem-Nuclear Systems, Inc.
l 220 Stoneridge Drive O
Columbia, South Carolina 29210 G703180498 070223 PDR ADOCK 07106601 l
C PDR
e 4
O TAaLE 0r C0aTEaTs PAGE LIST OF FIGURES 11 1.0 GENERAL INFORMATION A1-1
- 2. 0 STRUCTURAL EVALUATION A2-1
- 3. 0 THERMAL EVALUATION A3-1 4.0 CONTAIM4ENT A4-1 5.0 SHIELDING EVALUATION AS-1 O
e.0 CRITICALITT EvAtVATION Ae-,
)
7.0 OPERATING PROCEDURES A7-1 8.0 ACCEPTANCE TESTS AND MAINTENANCE PROGRM4 A8-1 REFERENCES l
i'!O l
m
LIST OF FIGURES A.1 OPTIONAL TIE-DOWN ARRANGEMENT 8-120A CASK A. 2 CASK TIE-DOWN TO THE VEHICLE WITH OPTIONAL TIE-DOWN ARRANGEMENT A.3 OPTIONAL TIE-DOWN LUG LOCATIONS 8-120A CASK A.4 OPTIONAL TIE-DOWN ARRANGEMENT AXIAL LUG 8-120A CASK A.5 FINITE ELEMENT MODEL OF THE OPTIONAL TIE-DOWN 8-120A CASK A.6 EXPLODED VIEW 0F FINITE ELEMENT MODEL IN THE VICINITY OF THE LUG 8-120A CASK A.7 STRESS CONT 0UR PLOT IN THE VICINITY OF THE LUG 8-120A CASK O
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APPENDIX A L) ^
8-120A CASK, OPTIONAL TIE-DOWN SYSTEM 1.0 GENERAL
1.1 INTRODUCTION
This Appendix provides a description and analysis of an optional cask tie-down system for the model CNS 8-120A package.
The present tie-down system is described and evaluated in the CNSI Safety Analysis Report, Revision 1, Decenber 1985 (Reference A.1).
1.2 DESCRIPTION
The original tie-down arrangement of the CNS 8-120A package, described in Section 2.4.4 of Revision 1 of the SAR, consists of a separate structure with no part attached to the cask body.
In the optional arrangemen t, this structure is replaced by four integral lug assenblies.
Each assembly consists of an axial lug and two circumferential lugs.
These l
lugs are welded to the cask body by full-penetration groove-welds.
In order to weld the lug assemblies directly to the cask body, portions of the ring plate (Reference Drawing C-110-D-29008-010, Rev., included in Section 1.3) have been removed and the exposed edges welded back to the cask body.
The cask is secured to the vehicle by steel ropes having shackles at the ends.
The tie-down points on the vehicle are selected in such a way that the loads in the steel ropes, due to accident conditions loading, are minimized.
Drawing C-110-D-29008-010, Rev., contains the details of the optional tie-down arrangement for the package.
Figure A.1 shows the optional tie-down arrangement.
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CASK BODY t
. TIE-DOWN I
LUG l
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O OPTIONAL TIE-DOWN ARRANGEMENT 8-120A CASK i
1 1.3 APPENDIX Chem-Nuclear Systems, Inc., Drawing No. C-110-D-29008-010, Rev..
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STRUCTURAL EVALUATION q
2.0 (s
2.1 INTRODUCTION
This section provides a discussion of the evaluation performed on the optional tie-down arrangement for the 8-120A package.
The existing tie-down arrangement-is discussed in Section 2.4.4 of Revision 1 of the SAR.
The evaluation performed complies with the Nuclear Regulatory Comission Regulation 10 CFR 71.45(b) governing tie-down devices.
Each component used in the optional tie-down arrangement is evaluated under conditions where a static force is applied to the center of gravity of the package.
This force is composed of a vertical component of two times the loaded package weight, a horizontal component along the direction of vehicle travel equal to ten times the loaded package weight and a horizontal component transverse to the direction of travel equal to five times the loaded package weight.
The results of the evaluation verify that the tie-down system is capable of withstanding this static force q
without generating stress in any part of the package in excess of its b
yield stren gth.
A summary of these results is provided in Table A.1 bel ow.
TABLE A.1 SUtHARY OF TIE-DOWN ARRANGEMENT STRESSES AND MINIMLN FACTOR OF SAFETY STRESS CALCULATED STRESS SAFETY COMPONENT CATEGORY STRESS LIMIT FACTOR Lug Shear 21,940 psi 22,800 psi 1.04 Lug Bending 21,619 psi 38,000 psi 1.76 Shell Bending 28,877 psi 32,000 psi 1.11 O
A2-1 (0087W)
A
- 2. 2 TIE-DOWN LOADS EVALUATION U
The tie-down of the 8-120A cask to the vehicle with the optional tie-down arrangement is as shown in Figure A.2.
The loads in the tie-down cables are obtained by statically applying the required 10W, SW and 2W loads on the cask C.G. along x, y and z directions respectively.
The weight (W) of a loaded package with optional tie-down arrangement is 70,000 pounds.
The total load in the cables is obtained as the sum of the cable load under each of these loading conditions.
2.2.1 Cable Load Under x-Direction Loading Due to negative x-direction loading, two of the four cables, namely cables 2 and 3, will be slack and the remaining two will carry the load.
Due to symmetry, both cables 1 and 4 will carry equal loads.
The magnitude of the load in each cable, T, can x
be calculated by moment balance about point A.
O F1A = 10We - 2B T h - 28 T a - WR = 0 xx zx
)
T = W(10c - R)/2(B h + B a) x x
7
- where, x !1 2+1 2,j 2 B
=1 x
x y
z
= 63.5 /!63.52 + 402 + 802
= 0.5789 1 !!I
+I
- I B
=
7 z
x y
z
= 80 //63.5
+ 40 + 80
= 0.7293 c = 46" R = 36.7 5" h = 85" l.
+ = tan-I (ly/1x) = 32.2*
a = R + 39 cos 4
= 36.75 + 39 cos 32.2*
= 69.75 W = 70,000 lbs.
A?-2
.(0087W)
therefore, Q}
r 70,000 (10 x 46 - 36.75)/2(0.5789 x 85 + 0.7293 x 69.75)
T
=
x
= 148,026 lbs.
we thus have, Tjx = 148,026 lbs., T2x = 0, T3x = 0 and T4x = 148,026 lbs.
2.2.2 Cable Load Under y-Direction Loading Due to negative y-direction loading, two of the four cables, namely cables 3 and 4, will be slack and the remaining two cables will carry the load.
Due to symmetry, both cables 1 and 2 will carry equal loads.
The magnitude of the load in each cable, T,
y can be calculated by moment balance about point B.
SWc - 28 T h - 2B T b - WR = 0 M
=
B yy zy T = W(Sc - R)/2(B h + B b) y y
z where.
= 1 !!1 2
2 2
+3
,3 B
0 y
y x
y z
= 40 !!.52 + 402 + 802 63
= 0.3647 b = R + 39 Sin &
= 36.75 + 39 Sin 32.2
= 57.53" there fore, 70,000 (5 x 46 - 36.75)/2(0.3647 x 85 + 0.7293 x 57.53)
T
=
y 92,710 lbs.
=
we thus have, Tjy = 92,710 lbs., T,y = 92,710 lbs., T3y = 0 and T4y = 0 O
A2-3 (0087W)
2.2.3 Cable Load Under z-Direction Loading v
Due to z-direction loading, all of the four cables are effective and because of symmetry, they carry equal loading.
The magnitude of the loading, T,
can be estimated by force balance along z-direction.
2W - 48,T
=0 F
=
z z
T, = W/( 2B )
= 70,000/( 2 x 0.7293)
= 47,991 lbs.
we thus have, 1z =
T2z = T3z = T
= 47,991 lbs.
T 47 2.2.4 Cable Load Under Combined Loading iV To obtain the load under the combined loading of 10W, SW and 2W along x,
y and z-directions, res pectively, the loads in a particular cable under these loadings can be added together.
We thus obtain,
=
+ T
+ T
= 148,026 + 92,710 + 47,991 = 288,727 lbs.
Tj T) j T2x + T2y + Tpg = 0 + 92,710 + 47,991
= 140,701 lbs.
T
=
2
+ T
= 0 + 0 + A7,991
= 47,991 lbs.
T3 3x 3y
- 3z T
T4z = 148,026 + 0 + 47,991
= 196,017 lbs.
T4x + T4y +
=
4 The largest tension under the combined loading occurs in Cable 1 and is equal to 288,727 lbs (4.125 times the total weight of the ca sk ).
The tie-down arrangement is designed to withstand this loading wi thout generating a stress in excess of i ts yiel d s tren gth.
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A2-4 i
(0087W)
2.3 TIE-DOWN STRESS EVALUATION q(./
2.3.1 Tie-Down Lug Stresses Four tie-down lug assemblies, constructed from 2-inch SA 516 Gr 70 steel (yield strength of 38,000 psi and ultimate strength of 70,000 psi) are welded to the cask body at locations shown in Figure A.3.
Each assedly is comprised of one axial lug and two circumferential lugs.
Under the accident conditions loading, the lug asseelies experience a di f ferent amount of loading as indicated in Section 2.2, the largest of which is 288,727 lbs.
along a line making 43.17* with the axis of the cask.
The stresses in the lug assembly due to this loading are calculated by conservatively disregarding the circumferential lugs.
The axial lug (Figure A.4) is analyzed for shear-out and bending and it is shown that under these conditions, stresses nowhere in the lug exceed the yield strength of the material.
IO v
Shear-Out of the Lug The maximum shear stress in the lug is calculated by assuming the shear-out of lug alcng a-a plane.
Shear force, V
= 288,727 lbs.
Lug width, b
= 2.0 inches o - r4 Sin 40' - rg Cos 40*
Shear-out length,1
=
(for 40* shear)
= [4
.8752 Sin? 40* - 0.875 Cos 40'
= 3.29 inches No. of surfaces, N
=?
Shear area, A
= N1b = 2 x 3.29 x ? = 13.16 in?
3 Shear stress, t
= V/As = ?88,727/13.16 = P1,940 psi Yield strength in shear = 0.60 x yield strength in tension
= 0.60 x 38,000 = P2,800 psi O
i
- V Therefore, the maximum shear stress in the lug is smaller than the yield strength of the material in shear.
A2-5 (0087W)
I Bending of the Lug gO The maximum bending stress in the lug occurs due to bending of section b-b about point o.
Bending moment about point o, M, = 210,576 x 2.25 - 197,537 x 1.75
= 128,106 in-lb Section width, b
= 2.0 inches L
Section depth, d
= 11.5 inches 2
b
= 6M,/(bd )
Max. bending stress, 2
= 6 x I?8,106/(2 x 11.5 )
= 2,906 psi Max, axial stress, o,
= 197,537/(2 x 11.5)
= 8,589 psi Max. axial plus bending stress,o o, + ob
=
= 8,589 + P,906
= 11,495 psi m
Max. shear stress, t
= 210,576/(2 x 11.5)
= 9.155 psi
)
Max. stress intensity, SI
= 2 x/t2 + ( a/p)2
=2x[9,1552 + 11,d95 /4 2
= 21,619 pst Tensile yield strength
= 38,000 pst Since the maximum stress intensity is smaller than the tensile
[
yield strength of the material, the maximum normal stress and maximum shear stress in the lug will be smaller than the L
corresponding yield strength of the material.
Stresses in the Welds i
i The tie-down lugs are welded to the cask body by full penetration groove welds.
Therefore, the wolds are implicttly qualificd for i
the Inading through the qualification of the lugs.
No separate analysis for the welds is needed.
A?-6 (0087W)
?. 3. 2 Shell Stresses o
(
I v
To evaluate the local stresses in the cask body, an ANSYS (Ref.
A.?) finite element model was used.
To simplify the analysis, it was assumed that the stresses in the cask body due to the tie-down loading could be calculated by superposing the effect of loading at each of the lugs separately.
This assumption is totally valid if the stresses in the cask are within the yield strength of the material.
Additionally, if the stresses in the cask are confined to a small region near the load application, no superposition is necessary to obtain the maximum stresses in the cask body.
A 180*
model of the cask was constructed with the load applied at only one lug location.
The results of the analysis did show that the stresses are confined to a
small region near the load application.
Hence, the estimate of maximum stresses in the cask body was directly obtained from this model, The model is comprised of the quadrilateral shcIl elements (STIF n
V>
- 63) to represent the cask shells, the bol ting ring and the tie-down lugs.
The bottom plate was represented by stiff beam elements (STIF
- 4) between the inner and outer shell s and interconnected at the centroid of the base plate.
No credit was taken for the stiffness of the cask lid.
The tie-down load was applied at the corresponding node of the axial lug as a nodal force.
Occause of the geometry of the cask (axisymetric) and the nature of loading (planer),
a plane of symmetry exists.
There fore, only one-hal f of the geome try needs to be rodeled.
Symmetry bound.iry conditions are defined at all the nodes lying on this plane.
The nodes on the lower plenum of the cask outer shell are restrained in the vertical direc tion.
A node on the outer shell diametrically opposite to the point of application of the load is restrained in the herizontal direction to remove the rigid body motion of the cask under the applied loading.
Figure A.5 shows the geometry of the finite element model along with the o
applied load and boundary conditions.
The model has fine mesh b
near the load application.
Figure A.6 shows the exploded view of the geometry near the tie-down arrangement.
A?-7 (0087W)
A linear static analysis of the model was puformed.
The output of the analysis (Reference A.3) included the nodal displacements, element stress components and reaction forces.
The entire model was scanned for stress intensity.
A stress intensity contour plot of the model is shown in Figure A.7.
The quantity plotted is nodal stress intensity which corresponds to the peak value.
However, selection of this cuantity to satisfy the maximum stress value is conservative.
The largest value of stress intensity in the model is 28,877 psi which occurs in the outer shell of the cask near the tie-down lug.
This value is smaller than 32,000 psi (yfeld strength of SA 516 Gr 60).
Therefore, the normal and the shear stresses everywhere in the cask will remain within the corresponding yield strength of the material.
O O
A?-11 (0087W)
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B
'x
.x FIGURE A.2 CASK TIE-DOWN TO THE VEHICLE
~
WITH OPTIONAL TIE-DOWN ARRANGEMENT
^~
(0087W) a
EX,1 STING C ASK
., -b) 64 ~1/2*
LIFT LOCATIONS s
C' s
\\
/
O*,360*
S 17 1/4" s
/
_ h_
9
~ 4
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._4
-t s
17 1/4 5
EXISTING DRAIN s
'y LOCATigN 64 1/2*
x r
p v
90*
(~ )
ALTERNATE gh TIE-DOWN LUG 11 1/2" Ij gy 4
f" tw
\\
l 73 1/2"
=
.DIA.
1
+,
./'
FIGURE A.3 OPTIONAL TIE-DOWN LUG LOCATIONS 8-120A CASK
/
A2-10 (0087w)
4 O
1/4" R l
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1 O
-B L E N D R n
1 3/4b~X
" R 397,837 tsS 7/8 11 1/2" 4
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/
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1 4"R a
b o
43.17*
--2 1/ 4 ":
288,727 LBS 210,576 LBS FIGURE A.4
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OPTIONAL TIE-DOWN ARRANGEMENT I
AXIAL LUG 8-120A CAS_K A2-11 (0087W)
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OUTER $MELL NODES ON TNIS PLANUM ARE FIXED IN INE Axtet DIRECT!CN.
8-120A TIE-DOHN MODIFICATION.
FIGlRE A.5 FINITE ELEMENT MODEL OF THE OPTIONAL TIE-DOWN 8-120A CASK A2-12 (0087W)
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.Y FIGlRE A.6 EXPLODED VIEW 0F FINITE ELEMENT MODEL IN THE VICINITY OF THE LUG
(
8-120A CASK A2-13 (0087W)
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4 FIGURE A.7 STRESS CONTOUR PLOT IN THE VICINITY OF THE LUG O-8-120A CASK A2-14 (0087W)
=-.
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f
- 3. 0 THERftAL EVALUATION The optional tie-down arrangement does not effect the results of the I
thermal analysis previously provided in Reference A.1.
I t
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l O
A3-1 (0087W)
- 4. 0 C01fTAIISIEllT The optional tie-down arrangement does not effect the containment boundary as discussed in Reference A.1.
f a
- I.
f d.
a f
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4 4
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A4-1 (0087W)
e
6.0 CRITICALITY EVALUATION
O Not applicable for the Model CNS 8-120A package.
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O A6-1 (0087w)
'w~~m' rw -
7.0 OPERATING PROCEDURES The cask loading and unloading procedures are essentially unchanged from those presented in Reference A.1.
The following revised steps are presented in Reference A.l.
The following revised steps re presented to acconmodate a cask with either the original tie-down arrangement or the optional tie-down arrangement.
The indicated step numbers are based on the nunbering scheme in Reference A.1.
Revised Step 7.1.3:
" Disconnect the trailer tie-down equipment and remove the tie-down crossmenber" or
" loosen and remove the cask tie-down cables" as applicable.
Revised Step 7.1.13:
"Using suitable lifting equipment, replace the tie-down crossmember and reconnect the trailer tie-down equipment" or " replace the cask tie-down cables and tighten" as applicable.
Revised Step 7.2.4:
" Disconnect the trailer tie-down equipment and remove the tie-down crossmenber" or
" loosen and remove the cask tie-down cabl es" as applicable.
OV A7 1
-(0087W)
8.0 ACCEPTANCE TESTS AND MAINTENANCE PROGRAM 8.1 ACCEPTANCE TEST The acceptance tests to be conducted prior to the first use of each CNS 8-120A package is described in Reference A.l.
The visual examination and acceptance criteria defined for cask material, fabrication, and welds will be applicable to verify the integrity of the cask tie-down lugs.
8.2 MAINTENANCE PROGRAM The 8-120A package will be subjected to routine and periodic inspections and maintenance as previously described in Peference A.l.
The cask tie-down lugs will be visually inspected for wear and defects and repaired 6s necessary.
O A8-1 (0087W)
REFERENCES TO APPENDIX A A.1 Safety Analysis Report for Chem-Nuclear Systems, Inc. Model CNS 8-120A Type A Radwaste Shipping Container, Revision 1, December 1985.
A.2 ANSYS, Engineering Analysis System, User's Manual Revision 4.1, Swanson Analysis Systems, Inc., Houston, Pennsylvania,1983.
A.3 Chem-Nuclear Systems, Inc., Engineering Analysis File No. ST-009, Septenber 29, 1986.
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