Conceptual Design Report on JT-60SA · Conceptual Design Report on JT-60SA _______ ... “Boiler...

Conceptual Design Report on JT-60SA ＿＿＿＿＿＿＿

3. Plant Description Sec. 3.4

3.4 Cryostat 3.4.1 Design Concept 3.4.1.1 Overview Cryostat is required to produce a vacuum insulating for superconducting magnets, bio-shielding and gravity support for the tokamak devices. The cryostat consists of vessel body and gravity support as shown in Figure 3.4.1.1. The vessel body consists of top plate and 8 parts of body split. The top plate has access hole for the central solenoid. The gravity support consists of a base plate with gravity support legs, cylindrical shell, double ring and outer ring. The gravity support also has several access holes for maintenances. The structural material of cryostat is type 304 stainless steel (Co <0.05 wt%). The conceptual design of cryostat is conducted by Japan (JA). The entire structure of cryostat in detail is designed by the European Union (EU).

Figure 3.4.1-1 Bird eyes’ view of cryostat.

Vessel body

Gravity support

Top Plate



3.4.1.2 Design JT-60SA is planned to improve existing facilities, such as heating devices of NBI and ECRH with improvements. These facilities constrain the geometry of the cryostat due to the installation into the JT-60 torus hall (Figure 3.4.1-2). (1) Original Vessel Body Design The spherical structure as a vessel body is adopted to achieve an effective utilization of the limited space. Public transport from EU to Naka-site also limits its size and weight. Entire dimensions of the original cryostat are given in Figure 3.4.1-3. Total height of the cryostat is more than 15 m and radius of the vessel body is 6.7 m. Bolt joint structure is applied to the most toroidal and poloidal joints. The vessel body is fabricated with a double walled structure, which is designed as an inner skin of 34 mmt and an outer skin of 6mmt. The distance between inner and outer skin is 220 mmt and this space is filled with boron doped concrete for bio-shielding. Primary structure is the inner skin and designed to withstand self-weight of cryostat and atmospheric pressure (vacuum level < 10-4 Pa) in the operational condition. Additional poloidal rib reinforcements support port flange structures, which contain plasma diagnostics and so on. The middle part of the vessel body is split in eight in Figure 3.4.1-3. Each flange is lip-sealed and jointed with bolt structures to adjust the position. (2) Expected Modification of Vessel Body The original cryostat is expected to be elongated in the vertical direction because of assembling and maintenance, especially for cryogenic devices, such as in-cryostat feeder, insulation breaks and TF terminal joints as shown in Figure 3.4.1-4. The in-cryostat feeder connects the feed-through and the terminals. The feeders covered with stainless steel conduit, which contains a pair of each superconducting bus-bar, cooling pipes and high-voltage instrumentation cables. Although the coil circuits cooled by the helium forced flow,

Figure 3.4.1-2 Layout of the cryostat in the torus hall.

N-NBI Tank

Cryostat

P-NBI TankP-NBI Tank

P-NB

I Tan

k

P-NB

I Tan

k

Rem

ote

Han

dlin

g

Rem

ote

Han

dlin

g

Coi

l Fee

der

T-NBI Tank

T-NBI Tank

Vacuum Pum

p

Remote Handling

Remote HandlingN-NBI Tank

Cryostat

P-NBI TankP-NBI Tank

P-NB

I Tan

k

P-NB

I Tan

k

Rem

ote

Han

dlin

g

Rem

ote

Han

dlin

g

Coi

l Fee

der

T-NBI Tank

T-NBI Tank

Vacuum Pum

p

Remote Handling

Remote Handling



insulation breaks are required to be isolated coil potential pipes from ground potential cryo-lines. The insulation breaks are subject to be replaced in case of a helium leakage since insulation breaks consist of glass epoxy plastic tube bonded to the steel tubes. TF terminal joint is also subject to maintenance because it cannot inspect before assembly. Original cryostat does not have sufficient space for maintenance so that additional 1 m collar on the top of vessel body is expected to keep access space as an option.

3.4.1-3 Dimension of Original Cryostat Structure

Upper View

Double Wall Structure (B)

B



3.4.1-4 Expected Modification of Cryostat Vessel Body

Vertical Port

EF 6 EF 5

TF TerminalCS



(3) Gravity support assembly The gravity support consists of the rigid double ring structure, wider outer ring, cylindrical shells and base plate anchored by 80 of M64 bolts. The thickness of most structural members is more than 100 mm to achieve higher rigidity and base plate is 150 mm. The double ring directly supports the weight of tokamak devices and is connected to the base plate through the nine gravity support legs. Base plate and outer ring are divided into three parts for transports. Detailed description of gravity support is discussed in 3.4.6 (4) Design code Design code is based on the American Society of Mechanical Engineers (ASME) “Boiler and Pressure Vessel Code VIII” or other code equivalent to this. (5) Size limit Transport conditions determine the size and weight of the parts split. Table 3.4.1-1 tabulates the transport conditions from Hitachi-port to Naka-site.

Table 3.4.1-1 Weight Width Length Height < 70 ton < 7 m < 12 m < 4.8 m

(6) Material conditions The structural material is type 304 stainless steel (Co: < 0.05 wt%), which prescribed in ASME section I. 3.4.2 Exhaust System One of the cryostat roles is to produce the vacuum insulation for the superconducting coils, and new exhaust system for the inside of the cryostat is required to keep the operational pressure less than 1.0 x 10-4 Pa. The inside of the cryostat is covered with super insulation (SI) to maintain the superconducting cooling, and more than 100,000 m2 of surface area should be considered for exhaust system specification. New exhaust system is connected to the cryostat by one exhaust port and consists of pumps as shown in Table 3.4.2-1. Figure 3.4.2-1 shows the exhaust system diagram (Cryo-effect is omitted). Oil Diffuser pumping system is not chosen because of oil disposal process in case of its decommission. The pressure expected in these exhaust system is 4.9 x 10-3 Pa. The parameter in the examination is summarized in Table 3.4.2-2, 3. Main pumping system is mainly utilized for helium gas and less than 5.0 Pa is the exhaust condition. Main pumping system consists of the main exhaust pump and main exhaust fore-pump. Main exhaust pump is two lines of magnetic levitation turbo molecular pumps (3.3 m3/s of nominal exhaust speed). Main exhaust fore-pump is an auxiliary pump, which consists of mechanical booster pump (1000 m3/s of nominal exhaust speed) and dry pump (1012 m3/s of nominal exhaust speed). A main exhaust fore-pump assist a line of main exhaust pump, but auxiliary pumping of the other fore-pump is possible by line switch valve in case of accident. Cryopump system is mainly utilized for water gas and less than 10 Pa is the exhaust condition. Cryopump system consists of the cryopump and cryo-fore-pump. Cryopump is two line (10 m3/s of nominal exhaust speed). Cryo-fore-pump is an auxiliary pump, which consists of mechanical booster pump (1000 m3/s of nominal exhaust speed) and dry pump (1012 m3/s of nominal exhaust speed). Cryo-fore-pump assist a line of cryopump, but auxiliary pumping of the other cryo-fore-pump is possible by line switch valve in case of accident. Roughing pump system is mainly utilized for air and the exhaust condition is up to 1.3 Pa from atmosphere.



Roughing pump system consists of mechanical booster pump (6200 m3/h of nominal exhaust speed) and dry pump (1701 m3/h of nominal exhaust speed). The operation checks of pump system for the environmental conditions, which are high magnetic field, radiations, are still under the examination. Maintenance space, piping, radiation controlled zone and so on are still issue of the exhaust system design.

Table 3.4.2-1 Basic composition of cryostat exhaust system

Exhaust system Exhaust speed Pressure range Pump

Main pump 2.42 m3/s 5.0 - 1.3×10-7 PaMagnetic levitation turbo molecular pump Mechanical booster pump Dry pump

Cryopump 6.04 m3/s 10 - 1.3×10-7 Pa Cryopump Mechanical booster pump Dry pump

Roughing pump ― 1×105 - 5.0 Pa Mechanical booster pump Dry pump

Figure 3.4.2-1 Exhaust system diagram for cryostat.



Table 3.4.2-2 Manifold line conductance

No. Item Size

N2 conductance

（m3/s）

H2 conductance

（m3/s）

1 Cryostat port φ800 × 762L 82.4 308.3

2 Manifold port φ800 × 2552L 24.6 92.0

3 Reducer (φ800 - φ1000) × 300L 286.8 1073.1

4 Manifold for cryo port φ1000 × 3200L 38.3 143.3

5 Total conductance(1 - 5) ― 12.1 45.4 Man

ifold

line

6 Manifold for TMP port φ1000 × 2000L 61.3 229.4

1 Orifice φ1000 ― φ496 30.1 112.6

2 Port φ496 × 150L 99.8 373.4

3 Vacuum valve ― 20.0 74.8

4 Pipe φ496 × 250L 59.9 224.1

5 Cryopump(Pumping speed) ― 10.0 18.0 Cry

opum

p lin

e

6 Total conductance(1 - 5) ― 4.8 11.8

1 Orifice φ1000 ― φ344 12.4 46.4

2 Port φ344 × 150L 33.3 124.6

3 Vacuum valve ― 7.2 26.9

4 Pipe φ344 × 250L 20.0 74.8

5 Mesh filter ― 40.0 149.7

6 TMP ― 3.3 2.4

Mai

n pu

mp

line

7 Total conductance(1 - 6) ― 1.6 1.99

Table 3.4.2-3 Surface of vacuum vessel

Item Material Surface area

（m2）

Outgas rate

（Pam3/s/m2）

Total outgas

（Pam3/s）

Cryostat 304 stainless steel

Port

80K shield plat 316L stainless steel

10,000 1.3×10-8 1.2×10-4

Supper insulation Aluminum 45,000 2.5×10-8 1.1×10-3

Supper insulation Polyimide 10,000 1.0×10-6 1.1×10-2

Supper insulation Polyethylene 35,000 5.0×10-7 1.8×10-2

Total 3.0×10-2



3.4.3 Thermal Shield Inner surface of the cryostat will be covered with an 80K thermal shield. Figure 3.4.3-1 shows a schematic of the 80K thermal shield. The 80K panel made of SS304L reinforced with C-channel frames is supported from the cryostat by Ti-6Al-4V legs and its total height is constrained to be less than 150 mm. The panel has coolant tube of 80K He gas flow on the magnet (4K) side and the cryostat (RT) side is covered with super-insulator (SI) to reduce heat load due to radiation from hot surface of the outside. Radiation heat intrusion through SI can be reduced to less than 1/100 of the non-covered region, which is dominant as the total heat load. The fraction of non-covered region is assumed to be 2% because of joints structure to the large ports and gravity supports of the vacuum vessel. The heat load due to radiation is less than 3W/m2. Detail geometry of each 80K panels has been under working conditions because of the thermo mechanical difficulties in structure and space with the vacuum vessel and magnets. To estimate total heat load on 80K shields, concept of an 80K panel is shown in fig. 3.4.3-1. Area of a panel is 1 m2, which determines height of a support leg as 80mm. Support leg is required to absorb differences in temperature expansions and should be less than 3.1 mm. Mechanical load due to disruption and the seismic are not so large for each panel on cryostat. The worse load is presumed to be in-cryostat works of human being as scaffolding. Mechanical load and moment on a panel are assumed as shown in Fig. 3.4.3-1. The width of support leg is

SI 16-24 layer Cooling tube (80K He gas)

C-channel

A

AA-A B

B-B

B

Support leg (Ti-6Al-4V)

Support leg (Ti-6Al-4V)

3 mm 80 mm

50 mm

<1.5 m

1 m2 Cryostat

Assumed load (2kN)

Assumed moment (2kNm)

Operation Baking -B

VV 316L 276 313 473

VV Port 316L 212 Transient Transient

VV Leg 316L 180 Transient Transient

VVTS 80K TS(VV) 316L 334 80 100

TFC Case 316LN 990 4 4

PFC Case 316LN 372 4 4

TFC Leg 316LN 52 Transient Transient

CTS 80K TS(Cryostat) SI (20-layer) 637 80 80

Cryostat Cryostat 304 637 293 293

Temperature [K]Surface Area[m2]

Vacuum Vessel

Magnets

Material

Table 3.4.3-1 Thermal conditions of each component



resulted in 50 mm for these mechanical loads and moment. Estimated heat load due to support legs is less than 12W/m2. Total heat load onto the inner surface of cryostat (~600m2) is presumed to be 9 kW. Because of the space limit around many ports structure, 80K panel will be segregated in peaces and the height is limited up to 100mm. These conditions of port-around (~300m2) resulted in the heat load of 9 kW. On the other hand, total heat quantities of vacuum vessel are 32kW during the operation and 165kW during the baking. The total description of the 80K thermal shield is showing table 3.4.3-1. 3.4.4 Ports and manhole Port allocations of the cryostat are shown in Figure 3.4.4-1. Port connected to the vacuum vessel is adjusted with bellows and insulator. The cryostat is grounded and gravity supports of vacuum vessel and TFC are also insulated at the double ring. Manifolds for vacuum vessel and in-vessel components are located through the gravity support as shown in Figure 3.4.4-2 on the left side. The spaces between cryostat and surrounding facilities, especially P-NBI systems, are so narrow that the cryostat is designed to keep each

P-NBI

Bellows

Support ring

Manifold

Figure 3.4.4-2 Allocation with the surrounding facilities and cryostat

Figure 3.4.4-1 Port allocation.



maintenance space for these gate valves without disassembling as shown in Figure 3.4.4-2 on the right side. The port structure (size and thickness of port, flanges joint and so on) in detail is still under the design work. 3.4.5 Vessel Structure 3.4.5.1 Background The vessel body is required of the light structure, which is expected as a toroidal one turn resistance of 25 μΩ, and robust structure against the operational load and buckling. The recent vessel body structure is modified into the cryostat elongated to secure maintenance space for cryogenic devices as shown in Figure 3.4.1-3. This section indicates the structural proposal and design study of original spherical vessel body from the FEM analyses results. 3.4.5.2 Structural analysis The weakest sections from P-10 to P-16 are modelled with single shell structure without poloidal ribs as shown in Figure 3.4.5-1. Static analysis against the vacuum pressure (0.1 MPa) and gravity load include the shielding material weight was performed with a cyclic symmetry condition. Large port bore of P-NBI is so effective to the rigidity of the vessel body, flange thickness is varied as shown in Table 3.4.5.1-1. Case_a is the thinnest flanges and the dependency on each large port (P-NBI and Rect. Port) is surveyed with other three cases. Buckling analysis and natural frequency analysis with the same model is also performed. The analyses results are summarized in Table 3.4.5-2. The thickness of the large bore of the P-NBI (P-15/17) is dominant condition for the reduction in stress and displacement rather than the large rectangular ports. The analyses results indicate that P-16 section is the weakest structure as shown in Figure 3.4.5-2

P-16 P-10

Upper

Lower

Large Rectangular Port(T-NBI/Exhaust)

Circular Port(Coolant/Exhaust)

Vertical Port

Small Rectangular Port(Measurement)

Toroidal flange

Poloidal flange

Cyclic symmetry boundary

Cramped boundary

Figure 3.4.5-1 FEM Analyses Model.

Case_a 0.050 0.050Case_b 0.100 0.050Case_c 0.100 0.100Case_d 0.200 0.050

8000

Thickness of shell element [m] Density [kg/m3]

0.034 0.200 0.200 0.050 0.050 20200

Rect. Port(Large)

Rect. Port(Small)

Vessel &Vert. Port

Joint andFlange

Model Vessel &Vert. Port

PoloidalFlange

ToroidalFlange P-NBI Circ. Port

Table 3.4.5-1 Analyses case and modelling conditions.



and the examination of the additional rib structure should be designed to reduce these bending deformations. This result is consistent with the natural frequency analysis, which is strongly affected by the P-NBI (P-16) port flange (Figure 3.4.5-3). On the other hands, critical buckling pressure is sufficiently higher than vacuum load as shown in Figure 3.4.5-4.

3.4.5.3 Structural proposal and further analyses requirement These analyses based on the single wall conditions and port structure and toroidal joint structure in detail should be confirmed. Especially, additional poloidal rib reinforcements should be clarified port flange structures, which contain plasma diagnostics and so on. The integrity with entire structure should be assured against accident cases. On the other hand, the 80 K panel as the thermal shielding should be confirmed against the operational eddy current and an adequate panel area segregated should be proposed for the design in detailed.

-

7.41P-16 Bottom NBI

6.02P-16 Bottom NBI

6.04P-16 Bottom NBI

-

3.16

11.83

Case_b120

P-16 Bottom NBI80

P-16 Bottom NBI12.62

60P-16 Bottom NBI

95P-16 Bottom NBI

80P-16 Bottom NBI

95P-16 Bottom NBI

150P-16 Bottom NBI

120P-16 Bottom NBI

Tresca Stress[MPa]

Displacement ?[mm]

NaturalFrequency

[Hz]

BucklingPressure

[MPa]Membrance Bending |?|

Model

Case_a

Case_c

Case_d 4.1113.96

12.53

4.10P-16 Upper NBI

Table 3.4.5-2 Analyses results of vessel body.

P-16 P-16

Membrane stress distribution(Case_b)

Max. shear [MPa]

Dsp.[m]

Displacement distribution(Case_b)

Tresca stress120 [MPa]

Displacement6.0 [mm]

Figure 3.4.5-2 Stress analyses results.



1st Mode of 12.62 HzCase_b

1st Mode of 13.96 HzCase_d

Figure 3.4.5-3 Natural frequency analyses results

1st Mode of 3.16 MPaCase_b

1st Mode of 4.11 MPaCase_d

Figure 3.4.5-4 Critical buckling pressure analyses results.



3.4.6 Gravity Support 3.4.6.1 Background The gravity support structure is required to support tokamak devices and also required to maintain accessibility for plasma diagnostics and other necessary pipes. The gravity support consists of a base plate, a cylindrical shell, a double ring and an outer ring as shown in Figure 3.4.6-1. Vacuum boundary is formed with the double ring, outer ring and cylindrical shell. The base plate is most basic gravity support structure, which has a diameter of 12 m and thickness of 150 mm, and nine gravity support legs are jointed onto the base plate. The base plate is split in three parts for transport and fixed on the existing building by 72 M64-bolts at the first assembling process of JT-60SA. The double ring and outer ring are jointed together with bolts and lip-sealed each other and cylindrical shell is welded to the inner side of double ring. Tokamak devices are directly bolted to the double ring so that higher rigidity is required to unify the operational electromagnetic (EM) loads. The double ring and outer ring are bolted onto the base plate. The double ring is one piece and outer ring is split in three pieces for transport.

Figure 3.4.6-1 Gravity Support



3.4.6.2 Structural Analyses As tabulated in Table 3.4.6-1, the structural integrity against the operational and seismic loads was evaluated by static analyses of finite element method (FEM). 360 degree of gravity support was modelled to perform the seismic analyses as shown in Figure 3.4.6-2. The gravity support is meshed at the middle of plate and there is a space between double ring, outer ring and 9 gravity support legs, but tying boundary (vertical direction) was applied. The anchor bolts of the base plate were modelled as the cramped mechanical boundary and bolt strength was evaluated with each reaction force. Vertical direction of the base plate is cramped and horizontal direction is freed, but vertical direction constraint is freed when reaction force is negative. Bolt between blocks split are jointed by beam elements with no frictions.

The stress evaluation is followed with Table 3.4.6-2. Anchor bolt material of MNJ-35A is the existing high-tensile strength steel and other necessary bolt will be determined by these analyses. (1) Electromagnetic load analyses EM load stress analyses evaluation is focused on the case 1A because the case 1A resulted in higher stress intensity than the case 1B. The EM load become internal force in the double ring structure, consequently the higher stress intensity is observed in the double ring structure and joint pad structure of base plate gravity support legs as shown in Figure 3.4.6-3. The rigidity as a gravity support is achieved since the maximum displacement is less than 1 mm. The stress evaluation, based on the local membrane (PL) stress and combination of PL and bending (PB) stress, is satisfied with the design criteria. Bolt joint structures between each block are also clarified as tabulated in the table 3.4.6-3. (2) Seismic load analyses Seismic load is evaluated with the factor as showing table 3.4.6-2. Asymmetric seismic load resulted in the higher stress intensity in the double ring structure and joint pad structure of base plate gravity support legs as shown in Figure 3.4.6-4. The rigidity as a gravity support is also confirmed that the maximum displacement is less than 1.5 mm. The higher membrane stress is observed in rib structure of the double ring, though the stress evaluation, based on the local membrane (PL) stress and combination of PL and bending (PB) stress, is satisfied with the design criteria. Bolt joint structures between each block are also clarified as tabulated in the table 3.4.6-4. 3.4.6.3 Structural proposal and further analyses requirement Evaluations of thermal stress due to the operational and accidental cases are required. Furthermore, detailed analyses, which are related to the bolt and key structure, are required.

Table 3.4.6-1 Analyses Category

ID Category Cryostat VesselBody Vacuum Vessel Superconducting

MagnetsVertical -16.5 16.5

Circumferential 2.3 -2.3Vertical 16.5 -16.5

Circumferential 2.3 -2.3Horizontal [MN] 1.23 1.2 4.26

Rocking Moment [MN m] 10.6 9.2 34.1Device Weight [MN] 4.1 4 14.2

Centre of Gravity [m] 8.6 7.7 8

Case 1A

Case 1B

Case 2

-

Seismic Load+ Dead Weight

Very Small Load[MN]

Dead Weight(Include vacuum pressure)

Electromagnetic Load+ Dead Weight

Table 3.4.6-2 Materials Sm [MPa] Local Membrane [MPa] (Membrane+Bending) [MPa] Factor (k)

115 172.5 172.5 1 (Seismic Case of 1.2)Sm [MPa] Allowable Stress [MPa] Allowable Shear Stress

229 114 87

304L

MNJ-35A



Vacuum Vessel Support (9)

TFC Support (18)

Rib for leg100mm

Pad50mm

Leg150mm

150mm

Figure 3.4.6-2 FEM Analyses Model.

Cylindrical shell 40mm

20mm

10mm72mm

150mm

Rib (small)40mm

Rib (large)100mm

170mm

100mm

84mmVertical port (large)

40mmRib Below VV100mm

Outer ring100mm

84mm



Mises [MPa] Mises [MPa]

max.bend.

Figure 3.4.6-3 Analysis Result of Case 1A (Electromagnetic Load).



Table 3.4.6-3 Stress Evaluation of Analyses Result Case 1A (Electromagnetic Load)

Stress Allowable stress（Mpa）（Mpa）

PL 17.86 172.50 ＯＫPL+Pb 35.81 172.50 ＯＫ

PL 9.32 172.50 ＯＫPL+Pb 10.60 172.50 ＯＫ

PL 8.83 172.50 ＯＫPL+Pb 10.41 172.50 ＯＫ

PL 8.77 172.50 ＯＫ

PL+Pb 10.67 172.50 ＯＫPL 17.13 172.50 ＯＫ

PL+Pb 45.14 172.50 ＯＫPL 16.17 172.50 ＯＫ

PL+Pb 48.40 172.50 ＯＫPL 25.97 172.50 ＯＫ

PL+Pb 28.19 172.50 ＯＫ

PL 17.78 172.50 ＯＫPL+Pb 70.54 172.50 ＯＫ

PL 51.31 172.50 ＯＫPL+Pb 117.55 172.50 ＯＫ

PL 55.41 172.50 ＯＫPL+Pb 75.50 172.50 ＯＫ

PL 50.71 172.50 ＯＫ

PL+Pb 81.97 172.50 ＯＫPL 24.08 172.50 ＯＫ

PL+Pb 58.90 172.50 ＯＫ

PL 12.56 172.50 ＯＫ

PL+Pb 58.24 172.50 ＯＫ

PL 11.62 172.50 ＯＫPL+Pb 66.58 172.50 ＯＫ

（１）

（２）

Rib below VV

Vertical port (large)

Outer ring

Symbol Judge

Vertical port (small)

Leg（１）

（２）

Rib for leg

Pad（１）

Cylindrical shell

Base plate

Evaluation part

Double ring

（２）

Rib (large)（１）

（２）

（１）

（２）

Stress Allowablestress Judge

58.01 115.00 ＯＫ57.62 115.00 ＯＫ

3.47 115.00 ＯＫ－－

10.62 ＯＫM64 anchor (inner)M64 anchor (outer) 114.00

Evaluation partM36 block connection between double and outer ringM48 block connection between legs and outer ringM48 block connection between legs and double ring



Mises [MPa] Mises [MPa]

max. bend.

Figure 3.4.6-4 Analysis Result of Case 2 (Seismic Load).



Table 3.4.6-4 Stress Evaluation of Analyses Result Case 2 (Seismic Load)

Stress Allowable stress（Mpa）（Mpa）

PL 75.46 207.00 ＯＫ

PL+Pb 90.19 207.00 ＯＫ

PL 72.59 207.00 ＯＫ

PL+Pb 91.18 207.00 ＯＫ

PL 12.96 207.00 ＯＫ

PL+Pb 14.62 207.00 ＯＫ

PL 11.76 207.00 ＯＫ

PL+Pb 14.65 207.00 ＯＫ

PL 10.75 207.00 ＯＫ

PL+Pb 11.27 207.00 ＯＫ

PL 18.15 207.00 ＯＫ

PL+Pb 86.60 207.00 ＯＫ

PL 109.85 207.00 ＯＫ

PL+Pb 111.58 207.00 ＯＫ

PL 44.71 207.00 ＯＫ

PL+Pb 92.10 207.00 ＯＫ

PL 31.28 207.00 ＯＫ

PL+Pb 63.24 207.00 ＯＫ

PL 34.84 207.00 ＯＫ

PL+Pb 69.64 207.00 ＯＫ

PL 11.78 207.00 ＯＫ

PL+Pb 67.11 207.00 ＯＫ

PL 11.68 207.00 ＯＫ

PL+Pb 76.66 207.00 ＯＫ

Outer ring（１）

（２）

Vertical port (large)

Evaluation part

Pad

Rib (large)

Rib below VV

Cylindrical shell

Base plate

Double ring

Symbol Judge

Vertical port (small)

（１）

（２）

（１）

（２）

Rib for leg

Leg

Stress Allowablestress Judge

49.10 138.00 ＯＫ75.12 138.00 ＯＫ42.53 138.00 ＯＫ12.81 ＯＫ11.31 ＯＫM64 anchor (inner)

M64 anchor (outer) 171.00

Evaluation partM36 block connection between double and outer ringM48 block connection between legs and outer ringM48 block connection between legs and double ring

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