ML20023D688
| ML20023D688 | |
| Person / Time | |
|---|---|
| Site: | 07105796 |
| Issue date: | 05/03/1983 |
| From: | Irwin H ATC MEDICAL TECHNOLOGY, INC. |
| To: | Macdonald C NRC OFFICE OF NUCLEAR MATERIAL SAFETY & SAFEGUARDS (NMSS) |
| References | |
| 22274, NUDOCS 8306020468 | |
| Download: ML20023D688 (24) | |
Text
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' 31cclicalTechnologyinc.
AT.(=4 13ctatron Corporation g (M iL Nivance(t Alectical Systems,Inc.
5463 Homing Road a Pittsburgh, PA 15236 = (412)655-3737 g
(o Y kb May 3,1983 M
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US Nuclear Regulatory Commission d-
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Transportation Certification Branch
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Division of Fuel Cycle and Material Safety NMSS Washington, DC 20555
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Re: Docket 71 - 5796 Attn: Mr. Charles E. MacDonald Gentlemen:
In response to your letter of December 29, 1982 and Februa.y 25, 1983 regarding our submission of an amendment to C.O.C No. 5796, Advanced Medical Systems submits the attached revised pages and drawings.
Drawing, D200016 and D200073 have been modified to clearly show that the four bolts on each side of the tie down assembly bolt into the machine irradiator head. Drawings A46686 and E63790 are submitted to show that portion of the machine irradiator head which receives the bolts.
Various parts of the application text have been modified to clarify the head tie down system description. Finally, section 2.1.10 has been com-pletely revised to demonstrate that the irradiator head remains inside the over-pack under the conditions of the 30ft. drop test.
This submittal should clarify the changes made in the head tie down system.
I trust gt this information will lead to your approval.
m O-Sincer ly yours, ladW Howard R. Irwin, Menager of Reliability Advanced Medical Systems, Inc.
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Enclosures:
10 copics revised pages S[hRMk cc:
T. Cameron
""d N. Kelbley 8306020468 830503
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Do cket 71 - 5796 Change 3 April 22,1983 Guide page for incorporatino revised paces into Application Remove the following paces 1 - 4,1 - 8 change 2 Drawings in Appendix 1.3.1 - D200016C, D200073C 2 - 3, 2 - 17 change 1, 2 - 17A change 1, 2 - 17B change 1, 2 - 29, 2 - 34, 2 - 35 change 2, 2 - 36 change 2, 2 - 36A change 2, 2 - 37 change 1, 2 - 38 change 1.
Insert the following revised pages (marked change 3, April 22,1983) 1 - 4,1 - 4a,.1 - 8, To Appendix 1.3.1 add drawings -
A46686 - A, E63790 - F, D200016 - D, D - 200073D 2 - 3, 2 - 3A, 2 - 17, 2 - 17A, 2 - 29, 2 - 3 4, 2 - 3 5, 2 - 3 6, 2 - 3 7,
2 - 38, 2 - 39, 2
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The machine head is held within the overpack by a steel tie down bracket and brace assembb, with wood front and rear support pads. Reference is made to drawings D200073, D200074,'D200075, D200079 in Appendix 1.3. The tie down M
bracket is a welded steel assembly that is bolted to the over-pack pallet base with four 1" - 8 hex head cap screws, and also bolted to the machine head with eight 1/2" - 20 socket head cap screws.
Drawings E - 63790 (section c - c) and A - 46686 in Appendix 1.3 show in greater detail the head bosses to which the tie down bracket is bolted. The bosses are 3/4" steel, brazed to the brass head.
c) The containment vessel is the gp i 1 f rm capsule design-0 ated as an AMS 3800 Series Cobalt source. It consists of a couble walled stainless steel capsule sealed by TIG wieding.
The unused space within the inner capsule is filled with stainless steel or tungsten slugs. The stainless steel capsules are housed in a tungsten capsule which is threaded on the outside. This threaded tungsten capsule is securely threaded into the shutter rotor at the center of the irradiator machine head.
Cobalt 60 sources meet the requirements for "special form" as per 10 CFR 71 and I.A.E.A. safety series 1973.
Additional details of the containment vessel may be found in Chapter 4 of this application Specifications for the containment vessel are as follows:
Overall exterior dimensions 2" Diam. x 2" L Weight 3 lbs.
The gross weight of the whole package is the sum of the component weights or 3750 lbs.
1.2.1.2 Source Exchance Package The source exchange package consists of the following basic components:
a) Overpack #181361 b) Shipping / Exchange container, Model 3320 AR c) Containment vessel, either AMS 3800 series n
60 U
Cobalt source, or Picker Cesium 137 source j
1-4 Change 3 April 22,1983
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Reference drawing D200017 in Appendix 1.3 for a view of the -
(
complete package. Each of these components will now be described in detail.
a) Overpack 181361 is composed of a pallet - bsse and cover which are rigidly secured together by I
l' 1 - 4a-Change 3 April 22,1983
.=
1.2.3 Contents of Packacino
-. O-For a machine package head, the follcwing data is applicable:
60 Maximum radioactive contents of Cobalt special form - 13, 680 curies Maximum decay heat load - 200 watts.
Maximum raciation leakage - less than 10 mrh at 3 ft.
from package surface.
Maximum surface leakage - less than 200 mrh.
For a source exchange package, the following data is applicable:
60 Maximum radioactive Cobalt material - 13, 680 curies 60 Maximum decay heat load of Cobalt special form -
200 watts.
13 7 Maximum radioactive Cesium material - 2200 curies.
I37 Maximum decay heat load of Cesium 17 watts.
Time maximum decay heat is insufficient to have any adverse effect on the package during normal conditions of transport.
'l.3 Appendix
- 1. 3.1 Drawing list for head package The following twelve drawings have been referenced in 1.2.1.1 Originator Drawino Number - Revision level AMS C16580 - E PICKER A46686 - A AMS E63790 - F AMS D181368 - E AMS D181369 - E 2 pages AMS D181375 - I AMS D200016 - D l
AMS D200073 - D I
AMS D200074 - C AMS D200075 - C AMS D200079 - B The drawings follow this index page in numerical drawing number order.
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1 Change 3 April 22,1983
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2.3 Mechanical Properties of Materials 7_
A36 steel Reference Source Minimum Tensile strength = 58,000 psi 1 - page 29
-6 Coefficient of linear expension = 6.3 x 10 in/in - P 3 - page 17 6
Modulus o.f elasticity = 30 x 10 psi 3 - page 12 Shear streng3 = 30 - 90,000 psi 4 - page 490 Yield strength (min.) = 36,000 psi 1 - page 29 3/8" x 4" ancle 4
Moment of inertia of section = 4.4 in 1 - page 88 Distance from neutral axis = 3.86 in.
1 - page 88 Cross sectional area = 2. 86 in2 1 - page 88 1" - 8 bolt, orade 8 2 tensile) 6 2 ((shear)
Cross sectional area = 0.606 in
- 0. 551 in Minimum tensile strength = 150,000 psi 2
Yield strength (min.j = 130,000 psi 2
Minimum shear strength = 112,500 psi 2
1/2" - 20 Socket head screw Cross sectional area = 0.1599 in2 (tensile) 6 0.1486 in2 (shear)
Minimum tensile strength = 180,000 psi 6
Minimum shear strength = 135, 000 psi 6
Yield strength
= 162,000 psi 6
Wood Coefficient of linear expansion = 2.7 x 10 -6 in/in OP 5 - page 4-9 Shear strength = 1850 psi 4 - page 493 The following references were used to obtain the data given above:
1.
Ryerson Data Book Joseph T. Ryerson & Sons, Inc.
Copyright 1975 2.
National Pastener Distributors Data Sheet 3.
Materials _ Selector 1974 Reinhold Publishing Co., Inc.
J 2-3 Change 3 April 22,1983 li
)
4.
Mechanical Behavior of Engineering Materials Joseph Marin June 1965 Prentice Hall Inc.
t 5.
Standard Handbook for Mechanical Encineers Baumeister & Marks 7th Edition 6.
Holo - Krome Technical Handbook 1976 Edition 7.
Design of Weldments J. A. Lincoln 1963 Edition, Section 6.3 4-I.O 2 - 3A Change 3 April 22,1983
2.6.6 Free Drop p)
The package was prototype tested and met the requirements of this test. Refer to 2.7.lb.
2.6.7 Corner Drop Same as 2.6.6 2.6.8 Penetration A 13 pound 11/4" diameter rod dopped from 40" would have no serious effect on the package considering the 16 gage thick steel Jacket and 3 5/8" thickness of hardwood maple.
2.6.9 Compression This requirement is covered by a theoretical 5 times load under section 2. 5.1.
2.7 Hypothetical Accident Conditions 2.7.1 Free Drop The drop orientation which would cause the most severe damage to the package was determined to be the upside down corner drop.
The following analysis was used to make this determination.
Regardless of drop orientation, the falling package will generate the same amount of energy, as energy le s function of mass and drop height.
The construction of the overpack is basically uniform over all of its surface (a combination of steel angles and flats welded to -
gether); therefore no configuration results in exposing a substan-tially weaker area to the force of impact, which might result in considerably more damages done by a lesser magnitude force. In-other words, for the sake of this analysis, all impact points are considered equally resistant to force. The following chart shows the package orientation and the area of impact as a result of falling onto an inelastic surface in a configuration normal to that surface.
..O. 17 -
Change 3 April 22,1983
n Source exchance packace
- LJ Con ficuratio__n Area of Impact 1736 in.2 Short side 44.5" x 39"
=
Long side 34.25" x 44.5" = 1524 in.2 1336 in.2 Top 34.25" x 39"
=
Bottom 2 x 39" x 3.662" = 286 in.2 Unobstructed top corner Nominal 1" x 1" = 1 in.
17 in.2 Shortest edge 34.25" x 1/2"
=
The machine head package, though lighter and smaller, will demonstrate the same relative forces as shown in this table.
It may be seen that the corner drop subjects the smallest pack-age area to the impact energy, resulting in the greatest con -
centratio" of force; therefore it will be the configuration which will cause the most severe damage to the package.
The assessment of the packages relative to the standards spec-ified in 10 CFR 71.36 is to be made by prototype testing.
Details of the test performed follow.
2.7. Ib Prototype testing A prototype package was drop tested on June 4,1981. This pack-age was not identical to the packages described in this application.
The following is a description of the actual test package, designed to represent a source exchange package.
An overpack, Model 181 361, Revision D_, was used. The tested overpack is the same as described in this application. Further revisions (to Revision,E_) are the result of drawing corrections, not component redesign.
A simulated 3320 AR shipping / exchange container was designed and built. Drawing D 2943 in Appendix 2.10 details this simulated container. The simulated container weighed 3000 lbs.
OV 2 - 17A Change 3 April 22,1983 t:
}
p The prototype package was designed to represent the source V
exchange package. It successfully passed the drop test. The head package, for which no prototype was tested, would perform in almost an identical manner. The package weight is 250 lbs.
less therefore the force of impact would be less. The overpack is constructed in the same manner, with the same materials.
Deformation from impact would be very similar. Instead of twenty 1/2" - 13 cover bolts, there are eight 1/2" - 13 and four 1" - 8 cover bolts, which would resist shearing under the force of impact.
The tie down system is very similar. Rather than being bolted directly to the overpack pallet - base (as is the case for the source exchange container), the machine head is held in place by a steel t
bracket that is bolted both to the pallet - base and to the machine head. In both packages, four 1" - 8 bolts are used to secure the tie down to the pallet base.
Calculations to show the design capacity of the tie down bracket and bolts may be found in 2.10.1.
2.7.2 Puncture Between the head package and the source exchange package the most severe damage would be encountered if the heavier package (source exchange weighing 4000 lbs.) were to fall 40 inches onto the end of a 6 in. diameter steel bar.
The following analysis will demonstrate that the effect of the puncture test would be superficial at best.
= 1.17 in.h (Diam.) (Thickness)
- I 7I Shear Area 16 ga. steel, As A = (TT) (6 ")
(. 062 ")
s Shear Force, F - AS 3
Where A = Area + 1.17 in.2 S = Shear strength = 30,000 psi Ps = (1.17 in.2) (30,000 psi) = 35,100 lbs.
The energy necessary to shear the 16 gage liner, E = Force (P ) X s
s Distance (Thickness)
E = (35,100 lbs.)
(.062 in.) = 2176 in. - lb.
s O
2 - 29 Change 3 April 22,1983 d
4 A
2.10 Appendix U
The following items have been referenced in the test of Chapter 2.
They may be found immediately following this index.
2.10.1 Calculations for machine head tie down bracket assembly.
l AMS Drawing D 2943 Rev. A Herron Testing laboratories report L - 4920 dated 3 79 Water Spray Test Herron Testing Laboratories report M - 5125 dated 10 79 Herron Testing Laboratories Test Certificate dated 9 80 1
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I 2 - 34 Change 3 April 22,1983 4
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.n 2.10.1 Analysis of Model 181375 package to demonstrate the irradiator i
head remains inside the overpack after the 30 foot drop test.
Prototype testing of a model 181361 package demonstrated by actual test that the overpack sustained minor damage and that the tie down system held the source exchange container in place.
The force of impact acting on the prototype 181361 package, can be determined by the following calculations.
Potential energy (Ep) = mgh Where m= mass of object = 4000 lbs = 1814 kg g = acceleration due to gravity = 9.78 m/sec2 h = distance traveled
= 32.2 ft. = 9.8 m Ep = (1814 kg)(9.78m/sec2) (9.8m) = 173,861 joules or 128,240 ft - Ibs The principle of conservation of energy applies; therefore we can assume that the maximum energy to be absorbed by the package is equal to the potential energy. We will neglect energy given off as heat or used in any other form.
From the actual drop test, we know that the corner of the package was deformed (compressed) 3 inches as a result of striking the un-yielding surface. The force necessary to deform the container this amount can be calculated as follows:
F
=_Ep a
F = 128,240 ft - Ibs = 512,960 lbs or 256.5 tons 3 in (ft/12 in)
Therefore, the force of impact acting on the 181361 package was 256.5 tons.
Using this same line of reasoning, the impact force on the head shipping package, 181375 may be calculated.
Ep = mgh m = 3750 lbs or 1701 kg Ep = (1701 kg)(9.78m/sec2)(9.8 m) = 163,031 joules or 120,251 ft - lbs
.h-l 2 - 35 Change 3 April 22,1983
It can be seen that under the same conditions there is less l V.
energy (6%) to be absorbed by this package. If we assume the same 3 in deformation at the corner, the force of impact becomes E = f = 120,2 51 ft lbs -
E
= 240.5 tons
.25 ft (2000 lb/ ton)
The design of the model 181375 overpack is similar to that of the 181361 overpack in most respects. Ths steel lattice work frame over sheet metal covered hardwood maple is the same. The bolt size and configuration used to attach the overpack cover to the pallet base is different, but just as secure. Therefore, it can be assum-ed that under the conditions of the drop test, the model 16375 overpack will sustain damages vary similar to the 181361 over -
pack and will retain its integrity.
4 The internal tie down system for the 1813-75 package is different than the system for the 181361 package. In the 181361 package, the source exchange container was bolted directly to the pallet base and further supported by two tie bars attached to both the overpack cover and pallet base. For the 181375 package, the irradiator machine head is not directly fastened to the pallet base or overpack cover. A tie down bracket assembly is used to hold the head in position. This assembly is bolted directly to the pallet, base and to the machine head. It also supports the top, front and back support pads. Other than eight 1/2" x 20 screws attached to the tie down bracket, the head is not fastened to the overpack. It should be noted that the wood support pads have been designed so that in place around a machine head, the over -
pack cavity is filled to within less than one inch clearance per s!de. Therefore, in the event the tie down system should fail, the machine head will not be able to move a significant distance.
Analysis of the tie down assembly will be done to demonstrate the design will not fail.
Under the conditions of the 30 ft fall, the machine irradiator head L
within the packages can be likened to the classic physics problem of an object within a falling elevator. It has been demonstrated that upon the sudden stopping of the elevator the object exerts a force. equal to twice its weight.
A suddenly applied load will produce the same deflection and therefore the same stress as a static load twice as great.
- (Reference Machinery Handbook,19th~ Edition, Page 443 lC 2. Change 3 April 22,1983
-j Therefore, the machine irradiator head will exert a force of tw' ice p
its weight or 4400 lbs against the tiedown system when the pack-age strikes an unyielding surface.
The following calculations will show that each of the three major components in the tiedown system will be able to withstand this force. Calculations will be shown for the component under both tension and shear conditions, which for this package means impacts with the head in a vertical or horizontal position. Angled impacts, l
such as the corner drops, will subject the tiedown system to com -
binations of tensile and shear loads, with each component of force being less than the maximum load.
A.
Head to bracket screws There are eight screws attaching the machine head to the two tiedown bracket assemblies.
Screw data Size / description:
1/2 - 20 UNF x 1" L Qty: 8 Tensile strength:
180,000 psi Yield strength:
162,000 psi Shear strength:
135,000 psi Stress area:
0.1599 sq in (tensile) 0.1486 sq in (shear)
Tensile load capacity per bolt Tensile load capacity = tensile strength x tensile stress area 180000 lb z
x 0.1599 in2 = 28,782 lbs per bolt in Shear load capacity per bolt Shear load capacity = Shear strength x shear stress area 135000 lb 2
x 0.1486 in2 = 20,061 lbs per bolt in
==
Conclusion:==
Each of the eight screws is capable of withstanding the entire stress load of 4400 lbs.
OG.
2 - 37 Change 3 April 22,'1983
l B.
Tie down bracket There are two tie down bracket assemblies used to attach the machine head to the overpack pallet base. These are fabricated from steel components. Drawing D 200073 in Appendix 1.3.1 illustrates these assemblies. For the purpose of this calculation, the side pieces will be subjected to the greatest loading.
D at?
ASTM A - 36 steel
==
Description:==
6" W x 0.375" thick Si:ie/ Dimensions:
Tensile strength:
58,000 psi Shear strength:
30.- 90,000 psi 2
Stress area (A):
6 x 0.375 = 2.25 in Tensile load capacity for one assembly Tensile load capacity = tensile strength x tensile stress area 58,000 lb 2
x 2.25 in2 = 130,500 lb g
Shear load capacity for one assembly 30,000lb 2
x 2.25 in2 = 67,500 lb in
==
Conclusion:==
Each of the two tie down bracket assemblies is capable of with-standing the entire stress load of 4400 lbs.
C.
Bracket to pallet base bolts There are four bolts attaching the two tie down bracket assemblies to the overpack pallet base.
Bolt data Size - description:
1 - 8 UNC x 7" SAE J429 Grade 8, Qty: 4 Tensile strength:
150,000 psi (min)
Yield strangth:
130,000 psi (min)
Proof load:
120,000 psi Shear strength:
112,500 psi (min)
O 0.606 sq. in. (tensile)
Stress area:
0.551 sq. in. (shear) 2 - 38 Change 3 April 22,1983
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. Tensile load capacity per bolt G'
Tensile load capacity = tensile strength x tensile stress area
~
150,000 lb x 0.606 in2 =~ 90,900 lbs per bolt inz.
Shear ' load cabacity per bolt Shear load capacity = shear strength x shear stress area
~s l
11' '; 500lb 2
inz x 0.551 in2 = 61, 988 lbs per bolt h
./; i
==
Conclusion:==
)
'Each of the four bolts is capable of withstanding the stress load of 4400 lbs.
t From the preceding calculations it may be seen that t,he tie down assembly can withstand the stresses brought on by-the 30 foot drop test.
However, the machine head itself will be subject to stress in the area of the two trunnion bosses where it is bolted to the tie down assembly. The following analysis will'show that the machine head will withstand the stress.
t' D.
Machine irradiator head From the description in 1.2.1.lb, and drawings E - 63790 and r
A'- 46686 in Appendix 1.3.1, it may be seen that the trunnion bosses are of 0.75" steel construction. The bosses are brazed to the brass head casting along their entira circumference.
~
1; Boss data 1b
==
Description:==
A36 steel Sizie/ dimension:
0.751n x 6" diam.
F111' t weld size:
- 0. Sin x 1B.84 in e
Weld cro'ss sectional area:
0.35 in2
_' Shear strength of-weld:
11,300 psi i.
e t
The trunnidn boss; weld inould beithe weakest part 'of this com-ponent. Tae follo'aing calculation will shokr the shear stress
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capability of the bo'ss welds.
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- Shear load capacity
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Shear strength x Area = Shear load capacity 11,300 lb x.35 in2 = 3955 lb Inz c.
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'The shear loading will take place along the entire length of the
'e s.
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- weld.
3 Therefore the shear load capacity for each boss equals c,-
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t 395516 i
.j 7'n.
x 18.84 in = 74,512 lb y
yn in
==
Conclusion:==
1-
- 'e Each of the two trunnion bosses is capable of withstanding the entire stress load of 4400 lbs.
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