[SKS] IMO TYPE C TANK DATA LIST

IMO TYPE C TANK DATA LIST π × (ø ｍ²ｍ³ ㄷ ＋－ × ÷ ± ≤ ≥ ^C ℃ ▶ ㅊ

나의바이오리듬
hangulTest.php PHP GD LIBRARY 한글테스트

1. SHI CP 11매 2. SHI Comment_C-Type LNG Fuel Tank 생산 개선아이디어

query[0] = [Select HTML FROM IMO_STD Where headType=0 and (sid=0 or (sid=1 and jNo=4)) Order By sid, headType, jNo, rNo]
IMO TYPE C - STANDARD SIZE and Volume Table

Head Type ; Spherical-Head

Material Selection for IMO TYPE C TANK (재질을 선택하세요,) Unit : MPa 1. Hign Mn (A1106-17) Base Metal Rm = 800 MPa, Re ≥ 400 MPa 2. 9% Nickel(A553-TYP1) Base Metal Rm = 690~825 MPa , Re ≥ 585 MPa
MATERIAL	Weld Metal(용접봉강도)			Allowable Membrane Stress(f) (by IGC, IGF)
MATERIAL	Tensile Re (=St)	Yield Rm (=Sy)	Div.1 S	f = Min(Rm/A, Re/B)	f (Mpa)	A	B
A1106(Hign Mn)	660	400	N/A	f = Min(660/3.5, 400/1.5)	188.6	3.5	1.5
A553-TYPE1	640	400	187.0	f = Min(640/3.0, 400/1.5)	213.3	3.0	1.5
LT-FH32(TM)	440~570	315	N/A	f = Min(440/3.0, 315/1.5)	146.67
LT-FH36(TM)	490~630	355	N/A	f = Min(490/3.0, 355/1.5)	163.33
SA240-304	515	205	138	f = Min(515/3.5, 205/1.5)	136.66	3.5	1.5
SA240-304L	485	170	115	f = Min(485/3.5, 170/1.5)	113.33
SA240-316	515	205	138	f = Min(515/3.5, 205/1.5)	136.66
SA240-316L	485	170	115	f = Min(485/3.5, 170/1.5)	113.33
NV 4-4L	490~610	325	N/A	f = Min(490/3.0, 325/1.5)	163.33	3.0	1.5
[Allowable Stress 계산 식 참고하기]

Design Data :

Class Society

Liquid

Material

Head Type

Design Pressure
Po, MARVS(bar.g)

Design External
Pressure MAEP(bar.g)

Corrosion
Allowance
CA (mm)

BOR Limit
(%/day)

Insulation Thk.
tInsu (mm)

Vacuum Ring
Pitch (mm)

Weld Metal
Tensile Stress
Rm (MPa)

Weld Metal
Yield Stress
Re (MPa)

Allowable Stress
f=Min(Rm/A, Re/B)
f = Min(515/3.5, 205/1.5)

REMARK

KR (한국선급)

LNG

SA240-304

[HH] Hemi-Spherical Head

9.51

0.45

1.0

0.35

400

3500

515

205

136.66

No.	Description	Symbol	This Tank TK-001	TNO-2	TNO-3	TNO-4	TNO-5	TNO-6	TNO-7	TNO-8	TNO-9	TNO-10	TNO-11	TNO-12	TNO-13	TNO-14	TNO-15	TNO-16	TNO-17	TNO-18	Unit
1	TANK In-Diameter	Di =	10500	12000	12500	12500	7500	8000	8000	8250	8500	9000	10000	3000	11000	11250	12000	12500	12000	12500	mm
2	Hemi-Spherical Depth	*z = 0.5D**	5250	6000	6250	6250	3750	4000	4000	4125	4250	4500	5000	1500	5500	5625	6000	6250	6000	6250	mm
3	Cylinder Straight Length (TL to TL : 10mm 단위올림)	TL =	17260	18530	20190	22230	18770	19540	24510	27240	29580	22300	16260	4720	24240	27720	25160	22230	27370	24270	mm
4	Total Length ( Head End to End ), L = 2*z +TL	L =	27760	30530	32690	34730	26270	27540	32510	35490	38080	31300	26260	7720	35240	38970	37160	34730	39370	36770	mm
5	Design Liquid Level	DLL =	9333	10661	11109	11118	6687	7132	7141	7368	7593	8024	8888	2665	9799	10030	10686	11118	10693	11125	mm
6
7	Gross Volume, Vnom = Vcyl+Vhead	Vnom =	2100	3000	3500	3750	1050	1250	1500	1750	2000	1800	1800	47.5	3000	3500	3750	3750	4000	4000	m³
8	Net Volume ( Vnet = 0.98*Vnom)	Vnet =	1988.5	2840.7	3314.2	3550.9	994.2	1183.6	1420.4	1657.1	1893.8	1704.4	1704.4	45.0	2840.7	3314.2	3550.9	3550.9	3787.6	3787.6	0.98*Vnom
9	Vhead = πD³ / 6	Vhead =	606.1	904.8	1022.7	1022.7	220.9	268.1	268.1	294.0	321.6	381.7	523.6	14.1	696.9	745.5	904.8	1022.7	904.8	1022.7	m³
10	Vcyl = πD² / 4 * L	Vcyl =	1493.9	2095.2	2477.3	2727.3	829.1	981.9	1231.9	1456.0	1678.4	1418.3	1276.4	33.4	2303.1	2754.5	2845.2	2727.3	3095.2	2977.3	m³
11	Storage Ratio = Vnet / Vnom * 100	Sratio =	94.69	94.69	94.69	94.69	94.69	94.69	94.69	94.69	94.69	94.69	94.69	94.69	94.69	94.69	94.69	94.69	94.69	94.69	%
12	Static Head Pressure, Ps = ρgh(h=DLL)	Ps =	0.0458	0.0523	0.0545	0.0545	0.0328	0.035	0.035	0.0361	0.0372	0.0393	0.0436	0.0131	0.048	0.0492	0.0524	0.0545	0.0524	0.0545	MPa
13	[ASME] Total Design Pressure, P = Po+Ps	P_ASME =	0.9968	1.0033	1.0055	1.0055	0.9838	0.986	0.986	0.9871	0.9882	0.9903	0.9946	0.9641	0.999	1.0002	1.0034	1.0055	1.0034	1.0055	MPa
14	[ASME] Cylinder Shell Thickness	t_Cyl =	39.45	45.23	47.18	47.18	28.11	29.98	29.98	30.92	31.86	33.75	37.54	11.63	41.37	42.34	45.24	47.18	45.24	47.18	mm
15	[ASME] Hemi-Spherical Head Thickness	t_HHead =	20.16	23.04	24.01	24.01	14.51	15.44	15.44	15.91	16.38	17.32	19.21	6.29	21.12	21.6	23.04	24.01	23.04	24.01	mm
16	[ASME] Cylinder Shell Thk (Vacuum Ring Pitch: 3.5m )	t_CylPe =	17.0	18.0	18.5	18.5	14.5	15.0	15.0	15.0	15.5	15.5	16.5	9.0	17.5	17.5	18.0	18.5	18.0	18.5	mm
17	[ASME] Allowable External Pressure(Shell), Pe < Pa_Cyl	Pa_Cyl =	0.0495	0.0479	0.0485	0.0485	0.0518	0.0515	0.0515	0.0489	0.0512	0.0475	0.0489	0.0544	0.0502	0.0487	0.0479	0.0485	0.0479	0.0485	MPa
18	[ASME] Allowable External Pressure(Head ), Pe < Pa_Head	Pa_Head =	0.1599	0.162	0.1627	0.1627	0.1557	0.1564	0.1564	0.1568	0.1571	0.1578	0.1592	0.1494	0.1606	0.161	0.162	0.1627	0.162	0.1627	MPa
19	[Class] Dynamic Pressure(Ship Motion)	Pgd(max) =	0.1258	0.1323	0.1345	0.1345	0.1328	0.135	0.135	0.1361	0.1372	0.1393	0.1236	0.1331	0.128	0.1292	0.1324	0.1345	0.1324	0.1345	MPa
20	[Class] Total Design Pressure, P = Po+Pgd(max)	P_Class =	0.951	0.951	0.951	0.951	0.951	0.951	0.951	0.951	0.951	0.951	0.951	0.951	0.951	0.951	0.951	0.951	0.951	0.951	MPa
21	[Class] Cylinder Shell Thickness	t_Cyl =	37.69	42.93	44.68	44.68	27.21	28.95	28.95	29.83	30.7	32.45	35.94	11.48	39.43	40.31	42.93	44.68	42.93	44.68	mm
22	[Class] Hemi-Spherical Head Thickness	t_HHead =	19.28	21.89	22.76	22.76	14.06	14.93	14.93	15.36	15.8	16.67	18.41	6.22	20.15	20.59	21.89	22.76	21.89	22.76	mm
23	[LR] Cylinder Shell Thk (Vacuum Ring: 3.5m )	t_CylPe =	18.0	19.5	19.5	19.5	15.0	15.5	15.5	15.5	16.0	16.5	17.5	9.0	18.5	18.5	19.5	19.5	19.5	19.5	mm
24	[DNV-GL] Hemi-Spherical Head Thk (For Vacuum ) Pc=2.4Et(t-c/Ro)²/ 3.7 [DNV-GL Pt4-Ch7]	t_HeadPe =	6.93	7.78	8.06	8.06	5.24	5.52	5.52	5.66	5.8	6.09	6.65	2.7	7.22	7.36	7.78	8.06	7.78	8.06	mm
25	[LR] Allowable External Pressure (Shell DNV-GL, LR, GV)	Pcr =	0.0498	0.0503	0.0477	0.0477	0.0519	0.0504	0.0504	0.0478	0.0498	0.0501	0.0503	0.0504	0.0509	0.0486	0.0503	0.0477	0.0503	0.0477	MPa
26	[NK] Allowable External Pressure (ClassNk equal ASME Div2. )	Pa_div2 =	0.5393	0.5773	0.5936	0.5936	0.3989	0.464	0.464	0.4731	0.4691	0.4872	0.5222	0.1622	0.5442	0.5526	0.5773	0.5936	0.5773	0.5936	MPa
27	PUF Insulation Volume	Vinsu =	389.77	487.05	542.04	575.35	267.36	297.83	350.68	393.78	434.31	378.09	352.08	35.12	515.61	581.96	591.12	575.35	625.82	608.67	m³
28	Min. Thickness for Internal Pressure 　tMinPo(DNV-GL) = 3+Di/1500+CA	tMinPo =	11.0	12.0	12.33	12.33	9.0	9.33	9.33	9.5	9.67	10.0	10.67	6.0	11.33	11.5	12.0	12.33	12.0	12.33	mm
29	Min. Thickness for Internal Pressure, (IGC_LR_ASME)	tMinBase =	3.0	3.0	3.0	3.0	3.0	3.0	3.0	3.0	3.0	3.0	3.0	3.0	3.0	3.0	3.0	3.0	3.0	3.0	mm
30	Min. Thickness for External Pressure, tMinPe = Do/850 ASME SECTION II, PART D - SUBPART 3 (METRIC), FIG. G	tMinPe =	13.35	15.12	15.71	15.71	9.82	10.41	10.41	10.71	11.0	11.59	12.76	4.53	13.94	14.24	15.12	15.71	15.12	15.71	mm
31
32	[Calc] Shell Thickness	tCyl =	39.45	45.23	47.18	47.18	28.11	29.98	29.98	30.92	31.86	33.75	37.54	11.63	41.37	42.34	45.24	47.18	45.24	47.18	mm
33	[Calc] Head Thickness	tHead =	20.16	23.04	24.01	24.01	14.51	15.44	15.44	15.91	16.38	17.32	19.21	6.29	21.12	21.60	23.04	24.01	23.04	24.01	mm
34	Nominal Shell Thickness (벤딩마진포함)	tu_Cyl =	40.50	46.00	48.00	48.00	29.00	31.00	31.00	32.00	32.50	34.50	38.50	12.50	42.00	43.00	46.00	48.00	46.00	48.00	mm
35	Nominal Head Thickness (성형마진포함)	tu_Head =	21.00	24.00	25.00	25.00	15.50	16.50	16.50	17.00	17.50	18.50	20.00	7.00	22.00	22.50	24.00	25.00	24.00	25.00	mm
36	Shell Thickness Margin, tMarginCyl = tuCyl - tCyl	tMarginCyl =	1.05	0.77	0.82	0.82	0.89	1.02	1.02	1.08	0.64	0.75	0.96	0.87	0.63	0.66	0.76	0.82	0.76	0.82	mm
37	Head Thickness Margin, tMarginHead = tuHead - tHead	tMarginHead =	0.84	0.96	0.99	0.99	0.99	1.06	1.06	1.09	1.12	1.18	0.79	0.71	0.88	0.9	0.96	0.99	0.96	0.99	mm
38
39
40	Shell Segment 수량	sQty =	6.0	6.0	6.0	7.0	6.0	6.0	8.0	9.0	9.0	7.0	5.0	2.0	8.0	9.0	8.0	7.0	9.0	8.0	sheets
41	Shell Segment Width	sWidth =	2893.33	3105.0	3381.67	3190.0	3145.0	3273.33	3076.25	3037.78	3297.78	3200.0	3272.0	2410.0	3042.5	3091.11	3157.5	3190.0	3052.22	3046.25	mm
42	Shell Cutting Plan Length, @SegmentWidth * sQty=	cpLength =	@2893.33x6 EA = 17360	@3105.0x6 EA = 18630	@3381.67x6 EA = 20290	@3190.0x7 EA = 22330	@3145.0x6 EA = 18870	@3273.33x6 EA = 19640	@3076.25x8 EA = 24610	@3037.78x9 EA = 27340	@3297.78x9 EA = 29680	@3200.0x7 EA = 22400	@3272.0x5 EA = 16360	@2410.0x2 EA = 4820	@3042.5x8 EA = 24340	@3091.11x9 EA = 27820	@3157.5x8 EA = 25260	@3190.0x7 EA = 22330	@3052.22x9 EA = 27470	@3046.25x8 EA = 24370	mm
43	Actual inertia moment of Saddle Ring	Ig_Saddle =	2247612.0	2746960.0	3246307.0	3246307.0	603778.0	635799.0	635799.0	966541.0	981052.0	1027569.0	1689587.0	111562.0	2315248.0	2611410.0	2746960.0	3246307.0	2746960.0	3246307.0	cm⁴
44	Saddle Ring (Qty) Saddle Ring (Size)	SRqty = SIZE =	2 S/Rings T1300x32+430x32	2 S/Rings T1350x32+450x32	2 S/Rings T1400x34+470x34	2 S/Rings T1400x34+470x34	2 S/Rings T900x25+350x25	2 S/Rings T900x25+350x25	2 S/Rings T900x25+350x25	2 S/Rings T1000x30+400x30	2 S/Rings T1000x30+400x30	2 S/Rings T1000x30+400x30	2 S/Rings T1200x30+400x30	2 S/Rings T600x22+300x22	2 S/Rings T1300x32+430x32	2 S/Rings T1350x32+450x32	2 S/Rings T1350x32+450x32	2 S/Rings T1400x34+470x34	2 S/Rings T1350x32+450x32	2 S/Rings T1400x34+470x34	Rings
45	Vacuum Ring (Qty) Vacuum Ring (Size)	VRqty = SIZE =	6 V/Rings T350x15+200x15	7 V/Rings T350x15+200x15	7 V/Rings T400x20+250x15	8 V/Rings T400x20+250x15	7 V/Rings T300x15+100x15	7 V/Rings T300x15+100x15	9 V/Rings T300x15+100x15	9 V/Rings T300x15+100x15	10 V/Rings T300x15+100x15	8 V/Rings T300x15+100x15	6 V/Rings T300x15+100x15	2 V/Rings FB150x20	8 V/Rings T350x15+200x15	10 V/Rings T350x15+200x15	9 V/Rings T350x15+200x15	8 V/Rings T400x20+250x15	9 V/Rings T350x15+200x15	8 V/Rings T400x20+250x15	Rings
46	Vacuum Ring @pitch	VR_pitch =	@3050×5 +2×1005	@2760×6 +2×985	@3030×6 +2×1005	@2890×7 +2×1000	@2800×6 +2×985	@2920×6 +2×1010	@2810×8 +2×1015	@3160×8 +2×980	@3060×9 +2×1020	@2900×7 +2×1000	@2850×5 +2×1005	@2720×1 +2×1000	@3180×7 +2×990	@2860×9 +2×990	@2900×8 +2×980	@2890×7 +2×1000	@3170×8 +2×1005	@3180×7 +2×1005	mm
47	Required inertia moment of Stiff. Ring 　Ix = 0.18 * D * Pe_MPa * L * Ds² / E ×10E-5	Ix =	16661.1	24875.5	28120.2	28120.2	6065.3	7363.2	7363.2	8076.4	8831.1	10485.7	14389.8	386.6	19154.4	20492.0	24875.5	28120.2	24875.5	28120.2	cm⁴
48	Actual inertia moment of Vacuum Ring	Ig =	51158.3	54435.3	91531.7	91531.7	21474.2	22248.9	22248.9	22616.6	22827.9	23515.9	24792.1	1497.3	52130.0	52724.3	54435.3	91531.7	54435.3	91531.7	cm⁴
49	Ix / Ig < 1.0 OK		0.3	0.5	0.3	0.3	0.3	0.3	0.3	0.4	0.4	0.4	0.6	0.3	0.4	0.4	0.5	0.3	0.5	0.3
50	Weight Summary
51	1) Shell Weight	wShell =	192.605	266.019	313.661	343.702	107.284	128.494	158.863	186.675	211.355	180.937	165.698	6.744	288.855	343.884	356.758	343.702	386.757	373.801	ton
52	2) Head Weight	wHead =	57.097	85.231	96.334	96.334	21.501	26.043	26.043	28.535	31.181	36.955	49.323	1.553	65.649	70.228	85.231	96.334	85.231	96.334	ton
53	3) Saddle Rins(Inside)	WsaddleRing =	41.074	51.11	57.65	57.65	18.057	19.973	19.973	25.127	26.014	28.084	35.028	3.934	43.543	46.118	51.11	57.65	51.11	57.65	ton
54	4) Vacuum Rings(Inside)	WvacuumRing =	13.024	17.903	25.176	28.596	7.25	7.894	10.092	11.04	12.495	10.654	9.302	0.69	17.74	22.682	22.52	28.596	22.52	28.596	ton
55	5) Swash Bulk Head and Attachment	WbulkHead =	31.449	39.744	42.643	42.643	17.994	20.333	20.333	21.338	22.241	24.378	28.982	4.918	33.862	35.186	39.744	42.643	39.744	42.643	ton
56	6) Saddle(CS/Bottom)	Wsaddle_CS =	29.574	48.879	57.18	57.18	12.109	13.883	13.883	14.954	16.025	18.561	25.059	1.482	34.751	37.749	48.879	57.18	48.879	57.18	ton
57	7) Accessory(CS/PlatForm)	Waccy_CS =																			ton
58	8) PUF ( Insulation ) Winsu = Vinsu * Density [ 40 kg/m³]	Winsu =	15.591	19.482	21.682	23.014	10.694	11.913	14.027	15.751	17.372	15.124	14.083	1.405	20.624	23.278	23.645	23.014	25.033	24.347	Ton
59	Empty Steel Weight(1~7)	Wempty =	380.414	528.368	614.326	649.119	194.889	228.533	263.214	303.42	336.683	314.693	327.475	20.726	505.024	579.125	627.887	649.119	659.274	680.551	Ton
60	at Operating Condition	Woper =	994.25	1420.35	1657.1	1775.45	497.1	591.8	710.2	828.55	946.9	852.2	852.2	22.5	1420.35	1657.1	1775.45	1775.45	1893.8	1893.8	Ton
61	at Hydrostatic-test Condition	Wtest =	2100.0	3000.0	3500.0	3750.0	1050.0	1250.0	1500.0	1750.0	2000.0	1800.0	1800.0	47.5	3000.0	3500.0	3750.0	3750.0	4000.0	4000.0	Ton
62	Dynamic Pressure due to Ship mortion)	PgdMax =																			bar.g
63	Surface Area Calculation for Net Weight
64	Shell Plate Surface Area (OD 기준)	suf_Shell =																			m2
65	Head Plate Surface Area (OD 기준)	suf_Head =																			m2
66
67
68
69	Surface Area Total	SArea																			m2
Weight Summary			[조 회]	[조 회]	[조 회]	[조 회]	[조 회]	[조 회]	[조 회]	[조 회]	[조 회]	[조 회]	[조 회]	[조 회]	[조 회]	[조 회]	[조 회]	[조 회]	[조 회]	[조 회]	Unit

[Table 1] Shell and Head Thickness Calculation
0　Head Type : [HH] Hemi-Spherical Head
　Vessel Size : 7500(D) × 18770(L) × 26270(TL) mm
　Where, z = R = 0.5×D = 3750 mm,　　C = 2z/D = 1.0
o (내압에 의한 필요두께의 계산)
　Design Code : KR (한국선급)
　Material of Shell and Head : SA537-CL1
　Allowable Stress, f = 136.66 MPa, Rm = 515.0, Re = 205.0, EM = 201,000 MPa
　Weld Joint Effciency, E = 1.0
　Design Internal Pressure, Po = 0.951 MPa
　Dynamic Pressure Subject to ship motion, Pgd(max) = 0.0 MPa
　Total Pressure, P = Po + Pgd(max) = 0.951 MPa
For 10% Dish Head M = 1/4 * [3 + SQRT(L/r)] = 1.54057, L=1.0D=7500, r=0.1*D=750,
　Min. Shell Plate Thickness　　, Rule-1) tMin(Pe) = Do/850 = 9.82 (mm)
　Min. Shell and Head Thickness, Rule-2) tMin(DNV-GL) = 3 + Di/1500 + CA = 9.0 (mm)
　Min. Shell and Head Thickness, Rule-3) tMin(IGC, IGF) = 5 mm
　Min. Ellipsoidal and 10% Dish Head Thickness, Rule-4) tMin(ASME UG-32) ≥ 0.002*R+CA = 8.5 (mm)
　Dertermine Min. Thickness, tMin = Max( Rule1, Rule2, Rule3) = 9.82 (mm)

MATERIAL	Weld Metal(용접봉강도), [MPa]			Allowable Membrane Stress(f) (by IGC, IGF)
MATERIAL	Tensile Re (=St)	Yield Rm (=Sy)	Div.3 S	f = Min(Rm/A, Re/B)	f [MPa]	A	B
SA537-CL1	515	205	N/A	f = Min(515/3.5, 205/1.5)	136.66	3.5	1.5

1. [KR (한국선급)] Strength of Shell and Head Plates Subjected to Internal Pressure

No.

ITEM

KR (한국선급) Formula

Requird Thick
t (mm)

Used Thick
Tu (mm)

Cylindrical Shell

T =

P D₁

2 f J － 1.2 P

＋ c

27.21

0.79

28.00

Hemi-Head

T =

P R₂

2 f J － 0.2 P

＋ c

14.06

0.90

0.04

15.00

Where,
Inside Diameter (Shell, Head)	D =	7500	mm	7.500	m
Inside Radius (Shell, Head )	R =	3750	mm	3.750	m
Min. Tensile Stress (Weld Metal)	Rm =	515	MPa
Min. Yield Stress (Weld Metal)	Re =	205	MPa
Allowbale Membrane Stress, f = Min(660/3.5, 400/1.5) ASME 자재 사용불가! 허용응력(f) 확인필요!!	f =	136.66	MPa	SA537-CL1
Design Pressure, P = Po + Pgd(max)	P =	0.951	MPa	9.51	bar.g
Corrosion Allowance	CA =	1.0	mm
Thickness margin of Bending or Forming	c1 =	Avobe Table
Thickness margin : c2 = Tu - (t + c1)	c2 =	Avobe Table

2. [KR (한국선급)] Strength of Shell and Head Plates Subjected to Hydrostatic-test condition at shop

No.

ITEM

KR (한국선급) Formula

Requird Thick
t (mm)

Used Thick
Tu (mm)

Cylindrical Shell

T =

P D₁

2 f J － 1.2 P

＋ c

29.13

0.79

28.00

Hemi-Head

T =

P R₂

2 f J － 0.2 P

＋ c

14.51

0.90

0.04

15.00

　Thickness margin of Bending or Forming

c1 =

Avobe Table

　Thickness margin : c2 = Tu - (t + c1)

c2 =

Avobe Table

Where,
Inside Diameter (Shell, Head)	D =	7500	mm	7.500	m
Inside Radius (Shell, Head )	R =	3750	mm	3.750	m
Min. Tensile Stress (Weld Metal)	Rm =	515	MPa
Min. Yield Stress (Weld Metal)	Re =	205	MPa
Allowbale Stress at Hydrostatic-Test, f = 0.9 * Rm	f =	184.5	MPa
Hydrostatic-test Pressure, P = Poper * 1.5	P =	1.4265	MPa	14.265	bar.g
Corrosion Allowance	CA =	0.00	mm

Shape factor For (2:1) Ellipsoidal Head(H/Do=0.25) and (10%)Dish head(H/Do=0.2)

1) DNV-Rules

2) LR-Rules

3) BV-Rules

5 편 기관장치 / 5 장 보일러 및 압력용기
309. 동판 및 경판
1. 동판 및 경판의 두께는 표 5.5.15의 식에 의한 소요두께 이상이어야 하며, 지름, 압력, 온도, 재료 등을 고려하여 우리 선급이 특별히 승인한 경우를 제외하고 5 mm 이상이어야 한다. 다만, 모든 반구형 경판을 제외한 곡면경판의두께는 그 경판이 부착된 동판이 이음매 없는 경우일 때의 그 동판의 소요두께 이상이어야 한다.

2. 보강을 필요로 하는 구멍이 있는 경우의 경판의 소요두께는 다음 각호에 따른다.
(1) 구멍의 보강을 115.의 2항에 의한 경우에는 표 5.5.15에 따른다.
(2) 맨홀 또는 최대치수가 150 mm 를 넘는 구멍으로서 그 주위를 115.의 6항에 규정하는 플랜지형으로 보강하였을경우에는 다음에 따른다.

(가) 접시형 또는 반구형 경판 : 표 5.5.15에 따라서 산정된 값에 그의 15% (3 mm 미만의 경우에는 3 mm) 이상의 값을 더한 두께 이상으로 하여야 한다. 이 경우에 경판의 중앙부에 있어서의 안쪽반지름이 동체의 안지름의80% 미만인 경우에는 경판의 중앙부에 있어서의 안쪽반지름을 동체의 안지름의 80% 로 하여 계산하여야 한다. 또한, 두 개의 맨홀이 있는 경판의 두께를 이와같이 정하였을 경우에는 두 개의 맨홀사이의 거리가 경판 바깥지름의 1/4 이상이어야 한다.
(나) 반타원형 경판 : 표 5.5.15에 따라서 계산하되 이 경우의 R 은 동체의 안지름의 80% 로 하고, E는 1.77 로 한다.

(비고)
(1) 접시형 경판의 중앙부에 있어서의 안쪽반지름은 경판의 플랜지 부분의 바깥지름보다 커서는 아니 된다. 또한, 경판의 모서리에 있어서의 안쪽반지름은 경판의 플랜지 부분의 바깥지름의 6 % 또는 경판 두께의 3 배 중 큰 것 이상이어야 한다.
(2) 반타원형 경판의 안쪽에서의 짧은 반지름은 긴 반지름의 1/2 이상이어야 한다.
(3) 부식 예비두께는 소요두께의 1/6 또는 1 mm 중 작은 것으로 한다. 다만 부식성 액체 또는 가스를 저장하는 압력용기는 부식 예비두께를 증가시킬 수 있으며 부식성이 없는 액체 또는 가스를 저장하는 압력용기 또는 내식성 재료를 사용하는 압력용기는 부식 예비두께를 감소시킬 수 있다. (2021)

3. 볼록면에 압력을 받는 경판의 소요두께는 오목면에 압력을 받는 경우의 경판 소요두께 산정식에서 설계압력의 P 대신에 p 의 1.67 배의 값을 적용하여 산정한 두께 이상이어야 한다.

3. IMO TYPE C Tank / Class Formula 비교표

1. Cylindrical Shell Plate

at Operation
t (mm)

at Test
(mm)

c1 (mm)

c2 (mm)

Tu (mm)

SKETCH
ASME SEC.VIII Div.1

KR (한국선급)

T =

P D₁

2 f J － 1.2 P

＋ c

27.205

29.13

0.79

28.00

LR (영국선급)

T =

P · R_j

10 · σ · J － 0.5 · P

＋ 0.75

27.187

28.88

0.81

28.00

DNV-GL(노르웨이)

S ≥

Pc ·D₀

20 · σt · v ＋ Pc

＋ c,　(PT4Ch7 3.2.1)

27.005

29.11

0.49

27.50

Class-Nk(일본선급)

Tr =

P R

f J － 0.5 P

＋ α

27.187

29.11

0.81

28.00

BV (프랑스)

T =

p · D

(2·K － p)·e

＋ 0.75

27.187

29.11

0.81

28.00

ABS (미국선급)

T =

W · R

f·S·E － (1－y) · W

＋ C

27.187

29.11

0.81

28.00

ASME SEC.VIII-Div.1(압력용기)

t =

P · R

S·E － 0.6·P

＋ CA

27.205

29.13

0.79

28.00

ASME SEC.VIII-Div.2(압력용기)

t =

· [exp(P / SE) － 1] ＋ CA

27.187

29.11

0.81

28.00

2. [HH] Hemi-Spherical Head

at Operation
t (mm)

at Test
(mm)

c1 (mm)

c2 (mm)

Tu (mm)

SKETCH
ASME SEC.VIII Div.1

KR (한국선급)

T =

P R₂

2 f J － 0.2 P

＋ c

14.057

14.51

0.9

0.04

15.00

LR (영국선급)

T =

P · R_j

20 · σ · J － 0.5 · P

＋ 0.75

14.071

14.47

0.9

0.03

15.00

DNV-GL(노르웨이)

S ≥

Pc ·D₀

40 · σt · v ＋ Pc

＋ c,　(PT4Ch7 3.3.1)

14.025

14.53

0.9

0.07

15.00

Class-Nk(일본선급)

Tr =

P R

2 f J － 0.5 P

＋ α

14.071

14.53

0.9

0.03

15.00

BV (프랑스)

T =

p · R

(2·K － p)·e

＋ 0.75

14.093

14.55

0.9

0.01

15.00

ABS (미국선급)

T =

W · R

2·f·S·E － (1－y) · W

＋ C

14.071

14.53

0.9

0.03

15.00

ASME SEC.VIII-Div.1(압력용기)

t =

P · R

2·S·E － 0.2·P

＋ CA

14.057

14.51

0.9

0.04

15.00

ASME SEC.VIII-Div.2(압력용기)

t =

· [exp(0.5P/SE) － 1] ＋ CA

14.071

14.53

0.9

0.03

15.00

3. [EE] 2:1 Ellipsoidal Head

at Operation
t (mm)

at Test
(mm)

c1 (mm)

c2 (mm)

Tu (mm)

SKETCH
ASME SEC.VIII Div.1

KR (한국선급)

T = [

P D₂

2 f J － 0.2 P

＋ c ] × 1.15

31.181

33.37

0.82

32.00

UG-32 FORMED HEADS, AND SECTIONS, PRESSURE ON CONCAVE SIDE
(c) Ellipsoidal Heads With ts/L ≥ 0.002
(d) Torispherical Heads With t s /L ≥ 0.002.
위 수식을 사용하기 위한 필수 조건임

( 2:1 Ellipsoidal head and Dish Head 필수조건 임 )
ts / L ≥ 0.002
tsMin = 0.002 * L + CA = 16 mm

LR (영국선급)

T =

P · D₀ ·K

20 · σ · J

＋ 0.75,　K=1.4

37.534

39.87

0.9

0.07

38.50

DNV-GL(노르웨이)

S ≥

Pc ·D₀ · β

20 · σt · v

＋ c,　β=1.375

36.882

39.87

0.62

37.50

Class-Nk(일본선급)

Tr =

P R

f J － 0.25 P

＋ α

27.141

29.05

0.86

28.00

BV (프랑스)

T =

p · D ·C

2 ·K · e

＋ 0.75,　C=1.65

44.058

47.84

0.9

0.04

45.00

ABS (미국선급)

T =

W · R ·K

2·f·S·E － 0.2·W

＋ C,　K=1

27.114

29.02

0.89

28.00

ASME SEC.VIII-Div.1(압력용기)

t =

P · D ·K

2·S·E － 0.2·P

＋ CA,　K=1.0

27.114

29.02

0.89

28.00

ASME SEC.VIII-Div.2(압력용기)

t =

P · D ·K

2·S·E － 0.2·P

＋ CA,　K=1.0

27.114

29.02

0.89

28.00

4. [DD] 10% Dish Head

at Operation
t (mm)

at Test
(mm)

c1 (mm)

c2 (mm)

Tu (mm)

SKETCH
ASME SEC.VIII Div.1

KR (한국선급)

T = [

P R₂E

2 f J － 0.2 P

＋ c ] × 1.15,　E=1.5406

54.305

59.06

0.7

55.00

LR (영국선급)

T =

P · D₀ ·K

20 · σ · J

＋ 0.75,　K=2.35

62.325

66.69

0.67

63.00

DNV-GL(노르웨이)

S ≥

Pc ·D₀ · β

20 · σt · v

＋ c,　β=2.30

61.020

66.69

0.9

0.08

62.00

Class-Nk(일본선급)

Tr =

P R₁ W

2 f J － 0.5 P

＋ α

41.273

44.75

0.73

42.00

BV (프랑스)

T =

p · D ·C

2 ·K · e

＋ 0.75,　C=2.30

61.020

66.69

0.9

0.08

62.00

ABS (미국선급)

T =

W · R ·M

2·f·S·E － 0.2·W

＋ C,　M=1.5406

41.231

44.70

0.77

42.00

ASME SEC.VIII-Div.1(압력용기)

t =

P · L ·M

2·S·E － 0.2·P

＋ CA,　L=1.0·D, M=1.5406

41.231

44.70

0.77

42.00

ASME SEC.VIII-Div.2(압력용기)

t =

P · L ·M

2·S·E － 0.2·P

＋ CA,　L=1.0·D, M=1.5406

41.231

44.70

0.77

42.00

Where,
Inside Diameter (Shell, Head)	D =	7500	mm	7.500	m
Inside Radius (Shell, Head )	R =	3750	mm	3.750	m
Min. Tensile Stress (Weld Metal)	Rm =	515	MPa
Min. Yield Stress (Weld Metal)	Re =	205	MPa
Allowbale Membrane Stress, f = Min(660/3.5, 400/1.5)	f =	136.66	MPa
at Ship Operation Condition
Design Pressure, P = Po + Pgd(max)	P =	0.951	MPa	9.51	bar.g
Allowbale Membrane Stress, f = Min(660/3.5, 400/1.5)	f =	136.66	MPa
Corrosion Allowance	CA =	1.0	mm
at Hydrostatic-Test Condition
Hydrostatic-test Pressure, P = Poper * 1.5	P =	1.4265	MPa	14.265	bar.g
Allowbale Stress, f = 0.9 * Rm	f =	184.5	MPa
Corrosion Allowance	CA =	0.00	mm

[TNO-5] Tank Size : ø7500 x 18770 (L = 26270 mm ) Weight Summary

5. Tank Capacity : 1050 ｍ³ 　Head Type ; [HH] Spherical-Head		Tank Size : ø7500 x 18770 (L = 26270 mm )						Plate 발주폭(Max) : 3400 mm Head Plate Surface Area(표면적) : 176.715 m²		Head Type ; [HH] Spherical-Head
No.	Name	MATERIAL	SIZE t x W X L (mm)			Quantity (SHT)	Weight (kg)	표면적 ｍ²/ pcs	Remark	SKETCH
1	Shell Plate (Center Part 일반부)	SA240-304	29.00	3,145	11,830	8	67,758	37.20535	길이분할: @3145.0×6 shts = 18870 > 18770 mm
2	Shell Plate (Saddle Support Part)	SA240-304	31.00	3,145	11,830	4	36,216	37.20535	원주분할: L=π×ø7531 = 23659mm / 2분할= 11830mm
3	Shell Plate (Dome Reinforcement)	SA240-304	31.00	3,400	4,000	1	3,310	13.60000	Dome Part
4	[HH] Hemi-Head Plate (Side)	SA240-304	15.50	2,361	3,176	20	15,725	129.24087	Angle = (#4WP: 47º, CP : 48.431º) [deg]
5	[HH] Hemi-Head Plate (Center)	SA240-304	15.50	2,820	5,640	4	5,776	47.47372	Angle = (#4WP: 47º + 43º : #5WP,CP) = 90º [deg]
6	Wear Plate and 지지금구(Fix / Sliding)	SA240-304	31.00	1,200	11,927	2	6,966	14.31240	For Saddle Support
7	SWASH Bulk Head ( Baffle Plate - Hole 중량 포함 )	SA240-304	10.00	4,776	7,200	2	5,399	34.38720	Baffle Plate Net Surface Area = 29.50906 ｍ²(Hole 면적포함)
8	Bulk Head (Baffle Stiffener Plate)	SA240-304	15.00	1,200	11,852	2	3,349	14.22240	10
9	Bulk Head (U-BAND Spring : 충격완화금구)	SA240-304	25.00	400	660	44	2,280	0.26400
10	Vacuum Ring (Web) T300x15+100x15	SA240-304	15.00	285	0	6	4,564	6.46000	A = π× (OD 7500²- ID : 6930²) / 4 = 6.46 m²
11	Vacuum Ring (Flange) T300x15+100x15	SA240-304	15.00	100	22,667	6	1,601	2.26670	L = π × (ø7215 ) = 22667 mm
12	Vacuum Ring (Rib Plate)	SA240-304	25.00	162	850	40	1,084	0.13813
13	Saddle Ring (Web) T900x25+350x25	SA240-304	25.00	875	0	2	7,148	18.21100	A = π× (OD 7500²- ID : 5750²) / 4 = 18.211 m²
14	Saddle Ring (Flange) T900x25+350x25	SA240-304	25.00	350	20,813	2	2,859	7.28455	L = π × (ø6625 ) = 20813 mm
15	Saddle Ring (Rib Plate)	SA240-304	25.00	162	850	40	1,084	0.13813
16	Saddle Support (Base Plate)	DH32 OR A516-60	41.00	920	9,300	2	5,507	8.55600	Base Plate : t41 mm
17	Saddle Support (Rib & Etc)	DH32 OR A516-60	35.00	3,048	7,883	1	6,602	24.02738	Rib Plate Thick. J=35.0 (mm) , tg=32.0 (mm)
[ONLY] Shell and head Plate Quentity						37 sht
Total Weight							177,229	kg

Vacuuring Ring (Stiffener) Size : T300x15+100x15　
Tank OD (Da) = 7558 mm, Shell Plate: t29 x W:513mm W=1.1*SQRT(D*t)
( IxReqd = 6065.3 < 21474.2 = IxActual ) OK

No.	b	d	A=b*d	y	A*y	h = y-C1	Ah²	Ig=b*d³/12	SKETCH
No.	cm	cm	cm²	cm	cm³	(cm)	cm⁴	cm⁴
3	10.0	1.5	15.0	32.15	482.25	25.22	9540.73	2.81
2	1.5	28.5	42.75	17.15	733.16	10.22	4465.17	2893.64
Shell	51.3	2.9	148.77	1.45	215.72	-5.48	4467.62	104.26
	SUM	∑ =	206.52		1431.13		18473.52	3000.72

C1	= ∑(AY) / ∑(A) (무게중심 위치)	C1 =	6.93	cm	무게중심에서 FLANGE 하단 까지 떨어진 거리
C2	= H - C1	C2 =	25.97	cm	무게중심에서 FLANGE 상단 까지 떨어진 거리
∑(A)	= Sum of Section Area (단면적)	∑(A)=	206.52	cm²	단면적 (빗금전체)
Ix	= ∑(Ah²) + ∑(Ig)	Ix =	21474.23	cm⁴	X축 단면2차모멘트 (Moment of inertia)
Zx	= Ix / Max(C1, C2)	Zx =	826.89	cm³	X축 단면계수 (Section Modulus)
Zmax	= Ix / Min(C1, C2)	Zmax =	3098.74	cm³	X축 (최대) 단면계수
Rx	= SQRT( Ix / A )	Rx =	10.2	cm	X축 회전반경
Ry	= SQRT( Iy / A )	Ry =	12.59	cm	Y축 회전반경
Section Area(Shell 포함)		Sarea =	206.52	cm²	Section Area(Shell 포함)
Ring 단면적 (Shell 제외)		ARing =	57.75	cm²	Ring 단면적 (Shell 제외)
Ring 원주길이		Leng =	6.26	m	Ring 길이(m) = 3.141592×(Di-C1)
Ring 단위중량 (kg/m),		WTm =	45.33	kg/m	단위중량(kg/m)
Ring Weight, Shell(1) 제외 중량		WT =	283.9	kg	Ring 1 PCS 중량(kg)

Saddle Ring Size : T900x25+350x25　
Tank OD (Da) = 7558 mm, Shell Plate: t29 x W:513mm W=1.1*SQRT(D*t)
( IxReqd = 6065.3 < 603778.2 = IxSadAct ) OK

No.	b	d	A=b*d	y	A*y	h = y-C1	Ah²	Ig=b*d³/12	SKETCH
No.	cm	cm	cm²	cm	cm³	(cm)	cm⁴	cm⁴
3	35.0	2.5	87.5	91.65	8019.38	51.13	228704.49	45.57
2	2.5	87.5	218.75	46.65	10204.69	6.13	8206.54	139567.06
Shell	51.3	2.9	148.77	1.45	215.72	-39.07	227150.31	104.26
	SUM	∑ =	455.02		18439.78		464061.35	139716.89

C1	= ∑(AY) / ∑(A) (무게중심 위치)	C1 =	40.525	cm	무게중심에서 FLANGE 하단 까지 떨어진 거리
C2	= H - C1	C2 =	52.375	cm	무게중심에서 FLANGE 상단 까지 떨어진 거리
∑(A)	= Sum of Section Area (단면적)	∑(A)=	455.02	cm²	단면적 (빗금전체)
Ix	= ∑(Ah²) + ∑(Ig)	Ix =	603,778	cm⁴	X축 단면2차모멘트 (Moment of inertia)
Zx	= Ix / Max(C1, C2)	Zx =	11527.99	cm³	X축 단면계수 (Section Modulus)
Zmax	= Ix / Min(C1, C2)	Zmax =	14898.91	cm³	X축 (최대) 단면계수
Rx	= SQRT( Ix / A )	Rx =	36.43	cm	X축 회전반경
Ry	= SQRT( Iy / A )	Ry =	9.57	cm	Y축 회전반경
Section Area(Shell 포함)		Sarea =	455.02	cm²	Section Area(Shell 포함)
Ring 단면적 (Shell 제외)		ARing =	306.25	cm²	Ring 단면적 (Shell 제외)
Ring 원주길이		Leng =	6.16	m	Ring 길이(m) = 3.141592×(Di-C1)
Ring 단위중량 (kg/m),		WTm =	240.41	kg/m	단위중량(kg/m)
Ring Weight, Shell(1) 제외 중량		WT =	1479.9	kg	Ring 1 PCS 중량(kg)

query[0] = [Select sid, headType, jNo, rNo, DESCR, SYMBOL, VALUE, UNIT FROM IMO_STD Where sid=2 and headType=0 and jNo=4 Order By sid, jNo, rNo]
getResult[2] = [

번호	0 sid	1 headType	2 jNo	3 rNo	4 DESCR	5 SYMBOL	6 VALUE	7 UNIT
1	2	0	4	1	TANK In-Diameter	Di =	7500.0	mm
2	2	0	4	2	Hemi-Spherical Depth	z = 0.5*D	3750.0	mm
3	2	0	4	3	Cylinder Straight Length (TL to TL : 10mm 단위올림)	TL =	18770.0	mm
4	2	0	4	4	Total Length ( Head End to End ), L = 2*z +TL	L =	26270.0	mm
5	2	0	4	5	Design Liquid Level	DLL =	6687.0	mm
6	2	0	4	6			0.0
7	2	0	4	7	Gross Volume, Vnom = Vcyl+Vhead	Vnom =	1050.0	m³
8	2	0	4	8	Net Volume ( Vnet = 0.98*Vnom)	Vnet =	994.2	0.98*Vnom
9	2	0	4	9	Vhead = πD³ / 6	Vhead =	220.9	m³
10	2	0	4	10	Vcyl = πD² / 4 * L	Vcyl =	829.1	m³
11	2	0	4	11	Storage Ratio = Vnet / Vnom * 100	Sratio =	94.69	%
12	2	0	4	12	Static Head Pressure, Ps = ρgh(h=DLL)	Ps =	0.0328	MPa
13	2	0	4	13	[ASME] Total Design Pressure, P = Po+Ps	P_ASME =	0.9838	MPa
14	2	0	4	14	[ASME] Cylinder Shell Thickness	t_Cyl =	28.11	mm
15	2	0	4	15	[ASME] Hemi-Spherical Head Thickness	t_HHead =	14.51	mm
16	2	0	4	16	[ASME] Cylinder Shell Thk (Vacuum Ring Pitch: 3.5m )	t_CylPe =	14.5	mm
17	2	0	4	17	[ASME] Allowable External Pressure(Shell), Pe < Pa_Cyl	Pa_Cyl =	0.0518	MPa
18	2	0	4	18	[ASME] Allowable External Pressure(Head ), Pe < Pa_Head	Pa_Head =	0.1557	MPa
19	2	0	4	19	[Class] Dynamic Pressure(Ship Motion)	Pgd(max) =	0.1328	MPa
20	2	0	4	20	[Class] Total Design Pressure, P = Po+Pgd(max)	P_Class =	0.951	MPa
21	2	0	4	21	[Class] Cylinder Shell Thickness	t_Cyl =	27.21	mm
22	2	0	4	22	[Class] Hemi-Spherical Head Thickness	t_HHead =	14.06	mm
23	2	0	4	23	[LR] Cylinder Shell Thk (Vacuum Ring: 3.5m )	t_CylPe =	15.0	mm
24	2	0	4	24	[DNV-GL] Hemi-Spherical Head Thk (For Vacuum ) Pc=2.4Et(t-c/Ro)²/ 3.7 [DNV-GL Pt4-Ch7]	t_HeadPe =	5.24	mm
25	2	0	4	25	[LR] Allowable External Pressure (Shell DNV-GL, LR, GV)	Pcr =	0.0519	MPa
26	2	0	4	26	[NK] Allowable External Pressure (ClassNk equal ASME Div2. )	Pa_div2 =	0.3989	MPa
27	2	0	4	27	PUF Insulation Volume	Vinsu =	267.36	m³
28	2	0	4	28	Min. Thickness for Internal Pressure 　tMinPo(DNV-GL) = 3+Di/1500+CA	tMinPo =	9.0	mm
29	2	0	4	29	Min. Thickness for Internal Pressure, (IGC_LR_ASME)	tMinBase =	3.0	mm
30	2	0	4	30	Min. Thickness for External Pressure, tMinPe = Do/850 ASME SECTION II, PART D - SUBPART 3 (METRIC), FIG. G	tMinPe =	9.82	mm
31	2	0	4	31			0.0
32	2	0	4	32	[Calc] Shell Thickness	tCyl =	28.11	mm
33	2	0	4	33	[Calc] Head Thickness	tHead =	14.51	mm
34	2	0	4	34	Nominal Shell Thickness (벤딩마진포함)	tu_Cyl =	29.0	mm
35	2	0	4	35	Nominal Head Thickness (성형마진포함)	tu_Head =	15.5	mm
36	2	0	4	36	Shell Thickness Margin, tMarginCyl = tuCyl - tCyl	tMarginCyl =	0.89	mm
37	2	0	4	37	Head Thickness Margin, tMarginHead = tuHead - tHead	tMarginHead =	0.99	mm
38	2	0	4	38			0.0
39	2	0	4	39			0.0
40	2	0	4	40	Shell Segment 수량	sQty =	6.0	sheets
41	2	0	4	41	Shell Segment Width	sWidth =	3145.0	mm
42	2	0	4	42	Shell Cutting Plan Length, @SegmentWidth * sQty=	cpLength =	0.0	mm
43	2	0	4	43	Actual inertia moment of Saddle Ring	Ig_Saddle =	603778.0	cm⁴
44	2	0	4	44	Saddle Ring (Qty) Saddle Ring (Size)	SRqty = SIZE =	0.0	Rings
45	2	0	4	45	Vacuum Ring (Qty) Vacuum Ring (Size)	VRqty = SIZE =	6.0	Rings
46	2	0	4	46	Vacuum Ring @pitch	VR_pitch =	2800.0	mm
47	2	0	4	47	Required inertia moment of Stiff. Ring 　Ix = 0.18 * D * Pe_MPa * L * Ds² / E ×10E-5	Ix =	6065.3	cm⁴
48	2	0	4	48	Actual inertia moment of Vacuum Ring	Ig =	21474.2	cm⁴
49	2	0	4	49	Ix / Ig < 1.0 OK		0.3
50	2	0	4	50	Weight Summary		0.0
51	2	0	4	51	1) Shell Weight	wShell =	107.284	ton
52	2	0	4	52	2) Head Weight	wHead =	21.501	ton
53	2	0	4	53	3) Saddle Rins(Inside)	WsaddleRing =	18.057	ton
54	2	0	4	54	4) Vacuum Rings(Inside)	WvacuumRing =	7.25	ton
55	2	0	4	55	5) Swash Bulk Head and Attachment	WbulkHead =	17.994	ton
56	2	0	4	56	6) Saddle(CS/Bottom)	Wsaddle_CS =	12.109	ton
57	2	0	4	57	7) Accessory(CS/PlatForm)	Waccy_CS =	0.0	ton
58	2	0	4	58	8) PUF ( Insulation ) Winsu = Vinsu * Density [ 40 kg/m³]	Winsu =	10.694	Ton
59	2	0	4	59	Empty Steel Weight(1~7)	Wempty =	194.889	Ton
60	2	0	4	60	at Operating Condition	Woper =	497.1	Ton
61	2	0	4	61	at Hydrostatic-test Condition	Wtest =	1050.0	Ton
62	2	0	4	62	Dynamic Pressure due to Ship mortion)	PgdMax =	0.0	bar.g
63	2	0	4	63	Surface Area Calculation for Net Weight		0.0
64	2	0	4	64	Shell Plate Surface Area (OD 기준)	suf_Shell =	0.0	m2
65	2	0	4	65	Head Plate Surface Area (OD 기준)	suf_Head =	0.0	m2
66	2	0	4	66			0.0
67	2	0	4	67			0.0
68	2	0	4	68			0.0
69	2	0	4	69	Surface Area Total	SArea	0.0	m2

]

매크로포함_SHI_SN2430_D12m_견적강도계산 (견적원가).xlsm - [PV4th SADDLES] Sheet 참고

Pressure Vessel Design Manulal (4th edition) / Table 4-27 Large diameter saddle supports

Vessel DIA.		BASE PLATE LENGTH	SADDLE HEIGHT	Bolt Hole Dia.	INNER RIB PITCH	BASE PLATE Width	BOLT PITCH	Saddle BTM Width	Saddle Top Width	Wear Plate Width	Rib Plate 두께	RIB 수량	BOLT 수량	Base Plate 두께	Gusset Plate 두께	Wear Plate 두께	Approx wt for 2 Saddles (kg)	Saddle RIB Height(Center)
DIA(ft)	DIA(mm)	A	B	D	E	F	G	GB=F-50.8	GT	H	J	N	n	tb	tg	tw	wt	h=B-D/2
14	4267	3937	2337	35	483	457	229	406	711	864	19	8	8	25	19	19	3175	203.2
15	4572	4343	2540	35	533	457	229	406	711	864	19	8	8	25	19	19	3629	254
16	4877	4648	2743	35	457	457	235	406	711	864	25	10	8	29	22	22	4536	304.8
17	5182	4902	2896	41	483	533	273	483	787	940	25	10	8	32	25	25	4990	304.8
18	5486	5258	3099	41	432	533	279	483	787	940	29	12	12	35	29	25	5443	355.6
20	6096	5258	3353	41	432	533	279	483	787	940	29	12	12	35	29	29	7031	304.8
22	6706	5563	3658	48	457	610	318	559	864	1016	32	12	12	38	32	32	8618	304.8
24	7315	6121	3962	48	432	610	318	559	864	1016	32	14	12	38	32	32	9979	304.8
26	7925	6477	4369	48	457	610	318	559	864	1016	35	14	12	41	32	32	11793	406.4
28	8534	6985	4674	54	432	686	356	635	940	1092	35	16	16	41	35	32	14061	406.4
30	9144	7823	4978	54	483	686	362	635	940	1092	38	16	16	44	38	35	16783	406.4
32	9754	8331	5283	54	457	686	362	635	940	1092	38	18	16	44	38	35	19958	406.4
34	10363	8788	5588	60	483	787	406	737	1041	1194	44	18	16	51	44	35	24494	406.4
36	10973	9246	5842	60	457	787	406	737	1041	1194	44	20	16	51	44	35	29937	355.6
38	11582	9754	6198	60	483	813	413	762	1067	1219	51	20	16	57	51	38	36287	406.4
40	12192	10262	6502	67	508	864	451	813	1118	1270	51	20	20	64	51	38	45359	406.4

Notes: [SADDLE STANDARD DWG(pdf)]
　1. All dimensions are in inches unless noted otherwise
　2. All saddles in this size range must be fully designed. The dimensions shown are a starting place or to be used for estimating only!
　3. Assume that anchor bolts diameter is d - 0.125, where d is the diameter of the hole. Assume that slots for sliding saddle are 6 d long.
　4. N = Number of ribs
　5. n = Number of anchor bolts

매크로포함_SHI_SN2430_D12m_견적강도계산 (견적원가).xlsm - [PV4th SADDLES] Sheet 참고

시작시간 = [2025-07-10 07:46:38.0076]
종료시간 = [2025-07-10 07:46:38.0093]

HTML END!!!