Man B&W S50ME-B9.3-TII Project Manual

MAN B&W S 50ME-B9.3
199 02 51-4. 0
This Project Guide is intended to provide the information necessary for the layout of a marine propulsion plant.
The information is to be considered as preliminary. It is intended for the project stage only and subject to modification in the interest of technical progress. The Project Guide provides the general technical data available at the date of issue.
It should be noted that all figures, values, measurements or information about performance stated in this project guide are for guidance only and should not be used for detailed design purposes or as a substi­tute for specific drawings and instructions prepared for such purposes.
Data updates
Data not finally calculated at the time of issue is marked ‘Available on request’. Such data may be made available at a later date, however, for a specific project the data can be requested. Pages and table entries marked ‘Not applicable’ represent an option, function or selection which is not valid.
The latest, most current version of the individual Project Guide sections are available on the Internet at: www.marine.man.eu ’Two - Stroke’.
Extent of Delivery
The final and binding design and outlines are to be supplied by our licensee, the engine maker, see Chap­ter 20 of this Project Guide.
In order to facilitate negotiations between the yard, the engine maker and the customer, a set of ‘Extent of Delivery’ forms is available in which the basic and the optional executions are specified.
Electronic versions
This Project Guide book and the ‘Extent of Delivery’ forms are available on the Internet at: www.marine.man.eu → ’Two-Stroke’, where they can be downloaded.
Edition 0.5
May 2014
MAN B&W S50ME-B9.3-TII
Project Guide
Electronically Controlled
Two-stroke Engines
with Camshaft Controlled Exhaust Valves
MAN B&W S 50ME-B9.3
199 02 51-4. 0
MAN Diesel & Turbo
Teglholmsgade 41 DK2450 Copenhagen SV Denmark Telephone +45 33 85 11 00 Telefax +45 33 85 10 30 mandiesel-cph@mandiesel.com www.mandieselturbo.com
Copyright 2014 © MAN Diesel & Turbo, branch of MAN Diesel & Turbo SE, Germany, registered with the Danish Commerce and Companies Agency under CVR Nr.: 31611792, (herein referred to as “MAN Diesel & Turbo”).
This document is the product and property of MAN Diesel & Turbo and is protected by applicable copyright laws. Subject to modification in the interest of technical progress. Reproduction permitted provided source is given. 7020-0215-00ppr May 2014
All data provided in this document is non-binding. This data serves informational purposes only and is espe­cially not guaranteed in any way.
Depending on the subsequent specic individual projects, the relevant data may be subject to changes and will be assessed and determined individually for each project. This will depend on the particular characteristics of each individual project, especially specic site and operational conditions.
If this document is delivered in another language than English and doubts arise concerning the translation, the
English text shall prevail.
MAN B&W
MAN Diesel
Engine Design ....................................................................... 1
Engine Layout and Load Diagrams, SFOC .............................. 2
Turbocharger Selection & Exhaust Gas By-pass .................... 3
Electricity Production ............................................................ 4
Installation Aspects ............................................................... 5
List of Capacities: Pumps, Coolers & Exhaust Gas ................. 6
Fuel ...................................................................................... 7
Lubricating Oil ...................................................................... 8
Cylinder Lubrication .............................................................. 9
Piston Rod Stuffing Box Drain Oil .......................................... 10
Central Cooling Water System ............................................... 11
Seawater Cooling System ..................................................... 12
Starting and Control Air ......................................................... 13
Scavenge Air ......................................................................... 14
Exhaust Gas .......................................................................... 15
Engine Control System .......................................................... 16
Vibration Aspects .................................................................. 17
Monitoring Systems and Instrumentation .............................. 18
Dispatch Pattern, Testing, Spares and Tools ........................... 19
Project Support and Documentation ...................................... 20
Appendix .............................................................................. A
Contents
MAN B&W Contents
Chapter Section
MAN Diesel
MAN B&W S 50ME-B9.3
1 Engine Design
The fuel optimised ME-B Tier II engine 1.01 1990113-7.0 Tier II fuel optimisation 1.01 1990112-5.0 Engine type designation 1.02 1983824-3.9 Power, speed, SFOC 1.03 1988502-3.1 Engine power range and fuel oil consumption 1.04 1984634-3.5 Performance curves 1.05 1985331-6.2 ME-B Mark 9 Engine description 1.06 1990120-8.0 Engine cross section 1.07 1988334-5.0
2 Engine Layout and Load Diagrams, SFOC
Engine layout and load diagrams 2.01 1983833-8.5 Propeller diameter and pitch, influence on optimum propeller speed 2.02 1983878-2.6 Layout diagram sizes 2.03 1988277-0.7 Engine layout and load diagrams 2.04 1986993-5.3 Diagram for actual project 2.05 1988329-8.1 Specific fuel oil consumption, ME versus MC engines 2.06 1983836-3.4 SFOC for high efficiency turbochargers 2.07 1987016-5.2 SFOC reference conditions and guarantee 2.08 1988341-6.1 Examples of graphic calculation of SFOC 2.08 1988278-2.2 SFOC calculations (80%-85%) 2.09 1988790-8.0 SFOC calculations, example 2.10 1988782-5.0 Fuel consumption at an arbitrary load 2.11 1983843-4.5
3 Turbocharger Selection & Exhaust Gas Bypass
Turbocharger selection 3.01 1990172-3.0 Exhaust gas bypass 3.02 1984593-4.6 Emission control 3.03 1988447-2.2
4 Electricity Production
Electricity production 4.01 1984155-0.5 Designation of PTO 4.01 1985385-5.5 PTO/RCF 4.01 1984300-0.3 Space requirements for side mounted PTO/RCF 4.02 1987927-2.1 Engine preparations for PTO 4.03 1984315-6.3 PTO/BW GCR 4.04 1984316-8.8 Waste Heat Recovery Systems (WHRS) 4.05 1986647-4.1 L16/24-TII GenSet data 4.06 1988280-4.0 L21/31TII GenSet data 4.07 1988281-6.0 L23/30H-TII GenSet data 4.08 1988282-8.0 L27/38-TII GenSet data 4.09 1988284-1.0 L28/32H-TII GenSet data 4.10 1988285-3.0
MAN B&W Contents
Chapter Section
MAN Diesel
MAN B&W S 50ME-B9.3
5 Installation Aspects
Space requirements and overhaul heights 5.01 1984375-4.7 Crane beam for overhaul of turbochargers 5.03 1988741-8.1 Crane beam for turbochargers 5.03 1987636-0.2 Engine room crane 5.04 1987936-7.0 Overhaul with Double-Jib crane 5.04 1984534-8.4 Double-Jib crane 5.04 1984541-9.2 Engine outline, galleries and pipe connections 5.05 1984715-8.3 Centre of gravity 5.07 1990161-5.0 Counterflanges, Connection D 5.10 1986670-0.6 Counterflanges, Connection E 5.10 1987027-3.4 Engine seating and holding down bolts 5.11 1984176-5.11 Engine seating profile 5.12 1987728-3.0 Engine top bracing 5.13 1984672-5.8 Mechanical top bracing 5.14 1987774-8.0 Components for Engine Control System 5.16 1988538-3.2 Shaftline earthing device 5.17 1984929-2.4 MAN Alpha Controllable Pitch (CP) propeller 5.18 1984695-3.6 Hydraulic Power Unit for MAN Alpha CP propeller 5.18 1985320-8.3 MAN Alphatronic 2000 Propulsion Control System 5.18 1985322-1.5
6 List of Capacities: Pumps, Coolers & Exhaust Gas
Calculation of capacities 6.01 1988291-2.0 List of capacities and cooling water systems 6.02 1987463-3.0 List of capacities, S50ME-B9.3 6.03 1988718-1.0 Auxiliary system capacities for derated engines 6.04 1987149-5.6 Pump capacities, pressures and flow velocities 6.04 1984385-0.3 Example 1, Pumps and Cooler Capacity 6.04 1989083-3.0 Freshwater Generator 6.04 1987145-8.1 Jacket cooling water temperature control 6.04 1987144-6.2 Example 2, Fresh Water Production 6.04 1989084-5.0 Calculation of exhaust gas amount and temperature 6.04 1984318-1.3 Diagram for change of exhaust gas amount 6.04 1986369-4.1 Exhaust gas correction formula 6.04 1987140-9.0 Example 3, Expected Exhaust Gas 6.04 1989085-7.0
7 Fuel
Pressurised fuel oil system 7.01 1984228-2.7 Fuel oil system 7.01 1987661-0.4 Fuel oils 7.02 1983880-4.7 Fuel oil pipes and drain pipes 7.03 1985052-4.3 Fuel oil pipe insulation 7.04 1984051-8.3 Fuel oil pipe heat tracing 7.04 1987662-2.0 Components for fuel oil system 7.05 1983951-2.8 Components for fuel oil system, venting box 7.05 1984735-0.3 Water in fuel emulsification 7.06 1983882-8.5
MAN B&W Contents
Chapter Section
MAN Diesel
MAN B&W S 50ME-B9.3
8 Lubricating Oil
Lubricating and cooling oil system 8.01 1985317-4.3 Hydraulic Power Supply unit 8.02 1985318-6.2 Lubricating oil pipes for turbochargers 8.03 1984232-8.5 Lubricating oil consumption, centrifuges and list of lubricating oils 8.04 1983886-5.10 Components for lube oil system 8.05 1988891-5.0 Flushing of lubricating oil components and piping system 8.05 1988026-6.0 Lubricating oil outlet 8.05 1987034-4.1 Crankcase venting and bedplate drain pipes 8.07 1987837-3.1 Engine and tank venting to the outside air 8.07 1989181-5.0 Hydraulic oil back-flushing 8.08 1984829-7.3 Separate system for hydraulic control unit 8.09 1985315-0.1
9 Cylinder Lubrication
Cylinder lubricating oil system 9.01 1988559-8.2 List of cylinder oils 9.01 1988566-9.1 MAN B&W Alpha cylinder lubrication system 9.02 1987611-9.1 Alpha Adaptive Cylinder Oil Control (Alpha ACC) 9.02 1987614-4.1 Cylinder oil pipe heating 9.02 1987612-0.1 Cylinder lubricating oil pipes 9.02 1985328-2.2 Small heating box with filter, suggestion for 9.02 1987937-9.1
10 Piston Rod Stuffing Box Drain Oil
Stuffing box drain oil system 10.01 1983974-0.7
11 Central Cooling Water System
Central cooling 11.01 1984696-5.5 Central cooling water system 11.02 1984057-9.5 Components for central cooling water system 11.03 1983987-2.6
12 Seawater Cooling
Seawater systems 12.01 1983892-4.4 Seawater cooling system 12.02 1983893-6.5 Cooling water pipes 12.03 1983978-8.7 Components for seawater cooling system 12.04 1983981-1.3 Jacket cooling water system 12.05 1988576-5.3 Components for jacket cooling water system 12.07 1984056-7.3 Deaerating tank 12.07 1984063-8.3 Temperature at start of engine 12.08 1988346-5.0
13 Starting and Control Air
Starting and control air systems 13.01 1985329-4.2 Components for starting air system 13.02 1986057-8.1 Starting and control air pipes 13.03 1985330-4.4
MAN B&W Contents
Chapter Section
MAN Diesel
MAN B&W S 50ME-B9.3
14 Scavenge Air
Scavenge air system 14.01 1984006-5.3 Auxiliary blowers 14.02 1986586-2.3 Operation panel for auxiliary blowers 14.02 1986587-4.0 Electric motor for auxiliary blower 14.04 1986677-3.2 Scavenge air cooler cleaning system 14.05 1987684-9.1 Air cooler cleaning unit 14.05 1987686-2.0 Scavenge air box drain system 14.06 1987693-3.2 Fire extinguishing system for scavenge air space 14.07 1984044-7.5 Fire extinguishing pipes in scavenge air space 14.07 1987681-3.2
15 Exhaust Gas
Exhaust gas system 15.01 1984045-9.5 Exhaust gas pipes 15.02 1984069-9.4 Cleaning systems, water and soft blast 15.02 1987916-4.0 Exhaust gas system for main engine 15.03 1984074-6.3 Components of the exhaust gas system 15.04 1984075-8.7 Exhaust gas silencer 15.04 1986396-8.0 Calculation of exhaust gas back-pressure 15.05 1984094-9.3 Forces and moments at turbocharger 15.06 1990055-0.0 Diameter of exhaust gas pipe 15.07 1985892-3.2
16 Engine Control System
Engine Control System ME-B 16.01 1985184-2.3 Pneumatic manoeuvring diagram 16.01 1987619-3.1
17 Vibration Aspects
2nd order moments on 4, 5 and 6-cylinder engines 17.01 1984140-5.3 1st order moments on 4-cylinder engines 17.02 1986884-5.4 Electrically driven moment compensator 17.02 1983925-0.5 Power Related Unbalance (PRU) 17.03 1986978-1.2 Guide force moments 17.04 1987680-1.1 Guide force moments, data 17.05 1984223-3.5 Vibration limits valid for single order harmonics 17.05 1987987-0.2 Axial vibrations 17.05 1988264-9.0 Critical running 17.06 1984224-5.4 External forces and moments in layout point 17.06 1984226-9.3
17.07 1989149-4.0
18 Monitoring Systems and Instrumentation
PMI Auto-tuning system 18.01 1988529-9.2 CoCoS-EDS systems 18.02 1988530-9.2 Alarm - slow down and shut down system 18.03 1984582-6.8 Class and MAN Diesel & Turbo requirements 18.04 1987040-3.4 Local instruments 18.04 1984583-8.10 Other alarm functions 18.05 1984586-3.9 Bearing monitoring systems 18.06 1984587-5.13 LDCL cooling water monitoring system 18.06 1986727-7.5 Control devices 18.06 1990197-5.0 Identification of instruments 18.06 1986728-9.4
18.07 1984585-1.6
MAN B&W Contents
Chapter Section
MAN Diesel
MAN B&W S 50ME-B9.3
19 Dispatch Pattern, Testing, Spares and Tools
Specification for painting of main engine 19.01 1987620-3.2 Dispatch pattern, list of masses and dimensions 19.02 1984516-9.6 List of spare parts, unrestricted service 19.05 1984612-7.8 Additional spares 19.06 1985324-5.12 Wearing parts 19.07 1985323-3.4 Large spare parts, dimensions and masses 19.08 1988371-5.2 Rotor for turbocharger 19.09 1987832-4.1
20 Project Support and Documentation
Project support and documentation 20.01 1984588-7.5 Installation data application 20.02 1984590-9.3 Extent of Delivery 20.03 1984591-0.6 Installation documentation 20.04 1984592-2.5
A Appendix
Symbols for piping A 1983866-2.3
MAN B&W
MAN Diesel
Engine Design
1
MAN B&W 1.01
Page 1 of 2
MAN Diesel
MAN B&W M E-B-TII .5/.3 engine s 199 01 13-7.0
The Fuel Optimised ME-B Tier II Engine
The ever valid requirement of ship operators is to obtain the lowest total operational costs, and especially the lowest possible specific fuel oil consumption at any load, and under the prevailing operating conditions.
However, lowspeed twostroke main engines of the MC-C type, with a chain driven camshaft, have limited flexibility with regard to fuel injection to match the prevailing operating conditions.
A system with electronically controlled hydraulic activation provides the required flexibility, this system form the core of the ME-B ‘Engine Control System’, described later in detail in Chapter 16.
Concept of the ME-B engine
The ME-B engine concept consists of a hydraulic mechanical system for activation of the fuel injec­tion. The actuator is electronically controlled by a number of control units forming the complete En­gine Control System.
MAN Diesel & Turbo has specifically developed both the hardware and the software inhouse, in order to obtain an integrated solution for the En­gine Control System.
The fuel pressure booster consists of a simple plunger powered by a hydraulic piston activated by oil pressure. The oil pressure is controlled by an electronically controlled proportional valve.
The exhaust valve is activated by a light camshaft, driven by a chain drive placed in the aft end of the engine. The closing timing of the exhaust valve is electronically controlled for lower fuel consump­tion at low load.
To have common spare parts, the exhaust valve used for the ME-B is the same as the one used for the MC-C. The exhaust valve is of the DuraSpin­dle type with a W-seat bottom piece.
In the hydraulic system, the normal lube oil is used as the medium. It is filtered and pressurised by an electrically driven Hydraulic Power Supply unit mounted on the engine.
The starting valves are opened pneumatically by the mechanically activated starting air distributor.
By electronic control of the above valve according to the measured instantaneous crankshaft posi­tion, the Engine Control System fully controls the combustion process.
System flexibility is obtained by means of different ‘Engine running modes’, which are selected either automatically, depending on the operating condi­tions, or manually by the operator to meet specific goals. The basic running mode is ‘Fuel economy mode’ to comply with IMO NOx emission limita­tion.
The market is always moving, and requirements for more competitive engines, i.e. the lowest pos­sible propeller speed, lower fuel consumption, lower lube oil consumption and more flexibility regarding emission and easy adjustment of the engine parameters, call for a re-evaluation of the design parameters, engine control and layout.
Engine design and IMO regulation compliance
For MAN B&W ME-B-TII designated engines, the design and performance parameters have been upgraded and optimised to comply with the Inter­national Maritime Organisation (IMO) Tier II emis­sion regulations.
The potential derating and part load SFOC figures for the Tier II engines have also been updated.
For engines built to comply with IMO Tier I emis­sion regulations, please refer to the Marine Engine IMO Tier I Project Guide.
MAN B&W 1.01
Page 2 of 2
MAN Diesel
199 01 12-5.0
MAN B&W M E-C/ME-B-TII .5 /.3 engin es
Tier II fuel optimisation
NOx regulations place a limit on the SFOC on two-stroke engines. In general, NOx emissions will increase if SFOC is decreased and vice versa. In the standard configuration, MAN B&W engines are optimised close to the IMO NOx limit and, there­fore, NOx emissions may not be further increased.
The IMO NOx limit is given as a weighted average of the NOx emission at 25, 50, 75 and 100% load. This relationship can be utilised to tilt the SFOC profile over the load range. This means that SFOC can be reduced at part load or low load at the expense of a higher SFOC in the high-load range without exceeding the IMO NOx limit.
Optimisation of SFOC in the part-load (50-85%) or low-load (25-70%) range requires selection of a tuning method:
• ECT: Engine Control Tuning
• VT: Variable Turbine Area
• EGB: Exhaust Gas Bypass
• HPT: High Pressure Tuning (only for ME-C)
Each tuning method makes it possible to optimise the fuel consumption when normally operating at low loads, while maintaining the possibility of op­erating at high load when needed.
The tuning methods are available for all SMCR in the specific engine layout diagram but they can­not be combined. The specific SFOC reduction potential of each tuning method together with full rated (L
1/L3
) and maximum derated (L2/L4) is
shown in Section 1.03.
For engine types 40 and smaller, as well as for larger types with conventional turbochargers, only high-load optimisation is applicable.
In general, data in this project guide is based on high-load optimisation unless explicitly noted. For part- and low-load optimisation, calculations can be made in the CEAS application described in Section 20.02.
MAN B&W M C/MC-C, ME/ MEC/MEB/-G I engines 198 38 24 3.9
MAN B&W 1.02
Page 1 of 1
MAN Diesel
Engine Type Designation
6 S 90 M E C 9 .2 -GI -TII
Engine programme
Diameter of piston in cm
G ‘Green’ Ultra long stroke
S Super long stroke L Long stroke K Short stroke
Stroke/bore ratio
Number of cylinders
Concept
E Electronically controlled C Camshaft controlled
Fuel injection concept
(blank) Fuel oil only
GI Gas injection
Emission regulation
TII IMO Tier level
Design
C Compact engine
B Exhaust valve controlled
by camshaft
Mark number
Version number
MAN B&W 1.03
Page 1 of 1
MAN Diesel
198 85 02- 3.1MAN B&W S 50ME-B9.3 -TII
Power, Speed and Fuel Oil
MAN B&W S50ME-B9.3-TII
Fig 1.03.01: Power, speed and fuel oil
MAN B&W S50ME-B9
Cyl. L1 kW Stroke: 2,214 mm
5 8,900 6 10,680 7 12,460 8 14,240 9 16,020
SFOC for engines with layout on L1 - L3 line [g/kWh]
L1/L3 MEP: 21.0 bar
SFOC optimised load range Tuning 50% 75% 100%
High load (85%-100%) - 167.5 165.0 168.0
Part load (50%-85%)
ECT 166.5 164.0 171.0 VT 164.5 163.5 168.5 EGB 164.5 163.5 169.5
Low load (25%-70%)
ECT 165.0 164.5 169.5 VT 162.5 164.5 168.5 EGB 162.5 164.5 169.5
SFOC for engines with layout on L2 - L4 line [g/kWh]
L2/L4 MEP: 16.8 bar
SFOC optimised load range Tuning 50% 75% 100%
High load (85%-100%) - 163.5 159.5 162.0
Part load (50%-85%)
ECT 162.5 158.5 165.0 VT 160.5 158.0 162.5 EGB 160.5 158.0 163.5
Low load (25%-70%)
ECT 161.0 159.0 163.5 VT 158.5 159.0 162.5 EGB 158.5 159.0 163.5
The SFOC excludes 1 g/kWh for the consumption of the electric HPS
kW/cyl.
r/min
L
1
L
2
1,780
1,510
1,420
1,210
99 117
L
3
L
4
MAN B&W 1.04
Page 1 of 1
MAN Diesel
MAN B&W M C/MC-C, ME/ ME-C/MEB en gines 198 4 6 343.5
Engine Power Range and Fuel Oil Consumption
Power
Speed
L
3
L
4
L
2
L
1
Specific Fuel Oil Consumption (SFOC)
The figures given in this folder represent the val­ues obtained when the engine and turbocharger are matched with a view to obtaining the lowest possible SFOC values while also fulfilling the IMO NOX Tier II emission limitations.
Stricter emission limits can be met on request, us­ing proven technologies.
The SFOC figures are given in g/kWh with a tol­erance of 5% (at 100% SMCR) and are based on the use of fuel with a lower calorific value of 42,700 kJ/kg (~10,200 kcal/kg) at ISO conditions:
Ambient air pressure .............................1,000 mbar
Ambient air temperature ................................25 °C
Cooling water temperature ............................ 25 °C
Although the engine will develop the power speci­fied up to tropical ambient conditions, specific fuel oil consumption varies with ambient condi­tions and fuel oil lower calorific value. For calcula­tion of these changes, see Chapter 2.
Lubricating oil data
The cylinder oil consumption figures stated in the tables are valid under normal conditions.
During runningin periods and under special con­ditions, feed rates of up to 1.5 times the stated values should be used.
Engine Power
The following tables contain data regarding the power, speed and specific fuel oil consumption of the engine.
Engine power is specified in kW for each cylinder number and layout points L1, L2, L3 and L4.
Discrepancies between kW and metric horsepow­er (1 BHP = 75 kpm/s = 0.7355 kW) are a conse­quence of the rounding off of the BHP values.
L1 designates nominal maximum continuous rating (nominal MCR), at 100% engine power and 100% engine speed.
L2, L3 and L4 designate layout points at the other three corners of the layout area, chosen for easy reference.
Fig. 1.04.01: Layout diagram for engine power and speed
Overload corresponds to 110% of the power at MCR, and may be permitted for a limited period of one hour every 12 hours.
The engine power figures given in the tables re­main valid up to tropical conditions at sea level as stated in IACS M28 (1978), i.e.:
Blower inlet temperature ................................45 °C
Blower inlet pressure ............................1,000 mbar
Seawater temperature .................................... 32 °C
Relative humidity ..............................................60%
178 51 489.0
MAN B&W
Page 1 of 1
MAN Diesel
198 53 31-6 .2MAN B&W MC/MC -C, ME/ME-C /MEB/ GI engines
Performance Curves
1.0 5
Updated engine and capacities data is available from the CEAS program on www.marine.man.eu ’Two-Stroke’ ’CEAS Engine Calculations’.
MAN B&W 1.06
Page 1 of 7
MAN Diesel
MAN B&W M E-B9.5/.3 engin es 199 01 20 -8.0
Please note that engines built by our licensees are in accordance with MAN Diesel & Turbo drawings and standards but, in certain cases, some lo­cal standards may be applied; however, all spare parts are interchangeable with MAN Diesel & Turbo designed parts.
Some components may differ from MAN Diesel & Turbo’s design because of local production facilities or the application of local standard components.
In the following, reference is made to the item numbers specified in the ‘Extent of Delivery’ (EoD) forms, both for the ‘Basic’ delivery extent and for some ‘Options’.
Bedplate and Main Bearing
The bedplate is made with the thrust bearing in the aft end of the engine. The bedplate is of the welded design and the normally cast part for the main bearing girders is made from either rolled steel plates or cast steel.
For fitting to the engine seating in the ship, long, elastic holdingdown bolts and hydraulic tighten­ing tools are used.
The bedplate is made without taper for engines mounted on epoxy chocks.
The oil pan, which is made of steel plate and is welded to the bedplate, collects the return oil from the forced lubricating and cooling oil system. The oil outlets from the oil pan are normally vertical and are provided with gratings.
Horizontal outlets at both ends can be arranged for some cylinder numbers, however this must be confirmed by the engine builder.
The main bearings consist of thin walled steel shells lined with bearing metal. The main bearing bottom shell can be rotated out and in by means of special tools in combination with hydraulic tools for lifting the crankshaft. The shells are kept in po­sition by a bearing cap.
Frame Box
The frame box is of welded design. On the ex­haust side, it is provided with relief valves for each cylinder while, on the manoeuvring side, it is pro­vided with a large hinged door for each cylinder.
The framebox is of the well-proven triangular guide-plane design with twin staybolts giving ex­cellent support for the guide shoe forces.
Cylinder Frame and Stuffing Box
For the cylinder frame, two possibilities are avail­able.
• Nodular cast iron
• Welded design with integrated scavenge air re­ceiver.
The cylinder frame is provided with access covers for cleaning the scavenge air space, if required, and for inspection of scavenge ports and piston rings from the manoeuvring side. Together with the cylinder liner it forms the scavenge air space.
The cylinder frame is fitted with pipes for the pis­ton cooling oil inlet. The scavenge air receiver, tur­bocharger, air cooler box and gallery brackets are located on the cylinder frame. At the bottom of the cylinder frame there is a piston rod stuffing box, provided with sealing rings for scavenge air, and with oil scraper rings which prevent crankcase oil from coming up into the scavenge air space.
Drains from the scavenge air space and the piston rod stuffing box are located at the bottom of the cylinder frame.
ME-B Mark 9 Engine Description
MAN B&W 1.06
Page 2 of 7
MAN Diesel
MAN B&W M E-B9.5/.3 engin es 199 01 20 -8.0
Cylinder Liner
The cylinder liner is made of alloyed cast iron and is suspended in the cylinder frame with a lowsituated flange. The top of the cylinder liner is fitted with a cooling jacket. The cylinder liner has scavenge ports and drilled holes for cylinder lubrication.
The Piston Cleaning ring (PC-ring) is installed be­tween the liner and the cylinder cover, scraping off excessive ash and carbon formations from the piston topland.
Cylinder Cover
The cylinder cover is of forged steel, made in one piece, and has bores for cooling water. It has a central bore for the exhaust valve, and bores for the fuel valves, a starting valve and an indicator valve.
The cylinder cover is attached to the cylinder frame with studs and nuts tightened with hydraulic jacks.
Crankshaft
The crankshaft is of the semi-built design, in one piece, and made from forged steel.
At the aft end, the crankshaft is provided with the collar for the thrust bearing, and the flange for the turning wheel and for the coupling bolts to an in­termediate shaft.
At the front end, the crankshaft is fitted with the collar for the axial vibration damper and a flange for the fitting of a tuning wheel. The flange can also be used for a Power Take Off, if so desired.
Coupling bolts and nuts for joining the crankshaft together with the intermediate shaft are not nor­mally supplied.
Thrust Bearing
The propeller thrust is transferred through the thrust collar, the segments, and the bedplate, to the end chocks and engine seating, and thus to the ship’s hull.
The thrust bearing is located in the aft end of the engine. The thrust bearing is of the B&WMichell type, and consists primarily of a thrust collar on the crankshaft, a bearing support, and segments of steel lined with white metal. The thrust shaft is an integrated part of the crankshaft and it is lubri­cated by the engine’s lubricating oil system.
As the propeller thrust is increasing due to the higher engine power, a flexible thrust cam has been introduced to obtain a more even force dis­tribution on the pads.
Turning Gear and Turning Wheel
The turning wheel is fitted to the thrust shaft, and it is driven by a pinion on the terminal shaft of the turning gear, which is mounted on the bedplate. The turning gear is driven by an electric motor.
A blocking device prevents the main engine from starting when the turning gear is engaged. En­gagement and disengagement of the turning gear is effected manually by an axial movement of the pinion.
The control device for the turning gear, consisting of starter and manual control box, can be ordered as an option.
Axial Vibration Damper
The engine is fitted with an axial vibration damper, mounted on the fore end of the crankshaft. The damper consists of a piston and a splittype hous­ing located forward of the foremost main bearing.
The piston is made as an integrated collar on the main journal, and the housing is fixed to the main bearing support.
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Tuning Wheel / Torsional Vibration Damper
A tuning wheel or torsional vibration damper may have to be ordered separately, depending on the final torsional vibration calculations.
Connecting Rod
The connecting rod is made of forged and pro­vided with bearing caps for the crosshead and crankpin bearings.
The crosshead and crankpin bearing caps are se­cured to the connecting rod with studs and nuts tightened by means of hydraulic jacks.
The crosshead bearing consists of a set of thinwalled steel shells, lined with bearing metal. The crosshead bearing cap is in one piece, with an angular cutout for the piston rod.
The crankpin bearing is provided with thinwalled steel shells, lined with bearing metal. Lube oil is supplied through ducts in the crosshead and con­necting rod.
Piston
The piston consists of a piston crown and piston skirt. The piston crown is made of heatresistant steel and has four ring grooves which are hardchrome plated on both the upper and lower surfaces of the grooves.
The piston is bore-cooled and with a high topland.
The piston ring pack is No. 1 piston ring, high CPR (Controlled Pressure Relief), Nos. 2 to 4, piston rings with angle cut. All rings are with Alu-coat on the running surface for safe running-in of the pis­ton ring.
The uppermost piston ring is higher than the oth­ers. The piston skirt is of cast iron with a bronze band.
Piston Rod
The piston rod is of forged steel and is surface hardened on the running surface for the stuffing box. The piston rod is connected to the crosshead with four bolts. The piston rod has a central bore which, in conjunction with a cooling oil pipe, forms the inlet and outlet for cooling oil.
Crosshead
The crosshead is of forged steel and is provided with cast steel guide shoes with white metal on the running surface.
The guide shoe is of the low friction design.
The telescopic pipe for oil inlet and the pipe for oil outlet are mounted on the guide shoes.
Scavenge Air System
The air intake to the turbocharger takes place directly from the engine room through the turbo­charger intake silencer. From the turbocharger, the air is led via the charging air pipe, air cooler and scavenge air receiver to the scavenge ports of the cylinder liners, see Chapter 14.
Scavenge Air Cooler
For each turbocharger is fitted a scavenge air cooler of the monoblock type designed for sea­water cooling at up to 2.0  2.5 bar working pres­sure, alternatively, a central cooling system can be chosen with freshwater of maximum 4.5 bar work­ing pressure.
The scavenge air cooler is so designed that the difference between the scavenge air temperature and the water inlet temperature at specified MCR can be kept at about 12 °C.
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MAN B&W M E-B9.5/.3 engin es 199 01 20 -8.0
Auxiliary Blower
The engine is provided with electricallydriven scavenge air blowers. The suction side of the blowers is connected to the scavenge air space after the air cooler.
Between the air cooler and the scavenge air re­ceiver, nonreturn valves are fitted which auto­matically close when the auxiliary blowers supply the air.
The auxiliary blowers will start operating con­secutively before the engine is started in order to ensure sufficient scavenge air pressure to obtain a safe start.
The auxiliary blower design is of the integrated type.
Further information is given in Chapter 14.
Exhaust Gas System
From the exhaust valves, exhaust gas is led to the exhaust gas receiver where the fluctuating pres­sure from the individual cylinders is equalised, and the total volume of gas is led further on to the turbocharger(s). After the turbocharger(s), the gas is led to the external exhaust pipe system.
Compensators are fitted between the exhaust valves and the receiver, and between the receiver and the turbocharger(s).
The exhaust gas receiver and exhaust pipes are provided with insulation, covered by galvanised steel plating.
A protective grating is installed between the ex­haust gas receiver and the turbocharger.
Exhaust Turbocharger
Three turbocharger makes are available for the ME-B engines, i.e. MAN, ABB and MHI. As an op­tion, MAN TCA turbochargers can be delivered with variable nozzle area technology that reduce the fuel consumption at part load by controlling the scavenge air pressure.
The turbocharger selection is described in Chap­ter 3, and the exhaust gas system in Chapter 15.
Camshaft and Cams
The camshaft is made in one piece with exhaust cams.
The exhaust cams are made of steel, with a hard­ened roller race, and are shrunk onto the shaft. They can be adjusted and dismantled hydrauli­ca lly.
The camshaft bearings consist of one lower half­shell fitted in a bearing support. The camshaft is lubricated by the main lubricating oil system.
Chain Drive
The camshaft is driven from the crankshaft by a chain drive, which is kept running tight by a manu­ally adjusted chain tightener. The long free lengths of chain are supported by rubber-clad guidebars and the chain is lubricated through oil spray pipes fitted at the chain wheels and guidebars.
2nd Order Moment Compensators
The 2nd order moment compensators are rel­evant only for 5 or 6-cylinder engines, and can be mounted either on the aft end or on both fore and aft end. The aft-end compensator consists of bal­ance weights built into the camshaft chain drive.
The fore-end compensator consists of balance weights driven from the fore end of the crankshaft. The 2nd order moment compensators as well as the basic design and options are described in Section 17.02.
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MAN Diesel
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Hydraulic Cylinder Unit
The hydraulic cylinder unit (HCU) consists of a base plate on which a distributor block is mount­ed. The distributor block is fitted with one accu­mulator to ensure that the necessary hydraulic oil peak flow is available for the Electronic Fuel Injec­tion.
The distributor block serves as a mechanical sup­port for the hydraulically activated fuel pressure booster.
There is one Hydraulic Cylinder Unit per two cyl­inders. The HCU is equipped with two pressure boosters, two ELFI valves and two Alpha Lubrica­tors. Thereby, one HCU is operating two cylinders.
The Hydraulic Power Supply
The Hydraulic Power Supply (HPS) is installed in the front end of the engine. The HPS is electrically driven and consists of two electric motors each driving a hydraulic pump.
The pressure for the hydraulic oil is 300 bar. Each of the pumps has a capacity corresponding to min. 55% of the engine power. In case of malfunc­tion of one of the pumps, it is still possible to op­erate the engine with 55% engine power, enabling around 80% ship speed.
Fuel Oil Pressure Booster and Fuel Oil High Pressure Pipes
The engine is provided with one hydraulically acti­vated fuel oil pressure booster for each cylinder.
Fuel injection is activated by a proportional valve, which is electronically controlled by the Cylinder Control Unit.
The fuel oil highpressure pipes are double-walled and insulated but not heated.
Further information is given in Section 7.01.
Fuel Valves and Starting Air Valve
Each cylinder cover is equipped with two fuel valves, starting valve, and indicator cock.
The opening of the fuel valves is controlled by the high pressure fuel oil created by the fuel oil pressure booster, and the valves are closed by a spring.
An automatic vent slide allows circulation of fuel oil through the valve and high pressure pipes when the engine is stopped. The vent slide also prevents the compression chamber from being filled up with fuel oil in the event that the valve spindle sticks. Oil from the vent slide and other drains is led away in a closed system.
The mechanically driven starting air distributor is the same as the one used on the MC-C engines.
The starting air system is described in detail in Section 13.01.
Engine Control System
The ME-B Engine Control System (ECS) controls the hydraulic fuel booster system, the fuel injec­tion, governor function and cylinder lubrication.
The ECS consists of a number of computer-based control units, operating panels and auxiliary equipment located in the engine room and the en­gine control room.
The ME-B Engine Control System is described in Chapter 16.
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Exhaust Valve
The exhaust valve consists of the valve housing and the valve spindle. The valve housing is made of cast iron and is arranged for water cooling. The housing is provided with a water cooled bottom piece of steel with a flame hardened seat of the W-seat design.
The exhaust valve spindle is a DuraSpindle, a spindle made of Nimonic is available as an option. The housing is provided with a spindle guide in any case.
The exhaust valve is tightened to the cylinder cov­er with studs and nuts. It is opened hydraulically and closed by means of air pressure. The hydrau­lic system consists of a piston actuator placed on the roller guide housing, a highpressure pipe, and a working cylinder on the exhaust valve.
The piston actuator is activated by a cam on the camshaft, a built-in timing piston and a control valve enables control of the closing time of the ex­haust valve.
In operation, the valve spindle slowly rotates, driv­en by the exhaust gas acting on small vanes fixed to the spindle.
Sealing of the exhaust valve spindle guide is pro­vided by means of Controlled Oil Level (COL), an oil bath in the bottom of the air cylinder, above the sealing ring. This oil bath lubricates the exhaust valve spindle guide and sealing ring as well.
Reversing
On reversible engines (with Fixed Pitch Propellers mainly), reversing of the engine is performed in the Engine Control System by letting the starting air distributor supply air to the cylinders in order of the desired direction of rotation and by timing the fuel injection accordingly.
The exhaust valve gear is not to be reversed.
Indicator Cock
The engine is fitted with an indicator cock to which the PMI pressure transducer is connected. The PMI system, a pressure analyser system, is described in Section 18.02.
MAN B&W Alpha Cylinder Lubrication
The electronically controlled MAN B&W Alpha cylinder lubrication system is applied to the ME-B engines.
The main advantages of the MAN B&W Alpha cyl­inder lubrication system, compared with the con­ventional mechanical lubricator, are:
• Improved injection timing
• Increased dosage flexibility
• Constant injection pressure
• Improved oil distribution in the cylinder liner
• Possibility for prelubrication before starting.
More details about the cylinder lubrication system can be found in Chapter 9.
Manoeuvring System
The engine is provided with a pneumatic/electric manoeuvring system. The system transmits orders from the Engine Control System to the engine.
The manoeuvring system makes it possible to start, stop, reverse the engine and control the en­gine speed.
The engine is provided with an engine side con­sole and instrument panel.
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Gallery Arrangement
The engine is provided with gallery brackets, stanchions, railings and platforms (exclusive of ladders). The brackets are placed at such a height as to provide the best possible overhauling and inspection conditions.
Some main pipes of the engine are suspended from the gallery brackets, and the topmost gallery platform on the manoeuvring side is provided with overhauling holes for the pistons.
The engine is prepared for top bracings on the ex­haust side, or on the manoeuvring side.
Piping Arrangements
The engine is delivered with piping arrangements for:
• Fuel oil
• Heating of fuel oil pipes
• Lubricating oil, piston cooling oil and hydraulic oil pipes
• Cylinder lubricating oil
• Cooling water to scavenge air cooler
• Jacket and turbocharger cooling water
• Cleaning of turbocharger
• Fire extinguishing in scavenge air space
• Starting air
• Control air
• Oil mist detector
• Various drain pipes.
All piping arrangements are made of steel piping, except the control air and steam heating of fuel pipes, which are made of copper.
The pipes are provided with sockets for local instruments, alarm and safety equipment and, furthermore, with a number of sockets for supple­mentary signal equipment. Chapter 18 deals with the instrumentation.
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MAN Diesel
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Engine Cross Section of S50ME-B9
526 56 24-2.0.0
Fig.: 1.07.01: Engine cross section
MAN B&W
MAN Diesel
Engine Layout and Load
Diagrams, SFOC
2
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Engine Layout and Load Diagrams
Introduction
The effective power ‘P’ of a diesel engine is pro­portional to the mean effective pressure pe and engine speed ‘n’, i.e. when using ‘c’ as a constant:
P = c × pe × n
so, for constant mep, the power is proportional to the speed:
P = c × n1 (for constant mep)
When running with a Fixed Pitch Propeller (FPP), the power may be expressed according to the propeller law as:
P = c × n3 (propeller law)
Thus, for the above examples, the power P may be expressed as a power function of the speed ‘n’ to the power of ‘i’, i.e.:
P = c × n
i
Fig. 2.01.01 shows the relationship for the linear functions, y = ax + b, using linear scales.
The power functions P = c × ni will be linear func­tions when using logarithmic scales:
log (P) = i × log (n) + log (c)
Fig. 2.01.01: Straight lines in linear scales
Fig. 2.01.02: Power function curves in logarithmic scales
Thus, propeller curves will be parallel to lines hav­ing the inclination i = 3, and lines with constant mep will be parallel to lines with the inclination i = 1.
Therefore, in the Layout Diagrams and Load Dia­grams for diesel engines, logarithmic scales are used, giving simple diagrams with straight lines.
Propulsion and Engine Running Points
Propeller curve
The relation between power and propeller speed for a fixed pitch propeller is as mentioned above described by means of the propeller law, i.e. the third power curve:
P = c × n3, in which:
P = engine power for propulsion n = propeller speed c = constant
Propeller design point
Normally, estimates of the necessary propeller power and speed are based on theoretical cal­culations for loaded ship, and often experimental tank tests, both assuming optimum operating conditions, i.e. a clean hull and good weather. The combination of speed and power obtained may be called the ship’s propeller design point (PD),
178 05 403.0
178 05 403.1
y
2
1
0
0
12
b
a
y=ax+b
x
y=log(P)
i = 0
i = 1
i = 2
i = 3
P = n x c
i
log (P) = i x log (n) + log (c)
x = log (n)
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placed on the light running propeller curve 6. See below figure. On the other hand, some shipyards, and/or propeller manufacturers sometimes use a propeller design point (PD) that incorporates all or part of the socalled sea margin described below.
the socalled sea margin, which is traditionally about 15% of the propeller design (PD) power.
Engine layout (heavy propeller)
When determining the necessary engine layout speed that considers the influence of a heavy run­ning propeller for operating at high extra ship resis­tance, it is (compared to line 6) recommended to choose a heavier propeller line 2. The propeller curve for clean hull and calm weather line 6 may then be said to represent a ‘light running’ (LR) propeller.
Compared to the heavy engine layout line 2, we recommend using a light running of 3.07.0% for design of the propeller.
Engine margin
Besides the sea margin, a socalled ‘engine mar­gin’ of some 10% or 15% is frequently added. The corresponding point is called the ‘specified MCR for propulsion’ (MP), and refers to the fact that the power for point SP is 10% or 15% lower than for point MP.
Point MP is identical to the engine’s specified MCR point (M) unless a main engine driven shaft generator is installed. In such a case, the extra power demand of the shaft generator must also be considered.
Constant ship speed lines
The constant ship speed lines , are shown at the very top of the figure. They indicate the power required at various propeller speeds in order to keep the same ship speed. It is assumed that, for each ship speed, the optimum propeller diameter is used, taking into consideration the total propul­sion efficiency. See definition of in Section 2.02.
Note:
Light/heavy running, fouling and sea margin are overlapping terms. Light/heavy running of the propeller refers to hull and propeller deterioration and heavy weather, whereas sea margin i.e. extra power to the propeller, refers to the influence of the wind and the sea. However, the degree of light running must be decided upon experience from the actual trade and hull design of the vessel.
Fig. 2.01.03: Ship propulsion running points and engine layout
Power, % af L
1
100%
= 0,15
= 0,20
= 0,25 = 0,30
L
3
100%
L
4
L
2
Engine margin (SP=90% of MP)
Sea margin (15% of PD)
Engine speed, % of L
1
L
1
MP
SP
PD
HR
LR
2 6
PD
Line 2 Propulsion curve, fouled hull and heavy weather (heavy running), recommended for engine layout Line 6 Propulsion curve, clean hull and calm weather (light
running), for propeller layout MP Specified MCR for propulsion SP Continuous service rating for propulsion PD Propeller design point HR Heavy running LR Light running
Fouled hull
When the ship has sailed for some time, the hull and propeller become fouled and the hull’s re­sistance will increase. Consequently, the ship’s speed will be reduced unless the engine delivers more power to the propeller, i.e. the propeller will be further loaded and will be heavy running (HR).
As modern vessels with a relatively high service speed are prepared with very smooth propeller and hull surfaces, the gradual fouling after sea trial will increase the hull’s resistance and make the propeller heavier running.
Sea margin and heavy weather
If, at the same time the weather is bad, with head winds, the ship’s resistance may increase com­pared to operating in calm weather conditions. When determining the necessary engine power, it is normal practice to add an extra power margin,
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