s50mcc
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The eng ine types of the MC progra mme a re
ide ntified by the follow ing letters a nd figures :
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
430 100 100 198 21 20
1.01
Fig. 1 .01: Engine type designation
178 34 41-3.1
S 50 MC
Diameter of piston in cm
S troke/b ore ra tio
Engine programme
C Compa ct engine
S S tationary engine
S S uper long stroke a pproxima tely 4.0
L Long s t roke approximately 3 .2
K Short s t roke approximately 2 .8
-C6
Numb er of cy linde rs
Design
Concept
C Ca msha ft co ntrolled
E Elec tronic co ntrolled (Intellig ent Engine)
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S50MC-CBore: 500mmStroke:2000mm
430 100 100 198 21 21
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
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Power and speed
LayoutEngine s peed
Mean effectivepressure
P ower kWB HP
Numbe r of cylinde rs
r/min ba r 4 5 6 7 8
L1 127 19.0 6320
85807900
107259480
128701106015015
1264017160
L2 127 12.2 4040
550050506875
60608250
70709625
808011000
L3 95 19.0 4740
644059258050
71109660
829511270
948012880
L4 95 12.2 30404120 38005150 45606180 53207210 60808240
Fuel and lubricating oil consumption
Specific fuel oilconsumption
g/kWhg /B HP h
Lubrica ting oil co nsumption
At loa dLayout po int
Withhigh efficiencyturbocharger
With conventionalturbocharger
Sys tem oilApproximate
kg/cyl. 24 ho urs
Cylinder oilg/kWhg /B HP h100% 80% 100% 80%
L1 171
126169124
174128
171126
4 - 5 0.95-1.5
0.7-1.1
L2 159
117156116
162119
160118
L3 171
126169124
174128
171126
L4 159
117156116
162119
160118
Fig. 1.02: Power, speed and SFOC 178 39 14-7.1
L3
L4
L2
L1
Po w e r
Speed
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EnginePowerRangeandFuel Consumption
Engine Power
The tab le co ntains da ta rega rding the engine power,
speed and s pecific fueloilc onsumption of the engine.
Engine power is specified in both BHP and kW, in
rounde d figures, for ea ch c ylinder number and layout
points L1, L2 , L3 and L4:
L1 designates nominal maximum continuous rating
(nominal MCR), at 100% engine power and 100%
engine speed . L2 , L3 and L4 des igna te la yout points
a t the other three co rners of the la yout a rea, cho s enfor ea s y reference . The mea n effective pres sure is:
L1 - L3 L2 - L4
ba rkp/cm 2
19.019.3
12.212.4
Overload corresponds to 110% of the power at
MCR, and may be permitted for a limited period of
one ho ur every 12 hours.
The engine power figures g iven in the ta bles rema in
va lid up to tropica l co nditions a t se a level, i.e.:
B low er inlet temp erature . . . . . . . . . . . . . . . . 45 °C
B low er inlet press ure . . . . . . . . . . . . . . . 1000 mba r
S ea wa ter temperature . . . . . . . . . . . . . . . . . . 32 °C
Specific fueloil consumption(SFOC)
Spec ific fuel oil consump tion values refer to brake
power, and the following reference conditions:
ISO 3046/1-1986:B low er inlet temp erature . . . . . . . . . . . . . . . . 25 °C
B low er inlet press ure . . . . . . . . . . . . . . 1000 mba r
Cha rge a ir coolant te mperature . . . . . . . . . . . 25 °C
Fuel oil low er c a lorific va lue . . . . . . . . 42,700 kJ /kg
(10,200 kca l/kg)
Although the engine will develop the power speci-
fied up to tropical ambient conditions, specific fuel
oil co nsumpt ion va ries w ith a mbient co nditions a nd
fuel oil low er ca lorific va lue. For ca lculation of these
changes, see the following pages.
Highefficiency/conventional turbochargers
The eng ine is in its b a sis d es ign ma de with a high
efficiency turboc ha rger in order to o bta in the low -es t pos sible S pec ific Fuel Oil Co nsumption
(S FOC ).
The a mount of a ir req uired for the comb ustion ca n
however be a djusted to provide a higher exhaust
ga s tempera ture, if this is needed for exhaust ga s
bo iler by a pplying “co nventiona l” turbo cha rger,
- see s ection 2.
VIT fuelpumps
The eng ine type is in its b asis d es ign not fitted with the
Variable Injec tion Timing (VIT) fuel pumps, - but they
can optionally (4 35 104)be equipped with VITpumps,
and in tha t ca se they ca n be optimised betw een 85 -
100% of spec ified MCR (point M), - see s ec tion 2.
SFOC guarantee
The figures g iven in this p rojec t g uid e repres ent the
values ob ta ined w hen the engine and turboc harger
are matched with a view to obtaining the lowest
possible SFOC values and fulfilling the IMO NOxemiss ion limita tions .
The S pec ific Fuel Oil C ons umption (S FOC) is gua r-anteed for one engine load (power-speed combina -tion), this being the one in which the engine is opti-mised. Theguaranteeisgivenwithamarginof5%.
As SFOC and NOx are interrelated parameters, anengine offered without fulfilling the IMO NOx limita -tions is sub jec t to a toleranc e of only 3% of the SFOC.
Lubricating oildata
The c ylinde r oil cons umption figures sta ted in the
tables are valid under normal conditions. During
running-in p eriode s a nd under s pecial c onditions,
feed rates of up to 1.5 t imes the stated values
should be used.
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
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430 100 500 198 21 23
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
1.04
Fig. 1 .03: Performance c urve for S50MC- C w i thout VIT fuel pumps
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The fra me b ox is atta ched to the b edplate with
sc rews. The fra me bo x, bedplate a nd cylinder fra me
a re tightened toge ther by tw in sta y bo lts. The sta ybo lts a re mad e in one or tw o pa rts (option: 4 30 132)
depending on the engine room height.
Cylinder Frame,Cylinder LinerandStuffing Box
The cylinde r fra me is c a st in one or more piec es w ith
integ rated c a ms ha ft fra me and the cha in drive at the
a ft end . It is ma de of ca st iron a nd is a tta c hed to the
fra me b ox w ith s crews . The c ylinder fra me is pro-
vided w ith a cc ess co vers for cleaning the sca venge
a ir spa ce a nd for inspec tion of sc a venge ports andpist on rings from the c a ms ha ft side . Tog ether with
the cylinder liner it forms the scavenge air space.
The c ylinde r frame ha s duc ts for pist on c oo ling o il
in le t . The sc a venge a ir rece iver , c ha in d rive ,
turboc harger, air cooler box and ga llery brackets
are located at the cylinder frame. Furthermore, the
supp ly pipe for the pisto n co oling o il a nd lubrica ting
oilis atta che d to the cy linde r fra me. At the botto m of
the c ylinde r fra me there is a piston rod s tuffing b ox,
which is provided with sealing rings for scavenge
a ir, a nd w ith oil sc rape r rings w hich prevent oil fromco ming up into the sc a venge a ir spa ce.
Drains from the scavenge air space and the piston
rod stuffing bo x are loc a ted a t the bo ttom of the cy l-
inde r fra me.
The cylind er liner is ma de o f alloyed c a s t iron and is
sus pended in the cylinder frame by mea ns of a low
situate d fla nge . The uppe rmost pa rt of the liner is
surrounded by a ca s t iron coo ling jac ket. The c ylin-
der liner has scavenge ports and drilled holes for
cylinder lubrication.
The c a msha ft is embed ded in b ea ring shells lined
with white meta l in the c a msha ft fra me.
Cylinder Cover
The c ylinder c over is of forged steel, ma de in one
piece , and ha s b ores for co oling wa ter. It has a cen-
tral bore for the exhaust valve a nd bores for fuel
valves, sa fety valve, sta rting valve a nd indica tor
valve.
The c ylinde r cover is a tta che d to the c ylinde r frame
w ith 8 stud s and nuts tighte ned by hydraulic ja c ks.
Exhaust Valve and Valve Gear
The exha ust va lve co nsists of a va lve housing and a
va lve s pindle. The va lve hous ing is of c a st iron a nd
a rra nge d for wa ter coo ling. The hous ing is provide d
with a bo ttom piece of steel with a fla me ha rdened
se a t. The bo ttom piece is w a ter coo led . The sp indle
is ma de of heat res ista nt steel with hardfa cing meta l
w elded o nto the se a t. The hous ing is provided w ith aspindle guide.
The exha ust va lve is tightene d to the cy linde r cover
with studs a nd nuts. The exhuas t valve is opened
hydra ulica lly and c los ed by mea ns of a ir press ure. In
operation, the va lve s pindle slowly rotates , d riven
by the exha ust ga s ac ting on sm a ll va nes fixed to the
spindle. The hydra ulic sys tem c onsists of a piston
pump mounted on the roller g uide housing, a
high-pressure pipe, and a working cylinder on the
exhaus t va lve. The piston pump is a ctiva ted by a
ca m on the ca mshaft.
Air sea ling of the exha ust va lve s pindle guide is
provided.
Fuel Valves, Starting Valve,Safety Valve and Indicator Valve
Each cylinder cover is eq uipped with tw o fuel
valves, one starting valve, one safety valve, and one
indica tor va lve. The opening of the fuel valves is
co ntrolled by the fuel oil high pressure c rea ted by
the fuel pumps , and the valve is clos ed by a s pring.
An a utoma tic vent s lide a llow s c ircula tion o f fuel oil
through the valve and high pres sure pipes , and p re-
vents the co mpress ion cha mb er from being filled up
with fuel oil in the event that the valve spindle is
sticking when the eng ine is s topped . Oil from the
vent slide a nd other drains is led a wa y in a c los ed
system.
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The s ta rting va lve is ope ned by co ntrol a ir from the
starting air distributor and is closed by a spring.
The sa fety valve is s pring-loa de d.
Indicator Drive
In its basic execution, the engine is fitted with an in-
dicator drive.
The indica tor drive c onsists of a ca m fitted on the
ca mshaft and a spring-loa ded spindle with roller
which moves up and dow n, corresponding to the
movem ent of the p is ton w ithin the eng ine c ylinde r.
At the top, the sp indle has a n eye to w hich the indi-ca tor cord is fastened after the indica tor has been
mounted on the indicator valve.
Crankshaft
The cra nksha ft is of the semi-built type . The se mi-built
type is mad e from forged or ca st steel throw s. The
crankshaft incorporates the thrust shaft.
At the aft end, the crankshaft is provided with a
fla nge for the turning w heel and for coupling to theintermediate shaft.
At the front end , the cra nksha ft is fitte d w ith a fla ng e
for the f it t ing of a tuning wheel a nd/or c oun-
terweights for ba la ncing purpos es, if neede d. The
flange can also be used for a power take-off, if so
de sired . The pow er ta ke-off ca n be supplied a t extra
cost, option: 4 85 000.
Coupling bolts and nuts for joining the crankshaft to-
ge ther with the intermediate sha ft a re not norma lly sup-
plied. These can be ordered a s a n option: 4 30 602.
Axial Vibration Damper
The eng ine is fitted with a n a xia l vibra tion d a mper,
w hich is mo unted on the fore end of the cra nksha ft.
The da mper cons ists of a piston a nd a split-type
housing loc a ted forwa rd of the foremos t main bear-
ing. The pis ton is ma de a s a n integ rated c olla r on the
main journal, and the housing is fixed to the main
bea ring s upport. A mecha nica l device for check of
the functioning o f the vibra tion d a mper is fitted .
5 and 6-cylinde r eng ines a re eq uipped w ith an a xia l
vibration monitor (4 31 117).
P la nts eq uipped w ith P ow er Ta ke Off a t the fore end
a re a lso to be eq uipped w ith the axial vibra tion mon-
itor, option: 4 31 116.
Connecting Rod
The connec ting rod is ma de o f forged o r ca st s teel
and provided with bea ring c aps for the crosshea d
a nd c rankpin bea rings .
The cross hea d and c rankpin bea ring ca ps a re se -
cured to the c onnect ing rod by s tuds and nuts
which a re tightened by hyd raulic ja cks.
Th e c r o s s h e a d b e a r in g c o n s is t s o f a s e t o f
thin-walled steel shells, lined with bearing metal.
The cross hea d b ea ring c a p is in one piece , with an
angular cut-out for the piston rod.
The cra nkpin bea ring is provided w ith thin-wa lled s tee l
shells, lined with bearing metal. Lub. oil is suppliedthrough ducts in the crosshead and connecting rod.
Piston, Piston Rod and Crosshead
The piston c onsists of a piston c rown and piston
skirt. The piston c row n is ma de of hea t-resista nt
s t e e l a n d h a s f o u r r in g g r o o v e s w h ic h a re
hard-chrome plated on b oth the upper and lower
surfa ces of the grooves . The piston c rown is with
“high topland”, i.e. the distance between the piston
top a nd the upper piston ring ha s b een increas ed.
The upper piston ring is a CP R type (Co ntrolled
P ressure Releif) a nd is higher than the other piston
rings. The other three piston rings are with a n
obliq ue cuts.
The pist on s kirt is o f ca s t iron.
The p is ton rod is o f fo rged s tee l a nd is sur-
face-hardened on the running surface for the stuff-
in g b o x . Th e p i s t o n ro d is co n n e c t e d t o t h e
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
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cross hea d w ith four sc rew s. The piston rod ha s a
ce ntral bore w hich, in conjunction w ith a co oling o il
pipe, forms the inlet and outlet for cooling oil.
The c ross head is of forged steel and is provided
with ca st s teel guide s hoes with white meta l on the
running surface.
The te les c op ic p ipe fo r oil inlet a nd t he pipe fo r oil
outlet a re mounted on the top o f the guide s hoes.
Fuel Pump and Fuel OilHigh-Pressure Pipes
The eng ine is provided w ith one fuel pump for ea chcy linde r. The fuel pump co nsists of a pump ho using
of nodular ca st iron, a c entrally pla ce d pump ba rrel,
a nd plunger of nitrated s teel. In orde r to prevent fuel
oil from being mixed with the lubricating oil, the
pump actuator is provided with a sealing arrange-
ment.
The pump is a ctivate d b y the fuel ca m, a nd the vol-
ume injected is controlled by turning the plunger by
mea ns of a toothed ra ck co nnected to the regulating
mechanism.
In the ba sic de s ign the a djustm ent of the pump lea d
is effecte d by inse rting shims betw een the top cover
a nd the pump housing.
The eng ine c a n a s a n option: 4 35 104 be fitted w ith
fuel pumps with Variable Injection Timing (VIT) for
optimise d fuel ec ono my a t pa rt loa d. The VITprinci-
ple uses the fuel regulating shaft position as the
controlling parameter.
The roller guide hous ing is provided w ith a ma nual
lifting de vice (4 35 130)w hich, d uring turning of the
eng ine, c a n lift the roller guide free of the ca m.
The fuel oil pumps a re provided with a puncture
valve, which prevents high pressure from building
up during normal stopping a nd s hut dow n.
The fuel oil high-press ure p ipes a re eq uipped w ith
protective hoses and are neither heated nor insu-
lated.
Camshaft and Cams
The ca msha ft is ma de in one or two pieces d epend-ing o n the number of c ylinde rs, w ith fuel ca ms , ex-
haust c ams , indica tor cams , thrust disc and cha in
wheel shrunk onto the s haft.
The exhaust ca ms a nd fuel ca ms a re of steel, with a
ha rdened roller rac e. They ca n be a djust ed a nd dis-
ma ntled hydra ulica lly.
Chain Drive
The ca ms ha ft is d riven from the cra nksha ft by two
cha ins. The c hain wheel is bo lted o n to the s ide ofthe thrus t co lla r. The c ha in drive is p rovided w ith a
cha in tightener and guide b a rs to s upport the long
cha in lengths.
Reversing
Reversing of the engine ta kes pla ce b y mea ns of a n
a ngular displac ea ble roller in the driving mecha nis m
for the fuel pump of ea c h eng ine c ylinde r. The re-
versing mechanism is activated and controlled by
co mpresse d a ir supplied to the engine.
The exha ust va lve g ea r is no t reversible.
2nd order Moment Compensators
These a re relevant only for 4, 5 or 6-cylinder e n-
gines, and c a n be mounted either on the aft end or
on both fore end and a ft end. In spec ia l ca ses only a
compensator on the fore end is necessary.
The af t-end co mpensa tor co nsists of ba la nce-
we ights built into the c a msha f t cha in drive , op-
tion: 4 31 203.
The fore-end compens a tor consists of ba la nce-
weights driven from the fore end of the crankshaft,
option: 4 31 213.
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tions a re ac hieved. S ome ma in pipes of the engine
are s uspended from the g allery brac kets, a nd the
upper gallery platform on the camshaft side is pro-vide d with ove rhauling holes for pisto n. The numbe r
of holes depend s on the number of cylinders.
The eng ine is prepa red for top brac ings on the ex-
ha ust s ide (4 83 110), or on the c a ms ha ft side (op-
tion: 4 83 111).
Scavenge AirSystem
The a ir intake to the turboc harger ta kes pla ce di-
rectly from the engine room through the intake si-
lencer of the turbo cha rger. From the turbocha rger,the a ir is led via the c ha rging a ir pipe, a ir coo ler and
scavenge air receiver to the scavenge ports of the
cy linde r liners. The c ha rging a ir pipe be tw een the
turboc harger a nd the a ir cooler is provided with a
compensator and is heat insulated on the outside.
See chapter 6.09.
Exhaust Turbocharger
The en g ine ca n be fitte d w ith MAN B&W (4 59 101) ,
AB B (4 59 102) or MHI (4 59 103)turboc ha rgers a r-rang ed on the a ft end o f the eng ine (4 59 121).
Alternatively, on this engine type the turbocharger
ca n be loca ted on the exhaust side of the engine,
option: 4 59 123.
The turboc ha rger is p rovide d w ith:
a ) Equipment for wa ter wa shing of thecompressor s ide
b) Eq uipment for dry clea ning o f the turbine side
c) Water washing on the turbine side is mountedfor the MAN B&W a nd AB B turbo cha rgers.
The g a s o utlet ca n be 15°/30°/45°/60°/75°/90° from
vertica l, aw a y from the engine. S ee either of options
4 59 301-309. The turboc ha rger is e q uipped w ith a n
electronic tacho system with pick-ups, converter
and indicator for mounting in the engine control
room.
Scavenge Air Cooler
The eng ine i s f it ted wi th a ir c oo ler(s) o f themonoblock type, one per turboc harger for a s ea wa -
ter cooling system designed for a pressure of up to
2.0-2.5 b a r w orking press ure (4 54 130) or central
co oling w ith fres hw a ter of ma ximum 4.5 ba r w orking
press ure, o ption: 4 54 132. The a ir coo ler is so de-
signed that the difference between the scavenge air
temperature a nd the w a ter inlet tempe ra ture (a t the
optimis ing point)ca n be kept a t a ma ximum of 12°C.
The end c ove rs a re of coa ted ca s t iron (4 54 150), or
a lternatively of b ronze, o ption: 4 54 151
The c oo ler is provide d w ith eq uipment forcleaning of:
Air side:
S tand ard s howering s ystem (cleaning pumpunit including tank and filter, yard supply)
Water side:
Cleaning brush
Exhaust Gas System
From the exhaust valves, the gas is led to the ex-haust gas receiver where the fluctuating pressure
from the individual cylinders is equalised, and the
t o t a l v o lu m e o f g a s le d f u rt h e r o n t o t h e
turboc harger at a consta nt press ure.
Compensa tors are f it ted be tween the exhaust
valves and the receiver, and between the receiver
and the turbocharger.
The exhaust ga s receiver and exhaust pipes are
provided with insulation, covered by ga lvanized
steel plating.
There is a protective g rating b etwe en the exha ust
ga s receiver a nd the turbocha rger.
After the turbo cha rger, the ga s is led via the exha ust
ga s outlet trans ition piece, o ption: 4 60 601 and a
co mpensa tor, option: 4 60 610 to the e xternal ex-haus t pipe sys tem, which is ya rd’s supply. Se e also
cha pter 6.10.
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Auxiliary Blower
The eng ine is pro vid ed w ith tw o elec tric a lly-drivenblow ers (4 55 150). The s uct ion s ide of the b lowe rs
is co nnected to the sca venge a ir spa ce a fter the air
cooler.
Betw een the airc ooler a nd the sca venge air receiver,
non-return valves a re fitted which a utoma tica lly
close when the auxiliary blowers supply the air.
B oth auxilia ry blow ers will sta rt ope rating before the
eng ine is sta rted and will ens ure suffic ient sca veng e
a ir pressure to obta in a s a fe sta rt.
During o pera tion o f the eng ine, b oth a uxilia ry blow -ers will s ta rt a utoma tica lly eac h time the engine loa d
is red uce d to a bo ut 30-40%, and the y w ill co ntinue
operating until the loa d ag ain exceeds approxi-
mately 40-50%.
In ca se s w here one of the auxilia ry blow ers is out of
se rvice , the other a uxilia ry blow er will a utoma tic a lly
compensate without any manual readjustment of
the valves, thus avo iding any eng ine loa d reduction.
This is a chieved by the automa tica lly working
non-return va lves in the s uction pipe of the blow ers.
The electric mo tors a re of the tota lly enc los ed , fan
co oled, single s peed type, w ith insulation min. clas s
B and enclosure minimum IP44.
The electrica l c ontrol pa nel a nd s ta rters for two
a uxilia ry blow ers ca n be del ivered a s a n option:
4 55 650.
Piping Arrangements
The eng ine is delivered w ith piping arra ng eme nts for:
Fuel oil
Heating of fuel oil pipes
Lubrica ting a nd pisto n co oling o il pipes
Cylinder lubricating oil
Lubricating of turbocharger
Sea cooling wa ter
J ac ket cooling wa ter
Cleaning of turboc harger
Fire extinguishing for scavenge air space
S tarting a ir
Co ntrol a ir
S afety air
Oil mist de tec tor.
The pipes for se a co oling wa ter to the a ir co olera re of:
G a lva nise d s teel . . . . . . . . . . . . . . . . . 4 45 130, or
Thick-wa lled, ga lvanised ste el . o ption 4 45 131, or
Aluminium bra ss . . . . . . . . . . . . o ption 4 45 132, or
Co pper nickel. . . . . . . . . . . . . . . . . option 4 45 133
In the cas e of central co oling, the pipes for fres hwa -ter to the a ir coo ler are of s teel.
The pipes a re provide d with so ckets for sta nda rd in-struments, alarm and safety equipment and, fur-thermore, with a numb er of so ckets fo r supp leme n-tary signal equipment and supplementary remote
instruments.
The inlet a nd return fuel oil pipes (exc ept bra nch
pipes)are heated with:
S tea m trac ing . . . . . . . . . . . . . . . . . . . 4 35 110, or
Elec trica l trac ing . . . . . . . . . . . option: 4 35 111, or
Therma l oil trac ing . . . . . . . . . . . . o ption: 4 35 112
The dra in pipe is hea ted b y fres h coo ling w a ter.
The a bove heating pipes a re normally delivered
without insulation, (4 35 120). If the engine is to be
tra nsported a s o ne unit, insula tion ca n be mounted
a s a n option: 4 35 121.
The eng ine’s e xterna l pipe conne c tions a re in ac -corda nce with DIN a nd IS O sta nda rds .
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2 EngineLayoutandLoadDiagrams
Introduction
The effec tive brake pow er “P b ” of a d ies el engine is
proportional to the mean effective pressure p e a nd
eng ine spee d “n”, i.e. when using “c” a s a co nsta nt:
P b = c x pe x n
so, for constant mep, the power is proportional to
the speed:
P b = c x n1
(for consta nt mep)
When running w ith a Fixed P itch P rope ller (FP P ), the
pow er ma y be express ed a cc ording to the propeller
law a s:
P b = c x n3
(prope ller la w )
Thus, for the a bo ve exa mples, the brake pow er P bma y be express ed a s a po we r function of the speed
“n” to the p ow er of “i”, i.e.:
P b = c x ni
Fig. 2.01a show s the relationship for the linea r func-
tions, y = a x + b, using linea r sc a les.
The po w er functions P b = c x ni, s ee Fig. 2.01b, w ill
be linear functions when using logarithmic scales.
log (P b ) = i x log (n) + log (c )
Thus, prope ller curves w ill be pa rallel to lines ha ving
the inclina tion i = 3, and lines w ith cons ta nt mep will
be parallel to lines with the inclination i = 1.
Therefore, in the Layout Diagrams a nd Loa d Dia-
grams for diesel engines, logarithmic scales are
used, making simple diagrams with straight lines.
Propulsion and Engine Running Points
Propellercurve
The rela tion betw een pow er a nd propeller spee d for
a fixed pitch propeller is as mentioned above de -
sc ribe d b y mea ns o f the prope ller la w , i.e. the third
pow er curve:
P b = c x n3
, in which:
Pb = eng ine pow er for propulsion
n = propeller speed
c = co ns t ant
Propeller designpoint
Norma lly, e stimations of the neces sa ry propeller
power and speed are ba sed on theoretica l ca lcula-
tions for loa ded ship, and often experimental tank
tests, both as suming optimum operating condi-
tions , i.e. a clea n hull a nd go od w ea ther. The com bi-
nation of speed a nd pow er obta ined ma y be ca lled
the ship’s propeller de s ign po int (P D), pla ce d on the
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2.01
Fig. 2.01b: Power function curves in logarithmic scales
178 05 40-3.0
Fig. 2.01a: Straight lines in linear scales
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lig ht running prope ller curve 6. S ee Fig. 2.02. On the
other hand, s ome shipyards, a nd/or propeller ma nu-
facturers sometimes use a propeller design point(P D’) that incorporates a ll or part o f the s o-ca lled
sea margin described below.
Fouledhull
When the ship ha s s a iled for s ome time, the hull a nd
propeller bec ome fouled a nd the hull’s res ista nce
will increas e. C onse q uently, the ship spee d will be
reduc ed unles s the eng ine d elivers more pow er to
the prop eller, i.e. the p rope ller will b e further loa de da nd w ill b e he a vy running (HR).
As mode rn vess els with a rela tively high s ervice
speed are prepared with very smooth propeller and
hull surfa ces , the fouling a fter sea tria l, therefore,
w ill involve a rela tively highe r resista nce a nd thereby
a heavier running propeller.
Seamarginand heavypropeller
If , at the s ame time the w eather is ba d, w ith headwinds, the ship’s resistance may increase com-
pa red to operating a t ca lm wea ther co nditions.
When de termining the ne ce ss a ry engine pow er, it is
therefore normal practice to add an extra power
ma rgin, the so -ca lled s ea m a rgin, which is trad ition-
a lly a bo ut 15% of the propeller des ign (P D) pow er.
Engine layout(heavypropeller)
When d etermining the nec ess a ry engine s peed
considering the influence of a heavy running propel-ler for operating at large extra ship resistance, it is
recommended - compared to the clean hull and
ca lm wea ther propeller curve 6 - to choos e a heavier
propeller curve 2 for eng ine la yout, a nd the propeller
curve for clean hull a nd c a lm w ea ther in curve 6 will
be s a id to repres ent a “lig ht running” (LR)prope ller.
Compa red to the hea vy engine layo ut curve 2 we
recommend to use a light running of 3.0-7.0% for
de s ign o f the propeller.
Engine margin
Bes ides the sea margin, a so-ca lled “engine mar -
gin” of s ome 10% is freq uently a dd ed . The c orre -
sp ond ing po int is c a lled the “spe cified MC R for pro -
pulsion” (MP), and refers to the fact that the power
for point SP is 10% lower than for point MP. Point
MP is ide ntica l to the eng ine’s s pec ified MCR point
(M)unles s a ma in engine driven sha ft genera tor is in-
stalled. In such a case, the extra power demand of
the shaft generator must also be considered.
Note:
Light/heavy running, fouling and sea margin are
overlapp ing terms. Light/heavy running of the p ro -
peller refers to hull and prop eller deterioration and
heavy weather and, –sea margin i.e. extra power to
the propeller, refers to the influence of the w ind and
the sea. However, the degree of light running must
be dec ided upon experience from the actual trade
and hull design.
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2.02
Line 2 P ropulsion curve, fouled hull a nd hea vywe a ther (hea vy running), rec omme nde d for en-gine layout
Line 6 P ropulsion curve, clea n hull and ca lm wea ther(light running), for propeller layout
MP Spec if ied MCR for propulsionSP Continuous service rating for propulsion
PD Propeller design point
HR Heav y run nin g
LR Light running
Fig. 2.02: Ship propulsion running points and engine layout
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Engine Layout Diagram
An engine’s layout d ia gram is limited by two co n-
sta nt mea n effec tive press ure (mep) lines L1-L3 and
L2-L4, a nd by two co nst a nt eng ine spee d lines L1-L2and L3-L4, s ee Fig. 2. 02. The L1 point refers to theengine’s nominal maximum continuous rating.
Within the layout area there is full freedom to select
the eng ine’s sp ec ified MC R point M w hich s uits the
dema nd of propeller pow er a nd spee d for the ship.
On the horizonta l a xis the e ngine s peed a nd on the
vertica l a xis the engine pow er a re show n in percent-
a ge sc a les . The sca les a re log a rithmic which mea ns
tha t, in this d ia gra m, pow er function curves like pro-
peller curves (3rd power), constant mean effective
pressure c urves (1st power) and consta nt s hipsp eed c urves (0.15 to 0.30 pow er)a re stra ight lines .
Specifiedmaximumcontinuous rating(M)
B a se d on the propuls ion a nd eng ine running po ints,
a s previous ly found, the la yout diag ram of a releva nt
ma in engine ma y be dra w n-in. The s pec ified MC R
point (M) must be inside the limita tion lines of t he
layout diagram; if it is not, the propeller speed will
have to be changed or another main engine type
must be c hosen. Yet, in spec ia l ca se s point M may
be located to the right of the line L 1-L2, se e “Opti -
mising P oint” be low .
Continuousservice rating(S)
The Co ntinuous s ervice rating is the p ow er at w hich
the engine is normally assumed to operate, and
point S is identical to the service propulsion point
(S P ) unles s a ma in engine driven sha ft generator is
installed.
Optimising point (O)=specified MCR (M)forenginewithoutVIT
The eng ine type is in its b a s ic d es ig n not fitted w ith
VITfuel pumps , so the s pec ified MC R is the po int at
which the engine is optimised –point M coincides
w ith po int O.
The optimising p oint O is the ra ting a t which the
turboc harger is matched, and at which the eng ine
timing a nd c ompress ion ratio a re a djusted.
Optimising point(O)forengine withVIT
The eng ine ca n be fitted w ith VIT fuel pumps , op-tion: 4 35 104, in orde r to improve the S FOC.
The op timising po int O is pla c ed o n line 1 of the loa d
diagra m, and the optimised pow er ca n be from 85 to
100% of point M's pow er, when turboc harger(s)a nd
engine timing are taken into consideration. When
optimising b etw een 93.5% and 100% of po int M's
pow er, overloa d running w ill still be p os s ible (110%
of M).
The op timis ing po int O is to b e plac ed inside th e la y-
out dia gra m. In fac t, the spec ified MCR point M c a n,in spec ial ca ses , be plac ed outside the layout d ia-
gram, but only by exceeding line L1-L2 , a n d o f
co urse , only provided tha t the op timising p oint O is
loc a ted inside the la yout dia gram a nd provided that
the MCR power is not higher than the L1 power.
Load Diagram
Definitions
The loa d d ia gra m, Fig. 2.03, defines the pow er and
speed limits for continuous as well as overload op-
eration of an installed engine having an optimising
point O a nd a sp ec ified MC R point M tha t co nfirms
the ship’s specification.
P oint A is a 100% s peed a nd pow er referenc e point
of the loa d diag ra m, and is d efined a s the point on
the propeller curve (line 1), through the optimising
point O, having the specified MCR power. Normally,
point M is e q ua l to po int A, but in spe cial ca s es , for
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2.03
Constantship speedlines
The co nsta nt ship spee d lines
, are shown at thevery top o f Fig. 2.02, indica ting the pow er req uired
at various propeller speeds in order to keep the
same ship speed, provided that the optimum pro -
peller diameter with a n optimum pitch/diameter
vatio is used at any given speed taking into consid -
eration the to ta l propulsion efficiency .
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exam ple if a s haft generator is insta lled, point M ma y
be p la ce d to the right o f point A on line 7.
The s ervice points o f the insta lled eng ine incorpo-
rate the engine power required for ship propulsion
a nd s haft g enerator, if insta lled.
Limits forcontinuousoperation
The co ntinuous service rang e is limited b y four lines :
Line 3 and line 9:
Line 3 represents the maximum acceptable speed
for co ntinuous ope ration, i.e. 105% of A.
If, in s pec ia l ca ses , A is loc a ted to the right o f line
L1-L2, the maximum limit, however, is 105% of L1 .
During tria l co nditions the ma ximum spe ed ma y be
extend ed to 107% of A, s ee line 9.
The a bove limits may in g enera l be extended to
105%, and during trial conditions to 107%, of the
nominal L1 speed of the engine, provided the tor-
siona l vibra tion c ond itions permit.
The ove rspe ed s et-po int is 109% of the s pe ed in A,howe ver, it may b e moved to 109% of the nominal
speed in L1, provide d that torsional vibra tion cond i-
tions permit.
Running a bo ve 100% of the no mina l L1 speed at a
load lower than about 65% specified MCR is, how -
ever, to be avoided for extended periods . Only
pla nts with controlla ble pitch propellers c a n reac h
this light running area.
Line 4:
Repres ents the limit a t w hic h an a mple air supp ly is
available for combustion and imposes a limitation
on the ma ximum co mbina tion of torque and s peed.
Line 5:
Represents the ma ximum mea n effective press ure
level (mep), w hich ca n be a cc epted for continuous
operation.
Line 7:
Represents the ma ximum pow er for co ntinuous
operat ion.
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Fig. 2.03b: Engine load diagram for engine with VIT
2.04
178 05 42-7.3
Fig. 2.03a: Engine load diagram for engine without VIT
A 100% re fe re nc e p oint
M S p e cifie d MC R p ointO O pt im is ing p oint
Line 1 P ropeller curve throug h optimising point (i = 3)(eng ine la yout curve)
Line 2 P ropeller curve, fouled hull a nd heavy w ea ther–heavy running (i = 3)
Line 3 S peed limitLine 4 Torq ue/sp ee d limit (i = 2)Line 5 Mea n effec tive pres sure limit (i = 1)
Line 6 P ropeller curve, clea n hull and ca lm wea ther –light running (i = 3), for propeller layout
Line 7 P ow er limit for co ntinuous running (i = 0)Line 8 Overloa d limitLine 9 S peed limit at sea trial
P oint M to b e loc a ted on line 7 (norma lly in point A)
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Limits foroverload operation
The overloa d s ervice rang e is limited a s fo llow s:
Line 8:
Represents the overload operation limitations.
The area b etw een lines 4, 5, 7 and the hea vy da she d
line 8 is a va ila ble for ove rloa d running for limited pe-
riod s only (1 hour pe r 12 hours).
Recommendation
Co ntinuous o pera tion w ithout limita tions is a llow ed
only within the a rea limited by lines 4, 5, 7 a nd 3 o fthe loa d diag ram, except for C P propeller plants
mentioned in the previous s ec tion.
The area be tw een lines 4 a nd 1 is a va ila ble for ope r-
ation in shallow waters, heavy weather and during
a cc eleration, i.e. for non-stea dy operation without
any strict time limitation.
After s ome time in opera tion, the ship’s hull a nd pro-
peller will be fouled, resulting in heavier running of
the prope ller, i.e. the prope ller curve w illmo ve to the
left from line 6 tow a rds line 2, and e xtra po w er is re-quired for propulsion in order to keep the ship’s
speed.
In ca lm wea ther co nditions , the extent of hea vy run-
ning o f the propeller will indica te the ne ed for clean-
ing the hull and possibly polishing the propeller.
Once the s pec ified MCR (a nd the o ptimising po int)
has been chosen, the capacities of the auxiliary
equipment will be adapted to the specified MCR,
a nd the turbocha rger etc. will be ma tched to the op-
timise d pow er, howe ver cons idering the s pec ified
MCR.
If the s pec ified MCR (a nd /or the o ptimis ing p oint) is
to be increa se d later on, this ma y involve a c hang e
of the pump a nd c ooler ca pa cities, retiming o f the
engine, c hang e o f the fuel valve nozzles, a djusting
of the cylinder liner coo ling, a s w ell a s rematc hing of
the turboc harger or even a cha nge to a la rger size of
turbocharger. In some cases i t can also require
la rger dimensions o f the piping sys tems.
It is the refore of utmos t importa nce to c ons ide r, al-
read y at the projec t sta ge , if the spe cifica tion sho uld
be p repa red for a la ter pow er increa se . This is to b eindica ted in item 4 02 010 of the Extent of Delivery.
ExamplesoftheuseoftheLoadDiagram
In the following are some examples illustrating the
flexibility of the layout and load diagrams and the
significa nt influence of the c hoice o f the o ptimising
point O.
The upper diag rams o f the exa mples sho w eng ines
without VIT fuel pumps , i.e. point A = O, the low er
diagrams show engines with VIT fuel pumps forwhich the optimising point O is normally different
from the specified MCR point M as this can improve
the S FOC a t pa rt loa d running.
Example 1 shows how to place the loa d diag ram for
a n eng ine w ithout sha ft ge nerato r co upled to a fixed
pitch propeller.
In example 2 are diagra ms for the sa me c onfigura-
tion, here with the optimising point to the left of the
heavy running propeller curve (2)obtaining an extra
eng ine ma rgin for hea vy running.
As for exa mple 1, example 3 show s the sa me la yout
for an eng ine w ith fixed pitch p ropeller (exa mple 1),
but with a s haft generato r.
Example 4 show s a spe cial ca se with a sha ft genera-
tor. In this c ase the sha ft generato r is c ut off, and the
GenS ets used when the engine runs at specified
MCR. This ma kes it pos sible to c hoos e a sm a ller en-
gine with a low er powe r output.
Example 5 show s diag ra ms for a n engine coupled to
a c ontrolla ble pitch propeller, with or w ithout a s ha ft
generato r, (cons ta nt speed or comb inato r curve
operation).
Example 6 shows where to place the optimising
point for an engine c oupled to a co ntrolla ble pitch
propeller, a nd operating a t cons tant sp eed.
For a p rojec t, the la yout diag ram s how n in Fig. 2.10
ma y be used for co nstruction of the ac tual loa d dia-
gram.
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For eng ines w itho ut VIT, the op timis ing po int O will
have the same power as point M and its propeller
curve 1 for engine layout will normally be selected
on the engine service curve 2 (for fouled hull and
heavy weather), as shown in the upper diagram of
Fig. 2.04a.
For eng ines with VIT, the optimising point O and its pro-peller curve 1 will normally be selected on the engine
service curve 2, see the lower diagram of Fig. 2.04a.
P oint A is then found a t the intersec tion betw een pro-peller curve 1 (2)and the consta nt power curve through
M, line 7. In this ca se point A is eq ual to po int M.
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2.06
Example1:Normal runningconditions.Enginecoupledtofixedpitchpropeller(FPP)andwithoutshaftgenerator
M Specif ied MCR of engine PointA of loaddiagramis found:S C o nt in uo us s e rvic e ra t in g o f e ng ine Line 1 P ro pe lle r c urve t hro ug h o pt im is ing p oint (O) is
eq ual to line 2O Optimising point of engineA Re fe re nc e po int o f lo a d d ia g ra m Line 7 C ons ta nt po we r line thro ug h s pe cifie d MC R (M)
MP S pe cifie d MC R fo r pro puls io n P o int A Inte rs ec tio n b etw ee n line 1 a nd 7
S P Continuous service rating of propulsion
Fig. 2.04a: Example 1, Layout diagram for normal running
conditions, engine with FPP, without shaft generator Fig. 2.04b: Example 1, Load diagram for normal running
conditions, engine with FPP, without shaft generator
WithVIT
WithoutVIT
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Once point A has bee n found in the la yout dia gram ,
the load diagram can be drawn, as shown in Fig.
2.04b and he nce the a ct ua l loa d limitation lines o f the
diesel engine may b e found by using the inclinations
from the co ns truction lines a nd the %-figures s ta ted .
A similar example 2 is shown in Fig. 2.05. In this
case , the optimising point O has been selected
mo re to the left tha n in example 1, ob ta ining a n extra
eng ine ma rgin for hea vy running o pera tion in hea vy
weather conditions. In principle, the light running
ma rgin has b een increas ed for this c a se.
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2.07
Example2:Special running conditions. Engine coupledtofixedpitchpropeller (FPP)and withoutshaftgenerator
M Sp ec ified MCR o f eng in e PointA of loaddiagramis found:S C o nt in uo us s e rvic e ra t ing o f e ng ine Line 1 P ro pe lle r c urve t hro ug h o pt im is ing p oint (O)
is eq ual to line 2O Opt imising point o f engine
A Re fe re nc e p oint o f lo a d d ia g ra m Line 7 C ons ta nt po we r line thro ug h s pe cifie d MC R (M)MP S pe cifie d MC R fo r pro puls io n P o int A Inte rs ec tio n b etw ee n line 1 a nd 7
SP Continuous service rating of propulsion
Fig. 2.05a: Example 2, Layout diagram for special running
conditions, engine with FPP, without shaft generator
178 39 23-1.0
WithVIT
WithoutVIT
178 05 46-4.6
Fig. 2.0b: Example 1, Load diagram for special running
conditions, engine with FPP, without shaft generator
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In examp le 3 a s ha ft ge nerato r (S G ) is inst a lled , and
therefore the service po w er of the eng ine also ha s to
incorporate the extra shaft power required for the
sha ft generator’s e lectrica l power prod uction.
In Fig. 2.06a, the engine service curve shown for
heavy running incorporates this extra power.
The optimising point O will b e cho sen on the eng ine
service c urve as show n, but ca n, by an a pproxima-tion, b e loc a ted on c urve 1, throug h point M.
P oint A is then found in the sa me wa y as in exa mple
1, and the loa d diagram ca n be drawn a s s hown in
Fig. 2.06b.
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2.08
Example3:Normal running conditions. Engine coupled tofixed pitch propeller (FPP)and withshaftgenerator
M Sp ec ified MCR o f eng in e PointA of load diagramis found:
S C o nt inuo us s e rvic e ra t ing o f e ng in e Lin e 1 P ro pe lle r c urve t hro ug h o pt im is ing p oint (O)
O Optimis ing po int o f e ng ine Line 7 C ons ta nt po we r line thro ug h s pe cified MC R (M)
A= O R efe re nc e p oin t o f lo a d d ia g ra m P o in t A Inte rs ec tio n b etw ee n line 1 a nd 7
MP Spec if ied MCR for propulsion
SP Continuous service rating of propulsion
S G S h a ft g e ne ra t or p ow e r
Fig. 2.06a: Example 3, Layout diagram for normal running
conditions, engine with FPP, without shaft generator
Fig. 2.06b: Example 3, Load diagram for normal running
conditions, engine with FPP, with shaft generator
178 39 25-5.1
178 05 48-8.6
WithVIT
WithoutVIT
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Example4:Special running conditions. Engine coupledtofixed pitch propeller (FPP)and withshaftgenerator
2.09
M Sp ec ified MCR o f eng in e PointA of loaddiagramis found:
S C o nt in uo us s e rvic e ra t ing o f e ng ine Line 1 P ro pe lle r c urve t hro ug h o pt im is ing p oint (O) o rpoint S
O Optimis ing po int o f eng ine P oint A Inte rs ec tio n b etw een line 1 a nd line L1 - L3
A Re fe re nc e po int o f lo a d d ia g ra m P o int M Lo ca te d o n c ons ta nt po we r line 7 thro ug hpo int A. (A = O if the e ng ine is w ithout VIT)and w ith MP's speed.
MP Spec if ied MCR for propulsion
SP Continuous service rating of propulsion
S G S ha ft g ene ra to r
See text on next page.
Fig. 2.07a: Example 4. Layout diagram for special running
conditions, engine with FPP, with shaft generator Fig. 2.07b: Example 4. Load diagram for special running
conditions, engine with FPP, with shaft generator
178 06 35-1.6
178 39 28-0.2
WithVIT
WithoutVIT
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Example4:
Also in this spec ia l cas e, a sha ft generator is in-sta lled b ut, compa red to Exa mple 3, this c a se ha s a
sp ec ified MCR for propulsion, MP , pla ce d a t the top
of the la yout diagra m, se e Fig. 2.07a.
This involves tha t the inten de d s pe c ified MC R of the
eng ine M’ w ill be plac ed o utside the top of the la yout
diagram.
One solution co uld b e to c hoos e a la rger diesel
engine w ith a n extra cylinder, but a nother and
chea per solution is to reduc e the e lec trica l power
production of the shaft generator when running in
the upper propulsion power range.
In choosing the latter solution, the required speci-
fied MCR power can be reduced from point M’ to
po int M a s s how n in Fig. 2.07a. Therefo re, whe n run-ning in the upper propulsion power range, a diesel
generato r has to ta ke over a ll or pa rt of the electrica l
pow er production.
However, such a situation will seldom occur, as
ships are rather infrequently running in the upper
propulsion pow er range.
Point A, having the highest possible power, is
then found a t the intersec tion of line L1-L3 w ith
line 1, see Fig. 2.07a, and the corresponding load
diag ram is d raw n in Fig. 2.07b. P oint M is found
on line 7 at MP’s spe ed.
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Fig. 2.08 shows two examples: on the left diagrams
for a n engine without VITfuel pump s (A = O = M), onthe rig ht, for a n engine w ith VITfuel pump s (A= M).
Layoutdiagram- withoutshaftgeneratorIf a c ontrolla ble pitc h propeller (CP P ) is a pplied , the
co mbinato r curve (of the propeller) w ill norma lly b e
selected for loaded ship including sea margin.
The comb inator curve may for a given prope ller spee d
have a given propeller pitch, and this may be heavy run-
ning in heavy weather like for a fixed pitch propeller.
Therefore it is recomme nded to use a light running
comb inator curve a s show n in Fig. 2.08 to ob tain an
increased operation margin of the diesel engine in
hea vy wea ther to the limit indica ted by curves 4 and 5.
Layoutdiagram- withshaftgeneratorThe ha tched area in Fig. 2.08 s hows the recom-
mended spe ed rang e betw een 100% a nd 96.7% of
the specified MCR speed for an engine with shaft
generator running at constant speed.
The service point S ca n be loca ted at any point
within the ha tched a rea.
The proced ure s hown in exa mples 3 a nd 4 for en-
gines w ith FP P c a n also be a pplied here for eng ineswith CP P running w ith a co mbina tor curve.
TheoptimisingpointO for eng ines w ith VITma y becho s en on the p ropeller curve throug h point A = M
with an optimised power from 85 to 100% of the
spe cified MCR a s mentioned before in the s ection
de a ling w ith op timising p oint O.
LoaddiagramTherefore, when the eng ine’s sp ec ified MCR po int
(M) has been chosen including engine margin, sea
margin a nd the pow er for a sha ft generator, if in-sta lled, point M may be us ed a s point A of the loa d
dia gram, which ca n then be draw n.
The po sition of the co mbina tor curve ens ures the
maximum load range within the permitted speed
rang e for engine opera tion, a nd it still lea ves a rea-sonable margin to the limit indicated by curves 4
a nd 5.
Example 6 will give a more detailed description of
how to run co nsta nt speed with a C P propeller.
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
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Example5:
Engine coupledtocontrollablepitchpropeller (CPP)withorwithoutshaftgenerator
M S pec ified MC R of eng ine O Optimis ing point o f eng ine
S C ontinuous s ervic e ra ting o f eng ine A Referenc e po int o f lo ad d ia g ra m
Fig. 2.08: Example 5: Engine with Controllable Pitch Propeller (CPP), with or without shaft generator
2.11
WithVITWithoutVIT 178 39 31-4.1
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Example 6:Engines withVIT fuelpumpsrun-ning atconstantspeed withcontrollablepitch
propeller (CPP)
Fig. 2.09a Constant speed curve through M , nor -
mal and correct location of the optimising po int O
Irres pec tive of w hether the eng ine is o pera ting o n a
prope lle r curve or on a constan t speed curve
through M, the optimising point O must be located
on the propeller curve through the specified MCR
point M or, in spe cial ca se s, to the left of point M.
The rea son is tha t the prope ller curve 1 throug h the
optimising point O is the layout curve of the engine,
a nd the interse ction betwee n curve 1 and the ma xi-mum pow er line 7 throug h point M is e q ua l to 100%
pow er a nd 100%s peed, point Ao f the loa d dia gram
- in this c a se A= M.
In Fig. 2.09a the optimising point O has been placed
co rrectly, and the step-up gea r a nd the sha ft gener-a tor, if insta lled, ma y be sync hronise d o n the con-sta nt speed curve through M.
Fig. 2.09b: Constant speed curve through M ,
wrongposition of optim ising point O
If the engine ha s b een s ervice -optimised in point O
on a c ons ta nt spee d curve throug h point M, then the
sp ec ified MCR point M wo uld be plac ed o utside the
load diagram, and this is not permissible.
Fig. 2.09c: Recommended constant speed run -
ning curve, lower than speed M
In this c a s e it is a ss umed tha t a s ha ft genera tor, if in-sta lled, is sync hronised a t a low er co nsta nt main en-gine speed (for example with speed equal to O or
low er) a t which improved C P propeller efficiency isobtained for part load running.
In this layout example where an improved CP pro-peller efficiency is o bta ined d uring e xtend ed peri-ods of part loa d running, the s tep-up ge a r and the
shaft generator have to be designed for the ap-plied lower co nsta nt engine spe ed.
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MAN B &W Diesel A/S S 50MC-C P rojec t G uide
2.12
Fig. 2.09: Running at constant speed with CPP
Fig. 2.09a: Normal proced ure
Constant speed servicecurve through M
Constant speed servicecurve through M
Fig. 2.09b: Wrong procedure
Logarithmic scales
M: Specified MCRO: Optimised pointA: 100% power and spee d o f loa d
dia g ram (norma lly A= M)
Fig. 2.09c: Rec ommended procedure
Constant speed servicecurve w ith a s peed low erthan M
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Fig. 2.10: Diagram for actual project
178 06 86-5.1
2.13
Fig. 2.10 contains a layo ut diag ram that ca n be use d for con-struction of the load diagram for an actual project, using the%-figures s ta ted a nd the inclina tions of the lines .
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Specific Fuel OilConsumption
Highefficiency/conventional turbochargers
The high efficiency turbocharger is applied to the
eng ine in the ba sic d es ign w ith the view to ob ta ining
the lowest possible Specific Fuel Oil Consumption
(SFOC)values.
With a conventional turboc harger the a mount of air
req uired for co mbustion purpos es c a n, how ever, be
a djusted to provide a higher exhaust g a s tempera -
ture, if this is nee d ed fo r the exha us t ga s b oiler. The
ma tching of the engine and the turboc harging s ys -
tem is then modified, thus increasing the exhaustga s temperature by 20 °C.
This mo dific a tion will lea d to a 7-8% reduc tion in the
exhaust gas amount, and involve an SFOC penalty
of up to 2 g /B HP h.
So this engine is available in two versions with re-
spec t to the SFOC, s ee Fig. 2.11.
• (A) With hig h effic ienc y turboc ha rger,
(4 59 104)
• (B ) With conventional turbo cha rger,
option: 4 59 107
The ca lculation of the expec ted s pec ific fuel oilc on-sumption (S FOC) can be ca rried out by means of
Fig. 2.12 for fixed pitc h propeller a nd 2.13 for con-trolla ble pitch propeller, co nsta nt sp eed . Through-out the whole loa d a rea the S FOC of the eng ine de-pends on where the optimising point O is chosen.
SFOC atreferenceconditions
The SFOC is ba se d on the referenc e amb ient cond i-tions s ta ted in IS O 3046/1-1986:
1,000 mba r amb ient a ir pres sure
25 °C ambient air temperature
25 °C s ca venge a ir co ola nt tempera ture
a nd is rela ted to a fuel oil w ith a low er ca lorific va lue
of 10,200 kca l/kg (42,700 kJ /kg).
For low er ca lorific va lues a nd for a mbient co nditions
tha t a re different from the ISO reference c ond itions ,
the SFOC w ill be a djusted a cc ording to the co nver-sion factors in the below table provided that the
ma ximum c ombus tion pressure (P ma x) is adjustedto the nominal value (left column), or if the P ma x is
not re-ad jus ted to the nom ina l va lue (righ t column).
WithP ma xadjusted
WithoutP ma xadjusted
P a ra me te r C o nd itio n c ha ng eSFOCchange
SFOCchange
Sc av. a ir coolanttemperature per 10 °C rise + 0 .60% + 0 .41%
Blow er inlettemperature per 10 °C rise
+ 0.20% + 0.71%
Blow er inletpressure per 10 mba r rise - 0.02% - 0.05%
Fuel oil lowe rcalorific value
rise 1%(42, 700 kJ /kg )
-1.00% - 1.00%
With for insta nce 1 °C increas e of the s ca venge a ir
coo la nt temperature , a corresponding 1 °C in -
crease of the s ca venge a ir temperature will occur
and involves an SFOC increase of 0.06% if P ma x is
adjusted.
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MAN B &W Diesel A/S S 50MC-C P rojec t G uide
Fig. 2.11: Example of part load SFOC curves for the two
engine versions
2.14
178 15 22-9.1
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SFOC guarantee
The S FOC gua rantee refers to the ab ove IS O refer-ence conditions and lower calorific value, and is
guaranteed for the power-speed combination in
which the engine is optimised (O) and fulfilling the
IMO NOx e miss ion limita tions .
The SFOC guarantee is given w ith a marg in of 5%.
As SFOC and NOx are interrelated paramaters, an
engine offered without fulfilling the IMO NO x limita -
tions only has a tolerance of 3% of the S FOC.
Without/withVIT fuel pumps
This e ng ine type is in its b a s ic d es ig n fitte d w ith fuel
pump s w itho ut Va ria b le Injec tion Timing (VIT), so
the optimis ing point " O" ha s then to be a t the sp ec i-
fied MCR pow er "M" .
VITfuel pumps c a n, how ever, be fitted a s a n option:
4 35 104, a nd in tha t ca s e they ca n be optimise d be -
tw een 85-100% of the s pec ified MCR, point " M" , as
for the other large MC engine types.
Engines w ith VITfuel pumps c a n be pa rt-loa d o pti-mised between 85-100% (normally at 93.5%)of the
specified MCR.
To fac ilita te the gra phic c a lculation of SFOC w e use
the sa me diagram 1 for guida nce in both ca se s, the
location of the optimising point is the only differ-
ence.
The exa ct S FOC ca lcula ted b y our computer pro-
gra m will in the part loa d a rea from ap prox. 60-95%
give a slightly improved S FOC co mpa red to engines
without VITfuel pumps.
Examples of graphic calculation of SFOC
Diagram 1 in figs. 2.12 and 2.13 valid for fixed pitch
propeller and constant speed, respectively, shows
the reduc tion in SFOC , rela tive to the S FOC a t nomi-
nal ra ted MCR L1 .
The s olid lines a re va lid a t 100, 80 a nd 50% of the
optimised power (O).
The op timising po int O is dra w n into the a bo ve-
mentioned Diag ram 1. A stra ight line a long the
constant mep curves (parallel to L1-L3) is drawn
throug h the o ptimis ing po int O. The line interse c-
tions of the s olid lines a nd the ob liq ue lines indi-ca te the reduc tion in s pec ific fuel oil co nsumpt ion
a t 100%, 80% a nd 50% of the optimis ed pow er,
rela ted to the SFOC sta ted for the nominal MCR
(L1) rating a t the a ctua lly a vaila ble engine version.
The S FOC c urve for an eng ine w ith co nventiona l
turbo cha rger is identica l to that for an e ngine w ith
high efficiency turboc harger, but loc a ted a t 2
g /B HP h highe r leve l.
In Fig. 2.14 an example of the calculated SFOC
curves a re show n on Dia gram 2, va lid for two a l-ternative engine ratings: O 1 = 100% M and
O2 = 85%M.
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402 000 004 198 21 26
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
Data at nominal MCR (L1): S 50MC -C Da ta of optimis ing point (O)
100% Po we r:
100% Speed :
High efficiency turbo cha rger:
Co nventiona l turboc harger:
127126128
B HPr/min
g/B HP hg/B HP h
P ow er: 100% of (O)
S peed : 100% of (O)
SFOC found:
B HP
r/ming/B HP h
Note: Engines without VITfuel pumps have to be optimised at the specified MCR power 178 88 08-5.0
178 15 92-3.0
Fig. 2.12: SFOC for engine with fixed pitch propeller
178 43 63-9.0
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MAN B &W Diesel A/S S 50MC-C P rojec t G uide
402 000 004 198 21 26
2.17
Data at nominal MCR (L1): S 50MC -C Da ta of optimis ing point (O)
100% Po we r:
100% Speed :
High efficiency turbo cha rger:Co nventiona l turboc harger:
127
126128
B HPr/min
g/B HP hg/B HP h
P ow er: 100% of (O)
S peed : 100% of (O)
SFOC found:
B HP
r/min
g/B HP h
Note: Engines without VITfuel pumps have to be optimised at the specified MCR power
178 15 91-1.0
Fig. 2.13: SFOC for engine with constant speed 178 43 63-9.0
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402 000 004 198 21 26
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
2.18
Data at nominal MCR (L1): 6S 50MC -C Da ta o f o ptimis ing po int (O) O1 O2
100% Po we r:
100% Speed :
High efficiency turbocharger:
12,870127126
B HPr/ming/B HP h
P ower: 100%of O
Speed: 100%of O
SFOC found:
10,680 B HP
114.3 r/min
124.3 g/B HP h
9,080 BHP
108.3 r/min
121.7 g/B HP h
Note: Engines without VITfuel pumps have to be optimised at the specified MCR power
178 15 88-8.0
Fig. 2.14: Example of SFOC for 6S50MC-C with fixed pitch propeller, high efficiency turbocharger and VIT fuel pumps
178 39 37-5.0
178 31 79-0.0
O1: Optimised in M
O2: Optimise d a t 85% of pow er M
P oint 3: is 80% of O2 = 0.80 x 85% of M = 68% M
P oint 4: is 50% of O2 = 0.50 x 85% of M = 42.5% M
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Fuel Consumption at an Arbitrary Load
Once the engine has been optimised in point O,sho w n on this Fig. , the spec ific fuel oilc ons umption
in an arbitrary point S 1, S 2 o r S 3 can be estimated
ba sed on the SFOC in points “1" a nd ”2" .
These S FOC values c a n be ca lcula ted b y using the
g rap hs in Fig . 2.12 for the fixed pitch prope ller curve
I a nd Fig. 2.13 for the co nsta nt spe ed curve II, ob -
ta ining the S FOC in points 1 a nd 2, respe ct ively.
Then the S FOC fo r po int S 1 can be calculated a s an
interpolation b etwe en the S FOC in points “1" a nd
”2" , a nd for point S 3 as a n extra polation.
The S FOC curve through points S 2, to the left ofpoint 1, is s ymme trica l a bo ut point 1, i.e. a t spe ed s
lower than that of point 1, the SFOC will also in-
crease.
The ab ove-mentioned metho d provide s only a n ap-
proximate figure. A more precise indication of the
expected S FOC a t any load ca n be ca lculated b y
using our co mputer progra m. This is a s ervice w hich
is a vaila ble to our cus tomers on reques t.
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
402 000 004 198 21 26
Fig. 2.15: SFOC at an arbitrary load
178 05 32-0.1
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EmissionControl
All MC engines are delivered so as to comply with
the IMO speed dependent NOx limit, mea sured a c-
co rding to IS O 8178 Tes t C yc les E2/E3 for Heavy
Duty Dies el Engines.
IMONOx limits, i.e.0-30% NOx reduction
The primary me thod of NOx co ntrol, i.e. eng ine a d -
justment a nd c omponent mod ifica tion to a ffect the
engine combustion proces s directly, enables re-
ductions of up to 30% to b e a chieved.
The S pec ific Fuel Oil Co nsump tion (S FOC) a nd the
NOx a re interrela ted pa ra meters, a nd a n engine of-
fered with a gua ra nteed SFOC a nd also guaranteed
to c om ply with the IMO NOx limitation willbe subject
to a 5% fuel consumption tolerance.
30-50% NOx reduction
Water emulsification of the heavy fuel oil is a well
proven prima ry method . The type o f homog enizer is
either ultrasonic or mechanical, using water fromt he f re s h w a t e r g e n e ra t o r a n d t he w a t e r m is t
ca tche r. The press ure of the homog enised fuel ha s
to be increased to prevent the formation of the
stea m and c a vitation. It may be nec ess a ry to modify
some of the engine components such as the fuel
pumps, camshaft, and the engine control system.
Upto 95-98% NOx reduction
This reduction ca n be ac hieved b y mea ns of s ec-
ondary methods, such as the SCR (Selective Cata -
lytic Reduction), which involves an after-treatment
of the exhaust ga s.
Plants designed ac cording to this method have
been in service since 1990 on four vessels, using
Haldor Topsøe ca talysts and ammonia as the re-
ducing ag ent, urea c an a lso b e used.
The compa ct S CR unit ca n be loc a ted s epa ra tely in
the eng ine room or horizonta lly on top of the engine.
The c ompac t S CR reac tor is mounted before the
turbo cha rger(s ) in order to have the optimum work-
ing tempe rature for the ca ta lyst.
More deta iled informa tion c a n be found in our publi-
cations:
P . 331 Emiss ions Co ntrol, Tw o-stroke Low -spee d
Engines
P. 333 How to deal with Emission Control.
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3. TurbochargerChoice
Turbocharger Types
The MC engines a re des igne d for the applica tion of
eithe r MAN B &W, AB B or Mits ub ishi (MHI) turbo -
cha rgers, a nd are ma tched to comply with the IMO
speed dependent NOx limitations, measured ac -
co rding to IS O 8178 Tes t C yc les E2/E3 for Heavy
Duty Dies el Engines.
The turbocha rger choice is ma de w ith a view to o bta in-
ing the lowes t possible Specific Fuel Oil Consumption
(SFOC) values, i.e. w ith the nominal MCR and the high
efficiency turbocha rgers sta ted in Fig. 3.01a .
The a mount of a ir req uired for the comb ustion ca n,
however be ad justed to provide a higher exhaust
gas temperature, if this is needed for the exhaust
ga s b oiler. In this c a se the co nventiona l turboc har-
ge rs a re to be a pplied , se e Fig. 3.01b. The S FOC is
then ab out 2g/B HPh higher, se e s ection 2.
For other la yout po ints tha n L1 , the size of turbo-
cha rger may be d ifferent, dep end ing on the point at
which the engine is to to be optimised, see the fol-
low ing layout diagra ms.
Figs . 3.02 a nd 3.06 show the a pproxima te limits for
a pplica tion o f the MAN B&W turboc ha rgers, Figs .
3.03, 3.04, 3.07 a nd 3.08 for ABB types TP L and
VTR, res pec tively, a nd Figs . 3.05 a nd 3.09 for MHI
turbochargers.
In order to clean the turbine blad es a nd the noz zle
ring assembly during operation, the exhaust gas in-
let to the turbocha rger(s) is provided with a dry
cleaning sys tem using nut shells a nd a w a ter wa sh-ing system.
As s tanda rd , the eng ine is equ ipped with one
turbo cha rger loc a ted on the a ft end (4 59 124).
The S 50MC-C type engine c a n, as a n option: 4 59
123, be supplied with the turboc harger loc a ted on
the exhaust side.
Tw o turboc ha rgers c a n optiona lly be a pplied , if this
is des ira ble due to s pa ce requirements, o r for other
reasons, option: 4 59 113.
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
459 100 250 198 21 27
3.01
Fig. 3.01b: Conventional turbochargers, option: 4 59 107
C yl. MAN B &W AB B AB B MHI
4 1 x NA48/S 1 x TP L73-B 12 1 x VTR564D-21 1 x MET53S E
5 1 x NA57/T9 1 x TP L77-B 11 1 x VTR564D-32 1 x MET53S E
6 1 x NA57/T9 1 x TP L77-B 12 1 x VTR564D-32 1 x MET66S E
7 1 X NA57/T9 1 x TP L80-B 11 1 x VTR714D-32 1 x MET66S E
8 1 X NA70/T9 1 x TP L80-B 12 1 x VTR714D-32 1 x MET66S E
Fig. 3.01a: High efficiency turboc hargers
C yl. MAN B &W AB B AB B MHI
4 1 x NA48/S 1 x TP L73-B 11 1 x VTR454D-32 1 x MET53S E
5 1 x NA48/S 1 x TP L73-B 12 1 x VTR564D-32 1 x MET53S E
6 1 x NA57/T9 1 x TP L77-B 11 1 x VTR564D-32 1 x MET66S E
7 1 X NA57/T9 1 x TP L77-B 12 1 x VTR564D-32 1 x MET66S E
8 1 X NA57/T9 1 x TP L80-B 11 1 x VTR714D-32 1 x MET66S E
178 39 04-2.1
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459 100 250 198 21 27
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
Fig. 3.02: Choice of high efficiency turbochargers, make MAN B&W
3.02
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MAN B &W Diesel A/S S 50MC-C P rojec t G uide
459 100 250 198 21 27
3.03
Fig. 3.03: Choice of high efficiency turbochargers, make ABB turbochargers, type TPL
178 39 08-8.1
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459 100 250 198 21 27
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
3.04
Fig. 3.04: Choice of high efficiency turbochargers, make ABB, type VTR
178 93 11-1.0
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MAN B &W Diesel A/S S 50MC-C P rojec t G uide
459 100 250 198 21 27
3.05
Fig. 3.05: Choice of high efficiency turbochargers, make MHI
178 39 12-3.1
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MAN B &W Diesel A/S S 50MC-C P rojec t G uide
459 100 250 198 21 27
3.07
Fig. 3.07: Choice of conventional turbochargers, make ABB, type TPL
178 47 21-1.0
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459 100 250 198 21 27
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
3.08
178 47 22-3.0
Fig. 3.08: Choice of conventional turbochargers, make ABB, type VTR
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MAN B &W Diesel A/S S 50MC-C P rojec t G uide
459 100 250 198 21 27
Fig. 3.09: Choice of conventional turbochargers, make MHI
3.09
178 47 23-5.0
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Cut-Off or By-Pass of Exhaust Gas
The exhaust ga s ca n be c ut-off or by-pass ed theturbo cha rgers using either of the follow ing four sys -
tems.
Turbochargercut-outsystemOption:460110
This s ys tem, Fig. 3.10, is to b e inves tiga ted c a se b y
ca se a s its a pplica tion depend s on the la yout of the
turbocharger(s), can be profitably to introduce on
engines with twoturbochargers if the engine is tooperate for long periods a t low loa ds of ab out 50%
of the optimise d po we r or below.
The adva ntag es a re:
Reduced S FOC if one turboc harger is cut-out
• Reduced heat load on essential engine compo-
nents, due to increas ed s ca venge a ir press ure.
This res ults in les s m a intena nce a nd lowe r spa re
parts requirements
• The increa se d sc a venge a ir press ure permits
running without a uxilia ry blowe rs d ow n to
20-30% of specified MCR, instead of 30-40%,
thus saving electrical power.
The s a ving in SFOC a t 50% of optimise d p ow er is
a bo ut 1-2 g/B HP h, while la rger sa vings in S FOC a reobta inable at lower loa ds .
459 100 250 198 21 27
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
3.10
Fig. 3.10: Position of turbocharger cut-out valves
178 06 93-6.0
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Valve forparticalby-passOption:460117
Va lve for pa rtica l by-pas s o f the exhaust g a s round
the hig h effic ienc y turbo cha rge r(s ), Fig. 3.11, c a n b e
used in order to obtain improved SFOC at part
loa ds. For engine loads ab ove 50% of optimised
pow er, the turboc harger allow s pa rt of the exha ust
ga s to be b y-pas sed round the turbo cha rger, giving
an increased exhaust temperature to the exhaust
ga s b oiler.
At loa ds be low 50% of op t imised power , the
by-pass closes automatically and the turbocharger
wo rks under improved co nditions with high effi-
ciency. Furthermore, the limit for activating the aux-ilia ry blow ers d ecrea ses co rrespondingly.
Totalby-pass foremergencyrunningOption:460119
By-pass of the total amount of exhaust g as round
the turbocharger, Fig. 3.12, is only used for emer-
gency running in case of turbocharger failure.
This e na bles the e ngine to run a t a higher loa d tha n
with a locked rotor under emergency conditions.
The eng ine’s exha ust g a s rec eiver will in this c a se
be fitted w ith a by-pa ss fla nge of the sa me diameter
a s the inlet pipe to the turboc ha rger. The emerg enc y
pipe is the ya rd’s d elivery.
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
459 100 250 198 21 27
Fig. 3.11: Valve for partical by-pass
3.11
Fig. 3.12: Total by-pass of exhaust for emergency running
178 06 72-1.1 178 06 69-8.0
178 44 67-1.0
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4 ElectricityProduction
Introduction
Next to po w er for propulsion, elec tricity produc tion
is the large s t fuel co nsumer on boa rd. The electricity
is produced by using one or more of the following
types o f ma chinery, either running a lone or in pa rallel:
Auxilia ry dies el g enera ting sets
• Main eng ine driven genera tors
• S team d riven turbog enera tors
• Emergenc y diese l generating sets .
The ma chinery insta lled should be se lected ba sed
on a n econo mica l eva luation of first cos t, operating
costs, and the demand of man-hours for mainte-
nance.
In the following, technical information is given re-
ga rding m a in eng ine d riven g enera tors (P TO) a nd
the auxiliary diesel generating sets produced by
MAN B &W.
The po s sibility of us ing a turbog enera tor driven b y
the steam produced by a n exhaust g as boiler ca n
be evaluated ba sed on the exhaust ga s da ta.
Power Take Off (PTO)
With a ge nerato r co upled to a P ow er Ta ke Off (P TO)
from the main engine, the electricity can be pro -
duced b as ed on the main engine’s low S FOC a nd
use of heavy fuel oil. Several sta nda rdise d P TO sys -
tems are available, see Fig. 4.01 and the designa -
tions on Fig. 4.02:
P TO/RC F
(Pow er Take Off/ Renk Constant Frequency):
G enerator giving c onstant freq uency, b as ed on
mecha nica l-hydraulica l spee d co ntrol.
P TO/C FE
(P ow er Ta ke Off/C ons ta nt Freq uenc y Elec tric a l):
G enerator giving c onstant freq uency, b as ed on
electrical frequency control.
P TO/G C R
(P ow er Ta ke Off/G ea r Cons ta nt Ra tio):
G enera tor co upled to a cons tant ra tio step-up gea r,
used only for engines running a t cons tant s peed.
The DMG /CFE (Direct Mounted Generator/Constant
Frequency Electrical) and the SMG/CFE (Shaft
Mounted Generator/Constant Frequency Electrical)
a re spec ial des igns within the P TO/CFE group in
w hich the g enerato r is c oupled d irectly to the ma in en-gine crankshaft and the intermediate shaft, respec-tively, w ithout a ge a r. The electrica l output of the g en-erato r is co ntrolled by elec trica l frequenc y c ontrol.
Within ea ch P TO sys tem, s everal designs a re a vail-a ble, depending on the pos itioning o f the gea r:
BWI:
G ea r with a vertica l generato r mounted onto the
fore end of the diesel engine, without any con-
nections to the ship structure.
BWII:
A free-sta nding gea r mounted on the tank top
and connected to the fore end of the diesel en -gine, w ith a ve rtica l or horizonta l ge nerato r.
B W III:
A cranksha ft gea r mounted o nto the fore end of
the diese l engine, with a s ide-mounted generato r
without any connections to the ship structure.
On this type of eng ine, spec ia l a ttention ha s to be
pa id to the spa ce req uirements for the BWIII sy s-tem if the turbocharger is located on the exhaust
side.
B W IV:
A free-standing step-up gear connected to the
intermediate shaft, with a horizontal generator.
The mos t popula r of the ge a r bas ed a lterna tives a re
the type des igna ted B W III/RCF for pla nts with a
fixed pitch p ropeller (FP P ) a nd the B W IV/G CR for
plan ts w ith a c ont rolla ble pitch prop eller (C P P ). The
B W III/RCF req uires no s epa rate s ea ting in the s hip
and only little attention from the shipyard with re-
spe ct to a lignment.
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
485 600 100 198 21 28
4.01
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485 600 100 198 21 28
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
4.02
Alterna tive types a nd la youts of s ha ft g enera tors Des ig n S ea ting Tota l
efficiency (%)
P T
O / R C F
1a 1b B W I/RC F On eng ine(vertical generator)
88-91
2a 2b B W II/RC F On ta nk top 88-91
3a 3b B W III/RC F On eng ine 88-91
4a 4b B W IV/RC F On ta nk top 88-91
P T
O / C F E
5a 5b DMG /C FE On eng ine 84-88
6a 6b S MG /CFE On ta nk top 84-88
P T O / G C R
7 B W I/G C R On eng ine(vertical generator)
92
8 B W II/G C R On ta nk top 92
9 B W III/G C R On eng ine 92
10 B W IV/G CR On ta nk top 92
Fig. 4.01: Types of PTO
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For further information pleas e refer to o ur publica tion:
P . 364 “Shaf t Genera torsP ow er Ta ke Off
from the Main Engine”
Which is also available at the Internet address:
ww w.ma nbw .dk under “Libraries”.
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
485 600 100 198 21 28
Fig. 4.02: Designation of PTO
4.03
Powertake off:BW III S50-C/RCF 700-60
178 39 55-6.0
50: 50 Hz
60: 60 Hz
kWo n g enerator terminals
RCF: Renk consta nt freq uency unitCFE: Elec trica lly freq uency co ntrolled unit
G CR: Step-up gea r with consta nt ratio
Engine type o n which it is a pplied
Layo ut of P TO: S ee Fig. 4.01
Ma ke: MAN B &W
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PTO/RCF
S id e mounte d g ene rat or, BWIII/RC F(Fig. 4.01, Alternative 3)
The P TO/RC F gene rator s ys tems ha ve be en de vel-
oped in close cooperation with the German gear
manufacturer Renk. A complete package solution is
offered, comprising a flexible coupling, a step-up
gear, an epicyclic, variable-ratio gear with built-in
clutch, hydraulic pump a nd moto r, a nd a sta nda rd
ge nerator, se e Fig. 4.03.
For marine engines with controllable pitch propel-
lers running a t cons ta nt engine s peed , the hydraulic
sys tem ca n be d ispens ed w ith, i.e. a P TO/G CR d e-sign is normally use d.
Fig. 4.03 sho w s the principles of the P TO/RCF a r-
rangement. As can be seen, a step-up gear box
(called crankshaft gear) with three gear wheels isbo lted d irectly to the frame b ox of the ma in engine.
The bea rings of the three g ea r w heels a re mounted
in the gea r bo x s o that the w eight of the wheels is not
ca rried by the cranks ha ft. In the fra me box, be tw een
the crankca se a nd the gea r drive, spa ce is a vaila ble
for tuning wheel, c ounterwe ights , a xia l vibration
da mper, etc.
The first gea r w heel is c onnec ted to the c ranksha ft
via a special flexible coupling made in one piece
with a tooth coupling driving the crankshaft gear,
thus is olating it a ga inst torsional a nd axial vibrations.
By m ea ns of a simple a rra ngement, the sha ft in the
crankshaft gearcarrying the first gearwheeland the
485 600 100 198 21 28
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
4.04
Fig. 4.03: Power Take Off with Renk constant frequency gear: BW III/RCF, option: 4 85 253
178 00 45-5.0
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Yard d eliveries a re:
1. Co oling wa ter pipes to the built-on lubrica ting oilcooling system, including the valves.
2. Electrica l pow er supply to the lubrica ting oil
sta nd-by pump built on to the RC F unit.
3. Wiring b etwe en the generator and the operator
co ntrol panel in the s witch-bo a rd.
4. An external permanent lubrica ting oil filling-up
connection ca n be esta blished in co nnection w ith
the RCF unit. The sys tem is sho wn in Fig. 4.07 “Lu -
brica ting oil system for RCF g ea r”. The d osa getank and the perta ining p iping a re to b e d elivered
by the ya rd. The size of the dosage ta nk is sta ted in
the ta ble for RCF gea r in “Neces sa ry ca pa cities for
P TO/RC F” (Fig. 4.06).
The neces sa ry preparations to b e ma de o n the en-gine are specified in Figs. 4.05a and 4.05b.
Additionalcapacities required forBWIII/RCF
The ca pa cities s ta ted in the “List of ca pa cities ” forthe main engine in q uestion a re to be increa sed by
the additional ca pac ities for the crankshaft gear and
the RCF ge a r sta ted in Fig. 4.06.
485 600 100 198 21 28
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
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MAN B &W Diesel A/S S 50MC-C P rojec t G uide
485 600 100 198 21 28
178 05 11-7.0
kW G enerato r
700-60 1200-60 1800-60 2600-60
A 2455 2455 2595 2595
B 776 776 776 776
C 3115 3115 3395 3395
D 3510 3510 3790 3790
F 1826 1946 2066 2176
G 2064 2064 2364 2364
H 2439 2941 3346 4676
S 380 470 500 590
System mass (kg) with generator:
22750 26500 37100 48550
System mass (kg) without generator:20750 23850 32800 43350
The sta ted kW, which is a t gene rato r termina ls, is a va ila ble betw een 70% a nd 100% of the engine spe ed a t
specified MCR
Space requirements for the 2600kWgenerator has to be investigated case by case
Dimens ion H: This is only valid for A. van Ka ick ge nerato r type DS G , enclos ure IP 23,
freq uency = 60 Hz, s peed = 1800 r/min
Fig. 4.04: Space requirement for side mounted generator PTO/RCF type BWlll S50-C/RCF
178 39 57-8.0
4.07
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485 600 100 198 21 28
MAN B &W Diesel A/S S 50MC-C P rojec t G uide
4.08
Fig. 4 .05a: Engine preparations for PTO 178 40 42-8.0
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MAN B &W Diesel A/S S 50MC-C P rojec t G uide
485 600 100 198 21 28
4.09
Pos . 1 Specia l face on bedpla te and frame box
P os. 2 Ribs a nd brackets for supporting the face and machined blocks for alignment of gea r or sta tor
housing
P os. 3 Mac hined was hers plac ed on frame box part of face to ensure, that it is f lush with the f