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1. INTRODUCTION

1.1 Description

a. Uni-lubricating Oil System

b. Cylinder Lubricating Oil System

1.2 Objective

This document purpose is to determine the technical specification of engine lubricating 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 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

hl = head losses

H = head total

TECHNICAL SPECIFICATION OF

ENGINE LUBRICATING SYSTEMS

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As a consequence the uni-lubricating oil, oil system is fitted, with two small booster pumps

for exhaust valve actuator lube oil supply. The system supplies lubricating oil to the engine

bearings through inlet, lubricating oil to the camshaft and cooling oil to the piston etc

through inlet lube oil supply and as mentioned lubricating oil to the exhaust valve actuators

through inlet engine. A butterfly valve at lubricating oil inlet lube oil supply is supplied with

the engine. The engine crankcase is vented through inlet engine by a pipe which extends

directly to the deck. This pipe has a drain arrangement so that oil condensed in the pipe can

be led to a drain tank. Drain from the engine bedplate are fitted on the both sides.

Lubricating oil is pumped from a bottom tank, by means of the main lubricating oil pump, to

the lubricating oil cooler, a thermostatic valve and through a full-flow filter, to the engine,

where it is distributed to pistons and bearings. The major part of the oil is divided between

piston cooling and crosshead lubrication. The booster pumps are introduced in order to

maintain the required oil pressure at inlet oil supply for the exhaust valve actuators.

The cylinder lubricators are supplied with oil from a gravity feed cylinder oil service tank,

and they are equipped with built in floats, which keep the oil level constant in the

lubricators. The size of the cylinder oil service tank depends on the owner's and yard's

requirements, and it is normally dimensioned for minimum two days consumption. Each

cylinder liner has a number of lubricating orifices (quils). The oil is delivered into the

cylinder via non return valves, when the piston rings pass the lubricating orifices, during the

upward stroke. The lubricator are fitted with electrical heating coils, low flow and low level

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4. DESIGN PARAMETER

4.1 Engine Selection Guide Requirement

a. Uni-lubricating Oil System

1. Lubricating Oil Centrifuge

(Engine Select ion Guide, Pages 6.03.03 - Lubri cat ing Oil Centrifuge)

2. List of Lubricating Oils

(Engine Select ion Guide, Pages 6.03.04 - List of lubri cat ing oil )

3. Lubricating Oil Pump

The lubricating pump can be of the screw wheel, or the centrifugal type:

Lubricating oil viscosity, specified 75 cSt at 500C, maximum 400 cSt

Lubricating oil flow will be take 135 m3/h according to the Table 4.2.

Manual cleaning centrifuges can only be used for attended machinery spaces (AMS). For

unattended machinery spaces (UMS), automatic centrifuges with total discharge or

partial discharge are to be used. The nominal capacity of the centrifuge is to be

according to the supplier's recommendation for lubricating oil, based on the 0.136

l/kWh or 0.1 l/BHPh. (The nominal MCR is used as the total installed effect)

The circulating oil (lubricating and cooling oil) must be a rust and oxidation inhibited

engine oil, of SAE 30 viscocity grade. In order to keep the crankcase and piston cooling

spaces clean of deposits, the oils should have adequate dispersion and detergent

properties. Alkaline circulating oils are generally superior in this respect. The oil list

will be shown in Table 4.1 below.

Table 4.1 List of lubricating oil



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400 cSt is specified, as it normal practice when starting on cold oil, to partly open the

by-pass valves of the lubricating oil pumps, so as the reduce the electric power

requirements for the pumps.

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Design pump head = 4.0 bar

Delivery pressure = 4.0 bar

Max working pressure = 500C

The flow capacity is to be within a tolerance of 0+12%

(Engine Select ion Guide, Pages 6.03.05 - Lubri cat ing oil pump)

4. Lubricating Oil Cooler

Lubricating oil viscosity = 75 cSt at 500C

Lubricating oil flow = 135 m3/h

Heat dissipation =

Lubricating oil temperature outlet cooler = 450C

Working pressure on oil side = 4 bar

Pressure drop on oil side = max 0.5 bar

Cooling water flow =

Cooling water temperature at inlet freshwater = 360C

Pressure drop on water side = max 0.2 bar(Engine Select ion Guide, Pages 6.03.05 - Lubri cat ing oil cooler)

Table 4.2 List of capacities

(Engine Select ion Guide, Pages 6.01.04 - List of capaci t ies wi th high eff iciency

t urbocharger and central cool ing syst em)

The pump head is based on the total pressure drop across coller and filter maximum 1

bar

The lubricating oil cooler is to be of the shell and tube type made of seawater resistant

material, or a plate type heat exchanger with plate material of titanium, unless

freshwater is used in a central cooling system.

If centrifugal pumps are used, it is recommended to install a throttle valve at position

'005', its function being to prevent an excessive oil level in the oil pan, if the

centrifugal pump supplies too much oil to the engine.



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5. Lubricating Oil Temperature Control Valve

Lubricating oil viscosity = 75 cSt at 500C


Temperature range, inlet to engine = 40-500C

(Engine Select ion Guide, Pages 6.03.05 - Lubricat ing Oil Temperature Cont rol Valve)

6. Lubricating Oil Full Flow Filter


Working pressure = 4.0 bar

Test pressure = according to the class rules

Working temperature = approximately 450C

Oil viscosity at working temperature = 90-100 cStPressure drop with clean filter = max 0.2 bar

b. Cylinder Lubricating Oil System

- Cylinder oils should, SAE 50 viscosity grade

- Cylinder oils feed rate according to the:

MEP dependent : 0.68 - 1.1 g/kWh / 0.50 - 0.8 g/BHP

5. DESIGN REQUIREMENT

5.1 Lubricating Oil Storage Tank

= BHP x SLOC x (S/Vdinas) x 1.3 x 10^-6 (1)

Where,

WLO str = Weight of lubricating oil in storage tankBHP = The maximum power of main engine

= kW

= HP

SLOC = Specific lubricating oil consumption

= g/BHPh

S = Radius of voyage

= Nm

Vdinas = knots

= WLO str/ LO (2)

Where,

LO = density of lubricating oil

= ton/m3

5.2 Lubricati ng Oil Service Tank

= BHP x SLOC x T x 1.3 x 10^-6 (3)

Where,

WLO srv = Weight of lubricating oil in service tank

= Time of used estimation

= 24 hours

= WLO srv/ LO (4)

5.3 Main Lubricating Oil Pump

WLO str . . . . . . . . . . . . . . . . . .

6320

8600

0.8

1200

14.5

VLO str . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

0.92

(Engine Select ion Guide, Pages 6.01.04 - List of capaci t ies wi th high eff iciency

t urbocharger and central cool ing syst em)

T

VLO srv . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

WLO srv . . . . . . . . . . . . . . . . . . . . . . . . .



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The temperature control system can, by means of a three-way valve unit, by-pass the

cooler totally or partly.

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Lubricating oil viscosity, specified 75 cSt at 500C, maximum 400 cSt

Lubricating oil flow will be take 135 m

3

/h according to the Table 4.2.Design pump head = 4.0 bar

Delivery pressure = 4.0 bar

Max working pressure = 500C

The flow capacity is to be within a tolerance of 0+12%

The pump head is based on the total pressure drop across coller and filter maximum 1 bar

(Engine Select ion Guide, Pages 6.03.05 - Lubri cat ing oi l pump)

The number of pump is two pumps, one as a standby pump.

Diameter Calculation:D = (4 x Q/ x v) (5)

Head Pump

i. Head Static (Hs)

height at z=0 to higer the discharge

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

ii. Head Pressure (Hp)

Hp = 4 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 = m2/s (at 50

0C)

v = fluid velocity

= m/sReynold number (Rn)

according to formula below:

If centrifugal pumps are used, it is recommended to install a throttle valve at position '005', its

function being to prevent an excessive oil level in the oil pan, if the centrifugal pump supplies

too much oil to the engine.



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0.000075

1.8

Table 5.1 Minimum wall thickness

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

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

l = 0.02+0.0005/dH (7)

Mayor losses (hf)

The following formula (8), as follow:

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

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

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 (6)

l = 0.02+0.0005/dH (7)

Mayor losses (hf)


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


= 23.22*(1.8^2)/(2*9.8)

= m

Therefore, the total of Heads are:

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

= 4.25+0+4+0.16+1.074+0.12+3.838= m

5.4 Lubricating Oil Feed Pump

Q = 0.136*Main Engine Power . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .(10)

Diameter Calculation:

D = (4 x Q/ x v) (11)

Head Pump

According to the engine guide selection 06.03.04 - lubricating oil centrifuge, the nominal

capacity of the centrifuge:



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

3.838

13.442

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

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

1.8

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

0.000075

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

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

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

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i. Head Static (Hs)


height at z=0 to the lower suction

Therefore, the value of Hs will be determined below:


Hp = 0 bar




iv.1 Suction


n = m2/s (at 50

0C)

v = fluid velocity

= m/s

l = 64/Rn (13)

hf = l*L*v2/(D*2g) (14)


iv.2 Discharge


n = m2/s (at 50

0C)

v = fluid velocity

= m/s

l = 64/Rn (17)

hf = l*L*v2

/(D*2g) (18)Minnor losses (hl)


= 24.03*(1.8^2)/(2*9.8)

= m



5.5 Cylinder Lubricating Oil Storage Tank

= BHP x SLOC x (S/Vdinas) x 1.3 x 10^-6 (20)

Where,

WLO str = Weight of cylinder lubricating oil in storage tankBHP = The maximum power of main engine

= kW

= HP

SLOC = Specific lubricating oil consumption

= g/BHPh

for 4 cyl = g/BHPh

S = Radius of voyage

= Nm

Vservice = knots

= WLO str/ LO (21)

Where, LO = density of lubricating oil

= ton/m3

8600

0.8

3.2

1200

0.000075

14.5

VLO str . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

6320

0.92



WLO str . . . . . . . . . . . . . . . . . .

3.972

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

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

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1.8

0.000075

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

: 01

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1.8

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

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5.6 Cyli nder Lubr icati ng Oil Service Tank

= BHP x SLOC x T x 1.3 x 10^-6 (22)

Where,

WLO srv = Weight of lubricating oil in service tank

= Time of used estimation

= 48 hours

= WLO srv/ LO. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (23)

5.7 Cylinder Lubricati ng Oil Pump

Q = VLO srv/t (24)

where,

The time estimation = 15 minutes

= 900 seconds

Diameter Calculation:

D = (4 x Q/ x v) (25)

Head Pump

i. Head Static (Hs)


height at z=0 to the lower suction

Therefore, the value of Hs will be determined below:


Hp = 0 bar




iv.1 Suction


n = m2/s (at 50

0C)

v = fluid velocity

= m/s

Reynold number (Rn)


Rn = (v*dH)/n (26)

1.8

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

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

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

T

VLO srv


0.000075

WLO srv . . . . . . . . . . . . . . . . . . . . . . . . .

: Philosophy



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l = 64/Rn (27)

hf = l*L*v

2

/(D*2g) (28)Minnor losses (hl)


iv.2 Discharge


n = m2/s (at 50

0C)

v = fluid velocity

= m/s

Reynold number (Rn)


Rn = (v*dH)/n (30)

l = 64/Rn (31)Mayor losses (hf)


hf = l*L*v2/(D*2g) (32)

Minnor losses (hl)




5.8 Area of Lubricat ing Cooler

Heat dissipation LO cooler (H) = 290 kW

= kcal/hHeat transfer coef. (K) = 260 kcal/m

2.h.

oC

Central cooling water quant (Qsw) = 38 m3/h

LO quantity (Qlo) = 80 m3/h

Density LO = 920 kg/m3

Density Water = kg/m3

Heat spec. of LO (Clo) = Btu/lb F

Heat spec. of Water (Csw) = 1 Btu/lb F

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

The area of lubricating oil cooler (A) = H/(K*LMTD)

5.9 Lubricating Oil Purifier

Q = 0.136*Power main engine

5.10 Power of Pre-heater Feed Pump

Temperature range (T) = 48oC

= 118oF

P = Q(l/h) x T/1700

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249355.108

1000

0.43

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

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

1.8

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

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

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

0.000075



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5.11 Valve and Fitting

a. Valve

1. Butterfly Valve

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.

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.

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



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5.12 Class Requirement

Germanischer Lloyd 2012, Chapter 2, Section 11, Page 11-29

a. General Requirements

b. Priming Pumps

c. Emergency Lubrication

d. Lubricating Oil Treatment

e. Lubricating Oil Circulating Tanks and Gravity Tanks

f. Filling and Suction Lines

- for valves which are kept closed during normal operation.



: DESIGN IV

Figure 5.4 Centrifugal Filter

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Lubricating oil system are to be so constructed to ensure reliable lubrication over the whole

range of speed and during run-down of the engines and to ensure adequate heat transfer.

Where necessary, priming pumps are to be provided for supplying lubricating oil to the

engines.

A suitable emergency lubricating oil supply (e.g. gravity tank) is to be arranged for

machinery which may be damaged in case of interuption of lubricating oil supply.

Equipment necessary for adequate treatment of lubricating oil is to be provided (purifiers,

automatic back-flushing filters, filters, free-jet centrifuges). In the case of auxiliary engines

running on heavy fuel which are supplied from a common lubricating oil tank, suitable

equipment is to be fitted to ensure that in case of failure of the common lubricating oil

treatment system or ingress of fuel or cooling water into the lubricating oil circuit, the

auxiliary engines required to safeguard the power supply.

Where an engine lubricating oil circulation tank extend to the double bottom shell plating

on ships for which a double bottom is required in the engine room, shutt-off valves are to be

fitted in the drain pipes between engine casing and circulating tank. These valves are to be

capable of being closed from a level above the lower platform. The suction connections of

lubricating oil pumps are to be located as far as possible from drain pipes. Gravity tanks are

to be fitted with an overflow pipe which leads to the circulating tank. Arrangements are to

be made for observing the flow of excess oil in the overflow pipe.

Filling and suction lines of lubricating oil tanks with a capacity of 500 liter and more located

above the double bottom and from which in case of their damage lubricating oil may leak,

are to be fitted directly on the tanks with shut-off devices. The remote operation of shut-

off valve may be dispensed with:

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-

g. Filters

6. SUMMARY

NO

1

2

4

5

6

For the main lubricating pump selection and spesification:

=

=

==

=

=

To reach the required capacities, we need to make a two pump with paralel.

For the lubricating oil feed pump selection and spesification:

=

=

=

=

==

NO

1

2

4

5

6



: DESIGN IV

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where an unintended operation of a quick closing valve would endager the safe

operation of the main propulsion plant or essential auxilliary machinery.

Lubricating oil filter are to be fitted in the delivery line of the lubricating oil pumps. Mesh

size and filter capacity are to be in accordance with the requirements of the manufacturer

of the engine. Uninterrupted supply of filtered lubricating oil has to be ensured under

cleaning conditions of the filter equipment. In case of automatic back-flushing filters it is to

be ensured that a failure of the automatic back-flushing will not lead to a total loss of

filtration. Engine for the exclusive operation of emergency generators and emergency fire

pumps may be fitted with simplex filters. For protection of the lubricating oil pumps

simplex filters may be installed on the suction side of the pump if they have a minimum

6.1 LUBRICATING OIL

CALCULATION SYMBOL RESULT

LO Storage Weight WLO str 0.7

LO Storage Volume VLO str 0.80457

8 bar

0.158

0.172

13.4

6.2 CYLINDER LUBRICATING OIL

CALCULATION

LO Service Weight WLO srv

LO Service Volume VLO srv

Head total H

Merk Taiko

Type HG-90

750 RPM

30 kW

SYMBOL RESULT

LO Storage Weight WLO str 3.0 tonnes

LO Storage Volume VLO str 3.21823 m3

Taiko

NHG-1.5

1.2 m3/h

bar

RPM2.2 kW

tonnes

m3

tonnes

m3

m

75 m3

/h

LO Service Weight WLO srv 1.262 tonnes

LO Service Volume VLO srv 1.372 m3

Head total H 10.7 m

QapacityTekanan

Rpm

Power

Merk

Type

Qapacity

Tekanan

RpmPower

1000

6

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For the cylinder lubricating oil pump selection and spesification:

=

=

=

=

=

=

6.3 Another

NO

1

2

3

The heater that will be used :Type = AALBORG

Power = 26 kW

Length = mm

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ENGINE LUBRICATING SYSTEMS: Philosophy

Qapacity

1000

Power 7.5

Taiko

NHG-7.5

6 m3/h

Merk

Type

CALCULATION

Area of Lubricating Cooler

Qapacity of Lubricating Purifier

Power of Pre-heater feed pump

RPM

kW

SYMBOL RESULT

A 43.2 m2

Q 859.5 l/h

P 24.3

Tekanan 6 bar

Rpm

1000

kW

P 13 f 13

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BOOK 16 (LO)