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DESIGN-IV: MACHINERY BASIC DESIGN

TECHNICAL SPECIFICATION OF

ENGINE COOLING SYSTEM

ATTACHMENT NO. 01 02 - - -

NUMBER OF PAGES 11 4 - -


DOCUMENT NO. DOC. NO. 17 - 42 09 050 - CO

Ir. Dwi Priyanta,

MSE.

Ir. Hari Prastowo,

MSc.01 10/5/12 Categorizing Eq.I Gusti N. Dirgantara

APPROVED BYREV. DATE DESCRIPTION PREPARED BY CHECKED BY

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TABLE OF CONTENTS

PHILOSOPHY

1. INTRODUCTION . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1

1.1 Description 1

1.2 Purpose 1

2. REFERENCES 1

3. ABBREVIATIONS 1

4. DESIGN PARAMETER 2

4.1 Engine Selection Guide Requirement 2

5. DESIGN REQUREMENTS 2

5.1 Seawater Cooling Pump 2

5.2 Central Cooling Water Pump 3

5.3 Jacket Water Cooler Pump 4

5.4 Central Cooler . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 55.5 Jacket Water Cooler 5

5.6 Lubricating Oil Cooler 6

5.7 Valve and Fitting 6

5.6 Class Requirement 7

6. SUMMARY . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 8

ATTACHMENT NO. 01 - CALCULATION

1. Seawater Cooling Pump 1

2. Central Cooling Water Pump 1

3. Jacket Water Cooler Pump 1

4. Central Cooler 5

5. Jacket Water Cooler 86. Lubricating Oil Cooler . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 8

LIST OF TABLE

Table 1 Minimum wall thickness 1

ATTACHMENT NO. 02 - PUMP SPECIFICATION


ENGINE COOLING SYSTEMS

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1. INTRODUCTION

1.1 Description

1.2 Objective

This document purpose is to determine the technical specification of engine cooling system.

2. REFERENCES

a. Germanischer Lloyd Rules and Guidelines 2011

b. Engine Selection Guide - Two Stroke MC/MC-C Engines, 6th Edition: January 2002, MAN B&W

3. ABBREVIATION

SLOC = Specific lubricating oil consumption [gr/BHP]

c = constant addition of fuel (1.3)

Q = Capacity

A = Area of Pipe that will be convert to diameter formulav = 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

hl = head lossesH = head total

H = heat dissipation aprox.

K = heat transfer coef.

The water cooling can be arranged in several configurations, the most common system choicebeing a low water temperature cooling system only for jacket cooling and a central cooling

water system with three circuit, a seawater system, a low temperature freshwater system for

central cooling and high temperature freshwater system for jacket water.

The advantages of the seawater cooling system are only to set of cooling water pumps (seawater

and jacket water) and simple installation with few piping system. The advantages are seawater

to all coolers and thereby higher maintenance cost and expensive seawater piping of non-

corrosive materials such as galvanised steel pipes or Cu-Ni pipes.

The advantages of the central cooling system are only one heat exchanger cooled by seawater,

only one exchanger to be overhauled, all other heat exchanger are freshwater cooled and can be

made of a less expensive material, few non-corrosive pipe to be installed, reduced maintenance

of cooler and components, increase heat utilisation. The advantages are three sets of cooling

water pumps (seawater, freshwater low temperature, and jacket water high temperature),

higher first cost.



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4. DESIGN PARAMETER

4.1 Engine Selection Guide Requirement

5. DESIGN REQUIREMENT

5.1 SEAWATER COOLING PUMP

D = (4 x Q/ x v) (1)

where,

D = Diameter of seawater cooling pump

Q = Capacity of seawater cooling pump according to engine selection guide 06.01.04

= m3/h

= m3/s

v = water velocities according to the engine selection guide 06.07.01

= m/s

Head Pump

i. Head Static (Hs)

height at z=0 to higer the discharge

height at z=0 to the lower suction

Therefore, the value of Hs will be determined below:

ii. Head Pressure (Hp)

Hp = 2.5 bar (engine selection guide requirements)

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 = m2/s (at 50

0C)

v = fluid velocity

= m/s

Reynold number (Rn)

according to formula below:

Rn = (v*dH)/n (2)

l = 0.02+0.0005/dH (3)

Mayor losses (hf)

hf = l*L*v2/(D*2g) (4)

where,

L = the length of suction pipe

= 5.5 m

Minnor losses (hl)

head losses = k total*v2/(2g) . . . . . . . . . . . . . . . . . . . . . . (5)

= 10.31*(3^2)/(2*9.8)

= m

The central cooling system is characterised by having only one heat exchanger cooled by seawater, and by the other coolers, including the jacket water cooler, being cooled by the

freshwater low temperature (FW-LT) system. In order to prevent too high a scavenge air

temperature, the cooling water design temperature in the FW-LT system is normally 360

corresponding to a maximum seawater temperature of 320C. For external pipe connections , we

prescribe the following maximum water velocities, jacket water, central cooling water (FW-LT)

and seawater each velocity is 3.0 m/s

190

0.05278

3



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0.00000105

4.734

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iv.2 Discharge


n = m

2

/s (at 50

0

C)v = fluid velocity

= m/s

Reynold number (Rn)


Rn = (v*dH)/n (6)

l = 0.02+0.0005/dH (7)

Mayor losses (hf)

hf = l*L*v2/(D*2g) (8)

where,


= 12 m

Minnor losses (hl)head losses = k total*v2/(2g) . . . . . . . . . . . . . . . . . . . . . . (9)

Therefore, the total of Heads are:

H = hs+hv+hp+hf1+hf2+hl1+hl2+pressure drop

5.2 CENTRAL COOLING WATER PUMP

D = (4 x Q/ x v) (10)

where,



= m3/h

= m3/s

v = water velocities according to the engine selection guide 06.07.01= m/s

Head Pump

i. Head Static (Hs)

height at z=0 to higer the discharge





= 25 m




iv.1 Suction


n = m2/s (at 50

0C)

v = fluid velocity

= m/s

Reynold number (Rn)


Rn = (v*dH)/n (11)

l = 0.02+0.0005/dH (12)



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0.00000105

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0.00000105

170

0.04722

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= 0.02+0.0005/0.14633

=

Mayor losses (hf)hf = l*L*v

2/(D*2g) (13)

where,


= 6.2 m

Minnor losses (hl)


iv.2 Discharge


n = m2/s (at 50

0C)

v = fluid velocity

= m/s

Reynold number (Rn)according to formula below:

Rn = (v*dH)/n (15)

l = 0.02+0.0005/dH (16)

Mayor losses (hf)

hf = l*L*v2/(D*2g) (17)

where,


= 4.8 m

Minnor losses (hl)




5.3 JACKET WATER COOLER PUMP

D = (4 x Q/ x v) (19)

where,



= m3/h

= m3/s


= m/s

Head Pump

i. Head Static (Hs)height at z=0 to higer the discharge





= 25 m






3

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0.00000105

0.023

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iv.1 Suction


n = m

2

/s (at 50

0

C)v = fluid velocity

= m/s

Reynold number (Rn)


Rn = (v*dH)/n (20)

l = 0.02+0.0005/dH (21)

Mayor losses (hf)

The following formula (8), as follow:

hf = l*L*v2/(D*2g) (22)

Minnor losses (hl)


iv.2 Dischargen = kinematic viscocity

n = m2/s (at 50

0C)

v = fluid velocity

= m/s

Reynold number (Rn)


Rn = (v*dH)/n (24)

l = 0.02+0.0005/dH (25)

Mayor losses (hf)

hf = l*L*v2/(D*2g) (26)


Therefore, the total of Heads are:H = hs+hv+hp+hf1+hf2+hl1+hl2+pressure drop

5.4 CENTRAL COOLER

Heat dissipation aprox. (H) = kW

= kcal/h

Heat transfer coef. (K) = kcal/m2.h.

0C

Sea water quantity (Qsw) = m3/h

Central cooling water quantity (Qlo) = m3/h

Fresh water density = kg/m3

Sea water density = kg/m3

Heat spec. LO (Clo) = Btu/lb0F

= kcal/kg0C

Heat spec. Sea Water (Csw) = Btu/lb0F

= kcal/kg0C

Outlet temperature (T2) =0C

Sea water inlet temperature (t1) =0C

5.5 JACKET WATER COOLER


= kcal/h

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0.00000105

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3

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1000

190

170

1000

1025

32

920

1

1

0.94

0.94

36

791058

3890

3344798

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0C

Central cooling water quantity (Qsw) = m3/h

Jacket cooling water quantity (Qlo) = m3/h

Jacket water density = kg/m3


Heat spec. jacket water (Clo) = Btu/lb0F

= kcal/kg0C

Heat spec. fresh water (Csw) = Btu/lb0F

= kcal/kg0C

Jacket water outlet temperature (T2 =0C

Fresh water inlet temperature (t1) =0C

5.6 LUBRICATING OIL COOLER

Heat dissipation aprox. (H) = kW= kcal/h


0C

Central cooling water quantity (Qsw) = m3/h

Lubricating oil quantity (Qlo) = m3/h

Lubricating oil density = kg/m3


Heat spec.LO (Clo) = Btu/lb0F

= kcal/kg0C

Heat spec.sea water (Csw) = Btu/lb0F

= kcal/kg0C

LO outlet temperature (T2) = 0C


5.7 VALVE AND FITTING

a. Valve

1. Butterfly Valve



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45

32

135

920

1000

0.43

0.43

1

1

920791058

480

67

80

42

1025

1

1

0.94

0.94

1000

67

53

1000

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.

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2. Non Return Valve

b. Fitting

Filter

The type used : Water Filter

- Sea Chest Strainer

- Fresh Water System Filter

5.8 CLASS REQUIREMENT

Germanishcer Lloyd 2012, Chapter 2, Setion 11, Page 11-32

a. General

- a single cooling circuit for the entire plant

- separate cooling circuits for the main and auxiliary plant

-

- separate cooling circuits for various temperature ranges

Fresh water cooling system are to be so arranged that the engines can be sufficiently cooled

under all operating conditions. Depending on the requirements of the engine plant, the

following fresh water cooling systems are allowed:

several independent cooling circuits for the main engine components which need

cooling (e.g. cylinders, piston and fuel valves) and for the auxiliary engines

Common engine cooling water systems for main and auxiliary plants are to be fitted with

shut-off valves to enable repairs to be performed without taking the entire plant out of

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 not back through the same line or just one-way direction.

The sea water and fresh water systems on board ship are provided with line filters in order

to trap the solid impurities flowing in the system. Normally the sea water sides has more

number of filters incorporated in the line as compared to the fresh water system as the

later is a closed system. The different applications for water filters are:

It is fitted in the main suction line of the sea water inlet system to the ship. The filteris casing normally fitted with marine growth preventive system. Normally a strainer is

used in the sea chest so that the flow of water in the sea line is always maintained.

All the fresh water system such as drinking water system, sanitary water system, boiler

feed water system etc. are incorporated with a line filter in the suction side of the



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b. Heat Exchangers, Coolers

c. Expansion Tanks

d. Fress Water Cooling Pumps

e. Temperature Control

6. SUMMARY

NO

1

2

3

For the pump selection and spesification:

=

=

=

=

=

=

To reach the required head, we need to make a two pump with series.

NO

1

2

3

Head Total H 42.16492 m

Capacity Q 190 m3/h

6.1 SEAWATER COOLING PUMP

CALCULATION SYMBOL

Capacity Q 170 m3/h

Inside diameter D 5.8 inches


Power 22 kW

6.2 CENTRAL COOLING WATER PUMP

CALCULATION SYMBOL RESULT

Head 25 m

Rpm 1800 RPM

Merk Taiko

Type EHC-201C

Qapacity 190 m3/h

RESULT


The coolers of cooling water systems, engines and equipment are to be so designed to

ensure that the specified cooling water temperatures can be maintained under all operatingconditions. Cooling water temperatures are to be adjusted to meet the requirements of

engines and equipment. Shut-off valves are to be provided at the inlet and outlet of all heat

exchangers. Every heat exchanger and cooler is to be provided with a vent and a drain.

Expansion tanks are to be arranged at sufficient height for every cooling water circuit.

Different cooling circuits may only be connected to a common expansion tank if they do not

interfece with each other. Care is to be taken here to ensure that damage to or faults in

one system cannot affect the other system. Expansion tanks are to be fitted with filling

connections, aeration/de-aeration devices, water level indicators and drains.

Main and stand-by cooling water pumps are to be provided for each fresh water cooling

system. Main cooling water pumps may be driven directly by the main or auxiliary engines

which they are intended to cool provided that a sufficient supply of cooling water is assured

under all operating conditions. The drives of stand-by cooling water pumps are to be

independent of the engines. Stand-by cooling water pumps are to have the same capacity as

main cooling water pumps. Main engines are to be fitted with at leat one main and one

stand-by cooling water pump. Where according to the construction of the engines more than

one water cooling circuit is necessary, a stand-by pump is to be fitted for each main cooling

water pump.

Cooling water circuits are to be provided with temperature controls in accordance with the

requirements. Control devices whose failure may impair the functional reliability of the

engine are to be equipped for manual operation.



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=

==

=

=

=

NO

1

2

3


==

=

=

=

=

6.4 CENTRAL COOLER

NO

1

2

3

4

6.5 JACKET WATER COOLER

NO

1

2

3

4

6.6 LUBRICATING OIL COOLER

NO

12

3

4

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Area A 50 m2



FW outlet temperature t2 43.80683oC

LMTD 33oC


LO inlet temperature T1 59.8

o

C

LMTD 91oC

Area A 9 m2

JW inlet temperature T1 94.9oC

FW outlet temperature t2 54.25410oC

Area A 311 m2


SW outlet temperature (t2) t2 50.27109oC

LMTD 11oC

RESULT

Inlet temperature (T1) T1 55.7oC

Power 15 kW

CALCULATION SYMBOL

Head 40 m

Rpm 1800 RPM

Type TMC-100D

Qapacity 55 m3/h

Capacity Q 53 m3/h

Merk Taiko



Power 37 kW

6.3 JACKET WATER COOLER PUMP


Head 42.5 bar

Rpm 1800 RPM

Type EHC-150EQapacity 170 m

3/h

Merk Taiko

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ATTACHMENT NO. 01 - CALCULATION

TECHNICAL SPECIFICATION OF ENGINE

COOLING SYSTEMS


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1. SEAWATER COOLING PUMP

D = (4 x Q/ x v) (1)

where,D = Diameter of seawater cooling pump


= m3/h

= m3/s


= m/s

for the result:

D = (4 x Q/ x v)

= ((4*0.05278)/(3.14*3))^0.5

= m

= inches

The pipe selection from ANSI, carbon steel with:Inside diameter = inches

Thickness = inches

Outside diameter = inches

Nominal pipe size = inches

Minimum thickness = 3.6 mm (According to Table 1)

= inches

Head Pump

i. Head Static (Hs)

height at z=0 to higer the discharge = m

height at z=0 to the lower suction = 0 m


Hs = 6+0

= m



= 25 m


0.142

Table 1 Minimum wall thickness



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6

6

190

0.052778

3

0.14971

5.89393

6.065

0.28

6.625

6

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iv.1 Suctionn = kinematic viscocity

n = m2/s (at 50

0C)

dH = Inside diameter

= inches

= m

v = fluid velocity

= m/s

Reynold number (Rn)


Rn = (v*dH)/n (2)

= (3*0.15405)/0.00000105

= (turbulen)

l = 0.02+0.0005/dH (3)

= 0.02+0.0005/0.15405

=

Mayor losses (hf)

The following formula, as follow:

hf = l*L*v2/(D*2g) (4)

where,


= 5.5 m

for the result according to formula:

hf = l*L*v2/(D*2g)

= 0.023*5.5*(3^2)/(0.15405*2*9.8)

= m

Minnor losses (hl)

No n

1 1

2 1

3 2

4 1

5 2


= 10.31*(3^2)/(2*9.8)

= m

iv.2 Discharge


n = m2/s (at 50

0C)


= inches

= m0.15405

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Elbow 900

0.75 0.75

total 10.31

4.734

0.00000105

6.065



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0.38

Types k nxk

Butterfly valve 0.6 0.6

T-join 2.9 5.8

Strainer

SDNRV

0.58 1.16

2 2

0.023

0.00000105

6.065

0.15405

3

. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

440143

For the frictional losses (l) will be determned if the value of reynold number

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Type

v = fluid velocity

= m/s

Reynold number (Rn)according to formula below:

Rn = (v*dH)/n (6)

= (3*0.14633)/0.00000105

= (turbulen)

l = 0.02+0.0005/dH (7)

= 0.02+0.0005/0.15405

=

Mayor losses (hf)


hf = l*L*v2/(D*2g) (8)

where,


= 12 m


hf = l*L*v2/(D*2g)

= 0.023*12*(3^2)/(0.15405*2*9.8)

= m

Minnor losses (hl)

No n

1 2

2 1

3 1

4 1


= 7*(3^2)/(2*9.8)

= m

Pressure drop in central cooler seawater side = 0.2 bar

= m



= 6+25+0+0.38+4.734+0.82+3.214+2.01692

= m

Pump Selection

Required:

Head = m

Capacity = m3/h


=

=

=



: DESIGN IV

: 17 - 42 09 050 - CO

: 0

: Attachment No. 01

Type EHC-201C

SDNRV 2

T-join 2.9

total

3.214

Qapacity 190 m3/h

2.01692

2

2.9

7

42.1649

42.16

190

Merk Taiko

3

Elbow 900

0.75 1.5


. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

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=

=

=To reach the required head, we need to make a two pump with series.

2. CENTRAL COOLING WATER PUMP

D = (4 x Q/ x v) (10)

where,



= m3/h

= m3/s


= m/s

for the result:D = (4 x Q/ x v)

= ((4*0.04722)/(3.14*3))^0.5

= m

= inches

The pipe selection from ANSI, carbon steel with:

Inside diameter = inches

Thickness = inches




= inches

Head Pump

i. Head Static (Hs)


height at z=0 to the lower suction = 0 m


: DESIGN IV

: 17 - 42 09 050 - CO

: 0

: Attachment No. 01

0.432

6.625

6

0.142


0

170

0.047222

3

0.1416

5.57485

5.761

Head 25 m

Rpm 1800 RPM



Power 22 kW

. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

Page 17 of 25

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Hs = 0+0

= m

ii. Head Pressure (Hp)Hp = 2.5 bar (engine selection guide requirements)

= 25 m




iv.1 Suction


n = m2/s (at 50

0C)


= inches

= m

v = fluid velocity

= m/s

Reynold number (Rn)


Rn = (v*dH)/n (11)

= (3*0.14633)/0.00000105

= (turbulen)

l = 0.02+0.0005/dH (12)

= 0.02+0.0005/0.14633

=

Mayor losses (hf)


hf = l*L*v2/(D*2g) (13)

where,


= 6.2 m


hf = l*L*v2/(D*2g)

= 0.023*6.2*(3^2)/(0.14633*2*9.8)

= m

Minnor losses (hl)

No n

1 4

2 1

4 1

5 3


= 14.3*(3^2)/(2*9.8)

= m



: DESIGN IV

: 17 - 42 09 050 - CO

: 0

: Attachment No. 01

. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

418086


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Type

iv.2 Discharge


n = m

2

/s (at 50

0

C)dH = Inside diameter

= inches

= m

v = fluid velocity

= m/s

Reynold number (Rn)


Rn = (v*dH)/n (15)

= (3*0.14633)/0.00000105

= (turbulen)

l = 0.02+0.0005/dH (16)

= 0.02+0.0005/0.14633

=

Mayor losses (hf)


hf = l*L*v2/(D*2g) (17)

where,


= 4.8 m


hf = l*L*v2/(D*2g)

= 0.023*4.8*(3^2)/(0.14633*2*9.8)

= m

Minnor losses (hl)

No n

1 4

2 1

3 1

4 3


= 14.3*(3^2)/(2*9.8)

= m

Pressure drop on central coolIing side = 0.2 bar

= m

Pressure drop ON seawater side = 0.2 bar

= m



= 0+25+0+0.45+4.734+0.35+6.566+2.017+2.017

= m

2.01692

Elbow 900

0.75 3


SDNRV 2 2

: Attachment No. 01

418086


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Rev.No

Type

Pump Selection

Required:

Head = m

Capacity = m

3

/hFor the pump selection and spesification:

=

=

=

=

=

=

3. JACKET WATER COOLER PUMP

D = (4 x Q/ x v) (19)

where,

D = Diameter of seawater cooling pumpQ = Capacity of seawater cooling pump according to engine selection guide 06.01.04

= m3/h

= m3/s


= m/s

for the result:

D = (4 x Q/ x v)

= ((4*0.01472)/(3.14*3))^0.5

= m

= inches

The pipe selection from ANSI, carbon steel with:

Inside diameter = inchesThickness = inches




= inches

: DESIGN IV

: 17 - 42 09 050 - CO

: 0

: Attachment No. 01

0.07906

3.1126

3.1520.674

5.563

5

0.102


Rpm 1800 RPM

Power kW

53

0.014722

3

Merk Taiko

Type EHC-150E

Qapacity 170 m3/h

Head 42.5 bar

37

170



41.13

. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

Page 20 of 25

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Rev.No

Type

Head Pump

i. Head Static (Hs)


height at z=0 to the lower suction = 0 mTherefore, the value of Hs will be determined below:

Hs = 0+0

= m



= 25 m




iv.1 Suction


n = m2/s (at 50

0C)


= inches

= m

v = fluid velocity

= m/s

Reynold number (Rn)


Rn = (v*dH)/n (20)

= (3*0.14633)/0.00000105

= (turbulen)

l = 0.02+0.0005/dH (21)

= 0.02+0.0005/0.08006

=

Mayor losses (hf)


hf = l*L*v2/(D*2g) (22)

where,


= 6 m


hf = l*L*v2/(D*2g)

= 0.026*6*(3^2)/(0.08006*2*9.8)

= m

Minnor losses (hl)

No n

1 2

2 2

4 2

5 2



: DESIGN IV

: 17 - 42 09 050 - CO

: 0

: Attachment No. 01

Elbow 900

0

0.75 1.5


Strainer

0

0.00000105

3.152

0.08006

3

. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

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= 9.66*(3^2)/(2*9.8)

= miv.2 Discharge


n = m2/s (at 50

0C)


= inches

= m

v = fluid velocity

= m/s

Reynold number (Rn)


Rn = (v*dH)/n (24)

= (3*0.08006)/0.00000105

= (turbulen)

l = 0.02+0.0005/dH (25)

= 0.02+0.0005/0.08006

=

Mayor losses (hf)


hf = l*L*v2/(D*2g) (26)

where,


= 4 m


hf = l*L*v2/(D*2g)

= 0.026*4*(3^2)/(0.08006*2*9.8)

= m

Minnor losses (hl)

No n

1 2

3 1

4 2


= 9.3*(3^2)/(2*9.8)

= m

Pressure drop on jacket water side = 0.2 bar

= m



= 0+25+0+0.89+4.436+0.6+4.27+2.01692

= m



: DESIGN IV

: 17 - 42 09 050 - CO

: 0

: Attachment No. 01

0.00000105

0.75 1.5

SDNRV 2 2

T-join

3

. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

228743


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Rev.No

Type

Pump Selection

Required:

Head = mCapacity = m

3/h


=

=

=

=

=

=

4. CENTRAL COOLER


= kcal/hHeat transfer coef. (K) = kcal/m

2.h.

0C

Sea water quantity (Qsw) = m3/h

Central cooling water quantity (Qlo) = m3/h



Heat spec. LO (Clo) = Btu/lb0F

= kcal/kg0C

Heat spec. Sea Water (Csw) = Btu/lb0F

= kcal/kg0C

Outlet temperature (T2) =0C

Inlet temperature (T1) = 0C

Sea water inlet temperature (t1) =0C

Sea water outlet temperature (t2) =0C

LMTD = [(T1-t2)-(T2-t1)]/log[(T1-t2)/(T2-t1)]

=0C

Area of central cooler (A) = H/(K x LMTD)

= 311 m2

5. JACKET WATER COOLER


= kcal/h

Heat transfer coef. (K) = kcal/m

2

.h.

0

CCentral cooling water quantity (Qsw) = m

3/h

Jacket cooling water quantity (Qlo) = m3/h

Jacket water density = kg/m3


Heat spec. jacket water (Clo) = Btu/lb0F

= kcal/kg0C

Heat spec. fresh water (Csw) = Btu/lb0F

= kcal/kg0C

: DESIGN IV

: 17 - 42 09 050 - CO

: 0

: Attachment No. 01

53

RPM

0.94

36

32

55.6753

50.2711

10.746

920

791058

Type TMC-100D

Merk Taiko

Power 15 kW

Qapacity 55 m3/h

Head 40 m

Rpm 1800

3890

1000

190

170

1000

1025

1

0.94

1

3344798

37.21



100067

53

1000

1025

1

1

0.94

0.94

Page 23 of 25

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Jacket water outlet temperature (T2) =0C

Jacket water inlet temperature (T1) =0C

Fresh water inlet temperature (t1) = 0C

Fresh water outlet temperature (t2) =0C

LMTD = [(T1-t2)-(T2-t1)]/log[(T1-t2)/(T2-t1)]

=0C

Area of jacket water cooler (A) = H/(K x LMTD)

= m2

6. LUBRICATING OIL COOLER


= kcal/h


0C

Central cooling water quantity (Qsw) =m

3/h

Lubricating oil quantity (Qlo) = m3/h

Lubricating oil density = kg/m3


Heat spec.LO (Clo) = Btu/lb0F

= kcal/kg0C

Heat spec.sea water (Csw) = Btu/lb0F

= kcal/kg0C

LO outlet temperature (T2) =0C

LO inlet temperature (T1) =0C


Fresh water outlet temperature (t2) = 0CLMTD = [(T1-t2)-(T2-t1)]/log[(T1-t2)/(T2-t1)]

=0C

Area of lubricating oil cooler (A) = H/(K x LMTD)

= m2



: DESIGN IV

: 17 - 42 09 050 - CO

: 0

: Attachment No. 01

791058

480

59.8121

32

43.8068

33.2738

49.5296

67135

920

1000

0.43

0.43

1

1

45

80

94.9256

42

54.2541

90.5391

8.73719

920

Page 24 of 25

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ATTACHMENT NO. 02 - PUMP SPECIFICATION

TECHNICAL SPECIFICATION OF ENGINE

COOLING SYSTEMS

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