ML20210F870

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Rev 1 to PGE-1076, Trojan Reactor Vessel Package Sar
ML20210F870
Person / Time
Site: 07109271, Trojan  File:Portland General Electric icon.png
Issue date: 07/22/1999
From:
PORTLAND GENERAL ELECTRIC CO.
To:
Shared Package
ML20210F864 List:
References
PGE-1076-01, PGE-1076-R01, NUDOCS 9908020164
Download: ML20210F870 (48)
v • d • e


Text

PGE-1076 PORTLAND GENERAL ELECTRIC COMPANY TROJAN REACTOR VERSEL PACKAGE i SAFETY ANALYSIS REPORT 7

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l Portland General Electric Company 121 SW Salmon Street Portisnd, Oregon 97204

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Trojan Reactor VesselPackage - Safety Analysis Report

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LIST OF FIGURES figins Shes1 Title 1-1 1 Reactor Pressure Vessel Package on Transporter 2 Reactor Vessel Package on Barge 1-2 1- General Arrangement Integral Shielding, Cradle, Tie Down Assembly and Foam Ring Impact Limiters .

1-3 1 Reactor Vessel and Internals 1-3A 1 Reactor Vessel Package 2 Reactor Vessel Package 1-4 1 Reactor Vessel Penetrations 2 Reactor Inlet Nozzle

's 3 Reactor Outlet Nozzle -

4 Drain Penetration 5 Incore Instrumentation Penetration 6 Head Vent Penetration 7 CRDM Penetration 8 Flange Monitoring Tube 1-5 l' Reactor Vessel Main Shielding Details 2 Reactor Vessel Supplemental Shielding Detail

3. Reactor Vessel Nozzles Supplemental Shielding Details
4. Reactor Vessel Nozzles Supplemental Shielding Details 5 Reactor Vessel Supplemental Shielding Attachment Detail at Main Shielding Closure Plates 6 Reactor Vessel Shielding Detail Notes 7 General Notes for Figures 1-4 and 1-5 x Revision I

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Trojan Reactor Vessel Package - Safety Analysis Report h 1-6 1 Impact Limiter Casing Assembly View From End 2 Impact Limiter Casing

  • uembly Reactor Head End (Elevation) 3 Impact Limiter Casing Assembly Reactor Head End (Elevation) 4 Impact Limiter Casing Assembly Reactor Bottom End (Elevation) 5 Impact Limiter Casing Assembly Reactor Bottom End (Elevation) 6 Impact Limiter Casing Assembly Assembly Details 7 Impact Limiter Casing Assembly Assembly Details 8 Impact Limiter Casing Assembly Assembly Details 9- Impact Limiter Casing Assembly Assembly Details 10 Impact Limiter Casing Assembly Notes 2-1 RVP Transport Configuration 2-2 RVP Puncture Event Orientations 2-3 RVP to Transporter Load Path (Longitudinal) 2-4 RVP to Transponer Load Path (Vertical)

RVP to Barge Load Path (Longitudinal) p 2-5

\ 2-6 ' RVP to Barge Load Path (Vertical) 2-7 RVP to Transponer and Barge Load Path (Transverse) 5-1 Reactor Vessel Model 5-2 Reactor Vessel Model Source Regions 5-3 Reactor Vessel Conveyance Dose Points 7-1 On-site Transport Route Trojan Nuclear Plant 7-2 River Transport Route Trojan to Port of Benton 7-3 Overland Transport Route Port of Benton to US Ecology V xi Revision 1

Trojan Reactor YesselPackage- Safety Analysis Report k's' LIST OF EFFECTIVE PAGES Paoe Number Revision Table of Contents i through ix 0 x and xi 1 xii 0 xiii and xiv 1 Page 1-1 0 Page 1-2 1 Page 1-3 0 Page 1-4 1 Pages 1-5 through 1-20 0 Tables 1-1 and 1-2 0 O Figures 1-1 through 1-3 Figure 1-4, Sheets 1-3 0

0 Figure 1-4, Sheet 5 1 Figure 1-4, Sheets 5-8 0 .

Figure 1-5, Sheets 1-7 1 Figure 1-6, Sheets 1-10 1 Pages 2-1 through 2-37 0 Pages 2-38 through 2-43 1 Pages 2-44 through 2-62 0 Tables 2-1 through 2-4 0 Table 2-5 1 Tables 2-6 through 2-18 0 Figures 2-1 through 2-7 0 xiii Revision 1

Trojan Reactor VesselPackage- Safety Analysis Report Pages 3-1 through 3-11 0 i Tables 3-1 through 3-4 0 l

Pages 4-1 through 4-6 0 Pages 5-1 through 5-11 0 Tables 5-1 through 5-12 0 Figures 5-1 through 5-3 0 Page 6-1. O Page 7-1 0 Page 7-2 1 Pages 7-3 through 7-5 0 Page 7-6 1 Pages 7-7 and 7-8 0 Figures 7-1 through 7-3 0 Pages 8-1 through 8-11 0 Table 8-1 0 l

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Traian Reactor vesset rakau - Safety Analvsis Reoort

4. The reactor vessel external attachments will be removed and all penetrations will be sealed with welded closures.
5. Shielding will be installed on the exterior surface of the reactor vessel, as necessary, to ensure compliance with the dose rate limits of 10 CFR 71.
5. Impact limiters will be attached to the RVP to limit stresses to values well below yield for the impact (drop) loads.

After preparation as a Type B (as exempted) shipping package, the RVP will be loaded onto a transporter and tied down and transponed as an exclusive use shipment. He transporter is a hydraulically leveled platfo m designed for transporting large, heavy loads. Once loaded onto the transporter and tied down, the RVP will remain attached to the transporter until the RVP is

. off-loaded at the disposal site. The RVP on the transporter is shown on Figure 1-1.

The loaded transporter will be moved from the Trojan Industrial Area to the barge slip on the TNP site where it will be moved onto the barge and secured. The loaded transporter will be barged to the Port of Benton in Washington. The loaded transporter on the barge is shown on Figure 1-1. The loaded transponer will be moved off of the barge and transported by road (less than 30 miles) to the disposal facility operated by US Ecology, near Richland, Washington. He O- RVP will be then be off-loaded from the transporter at the disposal facility.

The quality assurance requirements of 10 CFR 71, hbpart H, applicable to the design, fabrication, and use of packaging for radioactive materials are covered by TNP's NRC-approved 10 CFR 50, Appendix B quality assurance program (PGE-8010). PGE-8010," Trojan Nuclear Plant Nuclear Quality Assurance Program," was approved by the NRC for application to design, fabrication, assembly, and modification of transportation packages by NRC letter dated April 28,1999," Quality Assurance Program Approval for Radioactive Material Packages No.

0327, Revision No. 9."

1.1.1 APPLICATION APPROACH ne PGE application is based on altemative transport conditions due to the uniqueness of the RVP and its one-time shipment. Therefore, this PGE request requires NRC approval pursuant to 10 CFR 71.41(c) or alternatively,10 CFR 71.8. The 10 CFR 71 regulations provide the NRC with authorization to approve packaging and shipments based on attemative transport conditions.

These regulations recognize that special controls imposed by the shipper may provide equivalent safety as those specified in 10 CFR 71.

1-2 Revision 1

7 miaor naactor vessetrachaue- sderv Anaivsts nemort 1.1.1.2 Hvnothetient Accidaat Condition - RVP Dron ,

- The hypothetical accident condition specified by 10 CFR 71.73(c)(1) requires a drop of the specimen through a distance of 30 feet on a flat, essentially unyielding, horizontal surface, striking the surface in a position for which maximum damage is expected. PGE is taking special precautions to ensure the safe shipment of the RVP which are described in Chapter 7 of the SAR.

Based on the SAR specified transportation route, method of shipment, and special controls, the 30 foot drop should not be considered a hypothetical accident condition. Therefore, PGE  ;

requests NRC ==p-re of the conditions and controls for this shipment under 10 CFR 71.41(c) '

or an exemption under 10 CFR 71.8 based on the demonstration of adequate safety of the shipment. j

, 10 CFR 71.73 specifies the hypothetical accident conditions to which Type B radioactive material packages are to be designed for unrestricted use. According to a NRC-sponsored modal study, packages designed to 10 CFR 71.73 are capable of withe-ading greater than 99% of all credible accidents, rail and highway, without functional failure. As a consequence,10 CFR 71 does not require in-transit precautions such as escorts, routing restrictions, speed controls, moving safety zones, etc.

PGE has conducted a safety evaluation of the specific route, method of transport, and operational O controls and shipment specific conditions to be utilized during the transportation of the package.

1.1.1.2.1 Transportation Route Evaluation The overland route for the RVP from the Port of Benton to the US Ecology disposal site can be l considered as very benign in that: 1) the road is in good condition,2) there are no obstacles such I as heavy traffic, bridges or overpass'e s to cross,3) there are no "hard targets" or surfaces,4) the  !

area is essentially unpopulated,5) there are no hazardous terrain features, and 6) it is an area l where nuclear activities are well known and understood. A portion of the haul route was used for disposal of the TNP Steam Generators and Pressurizer and is routinely used for the transport of dare=missioned defueled naval submarine reactor plants.

1-4 Revision 1

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WELDING SHALL BE PERFORMED IN ACCORDANCE WITH THE APPLICABLE METHODS AND GUIDANCE PROVIDED IN SECTION Vill AND SECTION lil, SUB-SECTION ND AS APPROPRIATE.

2. WELD NDE SHALL BE PERFORMED IN ACCORDANCE WITH THE APPLICABLE METHODS AND GUIDANCE PROVIDED IN ASME SECTION lit, SUB-SECTION ND, OR ASME SECTION Vill AS APPROPRIATE.
3. WELDERS AND WELDING PROCEDURES SHALL BE IN ACCORDANCE WITH THE GUIDANCE OF ASME SECTION IX.

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1. FOAM CASING STEEL IS SHOP FABRICATED TO FORM THE ANGULAR SEGMENTS.
2. CASING IS CONSTRUCTED OF %" CARBON STEEL SA-516 GR.70:

SUPPORTING BRACKETS CONSTRUCTED OF SA-516 GR. 70 MATERIAL.

3. IMPACT LIMITER FOAM IS CLOSED-CELL POLYURETHANE LAST-A-FOAM FR-3720 WITH A DENSITY OF 20 pef +/- 10X IAW BURNS AND ROE ENTERPRISES,INC. FOAM IMPACT LIMITER TECHNICAL SPECIFICATION 2030-M002.
4. IMPACT LIMITER FOAM JOINTS MAY BE JOINED WITH MANUFACTURER APPROVED EPOXY MATERIAL AS REQUIRED.
5. ALL' FOAM ENCASING STEEL SEAMS WILL BE CLOSED BY WELDING.

~

6. IMPACT LIMITER WILL BE ASSEMBLED OUT OF TWO (2) i 70* SEGMENTS AND TWO (2) 134' SEGMENTS (APPROXIMATE ANGLES). l
7. REACTOR VESSEL REFUELING . SEAL LEDGE SHALL BE CUT AS FLUSH WITH FLANGE SURFACE AS PRACTICABLE BEFORE IMPACT LIMITER INSTALLATION. ,
8. ALL WELD SIZES ARE NOMINAL.
  • 9. TACK WELD THREADED ROD NUTS TO SURROUNDAC STEEL TO SECURE IMPACT LIMITER ASSEMBLY.
10. WELDING SHALL BE PERFORMED IN ACCORDANCE WITH THE APPLICABLE METHODS AND GUIDANCE PROVIDED IN ASME CODE SECTION Vill OR AISC AWS D1.1 AS APPROPRIATE.
11. WELD NDE SHALL BE PERFORMED IN ACCORDANCE WITH THE APPLICABLE METHODS AND GUIDANCE PROVIDED IN ASME SECTION VillOR AISC AWS D1.1 AS APPROPRIATE.
12. WELDER OUALIFICATIONS AND WELDING PROCEDURES SHALL BE IN ACCORDANCE WITH THE GUIDANCE OF ASME SECTION IX OR AISC AWS D1.1

/m1 AS APPROPRIATE.

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FIGURE 1-6 IMPACT LIMITER CASING ASSEMBLY NOTES 4 /a/MM9

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DWG N0_J-SJ64_,_)4 REV dSf4T.,1{,0F,1,0_ a b Revision 1

c a

Trolan Reactor VesselPackare- Safety Analysis Rer> ort @

(n

_)

than for an oblique orientation. Therefore, the secondary crush distance is also not goveming.

Impact calculations are performed using initial and environmental conditions which result in the maximum impact severity for the RVP. Subsequent evaluations of the ability of the package to withstand these loads without comp omise of the containment boundary utilize minimum material properties. Thus, all conditions of applied loading and structural strength are conservatively bounded. The maximum impact conditions correspond to the maximum mechanical strength of the polyurethane foam energy absorbing material, and occur at the minimum ambient temperature of-20 'F and without insolation, in accordance with Regulatory Guide 7.8. Additional calculations are performed to determine the maximum deformation under warm conditions, in order to demonstrate that the maximum impact level obtained under cold conditions is not exceeded by excessive crush of the polyurethane foam or by contact of a "hard point" (i.e., uncusMoned contact) with the ground.

Since impacts on the ends of the RVP are not credible, as discussed above, the impact limiters are required to protect the package in only side and relatively shallow oblique impacts. The -

impact limiters are, therefore, co ducted in the shape of annular rings and fastened to the RVP as shown in Figure 1-6. The outer diameter is 336", and the width is 58", dimensions which do not include the %" thick structural angles on the outer comer seams. The inner diameter of the O lower limiter is based on the outer diameter of the shield, approximately 202". The inner diameter of the uppe limiter is based on the outer diameter of the upper flange, or 205". These two inner diameters,202" and 205", differ by an insignificant amount, and a value of 205" is used conservatively for both. The outside edge of the upper impact limiter is located 99" above the nozzle centerline, and the outside edge of the lower impact limiter is located 246" below the nozzle centerline. The inside face of each impact limiter is buttressed by a steel structure to prevent the dislodging of the limiter in a drop event. The impact limiters are retained against the inboard buttresses by means of tie rods through their thickness. No welding is performed to the material of the vessel. The impact limiters are encased in %" thick steel shells of ASTM A516 Gr 70, but due to the case with which buckling may occur, this material does not add to impact severity. See Appendices 2-7A and 2-9 for f c.ner description of the impact limiter structure and impact stress analysis.

The maximum RVP protrusion is the inlet nozzle, which is conservatively taken as extending 41.i3" from the vessel wall. Since the vessel wall outer diameter is 192", the maximum protrusion diameter is 192 + 2(41.13) = 274.3". However, a distance of 275" is conservatively used. Since the impact limiter outer diameter is 336", the minimum distance from the limiter o.d. to the nearest protrusion is (336 - 275)/2 = 30.5". In the oblique drop case, the upper head attachment stud is nearest the ground. The studs are nominally 7" in diameter and located on a 95.94" radius, and the outer end typically extends above the sealing surface a maximum l 2 - 38 Revision 1

Trolan Reactor VesselPachate- Safety Analysis Report O of 47.5." Due to installation complexity, one stud extends approximately 49" nbove the sealing surface. However, adequate clearance is maintained during the drop analysis. The design weight of the RVP, including the impact limiters, is 2.04 x 10'lb. The CG is located approximately 155" below the sealing surface, which is essentially equidistant between the two impact limiters, at the geometric center of the package.

De free drop analysis is performed using the proprietary code CASKDROP, which is described in detail in Appendix 2-7B. In brief, the crush area of the impact limiter at each deformation step is calculated. The area is subdivided into equilateral cells, and for each cell, the strain is calculated. The force corresponding to each cell at the calculated strain is found using the foam stress-strain data, and added up to give the total force of the impact limiter at each deformation.

CASKDROP uses a quasi-static energy balance approach, in which the amount of energy consumed is the cumulative sum of crush force times deformation increment. When the total energy absorbed equals the total potential energy of the drop (including crush distance), the solution was complete. The impact force is equal to the total maximum crush force divided by the package weight.

The results of the free drop impact analyses are given in Table 2-15. All impact values are given for the package CG, defined in units ofg, and are normal to the ground. For the O horizontal drops, the package remains in a horizontal position throughout the drop event. The crush distance is defined as the total deformation of each limiter in a direction normal to the

. package axis. Maximum strain is the maximum value of the ratio: crush distance / original distance for the limiter. Strain has no absolute upper limit, but the values reached in this analysis are well below any strain hardening limit. The resulting maximum impact is 20.lg for the cold, -20 'F case, and the minimum clearance over the inlet nozzle is 6.4" in the warm case.

These values are conservatively approximated for use in the free drop stress analysis as 22g and 6.0". Since the impact limiter forces are well balanced and the package remains horizontal, no

~ forces are developed which would tend to dislodge the impact limiters from the package. Note also that, due to the relatively small strain, the global deformations of the impact limiters are small, and the overall integrity of the impact limiter structure is not significantly degraded. In the oblique drop case, the initial pivot point on the end of the lower hemispherical head is

- assumed to exist throughout the primary drop event. For a free drop height of I l' for the distant limiter, the CG drops 85.3 ", or 7', and has an initial impact orientation of 19* to the horizontal. The package continues to rotate throughout the impact until it comes to rest, but the added rotation is relatively small. The package can, therefore, be assumed to undergo the drop event at a constant orientation to the ground equal to the average of the initial and fmal crush angle, or an average of 22.5'(warm case). The results of the analysis are also given in Table 2-15. The maximum crush distance and corresponding strain are given for the edge of the limiter which is crushed the most (i.e., toward the upper head) and are measured normal to the 2 - 39 Revision 1

.E Trolan Reactor VesselPackare- Safety Analysis Report h e

d '

l ground. Relative to both impact severity at the package CG and to minimum ground clearance over uncushioned structure, the oblique drop event is not goveming compared to the horizontal drop. .

2.7.1.2 Reactor Ve==*1 Free Drop Stress Analysis The RVP is analyzed to show that, when exposed to the impact levels determined in Section 2.7.1.1 (22g for HAC horizontal drop), the acceptance criteria established in Section 2.1.2 are satisfied for the containment boundary. These criteria are, that stress remains clastic in the sealing region of the vessel bcdy and upper head; that attachment stud preload is not significantly affected; and that, in accordance with Regulatory Guide 7.6, stresses in the vessel components satisfy the following:

P < 2.4S. or 0.7S,, whichever is less P. + P < 3.6S, or S,, whichever is less In addition, Section 2.7.1.4 demonstrates that the maximum possible hypothetical flaw in the vessel containment boundary remains stable under the bounding conditions of ambient 7 temperature, material toughness, and applied stress.

De following analyses are performed and described in Appendix 2-9 to demonstrate the adequacy of the RVP design under free drop conditions.

2.7.1.2.1 Containment Boundary Stress Stresses in the RVP shell due to the governing 22g side drop impact are determined by means of the finite element model described in, Appendix 2-9. The resulting maximum ~ stress intensity in the vessel shell, P. + P., is 26,438 psi, located near the bottom of the vessel, on the outside surface, beneath the lower impact limiter. Since this stress includes bending components, the allowable stress is the lesser of 3.6S or S,. For the vessel wall material of SA-533 Grade B, Class 1, S, is governing and is 80,000 psi at the core region bounding temperature of 200 'F.

The margin of safety is 000 MS= -1 = + 2.03 26,438 he maximum membrane stress intensity, P,,, is 14,700 psi, located in the region just below the sealing flange, above the nozzles. In this case, the allowable stress is the lesser of 2.4S or 2 - 40 Revision 1 i

l

o Trolan Reactor VesselPackaer - Safety Analysis Rer> ort .

O 0.7S,. For SA-533, at 175 'F (outside the core region),0.7S, is governing, where S, is again 80,000 psi. The margin ofsafety is:

MS= -l = +2.81 14,700 Stresses in the nozzle region are determined by means of a submodel, based on the main finite element model, as described in Appendix 2-9. The maximum stress in the radius is 24,548 psi, and, since it is less than the maximum stress intensity of 26,438 psi, is not governing. Thus, the margin ofsafety on vessel body stress is positive during the free drop event. Further, all material in the region of the upper head seals remains completely clastic.

2.7.1.2.2 Upper Head Attachment Studs The upper head is attached using n = 54, norainally 7" diameter studs on a radius of R =

95.94", pretensioned to 720,000 lb. Since the internal cross sectional area of the head is A =

2 x(83.672) = 21,993 in and the intemal pressure is p = 100 psi, a tensile load is applied to each stud equal to F, = = 40,7281b In the horizontal side drop, a length of the head outer flange equal to 12.75" is loaded by the impact limiter in the upward vertical direction, with an additional inertia load downward equal to the head weight times the impact load of 22g, located at the head CG. Thus, there are two opposing forces on the upper head; the impact limiter transmitted load upward, and the head inertia load downward.

First, the impact limiter transmitted force is determined. The load on the head flange is

2.75/58 = 22% of the total impact limiter load, for a 58-inch wide limiter. For a total package weight of 2.04 x 10' lb and an impact of 22g, the load on the head flange, Fu, , is 4.94(106) lb.

The moment on the head due to the impact limiter transmitted force is, therefore, 12.75/2(Fu,) = 31.5 (106) in-lb, which is applied in a clockwise sense about the vessel sealing surface.

Next, the inertia load is determined. The location of the upper head CO is 35.2" above the  ;

vessel sealing surface, and has a weight which is bounded by 150,000 lb. The LDCC material l located within the head is assumed to break free of the remainder within the vessel and further

' load the head. For an intemal radius of r = 83.67", the volume of the head is 710 ft'. Since the 2 - 41 Revision 1

f Trolan Reactor vesselPackare- Safety Analdis Report O

maximum density of the LDCC material is 65 lb/ft', the total weight of head and contents is W6

150,000 + 710(65) = 196,150 lb. For a 22g impact, the moment is equal to W,(35.2)(22)

152 x 10' in-lb, in the counterclockwise sense. Note that the CO location of 35.2"

. conservatively neglects the effect of the LDCC, which would decrease the moment arm.

The net moment on the stnd pattern is, therefore, M = 152 x 105 - 31.5 x 10' = 121 x 10'in-lb.

A conservative estimate of the maximum stud force is found from F,= + F, = 87,4391b nR If friction between the upper head and the main vessel is neglected, the average shear load on a I stud is a function of the difference between the impact limiter transmitted force, Fu, and the downward shear load due to the inertia force, since these loads are in opposite directions. The average load per stud is:

Fu-22 W, F, = = 11,569lb n

These tensile and shear stud loads are now compared to those resulting from the oblique drop case. In this case, a vertical impact of 16.3g at the vessel CG is used (see Table 2-15). The upper head CG is a total of 177.9 + 240.4 = 418.3" from the pivot point, measured horizontally with the package axis 22.5' from the horizontal. The impact at the location of the head CG is, therefore:

G ,g = 240.4* 16.3 = 28.4g Again, the force on the head flange due to an impact limiter transmitted force is determined first. The component of total impact limiter force which is parallel to the sealing surface (and normal to the head flange OD) is 23.1 x 10' lb. As before, only 22% of this load is carried by the head flange, and, therefore, Fon = (0.22)23.1 x 10' = 5.08 x 10' lb. The moment generated is equal to 12.75/2(Fu) = 32.4 x 106 in-lb, clockwise.

The inertia load is determined next. The impact load, Gw, is resolved into components parallel and normal to the sealing surface. The parallel inertia force on the head is F i,= 5.14 x 10'lb. The resulting moment is 35.2F,, = 181 x 10'in-lb in the counterclockwise direction.

The net moment applied to the studs is, therefore, M = 181 x 10'- 32.4 x 106 = 149 x 106 in-lb.

2 -42 Revision 1

c Trolan Reactor VesselPackage- Safety Analysis Retsort O For the normal force, the weight of the entire intemal material (core materials plus LDCC),

rounded up to a value of 700,000 lb, is conservatively used in addition to the weight of the upper head itself. 'Ihis force is Fw = Gu(700,000 + 150,000) = 9.27 x 10'lb, which acts in parallel to the pressure load on the studs. The total maximum bolt force is:

+

F"" = nR n

+F' = 269,915 /b If friction between the upper head and the main vessel is neglected, the average shear load on a stud is a function of the difference between the impact limiter transmitted force, Fu, and the downward shear load due to the inertia force since these loads are in opposite directions. The q

average load per stud is:

i F, = " =1,Illib n

The goveming stud loads are, therefore,269,915 lb tensile from the oblique drop event, and 11,569 lb shear from the horizontal side drop event. Since the tensile load of 269,915 lb is small relative to the stud preload force of 720,000 lb, there is no added tensile load on the stud due to the free drop event, and the flange seal compression is unaffected.

If the coefficient of friction were as low as 0.1, the frictional shear resistance force of 1 (0.1)720,000 = 72,000 lb would still be greatly in excess of the maximum shear load of 11,569  !

lb. However, this is conservatively ignored and the stud stress due to both the maximum shear force and the preload forces are conservatively combined as follows. The area of the stud,

{

excluding the 0.75" central hole is 35.8 in 2. This results in a shear stress due to the drop load of 322 psi and a tensile stress due to the preload of 20,067 psi. These stresses may be combined to give 1

SI=/0 24 7 =20,070pst 2

For the ASTM SA 540 Grade B24 Class 3 studs, the value of S at a temperature of 175 'F is 41,875 psi. The margin of safety is:

MS= '

-1 = +1.09 20,070 Therefore, the head stud margin of safety is positive, and the upper head seals retain full effectiveness, during the worst case free drop event.

2 - 43 Revision I l

holan Reactor YesselPackage - Safety Analysis Rer> ort @

O 4 Table 2-5 l

1 Range of Minimum Mechanical Properties of Steel Materials (-40 *F - 200*F)'

Youn Yield Tensile 1 Material Applicr%n ~

Modus $u's Strength Strength l Specification E (x 105 ksi) Sy (ksi) S,(ksi)

SA-533 Gr.B Reactor Vessel Shell, Top 29.6 -28.5 50- 47.2 80 Class 1 Head SA-508 Inlet and Outlet Nozzles 28.2 - 27.1 50-47.1 80 Class 2 SA-240 Type Nozzle Closure Plates 28.8 - 27.6 25 - 21.3 70 - 66.2 304L SA-336 Nozzles Safe Ends 28.8 - 27.6 30- 25.8 70 Grade F316(F8m)

SA-540 Grade B24 Reactor Vessel Head Studs 28.2 -27.1 130 - 121.5 145 Class 3 SA-516 Grade 70 2" and 5" Main Shielding: 29.9 -28.8 38- 34.6 70 5/8 inches Penetration Closures 2 Other Shieldine 1

1 Notes:

1. HAC thermal (fire
2. Normalized, to fine) grainmetal temperature values are not included. See Appendix 3-1.

practice.

. Welding consumables:' Allowable stresses / stress intensities for welds are based on lower of the two base metals as referenced in Section 2.1.2.2.

O Revision 1 ,

l l

Trolan Reactor VesselPackare - Safety Analysis Report O Once loaded onto the transporter, the RVP will not be removed until it is off-loaded into the disposal trench at the disposal site (US Ecology).

De loaded transporter will be moved from the package preparation area in the Trojan Industrial ,

Area to the barge slip on the TNP site. Transporter speed will be limited to 5 mph. It will then l be moved onto the barge and secured by an engineered tiedown system. This tiedown system is designed to meet the requirements of ANSI N14.24-1985, except that the transverse collision acceleration loading was increased from 0.5g to 1.6g based on the probabilistic safety study for l river transport (Appendix l-1). Figure 7-1 shows the on-site transport route. The barge will then travel up the Columbia River approximately 270 miles to the Port of Benton in Washington where the loading process will be reversed (i.e., the loaded transporter will be moved off of the barge). Figure 7-2 shows the river transport route. The loaded transporter will be transported less than 30 miles by road to the disposal facility operated by US Ecology near Richland, Washington. Figure 7-3 shows the overland transport route from the Port of Benton to the US Ecology disposal facility. The RVP will then be removed from the transporter for disposal.

The shipment will comply with the specifications of ANSI N14.24-1985, "American National Standard for Highway Route Controlled Quantities ofRadioactive Materials - Domestic Barge

, Transport," and with the applicable requirements of 10 CFR 71 - Packaging and Transportation of Radioactive Material,33 CFR - Navigation and Navigable Waters,46 CFR - Shipping, and O 49 CFR - Transportation.

7.2 PREPARATIONS FOR TRANSPORT The RVP will be prepared as a Type B (as exempted) shipping package that meets 10 CFR 71 requirements prior to transport from the TNP Industrial Area. A discussion of the preparations required to achieve compliance with these requirements is provided in Chapter 2. Chapter 8 describes the inspections and tests that will be performed to verify the package has been properly constructed.

Sections 8.5.9 and 8.5.10 discuss the radiation surveys that will be performed to ensure compliance with 10 CFR 71 requirements prior to shipment. Additional surveys required by 49 CFR 173.443 will also be performed. Package markings will meet the requirements as stated in Section 8.4.

De transporter and prime mover will be inspected to ensure the vehicles are working properly and to ensure conformance with applicable state and federal standards. The structural adequacy of the transporter will be demonstrated by analysis and the transporter will be loaded in accordance with the manufacturer's specifications. Prior to transport of the RVP, the entire transportation route, onsite and offsite, will be evaluated to confirm that it is stmeturally capable

. 7-2 Revision 1

l Trolan Reactor Vessel Packaee - Safety Analysis Retsort O 16. The tugs will meet the applicable requirements of 46 CFR Subchapter C, "Uninspected Vessels." The tugs will be inspected by a marine surveyor prior to I departure.

During the river transport, the following restrictions apply:

1. The maximum speed will be 10 knots.
2. The backup tug will escort the barge when the package is on board and the barge is not moored.
3. Transit of the barge will be halted to avoid hazardous conditions or to await passage through a lock or to await safe navigation conditions such as upriver from the Port of Pasco where transit must be made during daylight hours. When moored, appropriate measures will be taken to restrict unauthorized access to the barge.
4. During the barge transport phase, the tugs will check in with the base station at least every four hours.

7.5 PORT OF BENTON TO US ECOLOGY SITE TRANSIT After arrival at the Port of Benton barge slip, the loading process will be reversed following the sequence listed below.

1. The barge will be grounded, the transporter-to-barge engineered tiedowns will be removed and the transporter will be moved off the barge onto the landing.
2. Prior to departing the Port of Benton Property, the Washington State Patrol may, at its option, perform a CVSA inspection of the loaded transporter and the prime mover.
3. The loaded transporter will travel to the US Ecology site, approximately 30 miles from the barge slip. A portion of the haul route has been used for the transport of decommissioned defueled naval submarine reactor compartments and for the l disposal of the TNP Steam Generators and Pressurizer (Reference 7-3). The following requirements will be met for the transit:
a. The entire route will be evaluated to ensure it is structurally capable of handling the load prior to the RVP shipment.

7-6 Revision 1

i PORTLAND GENERAL ELECTRIC COMPANY TROJAN NUCLEAR PLANT i

APPENDIX 2-10 f

RPV EXTERNAL SHIELDING STRUCTURAL INTEGRITY ANALYSIS PORTLAND GENERAL ELECTRIC COMPANY O w.. Aif M E rJ 6ND 394-2-2.

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May'10,1999 SUPpLIEn DOCUMENT STAMP E WMON3

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APPENDIX 2-10 Rev. 3 Table of Contents For

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RPV EXTERNAL SHIELDING STRUCTURAL INTEGRITY ANALYSIS FIGURES 2-10-1 Reactor Vessel Shielding Details (three sheets)

Reactor Vessel Supplemental Shielding, Attachment Detail at Main Shielding Closure Plates Reactor Vessel Supplemental Shielding, Alternate Attachment Detail at Main Shielding Closure Plates Reactor Vessel Nonles Supplemental Shielding Details Total pages in this appendix = 51 Revision Record:

Rev.1, initial SAR issue; Rev. 2, added pages 44 and 45, Supplemental Shielding Attach-ment Details at Main Shielding; Rev. 3, added new pages 33a through 33e and 42,43,43a to cover shielding figure updates and design of the supplementary RPV noule shielding, and updated title page and pages 11,4,16,17 and 38 to agree with as-built dimensions and

( welding details.

i

~..-_.... . ,, j i

i Appendix 2-10 Rev. 3 fG from the HAC's (oblique drop) 4.7 g LAF times the weight of the entire package, as the 10 g

() LAF longitudinal load from the NCT would be applied only to the weight of the shielding. A finite element analysis was also performed on the shield plates to determine the maximum bearing pressure and the Maximum Stress Intensity. The concurrent stresses in the reactor nozzles are also specified by this calculation, since they are equal to the stresses in the shield plate. The loads used in this analysis are fully described in the results table of section VU of this appendix. i The 5" plates were also analyzed for the bearing stresses (local membrane plus bending stress intensity (P + P S)) induced at the cradle location at the bottom of the RPV. The cradle bear-ing stresses were increased by a LAF of 1.6 g to account for the normal transportation loads that the cradles will see. This condition does not govem any of the design, but was analyzed for comparison purposes. ,

B. Shield Plate Seam Weld Sizing for the Worst Case Loading-The 2" and 5" shielding jackets are designed not to break apart or separate from the RPV, under any NCT event or any HAC event (including the 1l' drop). There are two specific weld types that are important to the overall integrity of the primary shield assembly (the 2" and 5" platejacket). The first weld type is the longitudinal (seam) weld in the main 2" and 5" shield plates (welded longitudinally as the vessel sits in the horizontal). In the case of the l 5" shielding, three seam welds join three 120' shield segments together in this manner. For the 2" shielding, eight segments arejoined with these longitudinal seam welds. The second O

O weld typejoins the 2" shield plates to the 5" plates circumferentially around the RPV.

To size the longitudinal welds, it was necessary to examine what forces might act to tear the plates apart from each other. For the HAC event, the worst case would be for the maximum impact LAF applied to separate one of the plates from its attachment weldjoints. Based on the impact analysis of Appendix 2-7, the worst case is the 4.7 g LAF resulting from the resul-tant from oblique drop from Il'. The longitudinal welds for both the 2" and 5" plates have been sized by applying an LAF of 4.7 to the total package weight of 1020 tons.

The circumferential welds are analyzed for the application of the 10 g (NCT) longitudinal load as the bounding case. The analysis is based on the weight of the total shielding (maximum, plus spot shielding) and both impact limiters.

C. Contact Local Stresses Between the Vessel Wall & Shielding-The RPV is jacketed by two sections of steel shielding that is 2" thick in the reactor nozzle area and 5" thick in the core region. As a result of fabrication tolerances in both the reactor and shield manufacturing, it is expected that there will be geometrical deviations in the ves-sel',s cylindrical shape. During transportation and vessel handling, it is essential that the there be no relative motion between the RPV and the shieldingjackets, so that the whole assembly acts as a rigid body. This motion can be eliminated by a combination of shimming and com-pressing the shield against the vessel wall. Two engineering concerns need to be addressed:

f3 V

d %girojan shlAsar dos 4

Appendix 2-10 ~ '

Rev. 3 g~

()/ B. Calculation for the Shield Plate Seam Weld Sizing for the Worst Case Loading -

I Weld sizing for cylindrical shield s1 = 5" and s2 = 2" thick .

{

The design requirements are specified as follows:

The total shield weight was calculated as being 241,292 lbs (including the skirt), the added supplementary shielding plates total of 14 tons, and the maximum impact limiter weight total of 7,3 torfs.

Circumferential and Longitudinal Welds:

Shield, as discussed in previous section, has two basic thicknesses. After assembly of 5" thick sections, the 2" sections are circumferentially welded to the bottom - 5" shield cylinder. The sizing of the circumferential weld is shown bellow.

Circumferential Weld Sizing The worst case longitudinal design load that acts upon the circumferential joint is based on the NCT 10 g LAF event acting on the total weight consisting of the main shielding, supplemental shielding and the two impact limiters.

Wrlong (241292.-(14 - 73) 2000) 10 Weld Design Load (lb) for NCT 10 g LAF,14 tons spot shielding and both of the impact limiters (73 tons)

Wrlong - 4.153 10' (Ib) D,= 196.125 (in) RPV max OD plus 2" shield thickness Awe : 2 x - - 12 Awe = 604.145 (in) " "E * * "8 * " #' we h consewabeh 2

reduced by 12.0" to account for possible variance between the 2" and 5" shield final seam length.

Weld line load fwc: twe = Wrlong twe = 6 874 10' (Ib/in)

Awe Sm 23300 Jef 0.5 ^S allowable stress for SA-516 Gr. 70 & fillet wel@d mt jo.

efficiency.

Weld NCT allowable stress limit: 2 Sm-Jef t = t.16510' (psi)

Fillet Weld throat: p v.c. a.=ro > l ir , c..r, cro .

I**

e= e =0.835 0.707 t (in) h,  ;

Use c) =7/8" min. fillet weld all around B W i:)

enet.2 "

tact - - . x (psi) l ='suae sa

\ I 8 eact tact = 1.111 10' Actual stress in the weld due to these loads.

Alternately, a single 7/8" groove weld may be used to replace the 7/8" fillet weld. This is conservative, as the joint efficiency for the groove weld is 1.0, whereas that for the fillet weld is 0.5, and both welds are applied through the same circumferential length.

shid_sar.med 16

Appe: dix 2-10 Rev. 3 A 8

(

v' Longitudinal Shield Welds Under the Longitudinal HAC Drop Load Effect.

Five inches shield longitudinal welds:

L = 206.5 Length of 5" cyUndrical shielding between lower head and bottom of nozzles (in) ~,'

m = 96 Length of 2" cylindrical shielQg between lower flange and top of nozzles (in) 31.= 5.0 Wall thickness (in) s2 = 2.0 Wall thickness (in) .3 = 1.0 Wallthickness (in)

WTd = N: WTd = 9.6 10' (lb) HAC oblique event load (4.7 g's) p := 6 Number oflongitudinal welds "L" long (Note:

three lapjoint plates with two fillets welds Aw5 = p L' AwS = 1.23910' each).

(in) -

ts = r5 - 7.748 10' (Ib/in) Tensile strength of SA-516 Gr.70 material:

Su = 70000 t = 0 6 0.7 Su t = 2.94 10' (psi)

Weld allowable limit g e5 = e5 = 0.373 (in) g 0.707 t-m mact = .375 Use 3/8" min. fillet weld conservatively e5 tact = t tact = 2.922 10' OSCt Actual stress in the weld due to these loads Two Inch Shield Longitudinal Welds:

i q = 16 Number oflongitudinal welds "m" long (Note eight lapjoint plates with two Aw2 = q m Aw2 = 1.53610' r2 = WTd f2 = 6.25 10' Tensile strength of SA-516 Gr.70 material:

Aw2 Su =70000  !

t = 0.6-0.7 Su t = 2.94 10' (psi) Weld allowable limit U

m2 = m2 = 0.301 0 707-t (in) meet = .375 Use 3/8" min. fillet weld conservatively m2 tact = t tact = 2.357 10' Actual stress in the weld due to these loads Wact shld_sar.med 17-

Appendix 2-10 Rev. 3 Individual " Cans" Like Shielding:

Shield Geometry Parameters for the nozzles: d8 / dd Note: "d" Discharge I

~ 8*

j , ps / pd

/  : \ "

rs/rd w1 p t

........j......... 4 W3 __.-

+ 4 i W2 i -

Suction Nozzles: Four to be covered by "can" shielding with dimensions as shown below:

Ds = 512 - 2.5 ds = 3 12 - -

8 w1s = 5 rs = 312 - 11 + $ - 8.5 32 w3s = .5 ps = 8.5 rs = 39.094 w4s = .5 1

Discharge Nozzles: Two to be covered by "can" shielding with dimensions as shown below:

i Dd = 412 + 9.5 dd = 3 12 + 1 + 3 '

8 wid.=.25 w2d = .25 rd = 3 12 + 5 + 9 -8.5 w3d = .25 i 16 i

= 5 Note: A!! dimension in (in) pd = 8.5 rd = 33.063 '

I p = 0.282 (iblin3) Density O

O shid_sar.med 33 a

Apperdix 2-10' Rev. 3 O

V Total Weight Calculation:

2 WI = f-[Ds* - (Ds - 2 j-w2s)2 (rs p 4) + f-[Dd - (Dd - 2 w2d)2)-(rd) p2 Bottom cens W2 = E-(Dd* - dd') w3d p2 + E-(Ds2 - ds 2) w3s p 4 4 4 Semicircular plates 2

W3 =4 E-[dd - (dd - 2 wid)2)-(pd) p 2 + E-(ds' - (ds - 2 wls)*)-(ps) p4 Top cans 4

W4 = -(Dd2) w4d p 2 + -(Ds') w4s P4 Tg he(aded conservatively)

W6 cans = (W1 + W2 + W3 + W4)

~

3 W6 cans = 9.26510 (Ib) '

= 4.633 (ton) 2000 Evaluation of the "can" shielding for structural integrity.

The cylindrical shell and plate bodies are judged to be structurally integral by comparison. The failure may p rather occur at the weld ar.achment between the can assembly and the 2" shield. The s! zing and weld design is y presented next.

Weld Sizing:

Loading:

The loading is related to the can weight assembly amplified by applicable "G" value.

Glong = 10 Overt = 0 Glateral = 0 Load for Suction Nozzle most critical can geometry:

2 Wbe = E-[Ds -(Ds - 2 w2s)2](rs p) Wbe = 1.074 10 3

4 (Ib) ,

Wpl = E-(Ds2 , ds 2).w3s.p Wp1 = 286.056 4 (Ib) 2

$/tc = E-[ds - (ds - 2 wis)2)-(ps) p Wtc = 135.077 4 (Ib)

Wtpl = E-(Ds2) w4s p Wtpl = 432.583.

4 (Ib)

Location of can CG in axial direction with respect to bottom (weld between the large can versus 2" shield) most critical weld.

Wtpl (ps - rs) - Wtc .' - rs + Wpl rs + Wbc "-

/9 As = #

.Q Wbe - Wpl - Wtc - Wtp!

As = 30.411 (in)

I shld_sar.med 33 b l

l l

Appendix 2-10 Rev.3

,m Wold is subjected to bending and shear loads.

Design Loading:

3 Ws - Wbc Wpl + Wtc + Wtpl Ws = 1.927 10 (Ib) One can most critical weight j Glong = 10 Wsdes Ws Glong Wmes = 1.927104 (Ib) Weld design load 1 1

' Bending: .

Lead vector is applied at the CG of the can assembly:

5  !

Msdes : As Wsdes Msdes = 5.861 10 (in Ib) Bending at the weld root 2

Ssw := { Ds Ssw =3.068103 fbs = 3, ibs = 191.048 Shear:  !

Aws n Ds Aws = 196.35 fss = 98.161 fss : Aws f Resultant line force:

i Using the fillet weld efficiency: eff : 0.5 i 2

fsresul : fbs2 _ r3,2 stesul = 214.79 Using the groove weld efficiency: erg 1.0 Fillet weld size (minimum required): ASME Section Vill. fillet weld efficiency Sm :23300 t ': Sm-eff AS E matenal aHowade $r SA-516 Gr 70 escan = 0.026 (in) mscan = 0 0 I

Use 7 = 0.125 (in) Fillet weld all around between the largo diameter can versus the 2" shield, otherwise use 1/16*' fillet except as noted.

Groove weld size (minimum required):

Sm = 23300 t e Sm cfg l

l escan = 0.013 (in) mscan = 0 07 1

Use g = 0.063 (in) groove weld all around, where specified

/Q O

shid_sar.med 33 c

Apper. dix 2-10 '

Rev.3 I

U Load for Discharge Noule most critical can Deometry:

Wbc = 3-[Dd' - (Dd - 2 w2d)2)-(rd p) Wbe = 419.228 (Ib) 4 WplJ= 3-(Dd3 - dd 2) w3d p Wpl = 105.722 (Ib) 4 Wtc = E-[dd2 -(dd - 2 wid)2)-(pd) p Wtc =69.892 (Ib) 4 Wipt := 3.(Dd2) w4d p - Wtpl = 183.069 4 (ib)

Location of can CG in axial drection with respect to bottom (weld betwaan the large can versus 2* shield) most s critical weld.

Wtpl-(pd + rd) + Wic- + rd + Wpl rd + Wbe Y Ad = k # (

Ad = 26.536 (in)

Wbc , Wpl + Wtc + Wtpl Weld is subjected to bending and shear loads Design Loading:

Wd = Wbe + Wpl + Wtc + wtpl Wd = 777.911 (Ib) One can most criticalweight .

Glong = 10 3

Wddes = Wd Gleng Wddes = 7.779 10 (Ib) Weld design load Bending:

Load vector is applied at the CG of the can assembly:

5 Mddes = Ad Wddes Mddes = 2.064 10 (n Ib) Bending at the weld root 1

2 3 Swd = E Dd Swd = 2.597 10 4

lbd = fbd =79.494 Swd '

Shear:

Awd=xDd Awd = 180.642

. fsd = fsd = 43.064

. Awd Resultant line force:

1 Using the fillet weld efficiency: eff = 0.5 3 2 2

fdresul = !.fbd - fid 3 fdresul = 90.409 Using the groove weld efficiency: efs = 1.0 shid_sar.med 33 d

1 t

i App:ndix 2-10 Rev.3 Fillet weld size (minimum required): ASME Section Vill, fillet weld efficiency Sm 23300 t : Sm eft ASME material al:owable for SA-516 Gr 70 ,

edcan = 0.0ll (in) edcan =0 07 1

Use y = 0.125 (in) Fillet weld all around between the large diameter can versus the 2" shield, '

otherwise use 1/16" fillet except as noted.

Groove weld size (minimum required):

Sm ' = 23300 t := Sm efs edcan = 0.005 (in) edcan := 0 7 7 1

Use p = 0.063 (in) groove weld all around, where specified i

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U V/ // H H H // H // // H H H H H H n A s i NOTE: ENTIRE WElGHT OF SPOT SHIELDING CAN BE SUPPORTED BY 16'-O' OF %'  %/

FILLET WELD. ACTUAL WELD USED WILL BE PROPORTIONAL TO THE AMOUNT OF SPOT MT SHIELDING INSTALLED.

FIGURE 2-10-1 (SH.2 OF 3) i REACTOR VESSEL SUPPLEMENTAL SHIELDING DETAll 1

(

n 9981-00/516 43 l

e App;nd!x 2 - 10 Rav. 3

=

S'- 2 *e = , FIELD CUT TO Sulf %' AND 8// PLATES l 3'- f/,.e TO AV010 INTERFERENCES WITH IMPACT LIMITER BRACKETS.

Es*V NO WELOING AT THESE PLACES.

n g gl..........;:

j DET All 9 .#~~*. .

.. . .. .. w -

N

, g,. h .- ' _ 3'-03/s** _ .

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e 9 N,, (........... ...........:.

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c' ;.

.:.u.. <

p,g i

j rDETAll 8 ', [***, * . .\L.p".*.,

g y' _

I

i '

i U '..

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............... j , , ,., .........

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s

\_ KI,"*

  • DETAIL 8 y

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=.

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8'-r . 5 g-s= ==

INLET N0ZZLE a,1 (TYP OF 4) .n N.T.S.

4 '- 9 'o t/, b.

_ 3'-2%'e - min 45' x O _

w

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y n  :::..... . . :. ::.,, ' g. y y, ym g h.)a d 3*I58eY1.,

p. ......... ...........g >

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N iiy g i j

. . . J. .,

Wv min.

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, , . . . . . - - '" --.......,, j m1n. j ,

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,[ h'.

-- W' SUPPL / SPOT g.THK t SHIELO FIELD (T YP)

CUT.AS RE0'O.

. (T YP).

DETAll 9 ET N0Z LE OUlpyp o 2) WELDING DETAILS N.T.S. TYPICAL FOR OUTLET N0ZZLES AND INLET N0ZZLES N.T.S.

g FIGURE 2-10-1 (SH 3 OF 3)

REACTOR VESSEL NOZZLES SUPPLEMENTAL SHIELDING DETAILS 430 a ,u m ar.

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