doc. no. 15 - 42 09 050 - fo
TRANSCRIPT
ATTACHMENT NO. 01 02 03 04
NUMBER OF PAGES 15 5 14 2
DOCUMENT NO. DOC. NO. 15 - 42 09 050 - FO
02 10/5/12 Categorizing Eq.I Gusti N. Dirgantara Ir. Dwi Priyanta, MSE. Ir. Hari Prastowo, MSc.
01 04/4/12 Document Format
REV. DATE DESCRIPTION PREPARED BY CHECKED BY APPROVED BY
DESIGN-IV: MACHINERY BASIC DESIGN
DESIGN-IV: MACHINERY BASIC DESIGN TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
DESIGN-IV: MACHINERY BASIC DESIGN
04 -
2 -
DOC. NO. 15 - 42 09 050 - FO
Ir. Hari Prastowo, MSc.
APPROVED BY
DESIGN-IV: MACHINERY BASIC DESIGN
DESIGN-IV: MACHINERY BASIC DESIGN TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
DESIGN-IV: MACHINERY BASIC DESIGN
Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Table of Contents
TABLE OF CONTENTS
PHILOSOPHY
1. INTRODUCTION . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
1.1 Description . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
1.2 Purpose . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
2. REFERENCES . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
3. ABBREVIATIONS . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
4. DESIGN PARAMETER . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
4.1 Principal Dimension . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
4.2 Coefficient and Constants. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
4.3 Project Guide's Data . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
5. DESIGN REQUREMENTS . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
5.1 Heavy Fuel Oil (HFO) . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
5.2 Marine Diesel Oil (MDO). . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
5.3 Separator . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
5.4 Heater Power for Feed Pump. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
5.5 Heater Power for Circulating Pump. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
5.6. Valve and Fitting . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
5.5 Class Requirement . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
6. SUMMARY . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
LIST OF TABLE
Table 1.7.1 Minimum wall thickness
ATTACHMENT NO. 01 - CALCULATION
1. HEAVY FUEL OIL (HFO). . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
1.1 HFO's weight . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
1.2 Storage Tank Volume. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
1.3 Storage Tank Heating. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
1.4 Settling Tank Volume. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
1.5 Settling Tank Heating. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
1.6 Service Tank Volume. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
1.7 HFO Transfer Pump . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
1.8 HFO Feed Pump . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
1.9 HFO Supply Pump. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
1.1 HFO Circulating Pump. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
2. MARINE DIESEL OIL (MDO). . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
2.1 MDO's weight . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
2.2 Storage Tank Volume. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
2.3 Service Tank Volume. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
2.4 MDO Feed Pump . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
3. SEPARATOR . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
4. HEATER POWER FOR FEED PUMP. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
5. HEATER POWER FOR CIRCULATING PUMP. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
LIST OF TABLE
Table 1.7.1 Minimum wall thickness
ATTACHMENT NO. 02 - IRON PUMP SPECIFICATION
ATTACHMENT NO. 03 - ALLWEILLER PUMP SPECIFICATION
ATTACHMENT NO. 04 - ELECTRIC HEATER AALBORG SPECIFICATION
: DESIGN IV
: 15 - 42 09 050 - FO
: 02
: Table of Contents
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Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Philosophy
1. INTRODUCTION
1.1 Description
1.2 Objective
2. REFERENCES
a. Germanischer Lloyd Rules and Guidelines 2011
b. Marine Engineering, Roy L. Harrington, "Chapter XX - Piping System" :1971
c. Engine Selection Guide - Two Stroke MC/MC-C Engines, 6th Edition: January 2002, MAN B&W
3. ABBREVIATIONS
P = Maximum power of main engine [kW]
SFOC = Specific fuel oil consumption [gr/kWh]
c = constant addition of fuel (1.3)
= Weight of HFO
= Volume of HFO
= Storage Tank Heating
= Settling Tank Volume
= Service Tank Volume
Q = Capacity
A = Area of Pipe that will be convert to diameter formula
v = flow velocity
vs = Velocity of fluid
d = Inside diameter
t = Wall thickness and time
Q = Qapacity
Rn = Reynold number
n = viscocity
hs = head static
hp = head pressure
hv = head velocity
hf = head friction
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
The fuel oil system on the ship was designed with either using 2 types of fuel, heavy fuel oil (HFO) and Diesel Oil (DO). On the system pumped with HFO, HFO (HFO transfer pump) driven pumps with electric motor toward settling tank. HFO from settling tank delivered to HFO service tank with HFO feed pump through the paralel centrifuge to separate between fuel, sludge occuring and also water. In feed pump, there are some equipments such as filter and heater. The heater function is to heating the fuel oil before entering the centrifuge. For the diesel oil system, the diesel oil storage was located in diesel oil storage tank and will be pumped by diesel oil feed pump through a centrifuge who separate the diesel oil with the sludge and also water to the diesel oil service tank. From service tank, the fuel were delivered with supply pump to circulating pump. And then the fuel delivered to the main engine through heater and full flow filter.
The purpose of this document is to determine the technical specification of fuel oil system and the equipments.
WHFO
VHFO
Qstr
Vstl
Vsrv
Page 10 of 110
hl = head losses
H = head total
Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Philosophy
4. DESIGN PARAMETER
4.1 Principal Dimension1. Lpp = 123 m
2. B = 20.2 m
3. T = 8.8 m
4. H = 11.5 m
= 127.92 m
6. Vs = 14.5 knot = 26.8308 km/hours
7. Distance = 1200 Nm = 2222.4 km
8. Endurance = 4 days = 96 hours
4.2 Coefficient and Constants
1. Cb disp = 125.46
2. Cb wl = 0.694385
3. Cp disp = 0.717
4. Cp wl = 0.703212
5. Am = 174.9158
6. Cm = 0.984
4.3 Project Guide's Data
1. BHP = 6320 kW
2. SFOC = 173 gr/kWh
= 0.991
4. MCR = 6258.88 kW
5. RPM = 127 r/min
6. SLOC = 0.95 g/BHPh
5. DESIGN REQUIREMENT
5.1. HEAVY FUEL OIL (HFO)
5.1.1 HFO's weight
Weight of HFO
= P x SFOC x endurance (hours) x c . . . . . . . . . . . . . . . (1)
where,
P = Maximum power of main engine [kW]
SFOC = Specific fuel oil consumption [gr/kWh]
c = constant addition of fuel (1.3)
5.1.2 Storage Tank Volume
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
5. LWL
3. ρ HFO ton/m3
WHFO
Page 11 of 110
Volume of HFO
= WHFO/γ FO . . . . . . . . . . . . . . . . . . . . . . . . . . . . (2)
where,
γ FO = 0.95
The addition of fuel volume by 4% due to expansion by temperature (Ship Design and Construction)
=
5.1.3 Storage Tank Heating
Heat specific of heavy fuel oil (C) = 1717
Therefore, ∆t = 35
Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Philosophy
Time for increases temperature is 8 hours = 28800 s
HFO tank is divided into two tank and each tank containt 75 tonnes
= (W each tank x C x ∆t)/t . . . . . . . . . . . . . . . . . . . . . . (3)
5.1.4 Settling Tank Volume
= (SFOC x t x P x 1.05)/ρ HFO . . . . . . . . . . . . . . . . . . (4)
where,
t = 24 hours (time of fuel to precipate is 1 day)
margin = 5%
ρ HFO = 991
5.1.5 Settling Tank Heating
Heat specific of heavy fuel oil (C) = 1717
Therefore, ∆t = 35
Time for increases temperature is 4 hours = 14400 s
= (W each tank x C x ∆t)/t . . . . . . . . . . . . . . . . . . . . . . (5)
5.1.6 Service Tank Volume
= (SFOC x t x P x 1.05)/ρ HFO . . . . . . . . . . . . . . . . . . (6)
where,
t = 8 hours (time of used)
margin = 5%
ρ HFO = 991
5.1.7 HFO Transfer Pump
a. Capacity
Capacity = V settling tank/t . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (7)
b. Pump Diameter
For external pipe connections, we prescribe the following maximum velocities:
VHFO
ton/m3
VHFO (1+0.04)xVHFO
J/Kg0C
Because of the fuel oil temperature at the beginning is 150C and to increases to 500C0C
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Qstr
Vstl
kg/m3
J/Kg0C
Because of the fuel oil temperature at the beginning is 150C and to increases to 500C0C
Qstr
Vsrv
kg/m3
Time estimation were planned one hour for the HFO transfer pump to delivered from storage to settling tank.
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities, that:
Page 12 of 110
Marine diesel oil = 1.0 m/s
Heavy fuel oil = 0.6 m/s
Lubricaring oil = 1.8 m/s
Cooiling water = 3.0 m/s
For the following formula:
Q = A x v . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (8)
where,
Q = Capacity
A = Area of Pipe that will be convert to diameter formula
v = flow velocity
The pipe selection from ANSI, carbon steel with:
Inside diameter = 5.187 inches
Thickness = 0.718 inches
Outside diameter = 6.625 inches
Nominal pipe size = 6 inches
Minimum thickness = 3.6 mm= 0.142 inches
Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Philosophy
Table 1.7.1 Minimum wall thickness
c. Head Pump
i. Head Static (Hs)
height at z=0 to higer the discharge = 2.65 m
height at z=0 to the lower suction = 0 m
Therefore, the value of Hs will be determined below:
ii. Head Pressure (Hp)
Hp = 0 m (the pressure in the suction and discharge has the same value)
iii. Head Velocity (Hv)
Hv = 0 m (the velocity in the suction and discharge has the same value)
(According to table 1.7.1 Minimum wall thickness)
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Page 13 of 110
iv. Head Losses (Hl)
iv.1 Suction
n = kinematic viscocity
n = 0.0007
dH = Inside diameter
v = fluid velocity
= 0.6 m/s
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (9)
for the friction losses (f) = 64/Rn
The length of pipe in suction is 8.5 m
major losses (hf1) = . . . . . . . . . (10)
minor losses (hl1)
No Types n k nxk
1 4 0.9 3.6
2 Filter 1 0.58 0.58
3 Buttterfly valve 2 0.6 1.2
5 T-joint 1 1.8 1.8
total 7.18
minnor losses (hl1) = k total*v2/(2g) . . . . . . (11)
iv.2 Discharge
n = kinematic viscocity
Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Philosophy
n = 0.0007
dH = Inside diameter
v = fluid velocity
= 0.6 m/s
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (12)
for the friction losses (f) = 64/Rn
The length of pipe in discharge is 8.23 m
major losses (hf2) = . . . . . . . . . (13)
minor losses (hl2)
No Types n k nxk
1 4 0.9 3.6
2 Safety valve 1 2.5 2.5
3 SDRNV 1 2 2
4 T-joint 1 1.8 1.8
5 Buttterfly valve 1 0.6 0.6
total 10.5
m2/s (700 cSt at 500C)
f x L x v2 / (D x 2g)
Elbow 900
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
m2/s (700 cSt at 500C)
f x L x v2 / (D x 2g)
Elbow 900
Page 14 of 110
minnor losses (hl2) = k total*v2/(2g) . . . . . . (14)
Therefore, the total head losses can be calculate:
hf1+hl1+hf2+hl2
Total Head
Hs+Hp+Hv+Hl
5.1.8 HFO Feed Pump
a. Capacity
Capacity = V service tank/t . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (15)
b. Pump Diameter
For external pipe connections, we prescribe the following maximum velocities:
Marine diesel oil = 1.0 m/s
Heavy fuel oil = 0.6 m/s
Lubricaring oil = 1.8 m/s
Cooiling water = 3.0 m/s
For the following formula:
Q = A x v . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (16)
where,
Q = Capacity
A = Area of Pipe that will be convert to diameter formula
v = flow velocity
The pipe selection from ANSI, carbon steel with:
Inside diameter = 3.068 inches
Thickness = 0.216 inches
Outside diameter = 3.5 inches
Nominal pipe size = 3 inches
Minimum thickness = 2.6 mm= 0.102 inches
Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Philosophy
Table 1.7.1 Minimum wall thickness
Time estimation were planned 0.5 hours for the HFO feed pump to delivered from settling tank to service tank.
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities, that:
(According to table 1.7.1 Minimum wall thickness)
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Page 15 of 110
c. Head Pump
i. Head Static (Hs)
height at z=0 to higer the discharge = 1 m
height at z=0 to the lower suction = 0 m
Therefore, the value of Hs will be determined below:
ii. Head Pressure (Hp)
Hp = 0 m (the pressure in the suction and discharge has the same value)
iii. Head Velocity (Hv)
Hv = 0 m (the velocity in the suction and discharge has the same value)
iv. Head Losses (Hl)
iv.1 Suction
n = kinematic viscocity
n = 0.0007
dH = Inside diameter
v = fluid velocity
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (17)
for the friction losses (f) = 64/Rn
= 0.958213
The length of pipe in suction is 1.75 m
major losses (hf1) = . . . . . . . . . (18)
minor losses (hl1)
No Types n k nxk
1 4 0.9 3.6
2 Filter 1 0.58 0.58
3 Buttterfly valve 2 0.6 1.2
5 T-joint 2 1.8 3.6
total 8.98
minnor losses (hl1) = k total*v2/(2g) . . . . . . (19)
iv.2 Discharge
n = kinematic viscocity
Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Philosophy
n = 0.0007
dH = Inside diameter
v = fluid velocity
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (20)
m2/s (700 cSt at 500C)
f x L x v2 / (D x 2g)
Elbow 900
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
m2/s (700 cSt at 500C)
Page 16 of 110
for the friction losses (f) = 64/Rn
The length of pipe in discharge is 14.5 m
major losses (hf2) = . . . . . . . . . (21)
minor losses (hl2)
No Types n k nxk
1 4 0.9 3.6
2 Safety valve 1 2.5 2.5
3 SDRNV 3 2 6
4 T-joint 1 1.8 1.8
5 Buttterfly valve 3 0.19 0.57
total 14.47
minnor losses (hl2) = k total*v2/(2g) . . . . . . (22)
Therefore, the total head losses can be calculate:
hf1+hl1+hf2+hl2
Total Head
Hs+Hp+Hv+Hl
5.1.9 HFO Supply Pump
a. Capacity
According to Project Guide Man B&W the value of capacity is
= 1.6
= 0.000444
= 26.66667 L/minute
b. Pump Diameter
For external pipe connections, we prescribe the following maximum velocities:
Marine diesel oil = 1.0 m/s
Heavy fuel oil = 0.6 m/s
Lubricaring oil = 1.8 m/s
Cooiling water = 3.0 m/s
For the following formula:
Q = A x v . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (23)
where,
Q = Capacity
A = Area of Pipe that will be convert to diameter formula
v = flow velocity
Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Philosophy
Table 1.7.1 Minimum wall thickness
f x L x v2 / (D x 2g)
Elbow 900
m3/h
m3/s
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities, that:
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Page 17 of 110
c. Head Pump
i. Head Static (Hs)
height at z=0 to higer the discharge = 0.6 m
height at z=0 to the lower suction = 0.5 m
Therefore, the value of Hs will be determined below:
ii. Head Pressure (Hp)
Hp = 4 bar
= 40 m
iii. Head Velocity (Hv)
Hv = 0 m (the velocity in the suction and discharge has the same value)
iv. Head Losses (Hl)
iv.1 Suction
n = kinematic viscocity
n = 0.0007
dH = Inside diameter
v = fluid velocity
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (24)
for the friction losses (f) = 64/Rn
The length of pipe in suction is 2 m
major losses (hf1) = . . . . . . . . . (25)
minor losses (hl1)
No Types n k nxk
1 3 0.9 2.7
2 3 way valve 1 0.14 0.14
3 Buttterfly valve 2 0.6 1.2
5 T-joint 1 1.8 1.8
total 5.84
minnor losses (hl1) = k total*v2/(2g) . . . . . . (26)
iv.2 Discharge
n = kinematic viscocity
m2/s (700 cSt at 500C)
f x L x v2 / (D x 2g)
Elbow 900
Page 18 of 110
Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Philosophy
n = 0.0007
dH = Inside diameter
v = fluid velocity
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (27)
for the friction losses (f) = 64/Rn
The length of pipe in discharge is 1.5 m
major losses (hf2) = . . . . . . . . . (28)
minor losses (hl2)
No Types n k nxk
1 1 0.9 0.9
2 SDRNV 1 2 2
3 T-joint 2 1.8 3.6
4 Buttterfly valve 1 0.19 0.19
total 6.69
minnor losses (hl2) = k total*v2/(2g) . . . . . . (29)
Therefore, the total head losses can be calculate:
hf1+hl1+hf2+hl2
Total Head
Hs+Hp+Hv+Hl
5.1.10 HFO Circulating Pump
a. Capacity
According to Project Guide Man B&W the value of capacity is
= 3.7
= 0.001028
= 61.66667 L/minute
b. Pump Diameter
For external pipe connections, we prescribe the following maximum velocities:
Marine diesel oil = 1.0 m/s
Heavy fuel oil = 0.6 m/s
Lubricaring oil = 1.8 m/s
Cooiling water = 3.0 m/s
For the following formula:
Q = A x v . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (23)
where,
Q = Capacity
A = Area of Pipe that will be convert to diameter formula
v = flow velocity
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
m2/s (700 cSt at 500C)
f x L x v2 / (D x 2g)
Elbow 900
m3/h
m3/s
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities, that:
Page 19 of 110
5.2. MARINE DIESEL OIL (MDO)
5.2.1 MDO's weight
Estimating, approximately 10-20% from HFO's weight
= 20%*136.45 . . . . . . . . . . . . . . . . . . . . . . . . . . . . (30)
5.2.2 Storage Tank Volume
Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Philosophy
ρDO = 0.85
and for the MDO's volume
5.2.3 Service Tank Volume
= {(SFOC x BHP)/ρ} x T x (1 + 0.02) . . . . . . . . . . . . . . . . . . (31)
where,
t = 8 hours (time of used)
margin = 2%
ρ DO = 850
5.2.4 MDO Feed Pump
a. Capacity
The estimation transfer from storage tank to service tank is 0.5 hours.
Q = V/t . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (32)
b. Pump Diameter
For external pipe connections, we prescribe the following maximum velocities:
Marine diesel oil = 1.0 m/s
Heavy fuel oil = 0.6 m/s
Lubricaring oil = 1.8 m/s
Cooiling water = 3.0 m/s
For the following formula:
Q = A x v . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (33)
where,
Q = Capacity
A = Area of Pipe that will be convert to diameter formula
v = flow velocity
The pipe selection from ANSI, carbon steel with:
Inside diameter = 3.548 inches
Thickness = 0.226 inches
Outside diameter = 4 inches
Nominal pipe size = 3.5 inches
Minimum thickness = 2.6 mm= 0.102 inches
Table 1.7.1 Minimum wall thickness
WMDO
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
ton/m3
Vsrv
kg/m3
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities, that:
(According to table 1.7.1 Minimum wall thickness)
Page 20 of 110
Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Philosophy
c. Head Pump
i. Head Static (Hs)
height at z=0 to higer the discharge = 1 m
height at z=0 to the lower suction = 0.5 m
Therefore, the value of Hs will be determined below:
ii. Head Pressure (Hp)
Hp = 0 bar
iii. Head Velocity (Hv)
Hv = 0 m (the velocity in the suction and discharge has the same value)
iv. Head Losses (Hl)
iv.1 Suction
n = kinematic viscocity
n = 0.0007
dH = Inside diameter
v = fluid velocity
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (34)
for the friction losses (f) = 64/Rn
The length of pipe in suction is 2.5 m
major losses (hf1) = . . . . . . . . . (35)
minor losses (hl1)
No Types n k nxk
1 2 0.9 1.8
2 Filter 1 0.58 0.58
3 Buttterfly valve 2 0.19 0.38
5 T-joint 1 1.8 1.8
total 4.56
minnor losses (hl1) = k total*v2/(2g) . . . . . . (36)
iv.2 Discharge
n = kinematic viscocity
n = 0.0007
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
m2/s (700 cSt at 500C)
f x L x v2 / (D x 2g)
Elbow 900
m2/s (700 cSt at 500C)
Page 21 of 110
dH = Inside diameter
v = fluid velocity
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (37)
for the friction losses (f) = 64/Rn
The length of pipe in discharge is 14 m
major losses (hf2) = . . . . . . . . . (38)
minor losses (hl2)
No Types n k nxk
1 2 0.9 1.8
2 T-joint 2 1.8 3.6
3 SDRNV 1 2 2
4 Safety valve 1 2.5 2.5
5 Buttterfly valve 3 0.19 0.57
total 10.47
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Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Philosophy
minnor losses (hl2) = k total*v2/(2g) . . . . . . (39)
Therefore, the total head losses can be calculate:
hf1+hl1+hf2+hl2 =
Total Head
Hs+Hp+Hv+Hl
5.3. SEPARATOR
Q(l/h) = (P x SFOC x 24)/(991 x 23.5) . . . . . . . . . . . . . . . . . . . (40)
Volume = 1.8
Head = 2-6 bar
5.4. HEATER POWER FOR FEED PUMP
P[kW] = Q(l/h) x Δt ('C) / 1700 . . . . . . . . . . . . . . . . . . . . . . (41)
where, L/h
Q = capacity of separator feed pump
= 711.39
t = temperature rise in heater
= 48
Type : Electric Heater
5.5. HEATER POWER FOR CIRCULATING PUMP
P[kW] = Q(l/h) x Δt ('C) / 1700 . . . . . . . . . . . . . . . . . . . . . . (42)
where,
Q = capacity ogr/h
t = temperature rise in heater
= 48
Type : Electric Heater
5.6. VALVE AND FITTING
a. Valve
f x L x v2 / (D x 2g)
Elbow 900
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
m3
oC
oC
Page 22 of 110
1. Butterfly Valve
Figure 5.3 Butterfly Valve
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Rev.No : 02
Type : Philosophy
2. Non Return Valve
3. Three Way Valve and Angle Valve
As a connect of pipe with simple used.
b. Fitting
1. Filter
A butterfly valve is a valve which can be used for isolating or regulating flow. The closing mechanism takes the form of a disk, which allows for quick shut off. Butterfly valve are generally favored because they are lower in cost to other valve designs as well as being lighter in weight, meaning less support is required. Used for stop valve only, for low working pressure. In this system, butterfly valve used in order before the pump, and as a connecting to another equipment to make a standby function. Below is the example of butterfly valve, shown in Figure 5.3 Butterfly Valve.
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Has same function with globe valve, working in very high pressure and just has one-way direction. Usually this valve is used in order after the pump and another lines that the fluids shall not back through the same line or just one-way direction.
Hyraulic filters are very useful for removing solid contamination from lube and fuel oil system of marine machinery. Withous filters in the lube or fuel oil system, the machinery internal parts, bearing, piston, rings, liners etc. can get damaged, which will result in inefficient working of the machinery. In this system will be used Centrifugal Filter. These filters work on the principal of centrifugal force removing high density fluids and impurity from the oil. It is normally used for lube oil systems. Most of the auxiliary engines have attaced centrifugal filters. The example will be shown in Figure 5.4 Centrifugal Filter below.
Page 23 of 110
Figure 5.4 Centrifugal Filter
5.7. CLASS REQUIREMENT
Germanischer Lloyd 2012, Chapter 2, Section 11, Page 11-26.
1. Bunker Lines
2. Tank Filling and Suction Lines
Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Philosophy
3. Pipe Layout
The bunkering of fuel oil is to be effected by means of permanently installed lines either from the open deck or from bunkering stations located below deck which are to be isolated from other spaces. Bunker station are to be so arranged that the bunkering can be performed from both sides of the ship without danger. This requirement is considered to be fulfilled where the bunkering line is extended to both sides of the ship. The bunkering lines are to be fitted with blind flanges on deck.
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Filling and suction lines from storage, settling and service tanks situated above the double bottom and from which in case of their damage fuel oil may leak, are to be fitted directly on the tanks with shut-off devices capable of being closed from a safe position outside the space concerned. In the case of deep tans situated in shaft or pipe tunnel or similar spaces, shut-off devices are to be fitted on the tanks. the control in the event of fire may be effected by means of an additional shut off device in the pipe outside the tunnel or similar space. If such additional shut-off device is fitted in the machinery space it is to be operated from a position outside this space. Shut-off device on fuel oil tans having a capacity of less than 500 l need not be provided with remote control. Filling lines are to extend to the botton of the tank. Short filling lines directed tothe side of the tank may be admissible. Storage tank suction line may also used as filling lines. Wher filling lines are led through the tank top and end below the maximum oil level in the tank, a non-return valve at the tank top is to be arranged. The inlet connection of suction lines are to be arranged far enough from the drains in the tank so that water and impurities which have settled out will non enter the suctions.
Page 24 of 110
The design pressure for fuel pipes is to be chosen according to Table 5.1 below:
Table 5.1 Design Pressure for Fuel Pipes
Pipe Thickness category will be used D and N
Project : DESIGN IV
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Rev.No : 02
Type : Philosophy
4. Fuel Transfer, Feed and Booster Pumps
5. Filters
Fuel lines may not pass through tanks containing feed water, drinking water, lubricating oil or thermal oil. Fuel lines which pass through ballast tank are to have an increased wall thickness.
Fuel lines are not to be laid directly above or in the vicinity of boilers, turbines or equipment with high surface temperatures (over 220 0C) or in way of other sources of ignition. Flanged and screwed socket connections in fuel oil lines are to be screened or otherwise suitably protected to avoid, as far as practible, oil spray or oil leakages onto hot surface, into machinery air intakes, or other source of ignition.
All Class I and II pipe as well as steam lines feed water pressure pipes, compressed air and fuel line having a design pressure PR greater than 3.5 bar together with their integral fittings,, connecting pieces, branches and bends, after completion of manufacture but before insulation and coating, if this is provided.
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Fuel transfer, feed and booster pumps are to be designed for the intended operating temperature. A fuel transfer pump is to be provided. Other service pump may be used as a stand-by pump provided they are suitable for this purpose. At least two means of oil fuel transfer are to be provided for filling the service tanks. Where a feed or booster pump is required to supply fuel to main or auxiliary engines, stand-by pumps are to be provided. Where pumps are attached to the engines, stand-by pumps may be dispensed with for auxiliary engines.
Page 25 of 110
6. Purifiers
7. Service Tanks
8. Operation Using Heavy Fuel Oil
9. Treatment of Heavy Fue Oil
10. Change-over Arrangement Diesel Oil/Heavy Oil
Project : DESIGN IV
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Type : Philosophy
11. Local Control Devices
The following local control devices are to be fitted directly before the engine:
- a gauge for operating pressure
Fuel oil filters are to be fitted in the delivery line of the fuel oil pumps. Fuel oil filters are to be fitted with differential pressure monitoring. On engines provided for operation with gas oil only, differential pressure monitoring may be dispensed with. Engine for the exclusive operation of emergency generators and emergency fire pumps may be fitted with simplex filter. Fuel transfer units are to be fitted with a simplex filter on the suctin side.
Where a fuel purifier may exceptionally be used to purify lubricating oil, the purifier supply and discharge lines are to be fitted with a change-over arrangement which prevents the possibility of fuel and lubricating oil mixed. Suitable equipment is also to be provided to prevent such mixing occuring over control and compression lines. The sludge tanks of purifiers are to be fitted with a level alarm which ensures that the level in the sludge tank cannot interfere with the operation of the purifier.
On cargo ships of 500 GT or above and all passenger ships two fuel oil service tanks for each type of fuel used on board necessary for propulsion and essential systems are to be provided. Equivalent arrangements may be permitted. Each service tank is to have a capacity of at least 8 hours at maximum continuous rating of the propulsion plant and normal operation load of the generator plant.
Heavy fuel oil tanks are to be fitted with a heating system. The capacity of the tank heating system is to be in accordance with the operating requirements and the quality of fuel oil intended to be used. With GL's content, storage tanks need not be fitted with a heating system provided it can be guaranteed that the proposed quality of fuel oil can be pumped under all ambient and environmental conditions.
Heavy fuel settling tanks or equivalent arrangements with sufficiently dimensioned heating systems are to be provided. Settling tanks are to be provided with drains, emptying arrangements and with temperature measuring instruments. For cleaning of heavy fuels, purifiers of purifiers combined with automatic filters are to be provided. The capactity of the service tanks is to be such that, should the treatment plant fail, the supply to all the connected consumers can be maintained for at least 8 hours.
The change-over arrangement of the fuel supply and return lines is to be so arranged that faulty switching is excluded and to ensure reliable separation of the fuels. Change-over valves which alow intermediate positions are not permitted.
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Page 26 of 110
- an indicator for the operating temperature
6. SUMMARY
HEAVY FUEL OIL (HFO)
NO CALCULATION SYMBOL RESULT
1 HFO's weight 136.5 tonnes
2 Storage Tank Volume 150
4 Storage Tank Heating 156.5 kW
5 Settling Tank Volume 27.8
6 Settling Tank Heating 116.9 kW
7 Service Tank Volume 9.3
HFO Transfer Pump
8 Capacity Q 28.0
9 Inside diameter DH 5.2 inches10 Head total H 4.3 m
Pump Selection
Merk = IRON PUMP
Type = ON-V:35/10
Capacity = 34
Head = 20 m
RPM = 850 rpm
Power = 9 HP = 6.62 kW
HFO FEED PUMP
11 Capacity Q 9.312 Inside diameter DH 3.1 inches13 Head total H 5.1 m
Pump Selection
Merk = IRON PUMP
Type = ON-V:6
Capacity = 11
Head = 20 m
RPM = 850 rpm
Power = 2.2 HP = 1.62 kW
Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
WHFO
Vstr m3
Qstr
Vstl m3
Qstl
Vsrv m3
m3/h
m3/h
m3/h
m3/h
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Page 27 of 110
Rev.No : 02
Type : Philosophy
HFO SUPPLY PUMP
14 Capacity Q 1.715 Inside diameter DH 1.3 inches16 Head total H 82.2 m
Pump Selection
Merk = Allweiler
Type = SPF 40-38
Capacity = 27.8 L/minute
= 1.668
Tekanan = 5 bar
RPM = 1450 rpm
Power = 0.37 kWHFO CIRCULATING PUMP
17 Capacity Q 4.018 Inside diameter DH 1.9 inches19 Head total H 104.4 m
Pump Selection
Merk = Allweiler
Type = SPF 40-38
Capacity = 67.2 L/Minute
= 4.032
Tekanan = 10 bar
RPM = 3400 rpm
Power = 1.6 kW
MARINE DIESEL OIL (MDO)
NO CALCULATION SYMBOL RESULT
20 MDO's weight 27.3 tonnes
21 Storage Tank Volume 32.1
22 Service Tank Volume 10.5MDO FEED PUMP
23 Capacity Q 21.024 Inside diameter DH 3.5 inches25 Head total H 6.6 m
Pump Selection
Merk = IRON PUMP
Type = ON-V:8
Capacity = 21
Head = 20 m
RPM = 950 rpm
Power = 3.4 HP = 2.5 kWSEPARATOR
26 Heating Q 1126.8 L/h
27 Volume V 1.828 Head H 2 ~ 6 bar
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
m3/h
m3/h
m3/h
m3/h
WMDO
Vstr m3
Vsrv m3
m3/h
m3/h
m3
Page 28 of 110
Project : DESIGN IV
Doc. No : 15 - 42 09 050 - FO
Rev.No : 02
Type : Philosophy
HEATER POWER FOR FEED PUMP
29 Power P 20.1 kW
To be choosen, the electric heater:
MERK = AALBORG
Type = 20
kW = 24 kWHEATER POWER FOR CIRCULATING PUMP
30 Power P 31.2 kW
To be choosen, the electric heater:
MERK = AALBORG
Type = 25
kW = 33 kW
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Page 29 of 110
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Engine Selection Guide - Two Stroke MC/MC-C Engines, 6th Edition: January 2002, MAN B&W
The fuel oil system on the ship was designed with either using 2 types of fuel, heavy fuel oil (HFO) and Diesel Oil (DO). On the system pumped with HFO, HFO (HFO transfer pump) driven pumps with electric motor toward settling tank. HFO from settling tank delivered to HFO service tank with HFO feed pump through the paralel centrifuge to separate between fuel, sludge occuring and also water. In feed pump, there are some equipments such as filter and heater. The heater function is to heating the fuel oil before entering the centrifuge. For the diesel oil system, the diesel oil storage was located in diesel oil storage tank and will be pumped by diesel oil feed pump through a centrifuge who separate the diesel oil with the sludge and also water to the diesel oil service tank. From service tank, the fuel were delivered with supply pump to circulating pump. And then the fuel delivered to the main engine through heater and full flow
The purpose of this document is to determine the technical specification of fuel oil system and the
Page 30 of 110
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Page 31 of 110
The addition of fuel volume by 4% due to expansion by temperature (Ship Design and Construction)
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: Philosophy
For external pipe connections, we prescribe the following maximum velocities:
C and to increases to 500C
C and to increases to 500C
Time estimation were planned one hour for the HFO transfer pump to delivered from storage to
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow
Page 32 of 110
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: Philosophy
Table 1.7.1 Minimum wall thickness
(the pressure in the suction and discharge has the same value)
(the velocity in the suction and discharge has the same value)
(According to table 1.7.1 Minimum wall
Page 33 of 110
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: Philosophy
Page 34 of 110
For external pipe connections, we prescribe the following maximum velocities:
: DESIGN IV
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: Philosophy
Table 1.7.1 Minimum wall thickness
Time estimation were planned 0.5 hours for the HFO feed pump to delivered from settling tank
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow
(According to table 1.7.1 Minimum wall thickness)
Page 35 of 110
(the pressure in the suction and discharge has the same value)
(the velocity in the suction and discharge has the same value)
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: Philosophy
Page 36 of 110
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: Philosophy
Table 1.7.1 Minimum wall thickness
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities,
Page 37 of 110
(the velocity in the suction and discharge has the same value)
Page 38 of 110
: DESIGN IV
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: 02
: Philosophy
For external pipe connections, we prescribe the following maximum velocities:
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow
Page 39 of 110
: DESIGN IV
: 15 - 42 09 050 - FO
: 02
: Philosophy
For external pipe connections, we prescribe the following maximum velocities:
Table 1.7.1 Minimum wall thickness
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow
(According to table 1.7.1 Minimum wall
Page 40 of 110
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: Philosophy
(the velocity in the suction and discharge has the same value)
Page 41 of 110
: DESIGN IV
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: Philosophy
Page 42 of 110
: DESIGN IV
: 15 - 42 09 050 - FO
: 02
: Philosophy
A butterfly valve is a valve which can be used for isolating or regulating flow. The closing mechanism takes the form of a disk, which allows for quick shut off. Butterfly valve are generally favored because they are lower in cost to other valve designs as well as being lighter in weight, meaning less support is required. Used for stop valve only, for low working pressure. In this system, butterfly valve used in order before the pump, and as a connecting to another equipment to make a standby function. Below is the example of butterfly valve, shown in Figure 5.3 Butterfly Valve.
Has same function with globe valve, working in very high pressure and just has one-way direction. Usually this valve is used in order after the pump and another lines that the fluids shall
Hyraulic filters are very useful for removing solid contamination from lube and fuel oil system of marine machinery. Withous filters in the lube or fuel oil system, the machinery internal parts, bearing, piston, rings, liners etc. can get damaged, which will result in inefficient working of the machinery. In this system will be used Centrifugal Filter. These filters work on the principal of centrifugal force removing high density fluids and impurity from the oil. It is normally used for lube oil systems. Most of the auxiliary engines have attaced centrifugal filters. The example will
Page 43 of 110
: DESIGN IV
: 15 - 42 09 050 - FO
: 02
: Philosophy
The bunkering of fuel oil is to be effected by means of permanently installed lines either from the open deck or from bunkering stations located below deck which are to be isolated from other spaces. Bunker station are to be so arranged that the bunkering can be performed from both sides of the ship without danger. This requirement is considered to be fulfilled where the bunkering line is extended to both sides of the ship. The bunkering lines are to be fitted with blind flanges on deck.
Filling and suction lines from storage, settling and service tanks situated above the double bottom and from which in case of their damage fuel oil may leak, are to be fitted directly on the tanks with shut-off devices capable of being closed from a safe position outside the space concerned. In the case of deep tans situated in shaft or pipe tunnel or similar spaces, shut-off devices are to be fitted on the tanks. the control in the event of fire may be effected by means of an additional shut off device in the pipe outside the tunnel or similar space. If such additional shut-off device is fitted in the machinery space it is to be operated from a position outside this space. Shut-off device on fuel oil tans having a capacity of less than 500 l need not be provided with remote control. Filling lines are to extend to the botton of the tank. Short filling lines directed tothe side of the tank may be admissible. Storage tank suction line may also used as filling lines. Wher filling lines are led through the tank top and end below the maximum oil level in the tank, a non-return valve at the tank top is to be arranged. The inlet connection of suction lines are to be arranged far enough from the drains in the tank so that water and impurities which have settled out will non enter the suctions.
Page 44 of 110
: DESIGN IV
: 15 - 42 09 050 - FO
: 02
: Philosophy
Fuel lines may not pass through tanks containing feed water, drinking water, lubricating oil or thermal oil. Fuel lines which pass through ballast tank are to have an increased wall thickness.
Fuel lines are not to be laid directly above or in the vicinity of boilers, turbines or equipment with C) or in way of other sources of ignition. Flanged and screwed
socket connections in fuel oil lines are to be screened or otherwise suitably protected to avoid, as far as practible, oil spray or oil leakages onto hot surface, into machinery air intakes, or other source of
All Class I and II pipe as well as steam lines feed water pressure pipes, compressed air and fuel line having a design pressure PR greater than 3.5 bar together with their integral fittings,, connecting pieces, branches and bends, after completion of manufacture but before insulation and coating, if
Fuel transfer, feed and booster pumps are to be designed for the intended operating temperature. A fuel transfer pump is to be provided. Other service pump may be used as a stand-by pump provided they are suitable for this purpose. At least two means of oil fuel transfer are to be provided for filling the service tanks. Where a feed or booster pump is required to supply fuel to main or auxiliary engines, stand-by pumps are to be provided. Where pumps are attached to the engines, stand-by
Page 45 of 110
: DESIGN IV
: 15 - 42 09 050 - FO
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: Philosophy
Fuel oil filters are to be fitted in the delivery line of the fuel oil pumps. Fuel oil filters are to be fitted with differential pressure monitoring. On engines provided for operation with gas oil only, differential pressure monitoring may be dispensed with. Engine for the exclusive operation of emergency generators and emergency fire pumps may be fitted with simplex filter. Fuel transfer units are to be
Where a fuel purifier may exceptionally be used to purify lubricating oil, the purifier supply and discharge lines are to be fitted with a change-over arrangement which prevents the possibility of fuel and lubricating oil mixed. Suitable equipment is also to be provided to prevent such mixing occuring over control and compression lines. The sludge tanks of purifiers are to be fitted with a level alarm which ensures that the level in the sludge tank cannot interfere with the operation of the
On cargo ships of 500 GT or above and all passenger ships two fuel oil service tanks for each type of fuel used on board necessary for propulsion and essential systems are to be provided. Equivalent arrangements may be permitted. Each service tank is to have a capacity of at least 8 hours at maximum continuous rating of the propulsion plant and normal operation load of the generator plant.
Heavy fuel oil tanks are to be fitted with a heating system. The capacity of the tank heating system is to be in accordance with the operating requirements and the quality of fuel oil intended to be used. With GL's content, storage tanks need not be fitted with a heating system provided it can be guaranteed that the proposed quality of fuel oil can be pumped under all ambient and environmental
Heavy fuel settling tanks or equivalent arrangements with sufficiently dimensioned heating systems are to be provided. Settling tanks are to be provided with drains, emptying arrangements and with temperature measuring instruments. For cleaning of heavy fuels, purifiers of purifiers combined with automatic filters are to be provided. The capactity of the service tanks is to be such that, should the treatment plant fail, the supply to all the connected consumers can be maintained for at least 8
The change-over arrangement of the fuel supply and return lines is to be so arranged that faulty switching is excluded and to ensure reliable separation of the fuels. Change-over valves which alow
Page 46 of 110
: DESIGN IV
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Page 47 of 110
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: Philosophy
Page 48 of 110
: DESIGN IV
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: Philosophy
DESIGN-IV: MACHINERY BASIC DESIGN
ATTACHMENT NO. 01 CALCULATION
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
ATTACHMENT NO. 01 CALCULATION
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
DESIGN-IV: MACHINERY BASIC DESIGN
ATTACHMENT NO. 01 CALCULATION
TECHNICAL SPECIFICATION OF FUEL OIL
ATTACHMENT NO. 01 CALCULATION
TECHNICAL SPECIFICATION OF FUEL OIL
Page 53 of 110
Project
Doc. No
Rev.No
Type
1. HEAVY FUEL OIL (HFO)
1.1 HFO's weight
Weight of HFO
= P x SFOC x endurance (hours) x c . . . . . . . . . . . . . . . (1)
where,
P = Maximum power of main engine [kW]
SFOC = Specific fuel oil consumption [gr/kWh]
c = constant addition of fuel (1.3)
for the result:
= P x SFOC x endurance (hours) x c
= 6320*173*96*1.3*10^-6
= 136.45 tonnes
1.2 Storage Tank Volume
Volume of HFO
= WHFO/γ FO . . . . . . . . . . . . . . . . . . . . . . . . . . . . (2)
where,
γ FO = 0.95
for the result:
=
= 136.45/0.95
= 144
The addition of fuel volume by 4% due to expansion by temperature (Ship Design and Construction)
=
= (1+0.04)x144
= 150
1.3 Storage Tank Heating
Heat specific of heavy fuel oil (C) = 1717
Therefore, ∆t = 35
Time for increases temperature is 8 hours = 28800 s
HFO tank is divided into two tank and each tank containt 75 tonnes
= (W each tank x C x ∆t)/t . . . . . . . . . . . . . . . . . . . . . . (3)
= (75*1717*35)/28800
= 156.5 kW
1.4 Settling Tank Volume
= (SFOC x t x P x 1.05)/ρ HFO . . . . . . . . . . . . . . . . . . (4)
where,
t = 24 hours (time of fuel to precipate is 1 day)
margin = 5%
ρ HFO = 991
for the result:
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
WHFO
WHFO
WHFO
VHFO
ton/m3
VHFO WHFO/γ FO
m3
VHFO (1+0.04)xVHFO
m3
J/Kg0C
Because of the fuel oil temperature at the beginning is 150C and to increases to 500C0C
Qstr
Vstl
kg/m3
Page 54 of 110
= (SFOC x t x P x 1.05)/ρ HFO
= (0.173*24*6320*1.05)/991
= 28
1.5 Settling Tank Heating
Heat specific of heavy fuel oil (C) = 1717
Project
Doc. No
Rev.No
Type
Therefore, ∆t = 35
Time for increases temperature is 4 hours = 14400 s
= (W each tank x C x ∆t)/t . . . . . . . . . . . . . . . . . . . . . . (5)
= (28*1717*35)/14400
= 116.85 kW
1.6 Service Tank Volume
= (SFOC x t x P x 1.05)/ρ HFO . . . . . . . . . . . . . . . . . . (6)
where,
t = 8 hours (time of used)
margin = 5%
ρ HFO = 991
for the result:
= (SFOC x t x P x 1.05)/ρ HFO
= (0.173*8*6320*1.05)/991
= 9.27
1.7 HFO Transfer Pump
a. Capacity
Capacity = V settling tank/t . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (7)
= 28/1
= 28
= 0.007778
b. Pump Diameter
For external pipe connections, we prescribe the following maximum velocities:
Marine diesel oil = 1.0 m/s
Heavy fuel oil = 0.6 m/s
Lubricaring oil = 1.8 m/s
Cooiling water = 3.0 m/s
For the following formula:
Q = A x v . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (8)
where,
Q = Capacity
A = Area of Pipe that will be convert to diameter formula
Vstl
m3
J/Kg0C
Because of the fuel oil temperature at the beginning is 150C and to increases to 500C
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
0C
Qstr
Vsrv
kg/m3
Vstl
m3
Time estimation were planned one hour for the HFO transfer pump to delivered from storage to settling tank.
m3/h
m2/s
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities, that:
Page 55 of 110
v = flow velocity
for the result:
Q = A x v
0.00778 = (1/4 x π x D²) x 0.6
0.00778 = (1/4*3.14* D²)*0.6
= 0.00778/(0.25*3.14*0.6)
= 0.016518 m
D = 0.12852 m
= 128.5226 mm
= 5.059943 inches
The pipe selection from ANSI, carbon steel with:
Inside diameter = 5.187 inches
Project
Doc. No
Rev.No
Type
Thickness = 0.718 inches
Outside diameter = 6.625 inches
Nominal pipe size = 6 inches
Minimum thickness = 3.6 mm= 0.142 inches
Table 1.7.1 Minimum wall thickness
c. Head Pump
i. Head Static (Hs)
height at z=0 to higer the discharge = 2.65 m
height at z=0 to the lower suction = 0 m
Therefore, the value of Hs will be determined below:
Hs = 2.65-0
= 2.65 m
ii. Head Pressure (Hp)
Hp = 0 m (the pressure in the suction and discharge has the same value)
D2
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
(According to table 1.7.1 Minimum wall thickness)
Page 56 of 110
iii. Head Velocity (Hv)
Hv = 0 m (the velocity in the suction and discharge has the same value)
iv. Head Losses (Hl)
iv.1 Suction
n = kinematic viscocity
n = 0.0007
dH = Inside diameter
= 5.187 inches
= 0.13175 m
v = fluid velocity
= 0.6 m/s
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (9)
= (0.6*0.13175)/0.0007
= 112.9286 (laminer)
for the friction losses (f) = 64/Rn
= 0.566728
Project
Doc. No
Rev.No
Type
The length of pipe in suction is 8.5 m
major losses (hf1) = . . . . . . . . . (10)
= 0.56673*8.5*0.6^2/(0.13175*2*9.8)
= 0.6715695 m
minor losses (hl1)
No Types n k nxk
1 4 0.9 3.6
2 Filter 1 0.58 0.58
3 Buttterfly valve 2 0.6 1.2
5 T-joint 1 1.8 1.8
total 7.18
minnor losses (hl1) = k total*v2/(2g) . . . . . . (11)
= 7.18*(0.6^2)/(2*9.8)
= 0.132 m
iv.2 Discharge
n = kinematic viscocity
n = 0.0007
dH = Inside diameter
= 5.187 inches
= 0.13175 m
v = fluid velocity
= 0.6 m/s
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (12)
m2/s (700 cSt at 500C)
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
f x L x v2 / (D x 2g)
Elbow 900
m2/s (700 cSt at 500C)
Page 57 of 110
= (0.6*0.13175)/0.0007
= 112.9286 (laminer)
for the friction losses (f) = 64/Rn
= 0.566728
The length of pipe in discharge is 8.23 m
major losses (hf2) = . . . . . . . . . (13)
= 0.56673*8.23*0.6^2/(0.13175*2*9.8)
= 0.6502372 m
minor losses (hl2)
No Types n k nxk
1 4 0.9 3.6
2 Safety valve 1 2.5 2.5
3 SDRNV 1 2 2
4 T-joint 1 1.8 1.8
5 Buttterfly valve 1 0.6 0.6
total 10.5
minnor losses (hl2) = k total*v2/(2g) . . . . . . (14)
= 10.5*(0.6^2)/(2*9.8)
= 0.193 m
Therefore, the total head losses can be calculate:
hf1+hl1+hf2+hl2 = 0.672+0.132+0.651+0.193
= 1.648 m
Project
Doc. No
Rev.No
Type
Total Head
Hs+Hp+Hv+Hl = 2.65+0+0+1.65
= 4.3 m
d. Pump Selection
Merk = IRON PUMP
Type = ON-V:35/10
Capacity = 34
Head = 20 m
RPM = 850 rpm
Power = 9 HP = 6.62 kW
1.8 HFO Feed Pump
a. Capacity
Capacity = V service tank/t . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (15)
= 9.3/1
= 9.3
= 0.002583
b. Pump Diameter
f x L x v2 / (D x 2g)
Elbow 900
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
m3/h
Time estimation were planned 1 hours for the HFO feed pump to delivered from settling tank to service tank.
m3/h
m3/s
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities, that:
Page 58 of 110
For external pipe connections, we prescribe the following maximum velocities:
Marine diesel oil = 1.0 m/s
Heavy fuel oil = 0.6 m/s
Lubricaring oil = 1.8 m/s
Cooiling water = 3.0 m/s
For the following formula:
Q = A x v . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (16)
where,
Q = Capacity
A = Area of Pipe that will be convert to diameter formula
v = flow velocity
for the result:
Q = A x v
0.00258 = (1/4 x π x D²) x 0.6
0.00258 = (1/4*3.14* D²)*0.6
= 0.00258/(0.25*3.14*0.6)
= 0.005478 m
D = 0.07401 m
= 74.01153 mm
= 2.91384 inches
The pipe selection from ANSI, carbon steel with:
Inside diameter = 3.068 inches
Thickness = 0.216 inches
Outside diameter = 3.5 inches
Nominal pipe size = 3 inches
Minimum thickness = 2.6 mm= 0.102 inches
Project
Doc. No
Rev.No
Type
Table 1.7.1 Minimum wall thickness
D2
(According to table 1.7.1 Minimum wall thickness)
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Page 59 of 110
c. Head Pump
i. Head Static (Hs)
height at z=0 to higer the discharge = 1 m
height at z=0 to the lower suction = 0 m
Therefore, the value of Hs will be determined below:
Hs = 1-0
= 1 m
ii. Head Pressure (Hp)
Hp = 0 m (the pressure in the suction and discharge has the same value)
iii. Head Velocity (Hv)
Hv = 0 m (the velocity in the suction and discharge has the same value)
iv. Head Losses (Hl)
iv.1 Suction
n = kinematic viscocity
n = 0.0007
dH = Inside diameter
= 3.068 inches
= 0.077927 m
v = fluid velocity
= 0.6 m/s
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (17)
= (0.6*0.07793)/0.0007
= 66.79714 (laminer)
for the friction losses (f) = 64/Rn
= 0.958213
The length of pipe in suction is 1.75 m
major losses (hf1) = . . . . . . . . . (18)
= 0.98521*1.75*0.6^2/(0.07793*2*9.8)
= 0.4063578 m
minor losses (hl1)
Project
Doc. No
Rev.No
Type
No Types n k nxk
1 4 0.9 3.6
2 Filter 1 0.58 0.58
3 Buttterfly valve 2 0.6 1.2
5 T-joint 2 1.8 3.6
total 8.98
minnor losses (hl1) = k total*v2/(2g) . . . . . . (19)
= 8.98*(0.6^2)/(2*9.8)
= 0.165 m
iv.2 Discharge
m2/s (700 cSt at 500C)
f x L x v2 / (D x 2g)
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Elbow 900
Page 60 of 110
n = kinematic viscocity
n = 0.0007
dH = Inside diameter
= 3.068 inches
= 0.077927 m
v = fluid velocity
= 0.6 m/s
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (20)
= (0.6*0.07793)/0.0007
= 66.79714 (laminer)
for the friction losses (f) = 64/Rn
= 0.958213
The length of pipe in discharge is 14.5 m
major losses (hf2) = . . . . . . . . . (21)
= 0.96*14.5*0.6^2/(0.07793*2*9.8)
= 3.2808093 m
minor losses (hl2)
No Types n k nxk
1 4 0.9 3.6
2 Safety valve 1 2.5 2.5
3 SDRNV 3 2 6
4 T-joint 1 1.8 1.8
5 Buttterfly valve 3 0.19 0.57
total 14.47
minnor losses (hl2) = k total*v2/(2g) . . . . . . (22)
= 14.47*(0.6^2)/(2*9.8)
= 0.266 m
Therefore, the total head losses can be calculate:
hf1+hl1+hf2+hl2 = 0.406+0.165+3.28+0.266
= 4.117 m
Total Head
Hs+Hp+Hv+Hl = 1+0+0+4.12
= 5.12 m
d. Pump Selection
Merk = IRON PUMP
Type = ON-V:6
Capacity = 11
Project
Doc. No
Rev.No
Type
Head = 20 m
RPM = 850 rpm
Power = 2.2 HP = 1.62 kW
1.9 HFO Supply Pump
m2/s (700 cSt at 500C)
f x L x v2 / (D x 2g)
Elbow 900
m3/h
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Page 61 of 110
a. Capacity
According to Project Guide Man B&W the value of capacity is
= 1.6
= 0.0004444
= 26.666667 L/minute
b. Pump Diameter
For external pipe connections, we prescribe the following maximum velocities:
Marine diesel oil = 1.0 m/s
Heavy fuel oil = 0.6 m/s
Lubricaring oil = 1.8 m/s
Cooiling water = 3.0 m/s
For the following formula:
Q = A x v . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (23)
where,
Q = Capacity
A = Area of Pipe that will be convert to diameter formula
v = flow velocity
for the result:
Q = A x v
0.000444 = (1/4 x π x D²) x 0.6
0.000444 = (1/4*3.14* D²)*0.6
= 0.000444/(0.25*3.14*0.6)
= 0.000943 m
D = 0.03070 m
= 30.70302 mm
= 1.20878 inches
The pipe selection from ANSI, carbon steel with:
Inside diameter = 1.278 inches
Thickness = 0.191 inches
Outside diameter = 1.66 inches
Nominal pipe size = 1.25 inches
Minimum thickness = 2 mm= 0.079 inches
Project
Doc. No
Rev.No
m3/h
m3/s
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities, that:
D2
(According to table 1.7.1 Minimum wall thickness)
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Page 62 of 110
Type
Table 1.7.1 Minimum wall thickness
c. Head Pump
i. Head Static (Hs)
height at z=0 to higer the discharge = 0.6 m
height at z=0 to the lower suction = 0.5 m
Therefore, the value of Hs will be determined below:
Hs = 0.6+0.5
= 1.1 m
ii. Head Pressure (Hp)
Hp = 4 bar
= 40.4 m
iii. Head Velocity (Hv)
Hv = 0 m (the velocity in the suction and discharge has the same value)
iv. Head Losses (Hl)
iv.1 Suction
n = kinematic viscocity
n = 0.0007
dH = Inside diameter
= 1.278 inches
= 0.032461 m
v = fluid velocity
= 0.6 m/s
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (24)
= (0.6*0.03246)/0.0007
= 27.82286 (laminer)
for the friction losses (f) = 64/Rn
= 33.25902
The length of pipe in suction is 2 m
major losses (hf1) = . . . . . . . . . (25)
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
m2/s (700 cSt at 500C)
f x L x v2 / (D x 2g)
Page 63 of 110
= 33.259*2*0.6^2/(0.03246*2*9.8)
= 37.638915 m
minor losses (hl1)
Project
Doc. No
Rev.No
Type
No Types n k nxk
1 3 0.9 2.7
2 3 way valve 1 0.14 0.14
3 Buttterfly valve 2 0.6 1.2
5 T-joint 1 1.8 1.8
total 5.84
minnor losses (hl1) = k total*v2/(2g) . . . . . . (26)
= 5.84*(0.6^2)/(2*9.8)
= 0.107 m
iv.2 Discharge
n = kinematic viscocity
n = 0.0007
dH = Inside diameter
= 1.278 inches
= 0.032461 m
v = fluid velocity
= 0.6 m/s
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (27)
= (0.6*0.03246)/0.0007
= 27.82286 (laminer)
for the friction losses (f) = 64/Rn
= 3.324848
The length of pipe in discharge is 1.5 m
major losses (hf2) = . . . . . . . . . (28)
= 3.325*1.5*0.6^2/(0.03246*2*9.8)
= 2.8221547 m
minor losses (hl2)
No Types n k nxk
1 1 0.9 0.9
2 SDRNV 1 2 2
3 T-joint 2 1.8 3.6
4 Buttterfly valve 1 0.19 0.19
total 6.69
minnor losses (hl2) = k total*v2/(2g) . . . . . . (29)
= 6.69*(0.6^2)/(2*9.8)
= 0.123 m
Therefore, the total head losses can be calculate:
hf1+hl1+hf2+hl2 = 37.64+0.107+2.822+0.123
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Elbow 900
m2/s (700 cSt at 500C)
f x L x v2 / (D x 2g)
Elbow 900
Page 64 of 110
= 40.69 m
Total Head
Hs+Hp+Hv+Hl = 1.1+40.4+0+40.7
= 82.2 m
d. Pump Selection
Merk = Allweiler
Type = SPF 40-38
Capacity = 27.8 L/minute
Project
Doc. No
Rev.No
Type
= 1.67
Tekanan = 5 bar
RPM = 1450 rpm
Power = 0.37 kW
1.10 HFO Circulating Pump
a. Capacity
According to Project Guide Man B&W the value of capacity is
= 3.7
= 0.0010278
= 61.666667 L/minute
b. Pump Diameter
For external pipe connections, we prescribe the following maximum velocities:
Marine diesel oil = 1.0 m/s
Heavy fuel oil = 0.6 m/s
Lubricaring oil = 1.8 m/s
Cooiling water = 3.0 m/s
For the following formula:
Q = A x v . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (23)
where,
Q = Capacity
A = Area of Pipe that will be convert to diameter formula
v = flow velocity
for the result:
Q = A x v
0.00103 = (1/4 x π x D²) x 0.6
0.00103 = (1/4*3.14* D²)*0.6
= 0.00103/(0.25*3.14*0.6)
= 0.002187 m
D = 0.04676 m
= 46.76362 mm
= 1.841088 inches
The pipe selection from ANSI, carbon steel with:
Inside diameter = 1.939 inches
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
m3/h
m3/h
m3/s
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities, that:
D2
Page 65 of 110
Thickness = 0.218 inches
Outside diameter = 2.375 inches
Nominal pipe size = 2 inches
Minimum thickness = 2 mm= 0.079 inches
Table 1.7.1 Minimum wall thickness
Project
Doc. No
Rev.No
Type
c. Head Pump
i. Head Static (Hs)
height at z=0 to higer the discharge = 0.4 m
height at z=0 to the lower suction = 0 m
Therefore, the value of Hs will be determined below:
Hs = 0.4+0
= 0.4 m
ii. Head Pressure (Hp)
Hp = 6 bar
= 61 m
iii. Head Velocity (Hv)
Hv = 0 m (the velocity in the suction and discharge has the same value)
iv. Head Losses (Hl)
iv.1 Suction
n = kinematic viscocity
(According to table 1.7.1 Minimum wall thickness)
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Page 66 of 110
n = 0.0007
dH = Inside diameter
= 1.939 inches
= 0.049251 m
v = fluid velocity
= 0.6 m/s
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . .
= (0.6*0.04925)/0.0007
= 42.21429 (laminer)
for the friction losses (f) = 64/Rn
= 33.25902
The length of pipe in suction is 3 m
major losses (hf1) = . . . . . . . . .
= 33.259*3*0.6^2/(0.04925*2*9.8)
= 37.21094 m
Project
Doc. No
Rev.No
Type
minor losses (hl1)
No Types n k nxk
1 2 0.9 1.8
2 SDRNV 1 2 2
3 Buttterfly valve 1 0.19 0.19
total 3.99
minnor losses (hl1) = k total*v2/(2g) . . . . . .
= 3.99*(0.6^2)/(2*9.8)
= 0.073 m
iv.2 Discharge
n = kinematic viscocity
n = 0.0007
dH = Inside diameter
= 1.939 inches
= 0.049251 m
v = fluid velocity
= 0.0007 m/s
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . .
= (0.6*0.04952)/0.0007
= 42.44571 (laminer)
for the friction losses (f) = 64/Rn
= 3.324848
m2/s (700 cSt at 500C)
f x L x v2 / (D x 2g)
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Elbow 900
m2/s (700 cSt at 500C)
Page 67 of 110
The length of pipe in discharge is 8.7 m
major losses (hf2) = . . . . . . . . .
= 3.325*8.7*0.6^2/(0.04952*2*9.8)
= 10.72943 m
minor losses (hl2)
No Types n k nxk
1 3 0.9 2.7
2 SDRNV 1 2 2
3 Filter 1 0.58 0.58
4 Safety Valve 1 2.5 2.5
5 T-joint 1 1.8 1.8
6 Buttterfly valve 3 0.19 0.57
total 10.15
minnor losses (hl2) = k total*v2/(2g) . . . . . .
= 10.15*(0.6^2)/(2*9.8)
= 0.186 m
Therefore, the total head losses can be calculate:
hf1+hl1+hf2+hl2 = 32.21+0.073+10.7294+0.186
= 43 m
Total Head
Hs+Hp+Hv+Hl = 0.4+61+43
= 104.4 m
Project
Doc. No
Rev.No
Type
d. Pump Selection
Merk = Allweiler
Type = SPF 40-38
Capacity = 67.2 L/Minute
= 4.032
Tekanan = 10 bar
RPM = 3400 rpm
Power = 1.6 kW
2. MARINE DIESEL OIL (MDO)
2.1 MDO's weight
Estimating, approximately 10-20% from HFO's weight
= 20%*136.45 . . . . . . . . . . . . . . . . . . . . . . . . . . . . (30)
= 27.3 tonnes
2.2 Storage Tank Volume
ρDO = 0.85
and for the MDO's volume
= 32.1
f x L x v2 / (D x 2g)
Elbow 900
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
m3/h
WMDO
ton/m3
VMDO m3
Page 68 of 110
2.3 Service Tank Volume
= {(SFOC x BHP)/ρ} x T x (1 + 0.02) . . . . . . . . . . . . . . . . . . (31)
where,
t = 8 hours (time of used)
margin = 2%
ρ DO = 850
for the result:
= {(SFOC x BHP)/ρ} x T x (1 + 0.02)
= ((0.173*6320)/850)*8*1.02
= 10.5
2.4 MDO Feed Pump
a. Capacity
The estimation transfer from storage tank to service tank is 0.5 hours.
Q = V/t . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (32)
= 10.5/(0.5*3600)
= 0.0058333
= 21
b. Pump Diameter
For external pipe connections, we prescribe the following maximum velocities:
Marine diesel oil = 1.0 m/s
Heavy fuel oil = 0.6 m/s
Lubricaring oil = 1.8 m/s
Cooiling water = 3.0 m/s
For the following formula:
Q = A x v . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (33)
where,
Q = Capacity
A = Area of Pipe that will be convert to diameter formula
Project
Doc. No
Rev.No
Type
v = flow velocity
for the result:
Q = A x v
0.005833 = (1/4 x π x D²) x 1
0.005833 = (1/4*3.14* D²)*1
= 0.005833/(0.25*3.14*1)
= 0.007431 m
D = 0.08620 m
= 86.20077 mm
= 3.393731 inches
The pipe selection from ANSI, carbon steel with:
Inside diameter = 3.548 inches
Vsrv
kg/m3
Vsrv
m3
m3/s
m3/h
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities, that:
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
D2
Page 69 of 110
Thickness = 0.226 inches
Outside diameter = 4 inches
Nominal pipe size = 3.5 inches
Minimum thickness = 2.6 mm= 0.102 inches
Table 1.7.1 Minimum wall thickness
c. Head Pump
i. Head Static (Hs)
height at z=0 to higer the discharge = 1 m
height at z=0 to the lower suction = 0.5 m
Therefore, the value of Hs will be determined below:
Hs = 1+0.5
= 1.5 m
ii. Head Pressure (Hp)
Hp = 0 bar
iii. Head Velocity (Hv)
Hv = 0 m (the velocity in the suction and discharge has the same value)
iv. Head Losses (Hl)
iv.1 Suction
n = kinematic viscocity
n = 0.0007
Project
Doc. No
Rev.No
Type
dH = Inside diameter
= 3.548 inches
= 0.090119 m
v = fluid velocity
= 1 m/s
Reynold number (Rn)
(According to table 1.7.1 Minimum wall thickness)
m2/s (700 cSt at 500C)
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Page 70 of 110
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (34)
= (1*0.09012)/0.0007
= 128.7429 (laminer)
for the friction losses (f) = 64/Rn
= 0.497114
The length of pipe in suction is 2.5 m
major losses (hf1) = . . . . . . . . . (35)
= 0.49711*2.5*1^2/(0.09012*2*9.8)
= 0.4063578 m
minor losses (hl1)
No Types n k nxk
1 2 0.9 1.8
2 Filter 1 0.58 0.58
3 Buttterfly valve 2 0.19 0.38
5 T-joint 1 1.8 1.8
total 4.56
minnor losses (hl1) = k total*v2/(2g) . . . . . . (36)
= 4.56*(1^2)/(2*9.8)
= 0.233 m
iv.2 Discharge
n = kinematic viscocity
n = 0.0007
dH = Inside diameter
= 3.548 inches
= 0.090119 m
v = fluid velocity
= 1 m/s
Reynold number (Rn)
according to formula below:
Rn = (v*dH)/n . . . . . . . . . . . . . . . . . . . . . . . . . (37)
= (1*0.09012)/0.0007
= 128.7429 (laminer)
for the friction losses (f) = 64/Rn
= 0.497114
The length of pipe in discharge is 14 m
major losses (hf2) = . . . . . . . . . (38)
= 0.49711*14*1^2/(0.09012*2*9.8)
= 3.940064 m
Project
Doc. No
Rev.No
Type
minor losses (hl2)
f x L x v2 / (D x 2g)
Elbow 900
m2/s (700 cSt at 500C)
f x L x v2 / (D x 2g)
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Page 71 of 110
No Types n k nxk
1 2 0.9 1.8
2 T-joint 2 1.8 3.6
3 SDRNV 1 2 2
4 Safety valve 1 2.5 2.5
5 Buttterfly valve 3 0.19 0.57
total 10.47
minnor losses (hl2) = k total*v2/(2g) . . . . . . (39)
= 10.47*(1^2)/(2*9.8)
= 0.534 m
Therefore, the total head losses can be calculate:
hf1+hl1+hf2+hl2 = 0.406+0.233+3.94+0.534
= 5.113 m
Total Head
Hs+Hp+Hv+Hl = 1.5+0+0+5.11
= 6.61 m
d. Pump Selection
Merk = IRON PUMP
Type = ON-V:8
Capacity = 21
Head = 20 m
RPM = 950 rpm
Power = 3.4 HP = 2.5 kW
3. SEPARATOR
Q(l/h) = (P x SFOC x 24)/(991 x 23.5) . . . . . . . . . . . . . . . . . . . . . . (40)
= (6320*173*24)/(991*23.5)
= 1126.764 L/h
Volume = 1.8
Head = 2-6 bar
4. HEATER POWER FOR FEED PUMP
P[kW] = Q(l/h) x Δt ('C) / 1700 . . . . . . . . . . . . . . . . . . . . . . . . . (41)
where,
Q = capacity of separator feed pump
= 711.39 L/h
t = temperature rise in heater
= 48
for the result:
P[kW] = Q(l/h) x Δt ('C) / 1700
= 711.39*48/1700
= 20.09 kW
To be choosen, the electric heater:
MERK = AALBORG
Type = 20
kW = 24 kW
Project
Elbow 900
m3/h
m3
oC
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
Page 72 of 110
Doc. No
Rev.No
Type
5. HEATER POWER FOR CIRCULATING PUMP
P[kW] = Q(l/h) x Δt ('C) / 1700 . . . . . . . . . . . . . . . . . . . . . . . . . (42)
where,
Q = capacity of separator feed pump
= 173*6320
= 1093360 gr/h
= 1103.2896 L/h
t = temperature rise in heater
= 48
for the result:
P[kW] = Q(l/h) x Δt ('C) / 1700
= 1103.29*48/1700
= 31 kW
To be choosen, the electric heater:
MERK = AALBORG
Type = 25
kW = 33 kW
TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM
oC
Page 73 of 110
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
The addition of fuel volume by 4% due to expansion by temperature (Ship Design and Construction)
C and to increases to 500C
Page 74 of 110
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
For external pipe connections, we prescribe the following maximum velocities:
C and to increases to 500C
Time estimation were planned one hour for the HFO transfer pump to delivered from storage to
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities,
Page 75 of 110
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
Table 1.7.1 Minimum wall thickness
(the pressure in the suction and discharge has the same value)
(According to table 1.7.1 Minimum wall thickness)
Page 76 of 110
(the velocity in the suction and discharge has the same value)
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
Page 77 of 110
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
Time estimation were planned 1 hours for the HFO feed pump to delivered from settling tank to
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities,
Page 78 of 110
For external pipe connections, we prescribe the following maximum velocities:
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
Table 1.7.1 Minimum wall thickness
(According to table 1.7.1 Minimum wall thickness)
Page 79 of 110
(the pressure in the suction and discharge has the same value)
(the velocity in the suction and discharge has the same value)
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
Page 80 of 110
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
Page 81 of 110
For external pipe connections, we prescribe the following maximum velocities:
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities,
(According to table 1.7.1 Minimum wall thickness)
Page 82 of 110
: Attachment No. 01
Table 1.7.1 Minimum wall thickness
(the velocity in the suction and discharge has the same value)
Page 83 of 110
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
Page 84 of 110
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
For external pipe connections, we prescribe the following maximum velocities:
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities,
Page 85 of 110
Table 1.7.1 Minimum wall thickness
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
(the velocity in the suction and discharge has the same value)
(According to table 1.7.1 Minimum wall thickness)
Page 86 of 110
(24)
(25)
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
(26)
(27)
Page 87 of 110
(28)
(29)
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
Page 88 of 110
For external pipe connections, we prescribe the following maximum velocities:
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities,
Page 89 of 110
Table 1.7.1 Minimum wall thickness
(the velocity in the suction and discharge has the same value)
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
(According to table 1.7.1 Minimum wall thickness)
Page 90 of 110
: DESIGN IV
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
Page 91 of 110
: DESIGN IV
Page 92 of 110
: 15 - 42 09 050 - FO
: 01
: Attachment No. 01
DESIGN-IV: MACHINERY BASIC DESIGN
ATTACHMENT NO. 02 IRON PUMP SPECIFICATION TECHNICAL SPECIFICATION OF FUEL
OIL SYSTEM
ATTACHMENT NO. 02 IRON PUMP SPECIFICATION TECHNICAL SPECIFICATION OF FUEL
OIL SYSTEM
DESIGN-IV: MACHINERY BASIC DESIGN
ATTACHMENT NO. 02 IRON PUMP SPECIFICATION TECHNICAL SPECIFICATION OF FUEL
ATTACHMENT NO. 02 IRON PUMP SPECIFICATION TECHNICAL SPECIFICATION OF FUEL
DESIGN-IV: MACHINERY BASIC DESIGN
ATTACHMENT NO. 03 ALWEILLER PUMP SPECIFICATION TECHNICAL SPECIFICATION OF
FUEL OIL SYSTEM
ATTACHMENT NO. 03 ALWEILLER PUMP SPECIFICATION TECHNICAL SPECIFICATION OF
FUEL OIL SYSTEM
DESIGN-IV: MACHINERY BASIC DESIGN
ATTACHMENT NO. 03 ALWEILLER PUMP SPECIFICATION TECHNICAL SPECIFICATION OF
ATTACHMENT NO. 03 ALWEILLER PUMP SPECIFICATION TECHNICAL SPECIFICATION OF
DESIGN-IV: MACHINERY BASIC DESIGN
ATTACHMENT NO. 04 ELECTRIC HEATER AALBORG SPECIFICATION TECHNICAL SPECIFICATION OF
FUEL OIL SYSTEM
ATTACHMENT NO. 04 ELECTRIC HEATER AALBORG SPECIFICATION TECHNICAL SPECIFICATION OF
FUEL OIL SYSTEM
DESIGN-IV: MACHINERY BASIC DESIGN
ATTACHMENT NO. 04 ELECTRIC HEATER AALBORG SPECIFICATION TECHNICAL SPECIFICATION OF
ATTACHMENT NO. 04 ELECTRIC HEATER AALBORG SPECIFICATION TECHNICAL SPECIFICATION OF