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Optimisation of pump- and cooling
water systems
A report made by Grontmij Carl Bro, APV and DESMI
2008
Page 1
TABLE OF CONTENT:
INTRODUCTION:..........................................................................................................2
CASE STUDIES............................................................................................................4
SPECIFICATION OF SW COMPONENTS:...........................................................................................4
SPECIFICATION OF OPERATING CONDITIONS:...............................................................................4
SPECIFICATION OF CALCULATION TOOL:.......................................................................................5
CASE STUDY NO. 1:....................................................................................................6
SPECIFICATION OF SW COMPONENTS:...........................................................................................6
CONCLUSION: CASE STUDY NO. 1: ..................................................................................................7
CASE STUDY NO. 2:....................................................................................................8
SPECIFICATION OF SW COMPONENTS:...........................................................................................8
CONCLUSION: CASE STUDY NO. 2: ..................................................................................................8
CASE STUDY NO. 3:....................................................................................................9
SPECIFICATION OF SW COMPONENTS:...........................................................................................9
CONCLUSION: CASE STUDY NO. 3: ..................................................................................................9
CASE STUDY NO. 4:..................................................................................................10
SPECIFICATION OF SW COMPONENTS:......................................................................................... 10
CONCLUSION: CASE STUDY NO. 4 ................................................................................................. 11
OVERALL CONCLUSION: .........................................................................................12
FUTURE INVESTIGATION POSSIBILITIES ..............................................................14
APPENDIX 1 CALCULATION DOCUMENTS
Page 2
INTRODUCTION:
The co-operation between DESMI, APV and Grontmij Carl Bro was established more than a year ago due to the increased demands for reduction of the CO2 emission to the environment.
The co-operation between the pump supplier, the heat exchange supplier, and the system designer was initiated with a view to trying to optimise auxiliary service systems on board ships by combining the designers knowledge and the practical experience of the two suppliers. The optimisations were centred on reducing the needed power for the pump and in that way reducing the CO2 emission to the environment.
The cooperation partners first focused on the seawater (SW) cooling system, being one of the parts in an ordinary central cooling water system. The chosen vessel type is a bulk carrier, which is very familiar to almost all, and in that way the conclusion of the studies in this report can easily be adopted to optimising projects at existing vessels and of course to optimising all new-building projects.
Page 3
DESCRIPTION OF THE SYSTEM USED IN ALL CALCULATION CASES
The pipe system showed on the simplified drawing 611-01 is a typical seawater (SW) cooling system for a handy size bulk carrier.
The two of the three SW pumps (two pumps rated at 50% of the specified flow one pump rated at 50% as standby pump) draw SW from a common manifold pipe, which is connected to a low sea chest and a high sea chest. The SW is discharged from the SW pumps through the two parallel-connected coolers and overboard to the sea again.
The system with three 50% pumps has been used because this is the most common way to design the system and because it ensures a flexible and reliable operation of the system.
System drawing: 611-01
Page 4
CASE STUDIES
SPECIFICATION OF SW COMPONENTS:
The case studies have been divided in different steps to illustrate the progress in the project. These steps have been named as follows:
CASE STUDY NO. 1: Calculation of the existing final design including the existing pumps and coolers.
CASE STUDY NO. 2: Same as case study No. 1 but with a new optimised pump.
CASE STUDY NO. 3: Calculation with a new cooler based on 2x50% instead of 2x65% cooling capacity, please see explanation later. New optimised pump, corresponding to the new coolers, has been used.
CASE STUDY NO. 4: Calculations with optimised coolers in respect of low-pressure drop. New optimised pumps, corresponding to the new coolers, have been used.
SPECIFICATION OF OPERATING CONDITIONS:
All of the evaluated case studies have been based on the same operating conditions e.g. same SW temperatures, same pipe diameters, same location of equipment etc.
Filter: Inline SW filter at suction side. High sea chest is closed.
Running time for pumps:
365 days per year
Pipes: Normal steel pipe. DIN sizes
Calculation: Operating conditions used in the FluidFlow calculation:
Ambient SW temperature: 32 deg.C FW temperature out: 36 deg.C Inlet location: 2.5 m above base line Outlet location: 6.0 m above base line Location of pumps: 3.5 m above base line Location of coolers: 9.5 m above base line Vessel draft aft: 7.0 m
Page 5
SPECIFICATION OF CALCULATION TOOL:
The case studies have been calculated and evaluated in a fluid calculation program named FluidFlow, which is a powerful design and simulation tool for pipe systems. The FluidFlow designing tool facilitates quick and effective evaluations such as:
Pressure loss calculations for fluid, gas and slurry systems Selection of optimal pumps / ventilators Cavitation control of pumps Calculation of air pipes connected to tanks for pressurized system
FluidFlow screen dump of present SW cooling system. Each case study has been calculated in FluidFlow. See Appendix 1 page 5-14
Page 6
CASE STUDY NO. 1:
The SW cooling water system was originally designed with a pump capacity / pressure from a preliminary specification stated in the building specification for the vessel, with no specific knowledge of flow resistance for coolers, filters and elevation location of each equipment.
The system was not optimised in the detailed production design by the yard when the other system-related equipment and the hydrostatic pressure heights were known. Furthermore the pump was bought as a standard stock pump in a low efficiency design.
The practice of using the first, qualified guess as the final specification for purchasing the pump has unfortunately been seen especially at the yards in the young shipbuilding nations, where the yards have less technical experience.
The coolers were selected with a cooling water heat transfer capacity each of 2x65% of the total heat transfer requirement, calculated according to a cooling water balance where the different cooling consumers, mainly the main engine and the auxiliary engines, were added and multiplied by an estimated load factor.
SPECIFICATION OF SW COMPONENTS:
Pumps: 3 x 230 m3/h at 3.0 barg.
Pump data appear from the component appendix.
Coolers: 2 X 4251 kW heat exchangers (cooling capacity based on cooling consumer load balance, Tropical see Appendix 1 page 3)
SW flow based on the preliminarily chosen pump capacity. Flow resistance for cooler is stated as 0,87 bar at 230 m3/h
Cooler data appear from the component appendix.
Page 7
CONCLUSION: CASE STUDY NO. 1:
We have focused on two scenarios when the 2 pumps are in operation. The first one is specified in case 1-1 and the second one is specified in case 1-2
1-1 The operator tries to keep each of the pumps at the 230 m3/h operation point. To ensure this it is necessary to throttle the discharge valves or insert an orifice due to the fact that the system pressure is lower than the specified operation point at 3.0 barg.
In this scenario the mechanical power in the duty point of each of the running pumps is 25.85 kW which corresponds to the below per year / pump:
Fuel consumption (ts/year/pump): 51.30 CO2 emission (ts/year): 159.6 Running cost (USD/year): 32,807.0 ref. calculation in appendix 1 page 2
1-2 The operator lets each of the pumps run at the system pressure. The pump is very close to run out of its curve and delivers approx. 321 m3/h SW at 2,4bar.
In this scenario the pumps mechanical power in the duty point is 29.09 kW which corresponds to the below per year / pump:
Fuel consumption (ts/year/pump): 57.70 CO2 emission (ts/year): 179,6 Running cost (USD/year): 36,919.0 ref. calculation in appendix 1 page 2
We have used 1-2 as reference condition.
Page 8
CASE STUDY NO. 2:
In this scenario we have kept the cooler as specified in order to evaluate the reduction of the power consumption when changing the pump head and optimising the pump efficiency to the system pressure.
SPECIFICATION OF SW COMPONENTS:
Pumps: 3 x 230 m3/h at 1.2 barg.
Pump data appear from the component appendix.
Coolers: 2 x 4251 kW heat exchangers (cooling capacity based on cooling consumer load balance, Tropical see Appendix 1 page 3)
SW flow based on the preliminary pump capacity chosen. Flow resistance for cooler is stated as 0.87 bar at 230 m3/h
Cooler data appear from the component appendix.
CONCLUSION: CASE STUDY NO. 2:
The pump is now running at the specified system pressure, and it is not necessary to throttle valves or insert an orifice to keep the pump at the specified operation point.
The necessary mechanical power for running each pump is 9.89 kW which corresponds to the below per year / pump:
Fuel consumption (ts/year/pump): 19.60 CO2 emission (ts/year): 61.0 Running cost (USD/year): 12,545.0 ref. calculation in appendix 1 page 2 The savings compared with:
Case study No. 1-2: 66%
Page 9
CASE STUDY NO. 3:
The total cooling capacity has now been reduced from a total duty of 2 x 65% into 2 x 50%. After reducing the total duty to 2 x 50% each cooler still has a built in Heat Transfer Coefficient (HTC) margin of 15%. We wish to emphasize that the 15% reduction of the HTC margin equals a 15% reduction of the K-value.
Unfortunately the way that designers, shipyards and ship owners specify coolers has resulted in a double safety factor for the cooler. This study tries to describe the consequence of this common mistake.
SPECIFICATION OF SW COMPONENTS:
Pumps: 3 x 205 m3/h at 0.9 barg.
Pump data appear from the component appendix.
Coolers: 2 X 3270 kW heat exchangers (cooling capacity based on cooling consumer load balance, Tropical see Appendix 1 page 4)
Flow resistance and SW flow for cooler is stated as 0.69 bar at 205 m3/h
Cooler data appear from the component appendix.
CONCLUSION: CASE STUDY NO. 3:
By using the built in safety HTC margin in the cooler, allows the cooler to operate at a lower flow / lower pressure drop which dramatically affects the fuel consumption / CO2 emission.
The necessary mechanical power for running each pump is 6.80 kW which corresponds to the below per year / pump:
Fuel consumption (ts/year/pump): 13.48 CO2 emission (ts/year): 42.0 Running cost (USD/year): 8,630.0 ref. calculation in appendix 1 page 2
The savings compared with:
Case study No. 1-2: 77% Case study No. 2: 31%
Page 10
CASE STUDY NO. 4:
As a result of the big savings in case study 2 and 3 compared to case study 1, the task was to optimise the coolers due to the pressure drop and compare the yearly costs / CO2 emission to the environment with the purchasing costs of the entire system. The purpose of this case study 4 was to determine the optimum between initial installation costs and operational costs.
SPECIFICATION OF SW COMPONENTS:
The study required that the following 6 scenarios/steps were considered: The pump and cooler data is mentioned in the component appendix.
Case 4-1: Pumps: 3 x 180 m3/h at 0.4 barg. Coolers: 2 X 3270 kW heat exchangers
SW flow 180 m3/h Pressure drop 0.2 bar
Case 4-2 Pumps: 3 x 180 m3/h at 0.5 barg. Coolers: 2 X 3270 kW heat exchangers
SW flow 180 m3/h Pressure drop 0.3 bar
Case 4-3 Pumps: 3 x 180 m3/h at 0.6 barg. Coolers: 2 X 3270 kW heat exchangers
SW flow 180 m3/h Pressure drop 0.4 bar
Case 4-4 Pumps: 3 x 180 m3/h at 0.7 barg. Coolers: 2 X 3270 kW heat exchangers
SW flow 180 m3/h Pressure drop 0.5 bar
Case 4-5 Pumps: 3 x 180 m3/h at 0.8 barg. Coolers: 2 X 3270 kW heat exchangers
SW flow 180 m3/h Pressure drop 0.6 bar
Case 4-6 Pumps: 3 x 180 m3/h at 0.9 barg. Coolers: 2 X 3270 kW heat exchangers
SW flow 180 m3/h Pressure drop 0.7 bar
Page 11
CONCLUSION: CASE STUDY NO. 4
It is very clear that a cooler with at pressure drop of 0.2 bar (Case study 4-1) is the most optimised SW cooling water system with regard to low yearly running costs and a very low CO2 emission to the environment. The necessary mechanical power for running each pump in each case study is: 4-1: 2.69 kW 4-2: 3.46 kW 4-3: 4.11 kW 4-4: 4.66 kW 4-5: 5.21 kW 4-6: 5.84 kW
The necessary power for case study 4-1 corresponds to the below per year / pump: Fuel consumption (ts/year/pump): 5.33 CO2 emission (ts/year): 16.1 Running cost (USD/year): 3,414 ref. calculation in appendix 1 page 2
The savings case study 4-1 compared with: Case study No. 1-2: 91% Case study No. 2: 73% Case study No. 3: 60%
It has to be mentioned that a cooler with a very low pressure drop is a larger cooler and of course in that way a more expensive cooler. The increased initial installation costs will afterwards be compared to the operational costs.
Case Study No. 4Accumulated Running Cost + Installation Cost
-
100.000
200.000
300.000
400.000
500.000
600.000
700.000
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24 25 26 27 28 29 30Year
USD
Case 4-1 Case 4-2 Case 4-3 Case 4-4 Case 4-5 Case 4-6
Page 12
OVERALL CONCLUSION:
The pressure drop of the cooler is essential. The cooler is the component in the sea water system causing the highest resistance, and consequently it has a significant impact on the overall system pressure and in that way facilitates the installation of smaller pumps. Therefore the chosen cooler pressure drop should be specified very clearly, when purchasing departments are purchasing the coolers.
Figures for one pump:
Fuel cons./ CO2 emission Case Study 1-2 (ts/year): 57.70 / 179.6 Fuel cons./ CO2 emission Case Study 3 (ts/year): 13.48 / 42.0 Fuel cons./ CO2 emission Case Study 4-1(ts/year): 5.33 / 16.6
Accumulated CO2 emission for two pumps running
ACCUMULATED CO2 EMISSION
-
2.000,00
4.000,00
6.000,00
8.000,00
10.000,00
12.000,00
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24 25 26 27 28 29 30Year
TONS
Case 1-2
Case 3
Case 4-1
Page 13
The overall costs, purchasing + running costs, indicate that the installation of coolers with a very low pressure drop is a good investment both for low overall costs, but also for the environment. Installation of 3 pumps + 2 coolers (only 2 pumps running).
Accumulated Cost
An additional benefit of a very low pressure drop on the SW cooler side is that the Fresh Water (FW) side also decreases dramatically and in that way also generates smaller FW pumps. These pumps have not been included in this report but will result in shorter investment payback time.
It is important that the pumps chosen are high efficiency pumps.
Let the pump specification be open until the pipe system has been designed in detail, so that all components are well known, e.g. location of equipment, pipe length, quantity of bends etc. In that way the pump can be optimised to exactly fit the system pressure.
Low pressure gives the benefit of less stress on all components.
Accumulated Running Cost + Installation Cost
-
500.000
1.000.000
1.500.000
2.000.000
2.500.000
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24 25 26 27 28 29 30Year
USD
Case 1-2
Case 3
Case 4-1
Page 14
FUTURE INVESTIGATION POSSIBILITIES
Fixed back flushing arrangement shall be installed together with a cleaning in place (CIP) arrangement to keep the pressure drop across the coolers as low as possible and the efficiency of the coolers as high as possible. Smaller cooler pressure drop more sensitive coolers.
SW pumps as 2x100% or 3x50% or another division of pump sizes.
Using a harbour cooling pump as a supplement to above.
2-speed pump, in order to adjust the pump capacity based on actual need.
Frequency controlled SW pumps regulated by temperature transmitter on the discharge side of the coolers. The result will be even better than the above speed regulation and the capacity of the pump can be adjusted very close to the actual need.
LT cooling water system optimisation bringing down the pump sizes, which results in further overall power reduction.
More Partners e.g. dialog with manufactures of FW cooling consumers, and dialog with ship owner regarding operation facts.
KQE / Grontmij | Carl Bro A/S / 2008-09-11
Page 15
For further information, please contact:
Granskoven 8 DK-2600 Glostrup Denmark
Karsten Elland Project Manager Industry, Marine & Environment
Phone: +45 4348 6060 E-mail: [email protected]
Heat Transfer Platinvej 8 DK-6000 Kolding Denmark
Kim Koldskov Sales Manager Global Marine Division
Phone: +45 7027 8444 E-mail: [email protected]
Tagholm 1 DK-9400 Nrresundby Denmark
Henrik Mrkholt Sales Director
Phone: +45 9632 8128 E-mail: [email protected]
Appendix 1Calculation Documents
1. Consumption & CO2 calculation............................................................
2. Cooling water balance 2 x 65% (Case 1 + 2).......................................
3. Cooling water balance 2 x 50% (Case 3 + 4).......................................
4. Fluid Flow calculations for each case story...................................
Page 2
Page 3
Page 4
Page 5 - 14
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Dat
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1 /
1
AP
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IX 1
- C
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DH
EAT
DIS
S.H
EAT
DIS
S. A
T LO
AD
TOL.
SPEC
. C
OO
L.
CO
OL.
WA
TER
FL
OW
INLE
T TE
MP.
OU
TLET
TE
MP.
A
T M
AX.
LO
AD
CO
OLI
NG
W
ATE
R
FLO
W
Del
ta P
REM
AR
K
[%]
[kW
][k
W]
[+%
][m
^3/H
][m
^3/H
][d
eg. C
][d
eg. C
][m
^3/H
][k
Pa]
563.
01M
/E L
O C
OO
LER
+
100%
700
700,
010
%95
104,
536
,042
,410
4,50
20,0
056
2.03
JAC
KE
T W
ATE
R C
OO
LER
100%
1240
1240
,010
%95
104,
542
,453
,720
,00
411.
01M
/E S
CA
VE
NG
ER
AIR
CO
OLE
R10
0%30
0030
00,0
0%13
713
736
,055
,013
7,00
50,0
043
1.01
A/E
1 T
OTA
L (L
O, J
AC
K. W
. AN
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CA
V. A
IR C
OO
LER
)90
%42
037
8,0
0%28
,728
,736
,047
,428
,70
39,2
043
1.02
A/E
2 T
OTA
L (L
O, J
AC
K. W
. AN
D S
CA
V. A
IR C
OO
LER
)90
%42
037
8,0
0%28
,728
,736
,047
,428
,70
39,2
043
1.03
A/E
3 T
OTA
L (L
O, J
AC
K. W
. AN
D S
CA
V. A
IR C
OO
LER
)0%
420
0,0
0%28
,728
,736
,036
,00,
0039
,20
312.
01R
EFR
. CO
MP
RE
SS
OR
UN
IT F
OR
A/C
PLA
NT
75%
196
147,
00%
4040
36,0
39,2
40,0
039
,20
312.
02R
EFR
. CO
MP
RE
SS
OR
UN
IT F
OR
A/C
PLA
NT
75%
196
147,
00%
4040
36,0
39,2
40,0
039
,20
355.
01P
RO
VIS
ON
CO
OLI
NG
CO
MP
RE
SS
OR
75%
9,5
7,1
0%4,
24,
236
,037
,54,
2015
,70
355.
02P
RO
VIS
ON
CO
OLI
NG
CO
MP
RE
SS
OR
75%
9,5
7,1
0%4,
24,
236
,037
,54,
2015
,70
314.
03R
EFR
. CO
MP
. FO
R A
/S U
NIT
GA
LLE
Y75
%17
,813
,40%
5,22
5,22
36,0
38,2
5,22
50,0
031
4.02
RE
FR. C
OM
P. F
OR
A/S
UN
IT E
NG
. CO
NTR
. RO
OM
75%
17,2
12,9
0%5,
225,
2236
,038
,15,
2250
,00
682.
01S
TEA
M D
UM
P C
OO
LER
50%
998
499,
00%
3636
36,0
48,0
36,0
056
2.07
SA
MP
LE C
OO
LER
0%2
0,0
0%2
236
,036
,00,
0042
3.03
SH
AFT
BE
AR
ING
100%
1,7
1,7
0%0,
150,
1536
,045
,80,
1546
1.01
STA
RTI
NG
AIR
CO
MP
RE
SS
OR
50%
16,7
8,4
0%3,
243,
2436
,038
,23,
2446
1.02
STA
RTI
NG
AIR
CO
MP
RE
SS
OR
0%16
,70,
00%
3,24
3,24
36,0
36,0
0,00
TOTA
L R
EQU
IREM
ENT:
6540
[kW
]TO
TAL
LT F
LOW
:43
7[m
^3/h
]TO
TAL
SW F
LOW
:46
0[m
^3/h
]FW
TEM
P O
UTL
ET O
F C
OO
LER
S:36
,0[d
eg. C
]FW
TEM
P IN
LET
TO C
OO
LER
S:49
,0[d
eg. C
]SW
TEM
P IN
LET
TO C
OO
LER
S:32
,0[d
eg. C
]SW
TEM
P O
UTL
ET O
F C
OO
LER
S:48
,0[d
eg. C
]TA
RG
ET
CO
OL.
REQ
. FO
R E
AC
H C
OO
LER
:50
%32
70[k
W]
LT F
LOW
FO
R E
AC
H C
OO
LER
:43
7[m
^3/h
]SW
FLO
W F
OR
EA
CH
CO
OLE
R:
460
[m^3
/h]
To b
e pr
ovid
ed b
y 2
x 50
% S
W p
umps
runn
ing
in p
aral
lel o
pera
tion
Dat
e: 1
4-09
-200
8P
age:
1 /
1
AP
PE
ND
IX 1
- C
ALC
ULA
TIO
N D
OC
UM
EN
TSP
AG
E N
O. 4
KQETypewritten Text615-00-2
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Low
sea c
hest
Flo
w =
463,3
51 m
3/h
Tem
pera
ture
= 3
2,0
C
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Hig
h s
ea c
hest
Uniq
ue N
am
e =
SW
Cool. p
um
p #
3Ele
vation =
3,5
mD
uty
Pow
er
= 0
,00 k
WD
uty
Eff
icie
ncy
(%
) =
0,0
0D
uty
Pre
ssure
Ris
e =
0,0
00 b
ar
Duty
Flo
w =
0,0
00 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
2Ele
vation =
3,5
mD
uty
Pow
er
= 2
6,0
5 k
WD
uty
Eff
icie
ncy
(%
) =
74,9
1D
uty
Pre
ssure
Ris
e =
2,9
48 b
ar
Duty
Flo
w =
238,3
13 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
1Ele
vation =
3,5
mD
uty
Pow
er
= 2
5,6
2 k
WD
uty
Eff
icie
ncy
(%
) =
73,5
8D
uty
Pre
ssure
Ris
e =
3,0
16 b
ar
Duty
Flo
w =
225,0
37 m
3/h
Orifice
Siz
e =
116 m
mTota
l Pre
ssure
Loss
= 1
,726 b
ar
Flo
w =
465,7
26 m
3/h
Pre
ssure
= 1
m F
luid
gEle
vation =
6 m
Uniq
ue N
am
e =
Overb
oard
Flo
w =
465,7
23 m
3/h
Tem
pera
ture
= 4
8,6
C
Out
Tem
pera
ture
= 4
8,5
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
4251,0
0 k
WTota
l Pre
ssure
Loss
= 0
,900 b
ar
Flo
w =
233,3
63 m
3/h
Out
Tem
pera
ture
= 4
8,8
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
4251,0
0 k
WTota
l Pre
ssure
Loss
= 0
,875 b
ar
Flo
w =
229,9
87 m
3/h
Uniq
ue N
am
e =
In lin
e F
ilter
Tota
l Pre
ssure
Loss
= 0
,045 b
ar
Cas
e 1
-1:
SW
coo
ling
sys
tem
AP
PE
ND
IX 1
- C
ALC
ULA
TIO
N D
OC
UM
EN
TSP
AG
E N
O. 5
KQETypewritten TextORIFICE INSERTED
KQETypewritten TextAverage Duty Power = 25,85 kWAverage Duty Efficiency (%) = 74,3
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Low
sea c
hest
Flo
w =
648,6
43 m
3/h
Tem
pera
ture
= 3
2,0
C
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Hig
h s
ea c
hest
Uniq
ue N
am
e =
SW
Cool. p
um
p #
3Ele
vation =
3,5
mD
uty
Pow
er
= 0
,00 k
WD
uty
Eff
icie
ncy
(%
) =
0,0
0D
uty
Pre
ssure
Ris
e =
0,0
00 b
ar
Duty
Flo
w =
0,0
00 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
2Ele
vation =
3,5
mD
uty
Pow
er
= 2
9,5
2 k
WD
uty
Eff
icie
ncy
(%
) =
75,4
2D
uty
Pre
ssure
Ris
e =
2,3
93 b
ar
Duty
Flo
w =
334,9
53 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
1Ele
vation =
3,5
mD
uty
Pow
er
= 2
8,6
6 k
WD
uty
Eff
icie
ncy
(%
) =
76,6
7D
uty
Pre
ssure
Ris
e =
2,5
22 b
ar
Duty
Flo
w =
313,6
90 m
3/h
Orifice
Siz
e =
320 m
mTota
l Pre
ssure
Loss
= 0
,000 b
ar
Flo
w =
650,9
38 m
3/h
Pre
ssure
= 1
m F
luid
gEle
vation =
6 m
Uniq
ue N
am
e =
Overb
oard
Flo
w =
650,9
38 m
3/h
Tem
pera
ture
= 4
3,9
C
Out
Tem
pera
ture
= 4
3,8
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
4251,0
0 k
WTota
l Pre
ssure
Loss
= 1
,758 b
ar
Flo
w =
326,6
75 m
3/h
Out
Tem
pera
ture
= 4
4,0
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
4251,0
0 k
WTota
l Pre
ssure
Loss
= 1
,708 b
ar
Flo
w =
321,9
68 m
3/h
Uniq
ue N
am
e =
In lin
e F
ilter
Tota
l Pre
ssure
Loss
= 0
,089 b
ar
Cas
e 1
-2:
SW
coo
ling
sys
tem
AP
PE
ND
IX 1
- C
ALC
ULA
TIO
N D
OC
UM
EN
TSP
AG
E N
O. 6
KQETypewritten TextAverage Duty Power = 29,09 kWAverage Duty Efficiency (%) = 76,0
Pres
sure
= 4
,5 m
Flu
id g
Elev
atio
n =
2,5
mU
niqu
e N
ame
= L
ow s
ea c
hest
Flow
= 4
57,3
85 m
3/h
Tem
pera
ture
= 3
2,0
C
Pres
sure
= 4
,5 m
Flu
id g
Elev
atio
n =
2,5
mU
niqu
e N
ame
= H
igh
sea
ches
t
Uni
que
Nam
e =
SW
Coo
l. p
ump
#3
Elev
atio
n =
3,5
mD
uty
NPS
H A
vaila
ble
= -
0,01
2 ba
r g
Dut
y N
PSH
Req
uire
d =
0,1
47 b
arD
uty
Pow
er =
0,0
0 kW
Dut
y Ef
ficie
ncy
(%)
= 0
,00
Dut
y Pr
essu
re R
ise
= 0
,000
bar
Dut
y Fl
ow =
0,0
00 m
3/h
Uni
que
Nam
e =
SW
Coo
l. p
ump
#2
Elev
atio
n =
3,5
mD
uty
NPS
H A
vaila
ble
= 0
,217
bar
gD
uty
NPS
H R
equi
red
= 0
,244
bar
Dut
y Po
wer
= 9
,97
kWD
uty
Effic
ienc
y (%
) =
78,
06D
uty
Pres
sure
Ris
e =
1,1
91 b
arD
uty
Flow
= 2
35,2
59 m
3/h
Uni
que
Nam
e =
SW
Coo
l. p
ump
#1
Elev
atio
n =
3,5
mD
uty
NPS
H A
vaila
ble
= 0
,223
bar
gD
uty
NPS
H R
equi
red
= 0
,232
bar
Dut
y Po
wer
= 9
,80
kWD
uty
Effic
ienc
y (%
) =
79,
16D
uty
Pres
sure
Ris
e =
1,2
57 b
arD
uty
Flow
= 2
22,1
26 m
3/h
Ori
fice
Siz
e =
320
mm
Tota
l Pre
ssur
e Lo
ss =
0,0
00 b
arFl
ow =
459
,766
m3/
hPr
essu
re =
1 m
Flu
id g
Elev
atio
n =
6 m
Uni
que
Nam
e =
Ove
rboa
rdFl
ow =
459
,766
m3/
hTe
mpe
ratu
re =
48,
9 C
Out
Tem
pera
ture
= 4
8,7
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tran
sfer
red
= 4
251,
00 k
WTo
tal P
ress
ure
Loss
= 0
,878
bar
Flow
= 2
30,3
59 m
3/h
Out
Tem
pera
ture
= 4
9,0
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tran
sfer
red
= 4
251,
00 k
WTo
tal P
ress
ure
Loss
= 0
,853
bar
Flow
= 2
27,0
26 m
3/h
Uni
que
Nam
e =
In
line
Filt
erTo
tal P
ress
ure
Loss
= 0
,044
bar
Cas
e 2:
SW c
oolin
g sy
stem
AP
PE
ND
IX 1
- C
ALC
ULA
TIO
N D
OC
UM
EN
TSP
AG
E N
O. 7
KQETypewritten TextDuty Power = 9,87 kWDuty Efficiency (%) = 78,88
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Low
sea c
hest
Flo
w =
405,5
59 m
3/h
Tem
pera
ture
= 3
2,0
C
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Hig
h s
ea c
hest
Uniq
ue N
am
e =
SW
Cool. p
um
p #
3Ele
vation =
3,5
mD
uty
NPSH
Availa
ble
= -
0,0
12 b
ar
gD
uty
NPSH
Required =
0,1
47 b
ar
Duty
Pow
er
= 0
,00 k
WD
uty
Eff
icie
ncy
(%
) =
0,0
0D
uty
Pre
ssure
Ris
e =
0,0
00 b
ar
Duty
Flo
w =
0,0
00 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
2Ele
vation =
3,5
mD
uty
NPSH
Availa
ble
= 0
,235 b
ar
gD
uty
NPSH
Required =
0,2
55 b
ar
Duty
Pow
er
= 6
,88 k
WD
uty
Eff
icie
ncy
(%
) =
79,6
4D
uty
Pre
ssure
Ris
e =
0,9
36 b
ar
Duty
Flo
w =
210,5
66 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
1Ele
vation =
3,5
mD
uty
NPSH
Availa
ble
= 0
,241 b
ar
gD
uty
NPSH
Required =
0,2
40 b
ar
Duty
Pow
er
= 6
,72 k
WD
uty
Eff
icie
ncy
(%
) =
79,2
8D
uty
Pre
ssure
Ris
e =
0,9
84 b
ar
Duty
Flo
w =
194,9
93 m
3/h
Orifice
Siz
e =
320 m
mTota
l Pre
ssure
Loss
= 0
,000 b
ar
Flo
w =
407,3
62 m
3/h
Pre
ssure
= 1
m F
luid
gEle
vation =
6 m
Uniq
ue N
am
e =
Overb
oard
Flo
w =
407,3
62 m
3/h
Tem
pera
ture
= 4
6,6
C
Out
Tem
pera
ture
= 4
6,5
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
3270,0
0 k
WTota
l Pre
ssure
Loss
= 0
,689 b
ar
Flo
w =
204,2
60 m
3/h
Out
Tem
pera
ture
= 4
6,7
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
3270,0
0 k
WTota
l Pre
ssure
Loss
= 0
,670 b
ar
Flo
w =
201,2
99 m
3/h
Uniq
ue N
am
e =
In lin
e F
ilter
Tota
l Pre
ssure
Loss
= 0
,035 b
ar
Cas
e 3
:S
W c
oolin
g s
yste
m
AP
PE
ND
IX 1
- C
ALC
ULA
TIO
N D
OC
UM
EN
TSP
AG
E N
O. 8
KQETypewritten TextAverage Duty Power = 6,80 kWAverage Duty Efficiency (%) = 79,5
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Low
sea c
hest
Flo
w =
358,1
15 m
3/h
Tem
pera
ture
= 3
2,0
C
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Hig
h s
ea c
hest
Uniq
ue N
am
e =
SW
Cool. p
um
p #
3Ele
vation =
3,5
mD
uty
Pow
er
= 0
,00 k
WD
uty
Eff
icie
ncy
(%
) =
0,0
0D
uty
Pre
ssure
Ris
e =
0,0
00 b
ar
Duty
Flo
w =
0,0
00 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
2Ele
vation =
3,5
mD
uty
Pow
er
= 2
,70 k
WD
uty
Eff
icie
ncy
(%
) =
76,5
1D
uty
Pre
ssure
Ris
e =
0,4
02 b
ar
Duty
Flo
w =
185,2
79 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
1Ele
vation =
3,5
mD
uty
Pow
er
= 2
,67 k
WD
uty
Eff
icie
ncy
(%
) =
79,0
0D
uty
Pre
ssure
Ris
e =
0,4
40 b
ar
Duty
Flo
w =
172,8
36 m
3/h
Orifice
Siz
e =
320 m
mTota
l Pre
ssure
Loss
= 0
,000 b
ar
Flo
w =
359,9
43 m
3/h
Pre
ssure
= 1
m F
luid
gEle
vation =
6 m
Uniq
ue N
am
e =
Overb
oard
Flo
w =
359,9
45 m
3/h
Tem
pera
ture
= 4
8,6
C
Out
Tem
pera
ture
= 4
8,3
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
3270,0
0 k
WTota
l Pre
ssure
Loss
= 0
,210 b
ar
Flo
w =
182,2
18 m
3/h
Out
Tem
pera
ture
= 4
8,9
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
3270,0
0 k
WTota
l Pre
ssure
Loss
= 0
,196 b
ar
Flo
w =
175,8
97 m
3/h
Uniq
ue N
am
e =
In lin
e F
ilter
Tota
l Pre
ssure
Loss
= 0
,027 b
ar
Cas
e 4
-1:
SW
coo
ling
sys
tem
AP
PE
ND
IX 1
- C
ALC
ULA
TIO
N D
OC
UM
EN
TSP
AG
E N
O. 9
KQETypewritten TextAverage Duty Power = 2,69 kWAverage Duty Efficiency (%) = 77,8
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Low
sea c
hest
Flo
w =
362,1
16 m
3/h
Tem
pera
ture
= 3
2,0
C
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Hig
h s
ea c
hest
Uniq
ue N
am
e =
SW
Cool. p
um
p #
3Pum
p M
odel =
CASE4-2
NSL2
00-2
65
Ele
vation =
3,5
mD
uty
Pow
er
= 0
,00 k
WD
uty
Eff
icie
ncy
(%
) =
0,0
0D
uty
Pre
ssure
Ris
e =
0,0
00 b
ar
Duty
Flo
w =
0,0
00 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
2Pum
p M
odel =
CASE4-2
NSL2
00-2
65
Ele
vation =
3,5
mD
uty
Pow
er
= 3
,51 k
WD
uty
Eff
icie
ncy
(%
) =
76,0
1D
uty
Pre
ssure
Ris
e =
0,5
12 b
ar
Duty
Flo
w =
187,7
65 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
1Pum
p M
odel =
CASE4-2
NSL2
00-2
65
Ele
vation =
3,5
mD
uty
Pow
er
= 3
,43 k
WD
uty
Eff
icie
ncy
(%
) =
77,7
1D
uty
Pre
ssure
Ris
e =
0,5
50 b
ar
Duty
Flo
w =
174,3
50 m
3/h
Orifice
Siz
e =
320 m
mTota
l Pre
ssure
Loss
= 0
,000 b
ar
Flo
w =
363,9
43 m
3/h
Pre
ssure
= 1
m F
luid
gEle
vation =
6 m
Uniq
ue N
am
e =
Overb
oard
Flo
w =
363,9
43 m
3/h
Tem
pera
ture
= 4
8,4
C
Out
Tem
pera
ture
= 4
8,2
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
3270,0
0 k
WTota
l Pre
ssure
Loss
= 0
,316 b
ar
Flo
w =
183,2
99 m
3/h
Out
Tem
pera
ture
= 4
8,6
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
3270,0
0 k
WTota
l Pre
ssure
Loss
= 0
,301 b
ar
Flo
w =
178,8
17 m
3/h
Uniq
ue N
am
e =
In lin
e F
ilter
Tota
l Pre
ssure
Loss
= 0
,028 b
ar
Cas
e 4
-2:
SW
coo
ling
sys
tem
AP
PE
ND
IX 1
- C
ALC
ULA
TIO
N D
OC
UM
EN
TSP
AG
E N
O. 1
0
KQETypewritten TextAverage Duty Power = 3,46 kWAverage Duty Efficiency (%) = 76,9
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Low
sea c
hest
Flo
w =
361,3
75 m
3/h
Tem
pera
ture
= 3
2,0
C
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Hig
h s
ea c
hest
Uniq
ue N
am
e =
SW
Cool. p
um
p #
3Pum
p M
odel =
CASE4-3
NSL1
50-3
30
Ele
vation =
3,5
mD
uty
Pow
er
= 0
,00 k
WD
uty
Eff
icie
ncy
(%
) =
0,0
0D
uty
Pre
ssure
Ris
e =
0,0
00 b
ar
Duty
Flo
w =
0,0
00 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
2Pum
p M
odel =
CASE4-3
NSL1
50-3
30
Ele
vation =
3,5
mD
uty
Pow
er
= 4
,14 k
WD
uty
Eff
icie
ncy
(%
) =
76,0
3D
uty
Pre
ssure
Ris
e =
0,6
10 b
ar
Duty
Flo
w =
185,7
17 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
1Pum
p M
odel =
CASE4-3
NSL1
50-3
30
Ele
vation =
3,5
mD
uty
Pow
er
= 4
,08 k
WD
uty
Eff
icie
ncy
(%
) =
77,9
2D
uty
Pre
ssure
Ris
e =
0,6
52 b
ar
Duty
Flo
w =
175,6
58 m
3/h
Orifice
Siz
e =
320 m
mTota
l Pre
ssure
Loss
= 0
,000 b
ar
Flo
w =
363,2
02 m
3/h
Pre
ssure
= 1
m F
luid
gEle
vation =
6 m
Uniq
ue N
am
e =
Overb
oard
Flo
w =
363,2
03 m
3/h
Tem
pera
ture
= 4
8,4
C
Out
Tem
pera
ture
= 4
8,3
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
3270,0
0 k
WTota
l Pre
ssure
Loss
= 0
,416 b
ar
Flo
w =
182,4
11 m
3/h
Out
Tem
pera
ture
= 4
8,6
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
3270,0
0 k
WTota
l Pre
ssure
Loss
= 0
,400 b
ar
Flo
w =
178,9
65 m
3/h
Uniq
ue N
am
e =
In lin
e F
ilter
Tota
l Pre
ssure
Loss
= 0
,028 b
ar
Cas
e 4
-3:
SW
coo
ling
sys
tem
AP
PE
ND
IX 1
- C
ALC
ULA
TIO
N D
OC
UM
EN
TSP
AG
E N
O. 1
1
KQETypewritten TextAverage Duty Power = 4,11 kWAverage Duty Efficiency (%) = 77,0
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Low
sea c
hest
Flo
w =
361,6
52 m
3/h
Tem
pera
ture
= 3
2,0
C
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Hig
h s
ea c
hest
Uniq
ue N
am
e =
SW
Cool. p
um
p #
3Pum
p M
odel =
CASE4-4
NSL1
50-3
30
Ele
vation =
3,5
mD
uty
Pow
er
= 0
,00 k
WD
uty
Eff
icie
ncy
(%
) =
0,0
0D
uty
Pre
ssure
Ris
e =
0,0
00 b
ar
Duty
Flo
w =
0,0
00 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
2Pum
p M
odel =
CASE4-4
NSL1
50-3
30
Ele
vation =
3,5
mD
uty
Pow
er
= 4
,70 k
WD
uty
Eff
icie
ncy
(%
) =
78,2
7D
uty
Pre
ssure
Ris
e =
0,7
12 b
ar
Duty
Flo
w =
186,1
09 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
1Pum
p M
odel =
CASE4-4
NSL1
50-3
30
Ele
vation =
3,5
mD
uty
Pow
er
= 4
,62 k
WD
uty
Eff
icie
ncy
(%
) =
79,4
4D
uty
Pre
ssure
Ris
e =
0,7
53 b
ar
Duty
Flo
w =
175,5
44 m
3/h
Orifice
Siz
e =
320 m
mTota
l Pre
ssure
Loss
= 0
,000 b
ar
Flo
w =
363,4
78 m
3/h
Pre
ssure
= 1
m F
luid
gEle
vation =
6 m
Uniq
ue N
am
e =
Overb
oard
Flo
w =
363,4
79 m
3/h
Tem
pera
ture
= 4
8,4
C
Out
Tem
pera
ture
= 4
8,3
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
3270,0
0 k
WTota
l Pre
ssure
Loss
= 0
,517 b
ar
Flo
w =
182,2
28 m
3/h
Out
Tem
pera
ture
= 4
8,5
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
3270,0
0 k
WTota
l Pre
ssure
Loss
= 0
,502 b
ar
Flo
w =
179,4
24 m
3/h
Uniq
ue N
am
e =
In lin
e F
ilter
Tota
l Pre
ssure
Loss
= 0
,028 b
ar
Cas
e 4
-4:
SW
coo
ling
sys
tem
AP
PE
ND
IX 1
- C
ALC
ULA
TIO
N D
OC
UM
EN
TSP
AG
E N
O. 1
2
KQETypewritten TextAverage Duty Power = 4,66 kWAverage Duty Efficiency (%) = 78,9
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Low
sea c
hest
Flo
w =
361,0
94 m
3/h
Tem
pera
ture
= 3
2,0
C
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Hig
h s
ea c
hest
Uniq
ue N
am
e =
SW
Cool. p
um
p #
3Pum
p M
odel =
CASE4-5
NSL1
50-3
30
Ele
vation =
3,5
mD
uty
Pow
er
= 0
,00 k
WD
uty
Eff
icie
ncy
(%
) =
0,0
0D
uty
Pre
ssure
Ris
e =
0,0
00 b
ar
Duty
Flo
w =
0,0
00 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
2Pum
p M
odel =
CASE4-5
NSL1
50-3
30
Ele
vation =
3,5
mD
uty
Pow
er
= 5
,27 k
WD
uty
Eff
icie
ncy
(%
) =
79,5
8D
uty
Pre
ssure
Ris
e =
0,8
10 b
ar
Duty
Flo
w =
186,1
41 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
1Pum
p M
odel =
CASE4-5
NSL1
50-3
30
Ele
vation =
3,5
mD
uty
Pow
er
= 5
,15 k
WD
uty
Eff
icie
ncy
(%
) =
80,2
3D
uty
Pre
ssure
Ris
e =
0,8
51 b
ar
Duty
Flo
w =
174,9
53 m
3/h
Orifice
Siz
e =
320 m
mTota
l Pre
ssure
Loss
= 0
,000 b
ar
Flo
w =
362,9
21 m
3/h
Pre
ssure
= 1
m F
luid
gEle
vation =
6 m
Uniq
ue N
am
e =
Overb
oard
Flo
w =
362,9
21 m
3/h
Tem
pera
ture
= 4
8,5
C
Out
Tem
pera
ture
= 4
8,3
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
3270,0
0 k
WTota
l Pre
ssure
Loss
= 0
,616 b
ar
Flo
w =
181,7
27 m
3/h
Out
Tem
pera
ture
= 4
8,5
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
3270,0
0 k
WTota
l Pre
ssure
Loss
= 0
,601 b
ar
Flo
w =
179,3
68 m
3/h
Uniq
ue N
am
e =
In lin
e F
ilter
Tota
l Pre
ssure
Loss
= 0
,027 b
ar
Cas
e 4
-5:
SW
coo
ling
sys
tem
AP
PE
ND
IX 1
- C
ALC
ULA
TIO
N D
OC
UM
EN
TSP
AG
E N
O. 1
3
KQETypewritten TextAverage Duty Power = 5,21 kWAverage Duty Efficiency (%) = 79,9
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Low
sea c
hest
Flo
w =
362,2
15 m
3/h
Tem
pera
ture
= 3
2,0
C
Pre
ssure
= 4
,5 m
Flu
id g
Ele
vation =
2,5
mU
niq
ue N
am
e =
Hig
h s
ea c
hest
Uniq
ue N
am
e =
SW
Cool. p
um
p #
3Pum
p M
odel =
CASE4-6
NSL1
50-3
30
Ele
vation =
3,5
mD
uty
Pow
er
= 0
,00 k
WD
uty
Eff
icie
ncy
(%
) =
0,0
0D
uty
Pre
ssure
Ris
e =
0,0
00 b
ar
Duty
Flo
w =
0,0
00 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
2Pum
p M
odel =
CASE4-6
NSL1
50-3
30
Ele
vation =
3,5
mD
uty
Pow
er
= 5
,91 k
WD
uty
Eff
icie
ncy
(%
) =
80,5
8D
uty
Pre
ssure
Ris
e =
0,9
17 b
ar
Duty
Flo
w =
186,9
56 m
3/h
Uniq
ue N
am
e =
SW
Cool. p
um
p #
1Pum
p M
odel =
CASE4-6
NSL1
50-3
30
Ele
vation =
3,5
mD
uty
Pow
er
= 5
,76 k
WD
uty
Eff
icie
ncy
(%
) =
80,8
5D
uty
Pre
ssure
Ris
e =
0,9
57 b
ar
Duty
Flo
w =
175,2
59 m
3/h
Orifice
Siz
e =
320 m
mTota
l Pre
ssure
Loss
= 0
,000 b
ar
Flo
w =
364,0
41 m
3/h
Pre
ssure
= 1
m F
luid
gEle
vation =
6 m
Uniq
ue N
am
e =
Overb
oard
Flo
w =
364,0
41 m
3/h
Tem
pera
ture
= 4
8,4
C
Out
Tem
pera
ture
= 4
8,3
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
3270,0
0 k
WTota
l Pre
ssure
Loss
= 0
,721 b
ar
Flo
w =
182,1
30 m
3/h
Out
Tem
pera
ture
= 4
8,5
CIn
Tem
pera
ture
= 3
2,0
CH
eat
Tra
nsf
err
ed =
3270,0
0 k
WTota
l Pre
ssure
Loss
= 0
,705 b
ar
Flo
w =
180,0
85 m
3/h
Uniq
ue N
am
e =
In lin
e F
ilter
Tota
l Pre
ssure
Loss
= 0
,028 b
ar
Cas
e 4
-6:
SW
coo
ling
sys
tem
AP
PE
ND
IX 1
- C
ALC
ULA
TIO
N D
OC
UM
EN
TSP
AG
E N
O. 1
4
KQETypewritten TextAverage Duty Power = 5,84 kWAverage Duty Efficiency (%) = 80,7
Member of
Green Ship of the Future
Calculation Appendix.pdfCALCULATION2.pdfCALCULATION