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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. Gusti N. Dirgantar 01 04/4/12 Document Format REV. DATE DESCRIPTION PREPARED BY CHECKED BY APPR DESIGN-IV: MACHINERY BASIC DESIGN DESIGN-IV: MACHINERY BASIC DESIGN TECHNICAL SPECIFICATION OF FU SYSTEM Ir. Dwi Priyanta, MSE. Ir. Prastow
Transcript
Page 1: Doc. No. 15 - 42 09 050 - FO

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

Page 2: Doc. No. 15 - 42 09 050 - FO

DESIGN-IV: MACHINERY BASIC DESIGN

Page 3: Doc. No. 15 - 42 09 050 - FO

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

Page 4: Doc. No. 15 - 42 09 050 - FO

DESIGN-IV: MACHINERY BASIC DESIGN

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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

Page 6: Doc. No. 15 - 42 09 050 - FO

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

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: DESIGN IV

: 15 - 42 09 050 - FO

: 02

: Table of Contents

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3

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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

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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

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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:

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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

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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

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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

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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)

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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

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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

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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:

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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

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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)

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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)

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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

Project : DESIGN IV

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

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1. Butterfly Valve

Figure 5.3 Butterfly Valve

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Doc. No : 15 - 42 09 050 - FO

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.

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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.

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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

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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.

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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

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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

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- 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

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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

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Project : DESIGN IV

Doc. No : 15 - 42 09 050 - FO

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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

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: Philosophy

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

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: DESIGN IV

: 15 - 42 09 050 - FO

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: Philosophy

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The addition of fuel volume by 4% due to expansion by temperature (Ship Design and Construction)

: DESIGN IV

: 15 - 42 09 050 - FO

: 02

: 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

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: DESIGN IV

: 15 - 42 09 050 - FO

: 02

: 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

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: DESIGN IV

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: Philosophy

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For external pipe connections, we prescribe the following maximum velocities:

: DESIGN IV

: 15 - 42 09 050 - FO

: 02

: 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)

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(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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Table 1.7.1 Minimum wall thickness

Flow velocity that determined by Engine Selection Guide Man B&W, page 198 29 00, Flow velocities,

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(the velocity in the suction and discharge has the same value)

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: 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

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: 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

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: DESIGN IV

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: Philosophy

(the velocity in the suction and discharge has the same value)

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: DESIGN IV

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: 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

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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.

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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

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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

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DESIGN-IV: MACHINERY BASIC DESIGN

ATTACHMENT NO. 01 CALCULATION

TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM

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ATTACHMENT NO. 01 CALCULATION

TECHNICAL SPECIFICATION OF FUEL OIL SYSTEM

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DESIGN-IV: MACHINERY BASIC DESIGN

ATTACHMENT NO. 01 CALCULATION

TECHNICAL SPECIFICATION OF FUEL OIL

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ATTACHMENT NO. 01 CALCULATION

TECHNICAL SPECIFICATION OF FUEL OIL

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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

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= (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:

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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)

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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)

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= (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:

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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

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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

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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

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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

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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)

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= 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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

Page 80 of 110

: DESIGN IV

: 15 - 42 09 050 - FO

: 01

: Attachment No. 01

Page 81: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

Page 83 of 110

: DESIGN IV

: 15 - 42 09 050 - FO

: 01

: Attachment No. 01

Page 84: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

Page 86 of 110

(24)

(25)

: DESIGN IV

: 15 - 42 09 050 - FO

: 01

: Attachment No. 01

(26)

(27)

Page 87: Doc. No. 15 - 42 09 050 - FO

Page 87 of 110

(28)

(29)

: DESIGN IV

: 15 - 42 09 050 - FO

: 01

: Attachment No. 01

Page 88: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

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: Doc. No. 15 - 42 09 050 - FO

Page 90 of 110

: DESIGN IV

: 15 - 42 09 050 - FO

: 01

: Attachment No. 01

Page 91: Doc. No. 15 - 42 09 050 - FO

Page 91 of 110

: DESIGN IV

Page 92: Doc. No. 15 - 42 09 050 - FO

Page 92 of 110

: 15 - 42 09 050 - FO

: 01

: Attachment No. 01

Page 93: Doc. No. 15 - 42 09 050 - FO

DESIGN-IV: MACHINERY BASIC DESIGN

ATTACHMENT NO. 02 IRON PUMP SPECIFICATION TECHNICAL SPECIFICATION OF FUEL

OIL SYSTEM

Page 94: Doc. No. 15 - 42 09 050 - FO

ATTACHMENT NO. 02 IRON PUMP SPECIFICATION TECHNICAL SPECIFICATION OF FUEL

OIL SYSTEM

Page 95: Doc. No. 15 - 42 09 050 - FO

DESIGN-IV: MACHINERY BASIC DESIGN

ATTACHMENT NO. 02 IRON PUMP SPECIFICATION TECHNICAL SPECIFICATION OF FUEL

Page 96: Doc. No. 15 - 42 09 050 - FO

ATTACHMENT NO. 02 IRON PUMP SPECIFICATION TECHNICAL SPECIFICATION OF FUEL

Page 97: Doc. No. 15 - 42 09 050 - FO

DESIGN-IV: MACHINERY BASIC DESIGN

ATTACHMENT NO. 03 ALWEILLER PUMP SPECIFICATION TECHNICAL SPECIFICATION OF

FUEL OIL SYSTEM

Page 98: Doc. No. 15 - 42 09 050 - FO

ATTACHMENT NO. 03 ALWEILLER PUMP SPECIFICATION TECHNICAL SPECIFICATION OF

FUEL OIL SYSTEM

Page 99: Doc. No. 15 - 42 09 050 - FO

DESIGN-IV: MACHINERY BASIC DESIGN

ATTACHMENT NO. 03 ALWEILLER PUMP SPECIFICATION TECHNICAL SPECIFICATION OF

Page 100: Doc. No. 15 - 42 09 050 - FO

ATTACHMENT NO. 03 ALWEILLER PUMP SPECIFICATION TECHNICAL SPECIFICATION OF

Page 101: Doc. No. 15 - 42 09 050 - FO

DESIGN-IV: MACHINERY BASIC DESIGN

ATTACHMENT NO. 04 ELECTRIC HEATER AALBORG SPECIFICATION TECHNICAL SPECIFICATION OF

FUEL OIL SYSTEM

Page 102: Doc. No. 15 - 42 09 050 - FO

ATTACHMENT NO. 04 ELECTRIC HEATER AALBORG SPECIFICATION TECHNICAL SPECIFICATION OF

FUEL OIL SYSTEM

Page 103: Doc. No. 15 - 42 09 050 - FO

DESIGN-IV: MACHINERY BASIC DESIGN

ATTACHMENT NO. 04 ELECTRIC HEATER AALBORG SPECIFICATION TECHNICAL SPECIFICATION OF

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ATTACHMENT NO. 04 ELECTRIC HEATER AALBORG SPECIFICATION TECHNICAL SPECIFICATION OF

Page 105: Doc. No. 15 - 42 09 050 - FO
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