ML12285A266
| ML12285A266 | |
| Person / Time | |
|---|---|
| Site: | San Onofre  |
| Issue date: | 10/01/2012 |
| From: | Mitsubishi Heavy Industries, Ltd, Southern California Edison Co |
| To: | Office of Nuclear Reactor Regulation, NRC Region 4 |
| References | |
| L5-04GA564 | |
| Download: ML12285A266 (226) | |
Text
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Document No.L5-04GA564(9)
At Appendix-2 Attachment-1 Tube-to-TSP wear depth diagram for Unit-2/3 MITSUBISHI HEAVY INDUSTRIES, LTD.
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Document No.L5-04GA564(9) 1., Introduction This attachment provides the tube-to-TSP wear depth at each TSP elevation for SONGS-2/3 RSGs.
- 2. Tube-to-TSP wear depth The following figures provide the tube-to-TSP wear depth in %. Note that the figures do not include the tubes with the wear in U-bend region.
MITSUBISHI HEAVY INDUSTRIES, LTD.
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S76-Cal 76-Col 0 81-Col 81-Col a, 86-Cal 86-Col I,,
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At Appendix-2 Attachment-2 Flow velocity data of analysis by ATHOS/SGAP for Unit-2/3 MITSUBISHI HEAVY INDUSTRIES, LTD.
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At Document No.L5-04GA564(9)
- 1. Introduction This attachment provides the data of flow velocity above tube sheet and at each TSPs analyzed by ATHOS/SGAP computer code.
- 2. Flow velocity data The following tables provide the data of flow velocity above tube sheet and at each TSPs (#1
-#7TSP). These data indicate superficial velocities in horizontal sections. The directions of these velocities are shown in figs. 5-24,--,5-31 in Appendix-2. Symbols IX and IY show the position of cells in horizontal sections (shown in following figure).
Position of cells MITSUBISHI HEAVY INDUSTRIES, LTD.
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I Velocity above tube sheet (1/2) 1 Ix Unit: ft/s 4 t F F + + + + 4 + F I t F +/- 1 4 t F ly MITSUBISHI HEAVY INDUSTRIES, LTD.
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AlA Velocity above tube sheet (2/2)
Ix Unit: ft/s ly MITSUBISHI HEAVY INDUSTRIES, LTD.
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-At Velocity at #1TSP (1/2) 1 Ix Unit: ft/s I_ _ _ _ _ _ _ 1111 _ _ _ _ _
4 4 4 + 4 + + 4 4 4 I 1 4 t 4 +~ + 1 4 + 4 1 4 4 4 4 4 1 4 4 +
ly 1 4 4 4 4 4 + I 4 4 4 MITSUBISHI HEAVY INDUSTRIES, LTD.
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I Velocity at #1TSP (2/2) 1 Ix Unit: ft/s ly MITSUBISHI HEAVY INDUSTRIES, LTD.
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Ak I Velocity at #2TSP (1/2) I Ix Unit: ft/s ly MITSUBISHI HEAVY INDUSTRIES, LTD.
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Ak I Velocity at #2TSP (2/2) I Ix Unit: ft/s-
_____ _____ .4 4 .4 + + + + * + +
.4 + .4 4 4 + .4 4. .4 .4 4 .4
.4 4- 4 1 4 .4 .4 .4 .4 1 1 I
.4- 4- 4- .4. .4 4 .4 .4 4 4 4 .4
+ + + + 1 4 4 4 .4 1 1 1
- 4. 4. 4. + 4- 4- .4 4- + + +
4L
- 4. 4. 4. -4. + + + + + 1- 4-ly
____ 4 4 4. 4. 4. 4- 4- 4- + + 4 +
4 4 4. 4. + + + + 4- 4. 4-
_____ 4 4 4 .4 4 4 I- 4. 4. 4. 4. ~4.
4 4 4 .4 4 4. 4. 4. 4. 4. 4. 4.
4 4 4 .4 .4 4. 4. 4. 4. 4. 4. 4.-
MITSUBISHI HEAVY INDUSTRIES, LTD.
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I Velocity at #3TSP (1/2) 1 Ix Unit: ft/s ly MITSUBISHI HEAVY INDUSTRIES, LTD.
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MAl I Velocity at #3TSP (2/2)
Ix Unit: ft/s ly MITSUBISHI HEAVY INDUSTRIES, LTD.
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AlW I Velocity at #4TSP (1/2) 1 Ix Unit: ft/s ly MITSUBISHI HEAVY INDUSTRIES, LTD.
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Af I Velocity at #4TSP (2/2)
Ix Unit: ft/s AL ly MITSUBISHI HEAVY INDUSTRIES, LTD.
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Ak I Velocity at #5TSP (1/2) 1 Ix Unit: ft/s ly MITSUBISHI HEAVY INDUSTRIES, LTD.
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AO I Velocity at #5TSP (2/2) 1 Ix Unit:
1y MITSUBISHI HEAVY INDUSTRIES, LTD.
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A, I Velocity at #6TSP (1/2) 1 Ix Unit: ft/s
+ 4 4 + + 4- 4- 4 4 4 4 t I 4 + + + 4 + 4 4 I t 4 4 +/- 1- 1 4 t 4 4 ly MITSUBISHI HEAVY INDUSTRIES, LTD.
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At I Velocity at #6TSP (2/2) 1 Ix Unit: ft/s I
__ I __ I __ __ I __ [ __ I __ I __ I __ I __ I __ I __ I __
4 4 4 i i i i i i i ii 4 4 4 4 I* I* 4 4 k
ly 4 4 4 4 + 4 4 + 4 + +
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IAt I Velocity at #7TSP (1/2) 1 Ix Unit: ft/s ly
_ I1tI1~1 _ It _ liii _
iI 4 i i i i + i
-I + I I t F + + +
MITSUBISHI HEAVY INDUSTRIES, LTD.
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I Velocity at #7TSP (2/2) 1 Ix Unit:
I ly MITSUBISHI HEAVY INDUSTRIES; LTD.
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Ak Appendix-2A Random Vibration Evaluation of Tube Straight Portion for Unit-2/3 MITSUBISHI HEAVY INDUSTRIES, LTD.
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- 1. Purpose Tube-to-tube support plate (TSP) wears at tube straight portions are detected in SONGS-2/3 RSGs. It is possible that the cause of the wears is the random vibration mechanism. The purpose of study provided in appendix-2A is to evaluate the possibility of random vibration of the tube straight portion, through the thermal and hydraulic calculations by ATHOS/SGAP computer code and vibration calculations by IVHET computer code.
- 2. Conclusion The tube wear depth for Row1 Column1 tube is calculated with assuming the tube-to-TSP contact force of( ). Since contact force due to the thermal expansion is 0.6N which can be variable because of manufacturing tolerances and fluid forces, the contact is a parameter for this case study(
The nonlinear analysis predicts that the contact force of 1.5N results in tube wear depth of 2
-Approx.20%, which is similar to the tube inspection results 0-19%. This parametric study implies that the random vibration mechanism is the probable cause of tube-to-TSP wear and the contact force at the locations where wear indications are detected happened to be larger than the locations where no indication is detected.
Table 2-1 Parameter survey result
[
Case Wear depth Note Calculation Approx. 2-20% Contact force off Jis assumed.
Tube inspection 0-19%
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- 3. Assumption The following assumptions are used in the tube vibration calculations.
- 1) The tube vibration is calculated based on the assumption that the cause of tube vibration is the tube cross flow and axial flow.
- 2) Since there are clearances between tubes and tube holes of TSPs, the tube support conditions are uncertain. However, most tube-to-TSP contact points are considered to be effective supports because of the differential thermal expansion of the tubesheet and TSPs (Refer to Assumption of Appendix-2). TSPs supports are generally expected to be in contact with the tubes.
For the tube-to-TSP contact point without tube-to-TSP wear identification, the tube is assumed to be in contact with the TSP (zero touch condition). For the contact point with tube-to-TSP wear indication, the contact force is considered.
- 3) The tube-to-TSP contact force ranging ( ) is assumed. Since the contact force due to the thermal expansion is ( )' the contact force( )is considered to be in the realistic range.
- 4) For the conservative evaluation, the large random excitation forces due to the flows are used in the vibration analysis.
- 4. Acceptance criteria There is no acceptance criterion because the purpose of the parametric survey is to trace the tube-to-TSP wear depth, which is identified by the tube inspection.
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Ak
- 5. Design input The nominal dimensions are obtained from the design drawings (Ref.3 to 20) and the manufacturing tolerances are not considered.
Flow characteristics are obtained from 3 dimensional thermal and hydraulic analysis (See Appendix-12) .Flow velocity, density, void fraction and hydrodynamic pressure are evaluated for Row 1 Column 1 tube (Fig. 5-1). The reason of selection of the tube is provided in section 6.3.
The velocity, density distribution and volume flow rate quality for tube straight portion are provided in Fig.5-2 and 5-3.
Fig.5-1 Evaluated tubes MITSUBISHI HEAVY INDUSTRIES, LTD.
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Fig 5-2 Flow distribution MITSUBISHI HEAVY INDUSTRIES, LTD.
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Fig 5-3 density and flow velocity multiplied MITSUBISHI HEAVY INDUSTRIES, LTD.
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- 6. Methodology 6.1 Outline of analysis Based on the design input of the operating conditions, the calculation of the circulation ratio is performed by evaluating the pressure loss and the recirculation head with SSPC, which is a 1 dimensional Thermal and Hydraulic parameter calculation code (Ref.21). Using ATHOS/SGAP, the thermal hydraulic analysis is performed to obtain the 3 dimensional flow distribution that includes the flow velocity, the flow density, and the void fraction (See Appendix-1 2). Then, IVHET is used to evaluate the non-linear tube vibration. The evaluation process is shown in Fig.6-1.
Design Input Operating conditions SSPC Circulation Ratio Calculation by evaluating pressure loss and recirculation head ATHOS/SGAP I Thermal Hydraulic Analysis 3,dimensional flow distribution
-Flow velocity
-Flow density
-Void fraction IVHET IL S Evaluation of non-linear tube vibration Fig.6-1 Flow of the evaluation MITSUBISHI HEAVY INDUSTRIES, LTD.
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6.2 Evaluation Parameters In general, larger thermal power is more severe for vibration, because the steam flow rate increases. At constant thermal power, lower steam pressure is more severe for vibration than higher pressure, because pU 2 increases - (the lower p causes the higher U).
Basic parameters required for calculations are shown in Table 6-1.
Table 6-1 Basic parameters for calculation Condition of Cycle 16 Plugging Tcold ('F)
Thot (Tsg-in) (oF)
Tsg-o.t (*F)
Tfeedwater (°F)
Saturation Steam Pressure (psia)
Steam Mass Flow (lb/hr)
Circulation ratio Thermal power (MWt/SG) _. __,
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Ar 6.3 Selection of tubes to be evaluated In all SGs, tube-to-TSP wear is present in many Row 1 tubes that border on the tube-free-lane.
In this case study, the Row1 Column1 tube is used for the evaluation -in order to compare the actual ECT inspection results of RIC1 of 2A-SG and 2B-SG, which are selected as worse cases.
Table 6-2 Tube-to-TSP wear depth of Row1 Column1 of 2B-SG Unit (%)
SG 01H 02H 03H 04H 05H 06H 07H 07C 06C 05C 04C 03C 02C 01C 2A "
2B1 HOT COLD MITSUBISHI HEAVY INDUSTRIES, LTD.
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Document No L5-04GA564(9) 6.4 Random excitation force The random excitation forces due to the cross flow and axial flow are considered.
(1) Random excitation force due to the cross flow The random excitation force due to the cross flow is calculated based on Fig.6-2 [22]. Since the "envelop spectrum" in the figure 6-2 is used, the random excitation force is overestimated.
The following equation is used for the calculation.
0.,~ =(pgD,ýD) 2 .(>D-qE U
fD, 0.ID lofj 5 ; f, < 0.06
{(2xl0-)f7-3 " f, >0.06 ' fr Umean ' f-mean where Dcross : Power spectrum density of fluid force per unit length (cross flow)
D Tube outer diameter p Density at each element U Flow force at each element Um.... : Average flow velocity between each span 6..ea. :Average volume flow velocity quality between each span g :Gravity acceleration 10 -
103 102 ".
x "envelope spectrum E 10 x .
0.
X X e..
10 X 0 freon-waer o freonR9 i air-water 10 3 x steam-water 10 31 100 0 red. frequency fr=(f'Dw)/V Fig 6-2 Power spectrum density of random excitation force due to the cross flow MITSUBISHI HEAVY INDUSTRIES, LTD.
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(2) Random excitation force due to the axial flow The random excitation force due to the axial flow is calculated based on Fig.6-3 [231. Since the design guideline covering most data is used, the random excitation force is overestimated.
The following equation is used for the calculation.
7 2 D,,,ia = (2.0 x 10- ) x (pUD) where Oaxiat Power spectrum density of fluid force per unit length (axial flow)
. 'Jm.. .
. m
- g g . .
... *.1I=
i.
TlillU..i i; . .
Pettlgrew (1992) 270
,0 Pettigrew and Gorman (1977) 270 Chalk River Lsboratoe.l$ BID 6
Unpublished Data 2.70 Igo DESIGN GUIDELINE Forrest & Sandlg (1971) 270 /
290 2x 10-7 m 2/s
- 0. O-(7b IJJ E3 0
"z 0 F 10-2 2 3 ' 6 6 789 10-1 i
2 4 6759 10o 2 3 4S 6789101 REDUCED FREQUENCY Fig 6-3 Power spectrum density of random excitation force due to the axial flow MITSUBISHI HEAVY INDUSTRIES, LTD.
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- 7. Results The vibration analysis results are provided in Fig.7-1. The parametric survey of the contact force shows that the contact force of( i gives the tube wear depth is ( 3, which is similar to the tube inspection results[ 3.
Fig 7-1 Wear depth of analysis result MITSUBISHI HEAVY INDUSTRIES, LTD.
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- 8. References
- 1) Deleted
- 2) Deleted
- 3) L5-04FU001 the latest revision, Component and Outline Drawing 1/3
- 4) L5-04FU002 the latest revision, Component and Outline Drawing 2/3
- 5) L5-04FU003 the latest revision, Component and Outline Drawing 3/3
- 6) L5-04FU021 the latest revision, Tube Sheet and Extension Ring 1/3
- 7) L5-04FU022 the latest revision, Tube Sheet and Extension Ring 2/3
- 8) L5-04FU023 the latest revision, Tube Sheet and Extension Ring 3/3
- 9) L5-04FU051 the latest revision, Tube Bundle 1/3
- 10) L5-04FU052 the latest revision, Tube Bundle 2/3
- 11) L5-04FU053 the latest revision, Tube Bundle 3/3
- 12) L5-04FU111 the latest revision, AVB assembly 1/9
- 13) L5-04FU112 the latest revision, AVB assembly 2/9
- 14) L5-04FU113 the latest revision, AVB assembly 3/9
- 15) L5-04FU114 the latest revision, AVB assembly 4/9
- 16) L5-04FU115 the latest revision, AVB assembly 5/9
- 17) L5-04FU116 the latest revision, AVB assembly 6/9
- 18) L5-04FU117 the latest revision, AVB assembly 7/9
- 19) L5-04FU118 the latest revision, AVB assembly 8/9
- 20) L5-04FU119 the latest revision, AVB assembly 9/9
- 21) L5-04GA510 the latest revision, Thermal and Hydraulic Parametric Calculations
- 22) "Flow-Induced Vibration", 107-117 P.W. Bearman (Edit) 23)" Two-Phase Flow-Induced Vibration An Overview", Journal of Pressure Vessel Technology 1994 , Vol.116, 233-253 M. J. Pettigrew, C. E. Taylor MITSUBISHI HEAVY INDUSTRIES, LTD.
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AO Appendix-3 FEI Evaluation of Tube U-bend Portion for Unit-2/3 Page 203 of 474 S023-617-1-M1538, REV. 0
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- 1. Purpose The analysis is conducted for 100% reactor power, zero plugged tubes and all AVB supports being active to evaluate design conditions of the RSGs in the first operating period.
The purpose of this appendix is to provide a fluid elastic instability evaluation of out-of-plane direction for the tubes of the San Onofre Units 2 and 3 Replacement Steam Generators (RSGs) in accordance with Section III Appendix N, Article N-1 330 based on U-bend flow conditions from the ATHOS/SGAP (EPRI) thermal-hydraulic analysis code instead of the evaluation based on the flow conditions obtained from FIT-Ill during the RSG design stage (Ref.1).
- 2. Conclusion The fluid elastic stability ratios are confirmed to be less than 1.0 at full power and with all AVBs active to satisfy the criteria of ASME Section III Appendix N, Article N-1330. This conclusion applies to all of the steam generator tubes. The results for the most limiting tubes are shown in Table 2-1 and indicate the occurrence of tube out-of-plane FEI is very unlikely when the gap between tube and AVB is very small and the AVB support point is active in the tube out-of-plane direction.
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Table 2-1 Fluid Elastic Stability Ratios for the Limiting Tubes Critical Effective Row Row olun Column 10 Damping torfrequency Critical Natural Flow flow Stability ratio Factor f (Hz) velocity Uc Velocity Ue (ft/s) (ft/s) ratio 142 88 47 89 47 7 26 88 26 4 1.5%* 2.4*
14 88 14 2 1 89 1 1 Note*: Values recommended by ASME Settion IIl Appendix N, Article N-1 331.3 Page 205 of 474 S023-617-1-M1538, REV. 0
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- 3. Assumption (1) Nominal tube thickness and nominal tube length are used in the evaluation model because the effect of the tolerances of these dimensions on the natural frequency is negligible.
(2) Contact condition between tube and tube support plate is pin-supported. Fixed supported condition at No. 1 TSP is added.
(3) Contact condition between tube and active support points by the anti-vibration bar (AVB) is pin-supported. And all points are active.
(4) Modulus of elasticity of tube is interpolated based on the tube average temperature of TL+T from table of ASME Boiler and Pressure Vessel Code, Sec II, Materials, 1998 2
Edition, 2000 addenda (Ref.23).
Where, Tav: Primary side average temperature (OF)
Ts Secondary side temperature (OF)
(5) Tube has the virtual added mass supposing the fluid-structure interaction (FSI) effect as shown in the following formula (Ref.24).
M, (Dý/D J)2 I (Ibm /ft) ............................................................ (1)
De/Do I 22 I p/Do P/Do ....................................................................... (2)
Where, m, :Virtual added mass per unit length due to FSI effect; po Average density of water outside the tube; Do :Tube outside diameter P Tube pitch.
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- 4. Acceptance criteria The ASME Section III, Appendix N (Ref. 22) methodology and acceptance criteria are used for this analysis. The acceptance criterion is that the effective flow velocity across the tubes be no greater than the Appendix N critical flow velocity. The ratio of these two velocities may not exceed 1.0. The ASME methodology includes conservatisms to account for practical design variability.
- 5. Design Inputs The nominal tube dimensions are used in the analysis and are obtained from the design drawings (Ref. 3 to 20). Manufacturing tolerances are not considered.
The basic operating parameters required for the calculations are shown in Table 5-1 (see Appendix-12 for details).
Table 5-1 Basic parameters Number of tubes plugged __
Thermal power (MWt/SG)
Tco1d ('F)
Thot (Tsg-in) (OF)
Tfeedwater (o F)
Saturation Steam Pressure (psia)
Steam Mass Flow (lb/hr)
Circulation ratio (Note) The primary inlet temperature range isl lIF. It is conservative for this analysis to use the lower inlet temperature ([)°F) because it produces a lower secondary pressure and a higher steam flow velocity.
The tubes selected for evaluation are listed in Table 5-2, which are the same tubes evaluated during the RSG design stage (Ref.1). These tubes have longer support spans, lower damping and higher flow excitation than others.
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Ak Table 5-2 Evaluated Tubes Row Column 142 88 (Center) 47 89 (Center) 47 7 (Outer-most) 26 88 (Center) 26 4 (Outer-most) 14 88 (Center) 14 2 (Outer-most) 1 89 (Center) 1 1 (Outer-most)
The flow conditions (flow velocity*, flow density and void fraction) applied to these limiting tubes are shown in Fig. 5-1 through 5-5. The ATHOS flow conditions are only applied over the U-bend portion of the tube. The structural model for the U-tubes includes the full tube length including the straight legs, but no cross flow velocities are applied to the straight legs.
Note)
- Flow velocity shown in Fig. 5-1 through 5-5 indicates the gap velocity in normal direction to tube in-plane.
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Fig.5-1 Flow distribution of Row 142 Col 88 Page 209 of 474 S023-617-1.-M1538, REV. 0
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Fig.5-2 Flow distribution of Row 47, Columns 89 and 7 Page 210 of 474 S023-617-1-M1538, REV. 0
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An Fig.5-3 Fiow distribution of Row 26, Columns 88 and 4 Page 211 of 474 S023-617-1-M1538, REV. 0
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Fig.5-5 Flow distribution of Row 1, Columns 89 and 1 Page 213 of 474 S023-617-1-M1538, REV. 0
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- 6. Methodology The term "fluid elastic instability" is generally used to refer to self-excited vibration of tube bundles due to cross flow. In .1969, Connors disclosed the presence of this phenomenon for the first time (Ref.25).
Causes of fluid elastic instability are considered to be the absorption of flow energy due to the interaction of fluid and structure. This phenomenon occurs on tube bundles, and is subjected to effects of tube bundle array. Thus, it is experimentally attempted to determine the criticality of occurrence in various tube bundle arrays.
The critical flow velocity Uc for generating fluid elastic instability is obtained 'in the following Connors' formula (Ref.25). This formula is employed in the TEMA (Standards of the Tubular Exchanger Manufactures Association), which is the industrial design standard in the United States.
uo _.../...........................
Uo K [_ mo- o
.. . . .3
........... ......... ......................................... (3 )
Where, Uc Critical flow velocity f Tube natural frequency D. Tube outside diameter.
K Critical factor M0 *Average tube mass per unit length
(
- Tube logarithmic decrement(= 2rrh) h Damping ratio Po Density of water outside the tube, The critical flow velocity Uc in eq. (3) is evaluated in case of tube vibration of single degree of freedom system with uniform cross flow along the tube axis. In actual tube, however, the vibration of the tube supported by the tube support plate is multi degrees of freedom system with beam type of vibration modes. Therefore, considering the vibration mode and fluid distribution, the effective flow'velocity Ue, is evaluated in the following formula.
2 U(X). (X). . . . . . . .dxj1.
p 0P U en 0L()
M(-Xo) - On (X) 2 dJx Page 214 of 474 S023-617-1-M1538, REV. 0
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Where, Uen " Nth mode effective flow velocity (Pn(X)
- Nth vibration mode p(x) Fluid density distribution of water outside the tube in tube axis direction m(x)
- Tube mass distribution per unit length in tube axis direction U(x)
- Flow velocity distribution orthogonal to tube axis in tube axis direction x Coordinate component along tube axis Po Average density of water outside the tube mo *Average tube mass per unit length L Tube length The stability ratio is determined as follows in each vibration mode by calculating the ratio of eq.
(3) and eq. (4).
SR,, =--Uc ........................... (5) where, I- -11/2 U- K mýc5.12..
2
.............................................................. '(6) f.D 'LPoD J This value is called the n-th mode stability ratio SRn, and if SRn > 1, fluid elastic instability occurs. Generally, the maximum stability ratio in each mode is called the stability ratio of the tube, which is simply expressed as SR.
Evaluation of occurrence of fluid elastic instability in U-tubes is carried out in the following steps :
T Using a 1-dimensional Thermal and Hydraulic parameter code (SSPC), determine the tube bundle circulation ratio and other secondary side operating conditions for the normal operating condition (Ref.21).
(2) Using the flow analysis code (ATHOS/SGAP), determine the distributions of flow velocity U(x) and density of the fluid p(x) along the tube axis.
© For the damping ratio h and critical factor K, the suggested values based on ASME Sec III Appendix N-1330 are used, and from eqs. (3) - (5) stability ratio is evaluated (Ref.24).
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At The critical factor K=2.4 in eq. (3) gives a conservative criteria for avoiding fluid-elastic instabilities of tube arrays. Also, the damping ratio h= 1.5% for wet steam or liquid is used.
Natural frequencies, vibration mode and stability ratio are calculated by vibration analysis code FIVATS.
Figure 6-1 describes this process.
Design Input Operating conditions SSPC Circulation Ratio Calculation by evaluating pressure loss and recirculation head ATHOS/SGAP I Thermal Hydraulic Analysis 3 dimensional flow distribution
-Flow velocity
-Flow density
-Void fraction
- Hydrodynamic pressure FIVATS SEvaluation ofInfluid elastic instability Fig.6-1 Steps in the Analysis Process Page 216 of 474 S023-617-1-M1538, REV. 0
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- 7. Results All of the stability ratios are less than the limiting value of 1.0. The results are summarized in Table 7-1. Figures 7-1 to 7-9 show examples of the tube vibration mode shapes that are associated with the maximum stability ratio for each tube.
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C:
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._)
ci
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"-o a)J Page 219 of 474 S023-617-1-M1538, REV. 0
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._j.
2, (I
An Co k-a).
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0 CU, K 2 Page 221 of 474 S023-617-1-M1538, REV. 0
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At MODE FREQ.(HZ) Uc (ft/s) Ue(ft/s) SR 1 r 2
3 4
5 6
7 8
9 10 11 12 13 14 15 16 18 19 20 21 22 23 24 25 26 27 28 29 30 Fig. 7-1 Vibration mode diagram for Row 142 Column 88 MITSUBISHI HEAVY INDUSTRIES, LTD.
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JAW MODE FREQ.(HZ) Uc (ft/s) Ue(ft/s) SR 1 r 2
3 4
5 6
7 8
9 10 11 12 13 14 15 16 17 18 19 20 21 22 24 25 26 27 28 29 30 Fig. 7-2 Vibration mode diagram for Row 47 Column 89 MITSUBISHI HEAVY INDUSTRIES, LTD.
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JAW MODE FREQ.(HZ) Uc (ft/s) Ue(ft/s) SR 1 f" 2
3 4
5 6
7 8
9 10 11 12 13 14 15 16 17 18 20 21 22 23 24 25 26 27 28 29 30 Fig. 7-3 Vibration mode diagram for Row 47 Column 7 MITSUBISHI HEAVY INDUSTRIES, LTD.
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At MODE FREQ.(HZ) Uc (ft/s) Ue(ft/s) SR 1 r 2
3 4
5 6
7 8
9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24 25 26 27 28 29 -
30 Fig. 7-4 Vibration mode diagram for Row 26 Column 88 MITSUBISHI HEAVY INDUSTRIES, LTD.
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[I Document No L5-04GA564(9) x MODE FREQ.(HZ) Uc (ft/s) Ue(ft/s) SR 1
2 3
4 5
6 7
8 9
10 11 12 13 14 15 16 17 18 19 20 21 22 23 24 25 26 28 29 30 Fig. 7-5 Vibration mode diagram for Row 26 Column 4 MITSUBISHI HEAVY INDUSTRIES, LTD.
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Ak MODE FREQ.(HZ) Uc (ft/s) Ue(ft/s) SR 1 ---
2 3
4 I
5 6
7 8
9 10 11 12 13 14 15 16 17 18 19 20 22 23 24 25 26 27 28 29 30
- Fig. 7-6 Vibration mode diagram for Row 14 Column 88 MITSUBISHI HEAVY INDUSTRIES, LTD.
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At MODE FREQ.(HZ) Uc (ftls) Ue(ft/s) SR 1 r 2
3 4
5 6
7 8
9 10 11 12 13 14 15 16 17 18 20 21 22 23 24 25 26 27 28 29 30 k.
Fig. 7-7 Vibration mode diagram for Row 14 Column 2 MITSUBISHI HEAVY INDUSTRIES, LTD.
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Document No L5-04GA564(9) x MODE FREQ.(HZ) Uc (ft/s) Ue(ft/s) SR 1 1 "1 2
3 4
5 6
7 8
9 10 11 12 13 14 15 16 17 18 19 20 21 22 24
-J 25 26 27 28 29 30 ý Fig. 7-8 Vibration mode diagram for Row 1 Column 89 MITSUBISHI HEAVY INDUSTRIES, LTD.
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At MODE FREQ.(HZ) Uc (ft/s) Ue(ft/s) SR 1 r 2
3 4
5 6
7 8
9 10 11 12 13 14 15 16 17 18 19 20 21 22 24 25 26 27 -d 28 29 30 Fig. 7-9 Vibration mode diagram for Row 1 Column 1 MITSUBISHI HEAVY INDUSTRIES, LTD.
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- 8. References
- 1) L5-04GA504 the latest revision, Evaluation of Tube Vibration
- 2) Deleted
- 3) L5-04FU001 the latest revision, Component and Outline Drawing 1/3
- 4) L5-04FU002 the latest revision, Component and Outline Drawing 2/3
- 5) L5-04FU003 the latest revision, Component and Outline Drawing 3/3
- 6) L5-04FU021 the latest revision, Tube Sheet and Extension Ring 1/3
- 7) L5-04FU022 the latest revision, Tube Sheet and Extension Ring 2/3
- 8) L5-04FU023 the latest revision, Tube Sheet and Extension Ring 3/3
- 9) L5-04FU051 the latest revision, Tube Bundle 1/3
- 10) L5-04FU052 the latest revision, Tube Bundle 2/3
- 11) L5-04FU053 the latest revision, Tube Bundle 3/3
- 12) L5-04FU111 the latest revision, AVB assembly 1/9
- 13) L5-04FU112 the latest revision, AVB assembly 2/9
- 14) L5-04FU113 the latest revision, AVB assembly 3/9
- 15) L5-04FU114 the latest revision, AVB assembly 4/9
- 16) L5-04FU115 the latest revision, AVB assembly 5/9
- 17) L5-04FU116 the latest revision, AVB assembly 6/9
- 18) L5-04FU117 the latest revision, AVB assembly 7/9
- 19) L5-04FU118 the latest revision, AVB assembly 8/9
- 20) L5-04FU119 the latest revision, AVB assembly 9/9
- 21) L5-04GA51 0 the latest revision, Thermal and Hydraulic Parametric Calculations
- 22) ASME Boiler and Pressure Vessel Code, Section III, 1998 edition, 2000 addenda 23)ASME Boiler and Pressure Vessel Code, Sec II, Materials, 1998 Edition through 2000 addenda.
- 24) Blevins, R. D., "Flow-induced Vibration", Krieger Publishing Company.
25)Connors, H.J., Fluid Elastic Vibration of Tube Arrays Excited by Cross Flow, ASME Annual Meeting, 1970.
MITSUBISHI HEAVY INDUSTRIES, LTD.
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Appendix-4' Investigation of Unit-2/3 Manufacturing and Inspection Records MITSUBISHI HEAVY INDUSTRIES, LTD.
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- 1. Purpose The purpose of this appendix is to investigate the manufacturing history of the Unit-2 and Unit-3 steam generators to identify differences in dimensions, materials, fabrication processes and inspections that may have a relationship to the differences in U-bend degradation patterns.
- 2. Conclusion The major differences between the Unit-2 and Unit-3 steam generators are listed below. The influences of these differences are evaluated in Section 5.2.3 of the main report.
(1) Number of Rotations due to Divider Plate Repair (2) Number of Hydrostatic Tests (3) Dimensional Control of Tubes andAVBs MITSUBISHIHEAVY INDUSTRIES, LTD.
Page 233 of 474 S023-617-1-M1538, RE'V. 0
Category Item Unit-2 Unit-3 Effect to the final AVB structure assembly and tube bundle 0 I
I_ I (especialy tube-to-AVB gap)
All tensile test and hardness test results are within specification for all Mechanical property of AVB There is no remarkable difference on any test results.
AVB material for all units.
0 Standard deviation of G value for Unit-3 RSGs were smaller 0 Design Material than that for Unit-2 RSGs. However, difference of the tube 0)
C Outer diameter of tube (G value) dimensions are small between all four SGs, as the tube .
W diameters are within the r land the standard deviation is within ( ) J 0*
- L IN 0)
Cn Number of tubing operators No impact is assumed at the point of this difference.
--I 0 Number of manual adjustment of Tube insertion Number of manual adjustment of U-bent portion for Unit-3 is 0.
Fn U-bend portion during tubing smaller than that for Unit-2, therefore configuration of U-benl AD I- installation (in case the gap tube for Unit-3 RSGs is better than that for Unit-2. z between the tubes are small) 0 AVB manufacturer, fabrication sequence, and procedure There is no difference.
Fabrication 8 '0 Inspection CD CA 0o to c AVB assembly The difference of thickness of AVBs are small between all Thickness of AVBs before CD-four SGs, as the thickness are within )vWith w standard nstallation deviations between ( ] Si2 Note *) For Unit-3, )) N pressing was used for AVB bend nose portion after bending in order to control the twist and flatness of AVB more precisely, while( )N pressing was used for Unit-2 as described inAppendix-9.
Categor Item Unit-2 Unit-3 Effect to the final AVB structure assembly and tube bundle
=Y 4(especialy tube-to-AVB gap)
The approved procedure(document) was revised up from Procedure of AVB assembling Unit-2A to Unit-3B. Those for Unit-2A are different from those for the others. However, there is no remarkable CD (Insertion, welding and fixuring the bridge and retainer bar) difference for Unit-2B and Unit-3 RSGs at the point of the basic manners for AVB assembly. CD Situation and condition of fixturing AVBs at tubes with tie ropes or 0 Same manners are applied to all units.
temporary fixturing equipments 0r C 0 Size of spacer for Unit-2A is different from that for the Size of spacer block used for others. Therefore there is no difference for Unit-2B and Unit-welding AVBs to retaining bar CL 3 RSGs.
0Z This operation might have led to some differnce. 0 m AVB assembly rotations for Unit-2A is different from that for AVB assembly rotations the others. Therefore there is no remarkable difference for 0 Fabrication & Unit-2B and Unit-3 RSGs.
49 Inspection AVB assembly Fillet weld size between retaining Fm bars and end-caps There is no remarkable difference. C) z 0
=3 Increased weld size between AVB 0 V There is no remarkable difference. 0 and retaining bar 0_-6, 3
IN) CD ii:
This operation was applied only for Unit-2A. There is no CD Re-insertion of AVBs remarkabledifference for Unit-2B and Unit-3 RSGs.
C.<
CD 0 -0,,
Re-welding retaining bars and end-This operation was applied only for Unit-2A. There is no caps after helium leak tests C1 remarkable difference for Unit-2B and Unit-3 RSGs.
,Z Category__Item_______________ Effect to the final AVB structure assembly and tube bundle Category Item Unit-2 Unit-3 (especialy tube-to-AVB gap)
Welding position for the bridge and Welding position for Unit-2A is different from that for the retainer bar assembling others. Therefore there is no difference for Unit-2B and Unit-3 RSGs.
Tube-to-AVB Gap measurement CD AVB assembly results at outermost tubes hese AVB-to-tube gaps were smaller in Unit-3 than in Unit-2. (D 0
CD) This difference influenced tle number of shell rotations - Unit C Time of tying retaining bar to tube 2 RSGs were rotated 60 more times than Unit 3 RSGs. Shell for prevention of pulling AVB out "otations are assumed to not impact the tube-to-AVB gapW 0*
size.
CL Tube support plate Tolerance for pitch of the upper Same tolerances are applied to all units.
most tube support plate 0
-0 Z Fabrication & This difference influenced the number of shell rotations - Unit Inspection Transition sition wrapper welding 2 RSGs were rotated 15 more times than Unit 3 RSGs. Shell welding rotations are assumed to not impact the tube-to-AVB gap.
4 IO This difference influenced the number of shell rotations - Unil (D
-4 Helium leak test Condition of helium leak test 2 RSGs were rotated 20 mOre times than Unit 3 RSGs. Shell 0D rolations are assumed to noi impact tire tube-to-AVB gap* Z 0D Tube expansion Hydro/mechanical tube expansion There is no difference. 0 Final dryer vane Time of final dryer vane jacking This difference influenced the number of shell rotations - Unit C CD jacking (tightening) (tightening) 2 RSGs were rotated 30 more times than Unit 3 RSGs. Shel rotations are assumed to not impact the tube-to-AVG gap*"
11*1 0
Bundle rotations after completion of Bundle rotations after completion of AVB assembly AVB assembly (excluding divider No impact is assumed for the point of this difference.
(excluding divider plate repair) plate repair)
G-(00
- Note.*) See Appendix-5 for details
gory tUnt-3 e Effect to the final AVB structure assembly and tube bundle Im(especialy tube-to-AVB gap)
Bundle rotations for divider plate Bundle rotations for divider plate K This difference Influenced the number of she I rotations - Urrit 2 RSGs were rotatec 30 more times than Unit 3 RSGs. Shell repair repair rotations are assumed to not impact the tube-Ia-AVB gapý'
ID Numoer of times w3ler ,xa3 pcured It is confirmed by deformation analysis result no remarkable Hydrostatic test into the shell for the hydros:atic (D test, and number of hydrostatic test. enlargement of tube-to-AVB gap is caused by this operation.
Fabrication &
Inspection Heat treatment Tubesheet to Channel Head C after AVB structure welding & PWHT for divider plate No impact is assumed for the point of this difference.
assembling repair CL
-ca Channel head Channel head removal by flame removal from cutting for divider plate repair No impact is assumed for the point of this difference.
0D tubesheet Indications of tube PSI results is not changed compared with 0 Tube PSI Time and situation of tube PSI latest ECT results. Therefore no impact is assumed at the point of this difference. 0 0*
I - Position of the shell during No impact is assumed for the point of this difference.
4I transport 0 0
Accelerations during transport There is no remarkable difference.
Nitrogen recharge system There is no remarkable difference.
z0 I-I.
_P1 '0 Ship name There is no remarkable difference.
CD Others Transport Tugboat company There is no remarkable difference.
0) 6)
Barge support stand There is no remarkable difference.
cn 0l Off load duration There is no remarkable difference.
Transportation time There is no remarkable difference.
Platform trailers
-1)
There is no remarkable difference.
- Note*) See Appendix-5 for details
I Non-proprietary Version I 1 (P.4-7)
( Document No.L5-04JA564(9)
Ak : Difference of fabrication history between Unit-2 and Unit-3 (113)
N/R: Number of Rotation, N/L: Number of Loading, SUM: Summation MITSUBISHI HEAVY INDUSTRIES, LTD.
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At : Difference of fabrication history between Unit-2 and Unit-3 (2/3)
N/R: Number of Rotation, NIL: Number of Loading, SUM: Summation
-MITSUBISHI HEAVY INDUSTRIES, LTD.
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I Non-proprietary Version I 1 (P.4-9)
I Document No.L5-04JA564(9) : Difference of fabrication history between Unit-2 and:Unit-3 (3/3)
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Document No.L5-04 A564(9) : Detail investigation of AVB assembly At MITSUBISHI HEAVY INDUSTRIES, LTD.
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AIA Appendix-5 Analytical Simulation of Tube Bundle Rotation and Hydro Static Test MITSUBISHI HEAVY INDUSTRIES, LTD.
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- 1. Purpose The purpose of this evaluation is to analytically simulate the SONGS SG U-bend to evaluate the behavior of the tube-to-AVB gaps during.gravitational sagging, shop rotation, and primary hydrotest.
- 2. Conclusion 2.1 Bundle Rotation The tube-to-AVB gaps near the center columns increase by [ ] mm in one rotation. Ifthis gap is postulated to occur at each rotation (which it doesn't), the total gap growth for 300 rotations would be [ ] mm, which is negligible. In the analyses, small plastic deformation occurred in limited portion, AVB outside the bundle. This small plastic strain level can not cause permanent deformation.
The tube-to-AVB gaps in the outer columns increase by [ j in the first rotation; but do not repeat or grow significantly during additional rotations. The difference of the tube-to-AVB gaps between Unit-2 and 3 due to the number of SG rotations is not judged to be significant, even if it is postulated that the increased gaps in the outer columns were redistributed to the center.
The gaps generated by the pressure tests are also determined to be negligible so the difference of the tube-to-AVB gaps between Unit-2 and 3 due to the number of pressure tests is negligible.
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- 3. Assumption
- 1) Nominal dimensions are used for analysis model.
- 2) The initial value of the tube-to-AVB gaps is assumed to be zero.
- 3) The tube pitch is assumed to be the same as the tube hole pitch of the TSP.
- 4. Acceptance Criteria The tube-to-AVB gaps are evaluated to determine if they get larger during SG shop rotations or during pressure tests. The results of the analysis are compared to see if there is a significant difference between Unit-2 and Unit-3.
Table 4-1 Difference between Unit-2 and 3 during fabrication Number of SG Number of pressure tests Unit or times the bundle was rotations filled with water 2 2A& 2B: 1 3 3A: 3, 3B: 2
- 5. Design Inputs 5.1 Geometry The nominal tube bundle dimensions are obtained from the design drawings MITSUBISHI HEAVY INDUSTRIES, LTD.
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- 6. Methodology 6.1 Analysis model The ABAQUS finite element program is used to perform the analysis. The model includes the tubes, AVBs, retaining bars, retainer bars, and bridges. The modeling assumptions are shown in Table 6.1-1 and Figure 6.1-1. The model is shown in Figure 6.1-2. The TSPs are treated as pinned supports. The tubes at the TSP #6 elevation are prevented from displacing in the lateral and axial directions but are free to rotate. The tubes at the TSP #7 elevation are restrained against lateral displacement but are free to displace axially and to rotate. It is appropriate not to simulate initial gaps between TSP and tubes, because all tubes laterally displace just same amount of initial gap in the case of cantilevered U-bend, and the tube pitch is not changed. Modeling the top two TSPs is sufficient to produce a reasonable replication of the cantilevered U-bend.
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Aw Table 6.1-1 Condition of analysis models (1/2)
Element Elastic Analysis - Plastic ,Retaining Retainer Tube .AVB Bridges Water bars bars.
(1) Validation of analysis model (2) Simulation of SG rotation (3) Simulation of pressure testing _-_ _
Table 6.1-1 Condition of analysis models (2/2)
Boundary condition Friction Analysis Coefficient Contact condition Fastening
(*1) _condition Tubes - Retainer bars -
Tubes - AVB Retaining bars Tube (1) Validation of analysis model (2) Simulation of SG rotation (3) Simulation of pressure testing _-
Note 1) See Fig. 6.1-1.
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A Fig. 6.1-1 Friction coefficient between Inconel 690 and 405 S.S MITSUBISHI HEAVY INDUSTRIES, LTD.
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Ak Fig. 6.1-2 Analysis Model MITSUBISHI HEAVY INDUSTRIES, LTD.
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Document No.L5-04GA564(9) 6.2 Evaluation cases The following three cases were evaluated.
(i) U-bend Sagging to validate the analytical model (ii) Simulation of bundle rotation (iii) Simulation of hydrostatic pressure testing 6.2.1 Validation of Analytical Model A simulation of the U-bend sag due to gravity was performed to compare to measurements made during manufacture to validate the analytical model. Gravity (1G) in the out-of-plane direction (i.e. with the U-tubes in the horizontal plane, perpendicular to the floor) produced sagging that was measured at the tips of AVBs #41 and #69. A one-half model of that shown in Figure 6.1-2 was used taking advantage of symmetry. Since the measurements were taken before the retaining bars, retainer bars, and bridges were installed, those features were excluded from the model.
6.2.2 Simulation of Bundle Rotation Since the objective of this evaluation is the tube-to-AVB gaps, bundle rotation was simulated by cycling a gravity load from plus to minus with the bundle oriented in the out-of-plane direction. A zero gravity load step was performed between each gravity load reversal. The following diagram describes this load cycle.
OG -4 +1G -4 OG -- -1G -- OG - +1G -) ...
This model includes the retainer bars, the retaining bars, and the bridges. Figure 6.2.2-1 shows the model and load sequence. Refer to Table 6.1-1 for additional information about this simulation.
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Ak Fig. 6.2.2-1 Load sequence for Shop Rolling MITSUBISHI HEAVY INDUSTRIES, LTD.
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6.2.3 Simulation of Hydrostatic Pressure Testing To evaluate difference of the tube-to-AVB gaps increment around the center column, where many wears have occurred, between Unit-2 and 3, due to the number of pressure testing, simulation of pressure testing is performed.
The weight of the tube bundle increases by the weight of water inside the tubes during the primary hydrostatic pressure test. The orientation of the tube bundle during pressure testing is with the tube lane inclined at an angle of 45 degrees - but is simulated with tube bundle in the out-of-plane orientation. The test sequence is adding water, pressurization, depressurization, and draining water. The tube mass is increased by a factor of 1.5 to account for the added weight of water. Although gravity is oriented at 45-degree orientation the simulation is run with the bundle in the out-of-plane direction. The out-of-plane equivalent loading for the hydrotest is +1G/12 x 1.5 = +1G. A 0.7G loading is used to represent the draining / depressurization step. The following load sequence is used to model two hydrotests.
OG-- +1G (adding water / pressurization) -- +0.7G. (draining water) -- +1 G (adding water pressurization) -- +0.7G (draining water) -4 OG MITSUBISHI HEAVY INDUSTRIES, LTD.
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Ak
- 7. Results 7.1 Validation of analysis model Measurement points of AVB #41 and #69 for sagging during fabrication are shown in Figure 7.1-1. Measurement and analysis results are compared in Table 7.1-1. The calculated sag is slightly less than what was actually measured, but is considered to be close enough to validate the model.
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Ak A
No.41 (1) Out-of-Plane Deformation (2) Section A-A Fig. 7.1-1 Out-of-Plane Deformation due to Sagging Table 7.1-1 Comparison Result of Out-of-plane Displacement during Sagging Displacement (mm)
Case AVB-Tube AVB AVB No.41 No.69 None Analysis (Retaining bars are not modeled)
Measurement Fastened MITSUBISHI HEAVY INDUSTRIES, LTD.
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Document No.L5-04GA564(9) 7.2 Simulation of SG rotation 7.2.1 Deformation and Gaps during SG rotation The deformation of tube bundle and the tube-to-AVB gaps during SG rotation are analyzed step by step, as follow.
(1) Step 0: Initial Condition
'--- AVB Gap element -
Blue color: AVB contacts the tube (zero gap)
Red color: There is a gap between AVB and tube Blue color: AVB contacts tube Red color: There is a gap between AVB and tube Green color AVBjust contacts tube Fig. 7.2.1-1 AVB-Tube Gap contour for initial condition MITSUBISHI HEAVY INDUSTRIES, LTD.
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Document No L5-04GA564(9) x (2) Step 1: +1G acting (1st turn)
Sagging of retaining bar depends Tubes gravity No gap is generated, on sagging of tubes in center deformation is different because retaining bar columns. Retaining bar and AVBs in each column, pull AVBs down push tubes down, because because gravity sagging of retaining bar is larger deformation is than gravity deformation of tubes proportional to 4th near both ends of retaining bars. power of tube radius.
/F~
Fig. 7.2.1-2 AVB-Tube Gap contour for +1G condition of first turn MITSUBISHI HEAVY INDUSTRIES, LTD.
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It appears that the gaps generated by +/-IG remain because AVB cannot move into tube bundle due to friction force.
Fig. 7.2.1-3 AVB-Tube Gap contour for OG condition of first turn MITSUBISHI HEAVY INDUSTRIES, LTD.
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(4) Step 3: -1G acting (1st turn)
Retaining bar is deformed in opposite direction of Step 1. AVB near both ends of the retaining bar is dragged by the deformed The gap is generated at symmetrical retaining bar.
position against Step 1.
/
Fig. 7.2.1-4 AVB-Tube Gap contour for -1 G condition of first turn MITSUBISHI HEAVY INDUSTRIES, LTD.
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(5) Step 4: Gravity free (After 1st turn)
/
I /!/ ,
/ /
The gaps generated by the gravity on Step 3 remain. The deformations of the retaining The gaps generated by the gravity on bar and AVB remain. It would Step 1 don't remain. appear that the AVB cannot move (The gaps contour is determined by into the tube bundle due to friction the last gravity.) force.
-1 Fig. 7.2.1-5 AVB-Tube Gap contour for OG condition of first turn MITSUBISHI HEAVY INDUSTRIES, LTD.
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At (6) Step 25-28 7th turn Fig. 7.2.1-6 AVB-Tube Gap contour of 7th turn MITSUBISHI HEAVY INDUSTRIES, LTD.
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Document No L5-04GA564(9) x~1 (7) Step 28 Gravity free (after 7th turn)
A-4B For one surface, there are some unsupported points in one tube. On the other hand, for the opposite surface, the tube contact with the AVB at all points.
y These tubes are unsupported by AVBs continuo There are consecutive small gaps at AVB support points.
However, the increases of gaps are negligibly small.
r.
K Fig. 7.2.1-7 AVB-Tube gap contour in Column 78 MITSUBISHI HEAVY INDUSTRIES, LTD.
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Document No.L5-04GA564(9) 7.2.2 Enlargement of tube bundle width Enlargement of tube bundle width (cross sections al, a2, and a3) is calculated from 1st to 7th turn at the points shown in Fig. 7.2.2-1.
The width of the tube bundle is not changed after the 3rd turn as shown in Fig. 7.2.2-2. The maximum change of the width is[ ) mm at cross-section a3. The expansion is caused by the AVB-Tube gaps near the edges at the retaining bars. It is theorized that during operation, the fluid hydrodynamic pressure might shift the gaps from the edges to the center. This would equate to a widening of [ Jnear the center column.
Fig. 7.2.2-1 Evaluated points of expansion
-I Fig. 7.2.2-2 Change per rotation of tube bundle width (first 7 rotations)
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Document No.L5-04GA564(9) 7.2.3 Change of the Tube-to-AVB gaps Changes of the AVB-tube gaps from 1st to 7th turn are investigated. Changes near Col90, 135, and 160 are shown in Fig. 7.2.3-1. Although the small gaps (about[ ]mm gaps) are generated near Col.90, the large gaps (about[ j mm) are generated near the retaining bars.
It suggests possibility of the larger gaps (about[ ] mm) near the center column by redistribution during operation.
Fig. 7.2.3-1 Change of the AVB-Tube gap between 1st turn through 7th turn MITSUBISHI HEAVY INDUSTRIES, LTD.
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Ak 7.3 Simulation of Hydro Test 7.3.1 Deformation and Gaps due to pressure testing The load direction and deformation during pressure testing is shown in Fig. 7.3.1-1. The tube-to-AVB gaps during pressure testing are shown in Fig. 7.3.1-2 and 7.3.1-3. The tube-to-AVB gaps generated by pressure testing are around [ ] mm, and are negligibly small.
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Ar Fig.7.3.1 -1 Load direction and deformation during pressure testing MITSUBISHI HEAVY INDUSTRIES, LTD.
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Fig. 7.3.1-2 AVB-Tube Gap Contour in 1st Pressure Testing MITSUBISHI HEAVY INDUSTRIES, LTD.
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Ak Fig. 7.3.1-3 AVB-Tube Gap Contour in 2nd Pressure Testing MITSUBISHI HEAVY INDUSTRIES, LTD.
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AW Appendix-6 Investigation of ISI ECT Data for AVB Support Condition for Unit-2/3 MITSUBISHI HEAVY INDUSTRIES, LTD.
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- 2 Document No.L5-04GA564(9)
- 1. Tube to AVB gap evaluation 1.1 Introduction ECT data was used to evaluate the tube-to-AVB gap sizes in the Unit 2 and Unit 3 SGs after 22 months and 11 months of operation, respectively.
Bobbin probe was used for the evaluation.
1.2 Evaluation method Effort was made to eliminate or minimize sources of error in the ECT data shown in Table 1.
Table 2 describes the countermeasures taken in this evaluation.
Table 1 The factors which influence the gap evaluation 140kHz Abs.
140kHz abs Peak-to-peak amplitude Integral Amplitude Thickness reduction or dent of tube X L X L Misalignment of AVB X L Dimensional error on calibration notch X M X M Variation of scanning speed of probe - X M Scale on tube outer surface X S X S Thickness of tube X S X S Width of AVB X S X S Note: "L","M" and "S" show the degree of influence on the evaluation.
L: Large, M: Medium, S: Small Table 2 Significant error factor and countermeasure Error factor Correction Differential,'channel is sensitive to the misalignment Misalignment of AVB factor. Absolute channel and the absolute amplitude integral method can reduce the factor. These two methods are adopted. (Attachment 2)
Dimensional error on Calibration notch Each of Cal std variability is corrected.
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At 1.3 Tube-to-AVB Gap Evaluation Color maps that show the bobbin absolute AVB signal amplitude for each tube at each AVB in each-of the 4 SGs (refer to Attachment 1). Measurements of larger amplitudes are associated with smaller gaps.
The large green areas of the Attachment 1 plots indicate gaps of( or less (approximate). The amplitudes in B01, B12 of SG-3B around Row 50 are slightly smaller than what is present in other SGs in the region, which potentially indicates larger gaps along Row 50.
Figure 1 shows an evaluation of average amplitude at each AVB of the four steam generators.
In this figure the ranking of SGs by average amplitude from large to small is 2B, 2A/3B, 3A -
where the larger amplitude is associated with smaller tube-to-AVB gaps. This indicates that (slightly) larger average gaps are present in the Unit-3 SGs than in the Unit-2 SGs. It is also noted that Figure 1 shows smaller gaps (larger amplitudes) in the region of the tubes that are closest to the top TSP. This may be related to the uniform tube support plate hole spacing.
Figure 2 shows the maximum gap, minimum gap and distribution of ECT amplitude value.
Mock up test results of tube-to-AVB gaps and AVB misalignment are shown in Attachment 2.
These results provide insight into the accuracy.of the data.
- Remarks for Attachment 1: The white color in 2A and 2B means that ECT data is missing at that location.
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I-K Fig.2 Distribution of ECT amplitude value (140kHz-Abs,integral)
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Ak 4 Conclusion The results of this evaluation show that the Unit-3 SGs have slightly larger average tube-to-AVB gaps than the Lnit-2 SGs, with the largest in SG-3A. This trend indicates the tube-to-AVB contact force of Unit-3 SGs are smaller than that of Unit-2 SGs. :Amplitude integral color map of Bobbin probe (Abs) : Mock up test result of gap and misalignment evaluation MITSUBISHI HEAVY INDUSTRIES, LTD.
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r z
0 CA 0 C
C<D
.- MI 5.
MZ U, ,5 CoC ma CD
-Iv z 01 Ampltud mp intgra
)As) 1/2 colr Page 272 of 474 S023-617-1-M1538, REV. 0
,z 0
0 CD
-o D I 0
-I E CC
.-I 0 cnn 0) i-0, 4*O.
9)
Amplitude integral color map (t Abs) (2/2)
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z 0
Ci CD 00 1
22 M
0 0 "SOD 0
C:
CD z
~3o Amplitude of Bobbin coil probe v.s. gap and misalignment (Mock-Up)
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At
- 2. AVB insertion depth evaluation Evaluation of as-built insertion depth of AVBs was conducted by the bobbin ISI-ECT data for representative columns for 3B-SG.
2.1 Sample tubes and AVBs used for evaluation See Table-i, 2, 3, 4 and 5.
2.2 Evaluation method Each AVB location on representative tubes is evaluated by estimating the arch length on tubes by ISI-ECT signal interval from #7 TSP. And these locations are plotted on the drawing for comparison with the design-based locations. (See Table-i, 2, 3, 4 and 5.)
2.3 Result ECT-based AVB locations are compared with design-based locations as shown in Fig.1, 2, 3, 4 and Fig.5. It is evaluated that AVB insertion depth in actual SG is not changed compared with the design-based location, where the measurement uncertainty of AVB position due to the difference of the scanning speed is considered approximately MITSUBISHI HEAVY INDUSTRIES, LTD.
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Ak Table-1 Distance between the center of #7TSP thickness and AVB position (3B-SG)
<Column 9>
Row B01 B02 B03 B04 B05 B06 B07 B08 B09 B10 B11 B12 I r 3
5 7
9 11 13 15 19 23 27 29 31 33 35 37 41 43 47 49 51 53 55 (unit; mm)
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A Table-2 Distance between the center of #7TSP thickness and AVB position (3B-SG)
<Column 10>
Row B01 B02 B03 B04 B05 B06 B07 B08 B09 B10 B1l B12 2
4 6
8 10 12 14 16 18 20 22 24 26 28 30 38 48 50 52 58 A (unit; mm)
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AO Table-3 Distance between the center of #7TSP thickness and AVB position (3B-SG)
<Column 11>
Row B01 B02 B03 B04 B05 B06 B07 B08 B09 B10 Bl B12 1 r 3
5 7
9 11 13 15 17 19 23 27 29 37 47 49 51 57 63 (unit; mm)
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AW Table-4 Distance between the center of #7TSP thickness and AVB position (3B-SG)
<Column 77>
RoW B01 B02 B03 B04 B05 B06 B07 B08 B09 B10 B11 B12 3
-7 15 17 19 21 23 25 27 37 47 67 87 107 127 141 (unit; mm)
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Ar Table-5 Distance between the center of #7TSP thickness and AVB position (3B-SG)
<Column 89>
Row BOI B02 B03 B04 B05 B06 B07 B08 B09 B10 Bl 612 1 r "
3 5
7 9
11 13 15 19 21 23 27 29 33 37 39 43 47 67 85 103 107 109 113 125 137 (unit; mm)
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At Fig.1 Column9 AVB Position (solid line design, broken line ISI-ECT)
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Fig.2 Column1O AVB Position (solid line ; design, broken line ; ISI-ECT)
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-di Fig.3 Columnl1 AVB Position (solid line design, broken line ISI-ECT)
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At Fig.4 Column77 AVB Position (solid line ; design, broken line ; ISI-ECT)
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Fig.5 Column89 AVB Position
~2 (solid line ; design, broken line; ISI-ECT)
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Appendix-7 Visual Inspection Results for U-Bend Region for Unit-2/3 MITSUBISHI HEAVY INDUSTRIES, LTD.
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Document No.L5-04GA564(9)
Ak
- 1. Purpose This appendix shows the visual inspection result of the tubes and AVBs in U-bend region of SONGS Unit 2 / Unit-3. These visual inspections were performed using a CCD camera inserted into the U-bend region and recorded on DVD by AREVA.
- 2. Location Inspected The locations inspected are shown below.
Unit-3 Unit-3A: AVB 04 Col. 87/86 -- 84/83 (4 columns)
Unit-3A: AVB 09 Col. 86/87 -- 80/81 (7 columns)
Unit-3B: AVB 04 Col. 82/81 -- 75/74 (8 columns)
Unit-3B: AVB 04 Col. 61/60 -- 50/49 (12 columns) Total 31 columns Unit-2 Unit-2A: AVB 04 Col. 88/87 -- 73/72 (16 columns)
Unit-2B: AVB 04 Col. 87/86 -4 76/75 (12 columns) Total 28 columns
- 3. Wear Patterns and Characteristics Two wear patterns were observed at the tube-to-AVB intersections. The wear patterns are described as follows.
3.1 Wear Pattern-1 (Regional Wear on Tube Surface)
Characteristics
() Tube wear scar indicates in-plane motion or vibration
() Evidence of both parallel and perpendicular movement relative to the AVB Fig-1 Wear Pattern 1 MITSUBISHI HEAVY INDUSTRIES, LTD.
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Characteristics ij Local wear occurs on the tube but the wear surface is not exposed (cannot be seen)
(2) Unable to determine if wear occurs on tube orAVB or both (3) Unable to determine the direction of motion or vibration
() An extreme interpretation is that both tube and AVB are worn into each other.
AVB Unable to see the metallic sheen due to narrow wear area (a) Case 1 (b) Case 2 Fig-2 Wear Pattern 2
- 4. Results of Visual Inspection of Unit-2 / Unit-3 4.1 Common Observations from Unit-2 and Unit-3 (See Photo-1 to Photo-8)
No large gaps between the AVBs and tubes AVBs appeared to be straight, no detectable abnormalities No abnormality in the orientation between the AVBs and tubes No abnormality in AVB positions or end cap-to-retaining bar welds 4.2 Unit-3 Pattern-1 wear due to high amplitude in-plane vibration, as shown in Photo-9 and Photo-1 0, were found in the free span region.
Pattern-2 wear as shown in Photo-11 and Photo-12 was found near where Pattern-1 occurred.
There is some Pattern-1 wear identified by visual inspection, for which Bobbin ECT was not able to detect as this type of wear. (See Table-i -- Table-4)
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- 2) Unit-2 As shown in Photo-13, Photo-14, Pattern-2 wear, which was found in Unit-3, was also found in Unit-2. However, no Pattern-i wear was found.
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AVB Photo-1 Visual Inspection Image of Outermost Tube Region [Unit-2A]
Image of Unit-2A Col. 72/73 tubes at AVB 04 Left side is Row 139, right side's far end is Row 140 and right side's closer end is Row 138.
The bottom of the End Cap is seen over the outermost tube.
AVB Photo-2 Tube Bundle Visual Inspection Image [Unit-2A]
Image of Unit-2A Col. 72/73 tubes around Row 95 at AVB 04 (Sample).
No gaps between the tube and AVB beyond 0.1mm and no twisting and bending on the AVB are observed.
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AAV AVB Photo-3 Visual Inspection Image of Outermost Tube Region [Unit-2B]
Image of Unit-2B Col. 78/79 tubes at AVB 04 Left side is Row 141, right side's far end is Row 142 and right side's closer end is Row 140.
The bottom of the End Cap is seen over the outermost tube.
AVB Photo-4 Tube Bundle Visual Inspection Image [Unit-2B1]
Image of Unit-2B Col. 78/79 tubes around Row 105 atAVB 04 (Sample).
No gaps between the tube and AVB beyond 0.1mm and no twisting and bending on the AVB are observed.
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AO AVB Photo-5 Visual Inspection Image of Outermost Tube Region [Unit-3A]
Image of Unit-3A Col. 84/83 tubes at AVB 04 Left side's far end is Row 142, right side is Row 141 and left side's closer end is Row 140.
The bottom of the End Cap is seen over the outermost tube.
AVB Photo-6 Tube Bundle Visual Inspection Image [Unit-3A]
Image of Unit-3A Col. 84/83 tubes around Row 125 at AVB 04 (Sample).
No gaps between the tube and AVB beyond 0.1mm and no twisting and bending on the AVB are observed.
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AVB Photo-7 Visual Inspection Image of Outermost Tube Region [Unit-3B]
Image of Unit-3B Col. 78/77 tubes at AVB 04 Left side's far end is Row 142, right side is Row 141 and left side's closer end is Row 140.
The bottom of the End Cap is seen over the outermost tube.
i AV13 Photo-8 Tube Bundle Visual Inspection Image [Unit-3B]
Image of Unit-3B Col. 78/77 tubes around Row 90 atAVB 04 (Sample).
No gaps between the tube and AVB beyond 0.1mm and no twisting and bending on the AVB are observed.
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Non-proprietary Version I Document No L5-04GA564(9) x Photo-9 Sample of Pattern-1 [Unit-3A]
Image of Unit-3A Col. 87/86 shows a sample of Pattem-1 wear.
Photo-10 Sample of Pattem-1 [Unit-3B]
Image of Unit-3B Col. 78/77 shows a sample of the Pattem-1 wear.
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At Photo-11 Sample of Pattern-2 [Unit-3A]
Image of Unit-3A Col. 87/86 shows a sample of Pattern-2 wear, where wear between tube and AVB cannot be distinguished.
Photo-12 Sample of Pattern-2 [Unit-3B]
Image of Unit-3B Col. 78/77 shows a sample of the most typical Pattern-2 wear, where wear between the tube and AVB cannot be distinguished.
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Document No L5-04GA564(9) x Photo-13 Sample of Pattern-2 [Unit-2A]
Image of Unit-2A Col. 88/87 shows a sample of Pattern-2 wear.
Photo-14 Sample of Pattem 2 [Unit-2B]
Image of Unit-2B Col. 85/84 shows a sample of Pattem-2 wear.
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Table-1 SONGS Unit-3AAVB 04 Visual inspection result ic C
w CA CD m (0
-A -
-0, M z 0
0 0 M.
CDC C<D 0 w r -: Free span indication by ECT CDN
Table-2(1/2) SONGS Unit-3AAVB 09 Visual inspection result COL81 TWD MI R- I Cali 141' 1391 PMiminor) 137 1 139 ni~or 14 15 P2mignor) I 1337 m~or1331 1311 131 5 19 129 (I) 127 C 8 125 w 123
- 127 121 z 119 1i17 1_ 125 1 10 115 m 123. 1 113 130 19 107 19 10 103 C 101 cn
-I or 9 111 1S 15 97 4
93 m 10 91 Si) 32rlnr I0 10 69 z0 I- 157
-I 1 89or 131 p 12 83 9
79 0 V
_77- C CD 73 73 3CD 71
Table-2(2/2) SONGS Unit-3AAVB 09 Visual inspection result CoL85_ Q L C01.85 TDM Ro" CoIJ85 139 ______
P mino ___ 137 _ ___
P mino ___ 135 P2Mrnor)
P2mino ___ 133 _ ___
P2minrw _ 131 ____
a3 129 ______
19 127 Co 1 7 125 1 P2(minor)
- Ci P2(mior) 7 123 _____
P2 nor) 9 __ 121 1______
1 6 119 1_____
P inor) 14 117 1______
11 115 1 _____
m IS 113 1_____
101
>9 24 1071 P2mWio,)
25 105 1 P2 mor.)
16 103 P2 mino 6 101 PI?
m 11 211 97 P1?
aI is16 95 1 P1?
I- 9 fin 16 11 z0 (A 9 65 8 63 9 81 0
I I I~
C: CD B ;.
.................... _,.: . ..... CD A
hZ CD
- Free span indication by ECT
~En
_) -4 c.4h
Table-3(1/5) SONGS Unit-3B AVB 04 Visual inspection result Col.1 82Ct.o8 CLa -081 /B 0 1 COL CoL80 /7 CooL79 CoL79 7 Col..78 13 P2Pw)i 123 C)
(D 0 Z 12 15 14 P21r 17 X
21 z 0
17* M resa niainb C 0
C MD 0
--4 CD 04 4h,'1 (d001
- 0
Table-3(2/5) SONGS Unit-3B AVB 04 Visual inspection result iC Ca wD
-A)
C) 0 z 0
4Ca) oo 0
C CD CD
- C-01 r-l* Free span indication by ECT 4s_.
Co)
CA) 90
Table-3(3/5) SONGS Unit-3B AVB 04 Visual inspection result i CoL61-0 I CoL.601 6059 C.59-58 I58-57 1 Co57 Ro1o6 o oC C01.6 TWO RowICoL60 RowI CoL59 PTWO KIIRow.1 Co5 Rw CoLM I TWO]( FRow ICoL58 1Row ICot.57 I WM I I I I I I I I I It I I I 4 -
Ch m
z 0
0v o M.
C: CD 3
. I I i -"
CD 0 U r- : Free span indication by ECT 0'-
Table-3(4/5) SONGS Unit-3B AVB 04 Visual inspection result (ID C0L xC RoL 129
'II Co5 ol.57/6 1 Row I
Col.56 Co.56 TW) M Row Col.56/5 o.55 Row CoIS I-Col. 55 Row COL o.5554 Row CoL54 CoL 54 TW MRow I oL54 o54 Row Col.3 j
I Col53 C Ti127 125 121 1219 P2(minor) 117 115 P inor 113 P2 minor)
I P2(minor) 109 107 105 CDm 103 P2(minor) 101 P2Mminor) 99 97 CA P2(minor) 95 93
.p,( 91 899 P2 ino, P2 minor) z 0
P2 minor)
P2(mnor) 85 P2 mnor) 93 P mnor) 0 81 79 77 C CD 75 73 71 CD z
Z3 0
r- : Free span indication by ECT 0*-0 Eno
Table-3(5/5) SONGS Unit-3B AVB 04 Visual inspection result P.*I &q TWDM Row CoL Row Co.52 TWD M Row CoL52 Row I ... MoL5 Row 50 M Row ..
I I I I I C) 4w 0u 4- (A Fn
(- z0 I. I : ' . '"" .
,. I " ,, . .... . 0 0 M.
- LL ; L
- T"T'-': C (D i i , ;",--
CD
- Free span indication by ECT HI 0
- 6) -4 4(. 10
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Table-4 Description of the abbreviations in Table-1 -Table-3 Abbreviation Description P1 Tube Confirmed with Wear Pattern-1 Pi? Tube Suspected with Wear Pattern-1 P2 Tube Confirmed with Wear Pattern-2 P2 (minor) Tube Confirmed with Minimal Wear Pattern-2 P2? Tube Suspected with Wear Pattern-2
? Tube that cannot be determined due to the inspection rate in (Unjudgeable) the video, etc MITSUBISHI HEAVY INDUSTRIES, LTD.
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At Appendix-8 SG Tube Flowering Analysis for Unit-2/3 MITSUBISHI HEAVY INDUSTRIES, LTD.
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- 1. Purpose There are many instances of tube wear in the central part of the Unit-2 and Unit-3 U-bends.
This wear should not be possible if the tubes were fully supported. This appendix contains an evaluation of the possible effects of fluid flow on the tubes and their support condition to determine how much influence they have on the tube support conditions.
- 2. Conclusion The analyses results are the following.
$ The distance between tubes within columns increases due to thermal elongation and dynamic pressure by a small amount relative to their nominal spacing (maximum change:1 I V The tube-to-AVB gaps in the center columns increase due to hydrodynamic pressure by I Iwhen the manufacturing tolerance dispersion is not taken into account (Case C3A').
V The tube-to-AVB gap increase due to hydrodynamic pressure is small when the manufacturing tolerance dispersion is taken.into account (Case D1).
, The area where the largest gaps are generated, correlates with the area with the most tube wear.
In the center columns and the outer rows the analysis shows that there are many AVB intersections with gaps on both sides of the- AVBs (inactive supports).
> There are many instances of consecutive inactive supports along tubes in the region.
V Increasing the retaining bar stiffness provides only a modest reduction in the gaps due to the hydrodynamic pressure. Such a change is not judged to be an effective countermeasure.
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- 3. Methodology and Assumptions
- 1) Analysis model The ABAQUS finite element program is used to model the U-bend. The tube bundle is symmetric about the central plane perpendicular to the tubelane, so a half-symmetry model is assumed. All of the U-tubes, AVBs, retaining bars, retainer bars, and bridges are modeled using beam elements. The model includes the U-bend and the straight leg of the tubes down to the elevation of the 6 th TSP. The model is shown in Figure 3-1. Nominal dimensions are used. Manufacturing tolerances are not considered.
The two TSPs are represented as pinned supports. All tubes at the TSP#6 elevation are prevented from displacing in the lateral and axial directions but are free to rotate. All tubes at the TSP#7 elevation are restrained against lateral displacement, but are free to displace axially and to rotate. Modeling the top two TSPs is sufficient to produce a reasonable structural representation of the U-bend portion of the tube bundle.
In Case C3A', all tubes at the TSP#6 elevation are able to displace in the lateral within gap range and free to rotate but axially fixed. All tubes at the TSP#7 elevation are restrained against lateral displacement by gap elements but are free to displace axially and to rotate.
Additional modeling details:
Water mass inside (and outside) the tubes is simulated by an increase in tube density.
- Contact between tubes and AVBs is simulated by gap elements.
The tube stiffness in compression is I which is the spring stiffness of the gap elements under compression when the tube-to-AVB gap is zero.
The initial tube-to-AVB gaps are set to zero. The gap elements exert a force on the tube when in compression, but displace freely under tension.
Al ]coefficient of friction for lateral movement between tubes and AVB is assumed.
Tube can slide along the AVB, if slide force is larger than the force multiplying the compression force by I]
The tube and AVB Modulus of Elasticity is specified based on operating temperature.
Elastic material behavior is assumed for all parts.
- 2) Loading conditions The hydrodynamic pressure across each tube is obtained from the ATHOS thermal hydraulic analysis and is applied to the tubes.
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Ak y
x
ý (i) Bird's-eye View of the Model
/ V \
I
-y.
(ii) Side View of the Model Fig. 3-1 ABAQUS model MITSUBISHI HEAVY INDUSTRIES, LTD.
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- 4. Analysis cases Table 4.1 describes the five cases that were analyzed. Cases C1 and C2 are used to confirm the influence of thermal elongation and hydrodynamic force on the tubes without any AVB supports. In these two cases the AVBs are not included so that the tubes can deform freely and so that the response of each tube can be evaluated independently.
Cases C3A and C3B are used to evaluate the tube-to-AVB gap behavior. In Case C3A the hydrodynamic force produced by ATHOS (both in-plane and out-of-plane) is applied to the tubes. In Case C3B, only the hydrodynamic forces in the out-of-plane direction are applied.
Case-C3C is a repeat of Case C3A but with much stiffer retaining bars (I J). This case was run to quantify its effectiveness as a countermeasure to prevent further tube wear.
In Case C3A', the latest ATOHS output is applied from Appendix-1 2. Additionally, Case D1 is used to evaluate effects the hydrodynamic force and manufacture dispersion, which is applied from Appendix-9 Case 2-1 analysis condition.
Table 4.1 analyses cases Analysis Model Analysis Friction Method Load Case Model Region AVB Assembly Factor Temperature C1 Only tubes No AVB distribution with water (Tubes only) Dynamic Pressure C2 (in-plane & out)
Dynamic Pressure A
Original Retaining (in-plane & out)
B Bar Dynamic Pressure Re_____________Bar (out of plane)
Gap elments Retaining Bar CA sGap elements A sfrcnatstiffness =1 I Elastic DnmcPesr Dynamic Pressure C3 C A sfor contact stfns Elsi (in-plane & out)
Retaining (Twice diameter) Analysis between AVBs bars, Bridges, and tubes Gap elements for Retainer bars, (Contact contact between DnmcPesr and tubes TSP and tubes Dynamic Pressure A'
spring : (in-plane & out) with wihwae water Ii[N/mm]) I(Contact J[N/mm])spring : From IAppendix-1 2 Manufacturing Apni-Dispeacursiong Dynamic Pressure D1 Dispersion From (npae&ot Appendix-9 (in-plane & out)
Case2-1'for Unit-3 MITSUBISHI HEAVY INDUSTRIES, LTD.
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At
- 5. Results of analyses
5.1 Case-Cl
Vertical Thermal Expansion Analysis (no AVB contact)
The total and vertical tube deformations of the tube bundle are shown in Figure 5.1-1. The top of the outermost tube grows by I I from the tubesheet surface. The vertical growth and total growth are essentially the same because the difference in the hot and cold side tube temperatures is small. This is because the average tube wall temperature is used, which is mid-way between the primary and secondary side temperatures.
Figure 5.1-2 shows the change in distance between tube rows in column 78 due to thermal expansion. The nominal distance of Igrows I Ito a value ofI I The change in distance between tubes of the same column, due to tube thermal expansion from room temperature to operating temperature is negligible.
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Fig. 5.1-1 Case-Cl: Thermal expansion due to tube temperature (ave. wall temp.)
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Fig. 5.1-2 Case-Cl: Distance between adjacent tubes in Col.78 after thermal elongation MITSUBISHI HEAVY INDUSTRIES, LTD.
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5.2 Case-C2
Tube Deformation from Hydrodynamic Force (no AVB contact)
In the U-bend at operating conditions (without any friction or restraint from the AVBs) the hydrodynamic forces cause the tubes to deform as shown in Figures 5.2-1 and 5.2-2.
Figure 5.2-1 shows the overall displacement of the U-bend at operating conditions. The hydrodynamic forces cause the tube columns to spread apart (view i) with the maximum out-of-plane displacement ofI INote that this view of the U-bend does not show the hot and cold sides. This will be important when visualizing the behavior of later load cases.
In the in-plane direction (views ii and iii) the bundle displaces (horizontally) toward the hot side because the hot side hydrodynamic forces are larger than the cold side forces. The outermost, central tube, R142C86, displaces downward byl Jat the apex and at about 450 off vertical on the hot side, where the hydrodynamic force is largest, it displaces upward byI In view ii at this same 45' zone, R142C86 displaces horizontally byl I Figure 5.2-2 displays the change in spacing between adjacent tubes within column 78 in response to the hydrodynamic forces. At the top of the bundle, the tube-to-tube spacing decreases by a maximum of f las the U-tubes are pulled downward. The tube-to-tube spacing on the hot side (450 off the vertical) has a greater increase in tube spacing than occurs on the cold side. The greater hydrodynamic force on the hot side has a greater effect than that of the cold side. The larger radius tubes have the greatest increases in spacing.
This case (C2) has no AVBs in it and helps understand how the fluid forces push the tubes and how the tubes deform at operating conditions. Case C3A is a repeat of this case, but with the effects of the AVBs, retaining bars, retainer bars, and bridges included.
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Ak Fig. 5.2-1 Case-C2: Deformation due to dynamic pressure (no AVBs)
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Ak Fig. 5.2-2 Case-C2: Distance between adjacent tubes in Col.78 due to dynamic pressure MITSUBISHI HEAVY INDUSTRIES, LTD.
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At
5.3 Case-C3A
Tube Deformation from Hydrodynamic Force (AVB assembly in)
Figure 5.3-1 (top 3D view) shows a similar overall displacement pattern for Case C3A and Case C2 (i.e. contraction on top and expansion on the hot and cold sides). Figure 5.3-1 (bottom view) shows the "total" tube deformation, which is the combination of the horizontal and vertical displacements. This view was not plotted for Case C2.
Figure 5.3-2 shows how the total deformation relates to the displacement in the vertical direction (top view) and in the horizontal direction (bottom view). The general trend seen in Case C2 where the hydrodynamic forces caused the bundle to displace toward the hot side and for the top of the bundle to move downward is also evident in Case C3A.
However, the influence of the AVBs, retaining bars, and retainer bars produces some added effects. Figure 5.3-2 (bottom view) shows that the maximum out-of-plane deformation occurs near Col.10 at the ends of the retaining bars, even though the maximum dynamic pressure is located above Col.30. The maximum out-of-plane deformation isi I Figure 5.3-2 (top view) shows the retaining bar deflection. As the pressure pushes the tubes away from the bundle central plane, they take the AVBs and retainer bars with them
- and stretch the retaining bars. This stretching of the retaining bars causes them to flatten out (displace downward) at the top of the bundle (in the center columns). The hot side I cold side hydrodynamic forces also cause the tubes to displace downward (at the top of the bundle). The maximum downward deformation isi I Figure 5.3-3 shows AVB and retaining bar deformation along AVB-B06. The bottom view with 100x magnification shows the downward displacement of the retaining bar at the center columns and shows AVB bending.
Figures 5.3-4 and 5.3-5 show the gap distributions between tubes and AVBs at cross sections along AVBs B06 and B(5. The largest gaps are found in the zone bounded by Columns 77 to 81 and Rows 104 to 122. This zone corresponds to the region with the most severe wear in Unit-2 and Unit-3. The largest increase in tube-to-AVB gap in this region is [ Ifor Section B6 andI Ifor Section B5. Figure 5.3-6 contains another display of the change in tube-to-AVB gaps within Section B5.
Figure 5.3-7 shows the regions along the AVBs in Column 78 where there is tube contact or a gap. On the side of the AVB in the A-direction (view i) there are gaps on the full population of tubes between Row 80 and Row 112. In the B-direction (view ii) there is intermittent contact. Support by an AVB on a single side of the tube is considered to be an MITSUBISHI HEAVY INDUSTRIES, LTD.
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At "active" support. Tubes with no AVB contact on either side are considered to be "inactive" supports. Within the Figure 5.3-7 population there are many tubes with consecutive inactive supports. The largest number of consecutive inactive supports in this figure is six.
Such an unsupported tube span would have a low natural frequency and would exhibit unstable vibration characteristics under normal operating conditions.
Figure 5.3-8 shows that the distance between Column 78 tubes increases the most on the hot side where the hydrodynamic force is largest. The increase is greatest between the largest radius tubes. Elastic tube bending produces the reduction in spacing on the cold side.
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Fig. 5.3-1 Case-C3A: Total deformation due to dynamic pressure (with AVB contact)
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A&L Fig. 5.3-2 Case-C3A: Deformation contour due to dynamic pressure (tubes-AVBs contact)
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Ak Fig. 5.3-3 Case-C3A: Deformation due to dynamic pressure (tubes-AVBs contact)
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I-Fig. 5.3-4 Case-C3A: Gap distribution between AVBs and tubes in B6 section MITSUBISHI HEAVY INDUSTRIES, LTD.
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Ak Fig. 5.3-5 Case-C3A: Gap distribution between AVBs and tubes in B5 section MITSUBISHI HEAVY INDUSTRIES, LTD.
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Ak Fig. 5.3-6 Case-C3A: Gaps between AVBs and tubes in each Column in B5 section MITSUBISHI HEAVY INDUSTRIES, LTD.
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Fig. 5.3-7 Case-C3A: Gaps of tubes in Col.78 to adjacent AVBs MITSUBISHI HEAVY INDUSTRIES, LTD.
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Fig. 5.3-8 Case-C3A: Gap between adjacent tubes in Col.78 under dynamic pressure MITSUBISHI HEAVY INDUSTRIES, LTD.
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5.4 Case-C3B
Tube deformation - Out-of-Plane Hydrodynamic Force Alone Case-C3B considers only the hydrodynamic pressure effects in the tube out-of-plane direction. Figure 5.4-1 shows a comparison of the horizontal tube displacement from Cases C3A and C3B. The Case C3B out-of-plane maximum displacement is I I Iand for Case C3A the result is I ]This indicates that the out-of-plane hydrodynamic pressurewithout the vertical, in-plane component produces a larger out-of-plane displacement.
Figure 5.4-2 compares the vertical displacements for these two cases. The maximum downward deflection at the top of the tube bundle for Case C3B is Jand for Case C3A it is I ISo, the out-of-plane load case has less downward displacement at the top of the bundle.
Figures 5.4-3 and 5.4-4 display the gap distributions between tubes and AVBs in cross sections along AVBs B06 and B05. These results are quite similar for both the C3A and C3B cases.
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-12 Fig. 5.4-1 Case-C3B: Deformation out of plane contour MITSUBISHI HEAVY INDUSTRIES, LTD.
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At Fig. 5.4-2 Case-C3B: Vertical deformation contour MITSUBISHI HEAVY INDUSTRIES, LTD.
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At Fig. 5.4-3 Case-C3B: Gap distribution between AVBs and tubes in B6 section MITSUBISHI HEAVY INDUSTRIES, LTD.
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Ak Fig. 5.4-4 Case-C3B: Gap distribution between AVBs and tubes in B5 section MITSUBISHI HEAVY INDUSTRIES, LTD.
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5.5 Case-C3C
Tube deformation with Stiffer Retaining Bars Case C3C is the same as case C3A, except that it has stiffer retainer bars. The retaining bar stiffness used in case C3C is 16 times larger than that of the actual bar. The factor of 16 results from doubling the retaining bar diameter based on the moment of inertia expressed by 7r/64 x d4 .
Figures 5.5-1 and 5.5-2 show a comparison of the out-of-plane displacement and the vertical displacement for cases C3A and C3C. Stiffening the retainer bar by a factor of 16x produces a 15% reduction in deflection, which is small.
Figure 5.5-3 shows that the retaining bar and AVB deflection shapes are nearly the same.
This further demonstrated in Figures 5.5-4 and 5.5-5 show the tube-to-AVB gap distributions at Sections B6 and B5 for cases C3A and C3C. All four cases have a maximum gap change of I ](when rounded off to the nearest mil). If the analytical results are used with their reported number of digits, it might be concluded that there is a 20% reduction in gaps due to the stiffening of the retaining bars.
It is concluded that increasing the retaining bar stiffness is not an effective way to reduce the tube-to-AVB gaps.
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Document No.L5-04GA564(9) r Fig. 5.5-1 Case-C3C: Out-of-Plane Deformation based on Retainer Bar Stiffness MITSUBISHI HEAVY INDUSTRIES, LTD.
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Aar Fig. 5.5-2 Case-C3C: Vertical Displacement based on Retainer Bar Stiffness MITSUBISHI HEAVY INDUSTRIES, LTD.
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Fig. 5.5-3 Case-C3C: Deformation mode due to dynamic pressure MITSUBISHI HEAVY INDUSTRIES, LTD.
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Ak Fig. 5.5-4 Case-C3C: Gap distribution between AVBs and tubes in Section B6 MITSUBISHI HEAVY INDUSTRIES, LTD.
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AO Fig. 5.5-5 Case-C3C: Gap distribution between AVBs and tubes in Section B5 MITSUBISHI HEAVY INDUSTRIES, LTD.
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5.6 Case-C3A'
Tube Deformation from the latest Hydrodynamic Force (AVB assembly in)
Figure 5.6-1 shows the "total" tube deformation, which is the combination of the horizontal and vertical displacements. Horizontal deformation is dominant to total. The large hydrodynamic force in HOT side makes this horizontal displacement.
Figure 5.6-2 shows how the total deformation relates to the displacement in the vertical direction (top view) and in the horizontal direction (bottom view). The general trend is almost same as Case C3A. The hot side / cold side hydrodynamic forces also cause the tubes to displace downward (at the top of the bundle). The maximum downward deformation is l Figure 5.6-3 shows AVB and retaining bar deformation along AVB-B06. The deformation trend is same as Case C3A.
Figures 5.6-4 and 5.6-5 show the gap distributions between tubes and AVBs at cross sections along AVBs B06 and B05. The largest gaps are found in the center column and high row zone. This zone corresponds to the region with the most severe wear in Unit-2 and Unit-3. The largest increase in tube-to-AVB gap in this region is I for Section B6 and B5.
Figure 5.6-6 shows the regions along the AVBs in Column 78 where there is tube contact or a gap. In Case C3A', there are many tubes with consecutive inactive supports as same as Case C3A. Such an unsupported tube span would have a low natural frequency and would exhibit unstable vibration characteristics under normal operating conditions.
Figure 5.6-7 shows the distribution of contact forces between tubes and AVBs. This contour just express compression magnitude, however contact forces can be obtained by multiplying by compression spring stiffnessl .1 In the center column and high Row area, where severe wear occurred, the contact forces are around IThis small force hardly supports and fixes a tube.
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Ak Fig. 5.6-1 Case-C3A': Total deformation due to dynamic pressure (with AVB contact)
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Fig. 5.6-2 Case-C3A': Deformation contour due to dynamic pressure (tubes-AVBs contact)
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Ak Fig. 5.6-3,Case-C3A': Deformation due to dynamic pressure (tubes-AVBs contact)
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Ak Fig. 5.6-4 Case-CaA': Gap distribution between AVBs and tubes in B6 section MITSUBISHI HEAVY INDUSTRIES, LTD.
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Fig. 5.6-5 Case-C3A': Gap distribution between AVBs and tubes in B5 section MITSUBISHI HEAVY INDUSTRIES, LTD.
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/I-Fig. 5.6-6 Case-C3A': Gaps of tubes in Col.78 to adjacent AVBs MITSUBISHI HEAVY INDUSTRIES, LTD.
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Fig. 5.6-7 Case-C3A': Distribution of contact forces between tubes and AVBs MITSUBISHI HEAVY INDUSTRIES, LTD.
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5.7 Case-D1
Tube Deformation with manufacturing dispersion and the latest Hydrodynamic Force (AVB assembly in)
Figure 5.7-1 shows the "total" tube deformation. Tube bundle expands by manufacturing dispersion. Color counter shows no tendency of hydrodynamic force such as Case C3 series. This indicates that manufacturing dispersion is dominant for tube deformation and prevents hydrodynamic deformation due to large friction force.
In Case C3A', out-of-plane tube displacement pulls AVBs and retainer bars outward. In the center columns, this causes the retaining bars to displace downward. Figure 5.7-2 presents the displacement in vertical direction in Case D1. The center column AVBs in Case D1 seem to be fixed because friction force due to manufacturing dispersion is higher than Case C3A'.
Figure 5.7-3 shows AVB and retaining bar deformation mode along AVB-B06. The deformation mode is different from Case C3 series. The center column AVBs are fixed by high friction force. Outer column AVBs are moved up due to outer column tubes outward displacement.
Figures 5.7-4 shows the gap distributions between tubes and AVBs at cross sections along AVBs B01, B02, and B05. The gaps are scattering by manufacturing dispersion distribution. The color contour in section BI1 and B2 includes many blue (compression) plots than section B5. This indicates that reaction forces at B1 and B2 are larger than B5.
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Ar Fig. 5.7-1 Case-D1: Deformations due to dynamic pressure and manufacturing dispersion MITSUBISHI HEAVY INDUSTRIES, LTD.
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-J Fig. 5.7-2 Case-D1: Vertical deformation contour due to dynamic pressure and manufacturing dispersion J
Fig. 5.7-3 Case-D1: Deformation mode due to dynamic pressure and manufacturing dispersion MITSUBISHI HEAVY INDUSTRIES, LTD.
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Fig. 5.7-4 Case-D1: Gap distribution between AVBs and tubes in B1, B2, and B5 section MITSUBISHI HEAVY INDUSTRIES, LTD.
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Appendix-9 Simulation of Manufacturing Dispersion for Unit-2/3 MITSUBISHI HEAVY INDUSTRIES, LTD.
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- 1. Purpose The wear in Unit-3 is more severe than Unit-2. This seems to be caused by difference of AVB-tube contact forces between Unit-2 and Unit-3. The contact force is generated by manufacturing dispersion; tube ovality, tube flatness, tube true position, AVB thickness deviation, AVB flatness, AVB twist. This appendix contains the evaluation of contact forces due to manufacturing dispersion between Unit-2 and Unit-3, and simulation of Ding signals in Unit-2. Fig.2-1 Distribution of contact forces in manufacturing dispersion analysis
- 2. Conclusion The analyses results show a consistent with the Ding signal distributions (as shown in Fig.2-1) and trend that contact forces between tube and AVB in Unit-3 are less than half of Unit-2 contact force (as shown in Fig.2-2).
Unit-2 Unit-3 Fig.2-1 Distribution of contact forces in manufacturing dispersion analysis r
Unit-2 Unit-3 Fig.2-2 Distribution of contact forces in manufacturing dispersion analysis MITSUBISHI HEAVY INDUSTRIES, LTD.
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- 3. Assumption
- 1) The manufacturing dispersion of Unit-2 A-SG (E089) represents Unit-2, and Unit-3 A-SG(E089) represents Unit-3.
- 2) Tube G value, tube pitch, tube flatness, AVB thickness and AVB twist deviations are considered as manufacturing dispersion. AVB flatness regards as 0, because AVB flatness means not micro winding beyond each row but macro winding beyond scores rows, and this macro winding makes negligible small contact force due to less stiffness of AVB beyond scores rows. The initial gap, between tube and AVB is nominal gap C in cold condition, and this gap is changed according to deviation of above values. Each deviation is randomly given to the gap in the analysis model. The contact force of tube to AVB is generated as reaction force due to accumulation of each deviation.
- 3) The manufacturing deviation is assumed to follow normal distribution, so the standard deviation is adopted in the analysis. The actual standard deviation is used for measured dimensions. AVB twist is deviates based on the actual distribution in the verification test for AVB press load (refer to Attachment 9-1) in this study.
- 4) AVB nose thickness and twist for Unit-3 are assumed to be smaller than Unit-2 as shown in Table 6-1. In a process of AVB making up in shop, AVB nose area is pressed in order to flattening increased inside thickness due to bending. The press !oad was[ J[NJ for Unit-2 and[ J[N] for Unit-3. The reason of this change is to improve AVB thickness and twist accuracy. All AVB twists for both Unit-2 and Unit-3 are satisfied with the tolerance specified in the design drawing, however checked by Go/No-go. Before adoptingC ) [N]
pressing for Unit-3, a verification testing was performed. Attachment 9-1 shows a
- summary of the test results and AVB twist in C )[N] press is better than[ ) [N].
- 5) ECT ding signals are supposed to indicate elastic ding by reaction force due to manufacturing dispersion. C ) [N] is a threshold of elastic ding as a result of ding testing.
[ ) [N] is necessary to make plastic ding on tube, however such high reaction force is hardly generated in bundle rotation analysis and flowering analysis. Attachment 9-2 presents a result of simple ding testing.
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- 4. Acceptance criteria There are no acceptance criteria associated with this report since this evaluation is performed to compare the trend of the tube-to-AVB contact force in Unit-2 and Unit-3.
- 5. Design Inputs 5.1 Geometry The nominal dimensions are obtained from the design drawings (Ref.1 to 7).
5.2 Manufacturing dispersion and tolerances Tube G value, tube pitch, tube flatness, AVB thickness deviation, AVB twist, and AVB flatness are considered in manufacturing dispersion analysis. Figure 5.2-1 shows image of each deviation. Table 5.2-1 shows the manufacturing dimensions and tolerances. Table 5.2-2 presents measurement results of the dimensions. AVB thickness in bending portion is measured separately from straight bar, because AVB bending process makes AVB inside thickness increase.
Tube G value Tube pitch Tube Flatness (True position of land) 4J AVB thickness AVB twist AVB Flatness Figure 5.2-1 Image of manufacturing dispersion MITSUBISHI HEAVY INDUSTRIES, LTD.
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Table 5.2-1 Dimensions and tolerances AVB Tube Thickness Twist Flatness G value Pitch Flatness Nominal Tolerance Note Measured Go/No-go checked Go/No-go checked Measured - Go/No-go checked Note: The tolerances are specified in the design drawings (Ref.4 and 7) and material specification (Ref.8)
Table 5.2-2 Measurement results of the dimensions AVB thickness change from nominal Standard deviation TA vi AVB thickness change from nominal aA Tube ovality Bending portion Straight Bar Bending portion Straight Bar GH 2A 2B 3A 3B MITSUBISHI HEAVY INDUSTRIES, LTD.
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- 6. Methodology 6.1 Analysis model All parts of the U-bend assembly above the #6 TSP (Tubes, AVBs, Retaining bars, Retainer bars and Bridges) are modeled as beam elements. Figure 6.1-1 shows overview of the analysis model. The model area is a quarter by taking into account symmetry. The contact points between tube to AVB, and tube to TSP are modeled as gap elements, which show spring property in compression. This model is same as the flowering analysis model in Appendix-6. FEA code used is ABAQUS.
Bird's-eye View of the Model Front View of the Model Figure 6.1-1 Analysis model 6.2 Inputs of manufacturing dispersion 6 types of the manufacturing dispersion introduced in Section 5.2 are considered in the analysis model. The deviation is generated according to random number and inputted to the gap elements in the analysis model. The random number dispersion follows normal distribution. Figure 6.2-1 indicates how to input the deviation to gap element in the analysis model. Especially for AVB twist, AVB twist factor in consideration of torsion stiffness is defined as a decrease function of distance from AVB bending peak, because the more contact points leave from AVB nose, the less AVB torsion stiffness is. Figure 6.2.2 shows AVB twist factor. In AVB nose area, the factor is always 1, because increased twist from nose tip and decreased stiffness from nose tip cancel each other. On the other hands, AVB twist is considered to be kept along the straight bar, so the factor decreases according to far from AVB nose.
Table 6.2-1 shows inputs used as manufacturing dispersion for the analysis model.
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At I Total deviation = 60 + (5A+/- 3 0A)/ 2 + (6 H+/-3 0H)/ 2 + (+/-3 Os) + I+/-3aTA 1/2 + (+/-3aBA)/2 + (+/-30aB)/2 positiont3as Tube AVB nose Figure 6.2-2 how to consider manufacturing dispersion 6.3 Analysis cases The manufacturing dispersion analyses are performed for the cases as shown in Table 6.2-1.
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~Non-proprietary Version ) P98 Document No.L5-04GA564(9) 4A1k Table 6.2-1 Measurement results of the dimensions Unit: mm (mils)
Standard deviation c AVB thickness change from nominal Tube Unit 6A ovality AVB thickness change from Tube AVB twist 2 AVB Tube 6H nominal OA ovality Flatness"3 Flatness Bending portion Straight Bar Bending portion Straight Bar OyH OBA (YB Case 1 Unit-2A (U2-E089)
Case 2 Unit-3A (U3-E089)
Note I Measured' Measured Measured Measured Measured Measured Go/No-go [ Go/No-go Go/No-go
____~ _ _ _ I___ _ _ I__ _ _ checked checked checked Note)*I:AVB thickness of bending portion is assumed based on the fact obtained by the AVB pressing test results(See Attachment 9-2 for details), which indicated that AVB nose thicknesses of Unit-2 SGs are larger than Unit-3 SGs due to the difference of AVB pressing load (( ) N for Unit-2 SGs and
( ) Nfor Unit-3 SGs) and the side wide AVBs of Unit-2 are thinner than other types of AVBs.
- 2:AVB twist probability distributions are assumed based on the AVB pressing test results(See Attachment 9-2 for details). The probability distribution multiplied by the factor of each AVB type, shown in this table; is assumed.
- 3: AVB Flatness is judged as 0, because AVB flatness is assumed macro distortion.
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- 7. 7. Results Ak 7.1 Simulation of Ding signals Figure7.1-1 shows the distribution of contact forces over( )[N], that is threshold of Ding signal, of Casel and Figure7.1-2 shows the result of Case2. Casel simulates Unit-2 and Case2 simulates Unit-3. The results are similar to Fig 1 of Attachment 9-3 of Ding signals distributions on PSI-ECT.
The manufacturing dispersion makes a lot of off-set points between tubes and AVBs. The higher force is generated at stiffer portion of tube and AVB, because the off-set is displacement control type loading. In AVB bending portion, AVB and tube (support span is shorter) are stiffer than straight bar region, so that much higher forces are generated at around Row 15(Center Wide AVBs nose), around Row 30(Side Narrow AVBs nose) and around Row 50(Center narrow AVBs nose). In the manufacturing dispersion analyses, much higher reaction forces are generated at AVB bending portion in Unit-2 than Unit-3, because AVB nose thickness and twist for Unit-2 is larger than those of Unit-3 due to difference of the press loads for flattening. This is assumed to be a mechanism of Ding signals and a cause of Ding signals difference between Unit-2 and Unit-3. Also, the assumptions in this study are supposed to be adequate by showing the similar contact force distributions to Ding signals.
7.2 Contact forces Figure 7.2-1 and 7-2-2 present the distributions of the average contact forces of each row are shown for both Units and indicate that Unit-3 has smaller contact forces at AVB supports than Unit-2. This difference is one of causes that Unit-3 has more severe wears, because contact forces have a role to restrict tube vibration.
Fig.7.2-3 presents the displacement tendency of a representative tube (RowlOO) in Unit 3 and shows tube bundle expansion at each AVB contact point due to the dimensional variation.
The displacements of tubes in outer columns and center AVB support points are larger than, those in center columns and side AVB points. This tendency can be explained by Fig.7.2-4 that shows the image that tubes displacement is restricted by TSP.
This tube displacement means bundle expansion, and the equivalent average gap per each column in each AVB support point is found by dividing the expansion by the number of column. Fig.7.2-5 shows inverse of the average gap at each AVB support point. The inverse of the gap corresponds with ECT Voltage, because if gap increase, ECT voltage will decrease.
Fig.7.2-5 is similar to the distribution of ECT signals shown in Fig.1 of Appendix-6.
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Fig.7.1-1 distribution of contact forces in Case 1 [Unit-2]
Fig.7.1-2 distribution of contact forces in Case 2 [Unit-3]
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)
Fig.7.2-1 Distributions of the average contact forces of each row in Case 1
[Unit-2]
-I2 Fig.7.2-2 Distributions of the average contact forces of each row in Case 2
[Unit-3]
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Fig.7.2-3 Displacement tendency at each AVB contact point of Row100 tubes in Case 2
[Unit-3a I
Tube bundle expands to AVB outward "Ol0i
)
Displacements of tubes close to TSP are restricted.
TSP I uDe Fig.7.2-4 Interaction of TSP to tube displacement MITSUBISHI HEAVY INDUSTRIES, LTD.
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Fig.7.2-5 Inverse of average gap at each AVB point RowlOO tubes in Case 2
[Unit-3]
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- 8. References
- 1) L5-04FU051 Rev.1 Design drawing of Tube Bundle 1/3
- 2) L5-04FU052 Rev.1 Design drawing of Tube Bundle 2/3
- 3) L5-04FU053 Rev.3 Design drawing of Tube Bundle 3/3
- 4) L5-04FU108 Rev.3 Design drawing of Tube Support Plate Assembly 3/3
- 5) L5-04FU111 Rev.2 Design drawing of Anti-Vibration Bar Assembly 1/9
- 6) L5-04FU112 Rev.1 Design drawing of Anti-Vibration Bar Assembly 2/9
- 7) L5-04FU118 Rev.3 Design drawing of Anti-Vibration Bar Assembly 8/9
- 8) L5-04FZ014 Rev.4, Purchase specification of heat transfer tubing MITSUBISHI HEAVY INDUSTRIES, LTD.
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A~k Attachment 9-1 Summary of verification test for AVB press load improvement There is an AVB bending process in shop for AVB making up. In this process, AVB inside thickness increases due to bending. If as bent, AVB bending portion thickness deviate from the maximum tolerance specified in design drawing, so MHI presses AVB bending portion for flattening. In Unit-2, the press load is[ ), and it is necessary to touch up AVB bending inside portion after bending, because press load is insufficient to make the thickness within the maximum tolerance. In Unit-3, the press load is changed from C )[N] to )I[N] in order to improve AVB bending portion accuracy.
This attachment introduces the result of verification test for AVB press load change performed at that time.
> press load:( ) [N],C ))[NJ, t J[N]
> AVB twist measurement area Twist measured Twist measured area area Marking AVB3 press
> Twist results machine
> Summary In Unit-2, AVB which twist deviates from the tolerance is needed to be flattened and touched up by hand, so that AVB twist satisfies the tolerance. In Unit-3, it comes to be not necessary to touch up after the( )[N] press adopted.
The standard deviation of [ JIN] press is supposed to be about a half of J [N]
press.
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Attachment 9-2 Confirmation test for Ding load There are a lot of Ding ECT signals indicated in Unit-2. The distribution trends of Ding signals are quite different between Unit-2 and Unit-3. So, MHI performed a simple mechanical load test in order to confirm that how much load was necessary to make Ding ECT signal (>[C V).
This attachment provides the summary of the confirmation test.
- The correlation between load and ECT Ding signal is achieved by ECT testing at each load step. load AVB AVB load I 15mm
-1*1ý- 2mm Summary Inthe case that( JV Ding signal means elastic ding, the minimum load is C )NJ. If
[ J Ding signal means plastic ding, the minimum load ) [N] will be necessary.
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Attachment 9-3 Ding Signals at U-bend Region from PSI AO The PSI-ECT inspection was performed with all four SGs in the horizontal position. The Unit-2 SG inspection was performed at the SONGS site and the Unit-3 SG inspection was performed in the MHI shop prior to shipment. Analysis of the PSI data shows a distinct difference between the Unit-2 and Unit-3 SG. In the Unit-2 SGs there were many ding signals at the AVB tips that were not evident in the Unit-3 SGs as shown in Fig. 1. The greater number of dings implies more interference between the tubes and AVBs, which correlates with a larger variation in gaps and presumably greater average tube-to-AVB contact force during operation. This is consistent with the finding that the tube-to-AVB gaps in the Unit-3 SG are slightly larger and that the average contact force is smaller in the Unit-3 SGs than in the Unit-2 SGs (refer to Appendix-6).
MITSUBISHI HEAVY INDUSTRIES, LTD.
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- Non-proprietary Version I[ ] (P.9-18)
Document No.L5-04GA564(9)
(a) Unit-2 K
(b) Unit-3
-3 Ding signals at U-bend region from PSI ECT MITSUBISHI HEAVY INDUSTRIES, LTD.
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