CN101283171A - Propulsion system of ship - Google Patents
Propulsion system of ship Download PDFInfo
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- CN101283171A CN101283171A CNA200580051784XA CN200580051784A CN101283171A CN 101283171 A CN101283171 A CN 101283171A CN A200580051784X A CNA200580051784X A CN A200580051784XA CN 200580051784 A CN200580051784 A CN 200580051784A CN 101283171 A CN101283171 A CN 101283171A
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- motor
- power
- diesel engine
- hydraulic
- stroke
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/02—Drives of pumps; Varying pump drive gear ratio
- F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
- F02B39/10—Non-mechanical drives, e.g. fluid drives having variable gear ratio electric
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H21/00—Use of propulsion power plant or units on vessels
- B63H21/12—Use of propulsion power plant or units on vessels the vessels being motor-driven
- B63H21/14—Use of propulsion power plant or units on vessels the vessels being motor-driven relating to internal-combustion engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
- F02B37/10—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/02—Drives of pumps; Varying pump drive gear ratio
- F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
- F02B67/10—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of charging or scavenging apparatus
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B61/00—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing
- F02B61/04—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving propellers
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Ocean & Marine Engineering (AREA)
- Supercharger (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
A propulsion system for large ocean going vessels. The system includes a large turbo charged multi-cylinder two-stroke diesel engine of the crosshead type coupled to the propeller shaft as a main prime mover and one or more substantially smaller diesel engines coupled to generators as secondary prime movers. The main engine requires electric, hydraulic and pneumatic power in order to be able to startup and operate. The main engine requires heat and small hydraulic power during short stops, and hydraulic power, pneumatic and electrical power during startup. Hydraulic power is provided by one or more high-pressure pumps or pumping stations that are driven by power takeoff from the crankshaft of the large two-stroke diesel engine, by electric motors or by auxiliary diesel engines.
Description
Technical field
The present invention relates to a kind of marine propuision system that comprises the large-sized two-stroke crosshead diesel engine.
Background technique
The large-sized two-stroke diesel engine that is used for the ship propelling is a kind of machine of complexity, and its core that forms ship power and propulsion system also comprises a series of supplementary equipment.
The large-sized two-stroke crosshead diesel engine of these low cruises is huge and the machine of power generation efficiently.The maximum in these motors produces the power of about 100.000kW in the time of 94 rev/mins, total length is that 33 meters and weight are near 3500 tons.
The auxiliary diesel engine that these motors---are so-called generator set---with the driving generator.Generator set is in generator stopping period and power supply and heat supply in start-up course.
The supplementary equipment of two-stroke diesel engine comprises for example high-pressure hydraulic pump, pneumatic pump (compressor), lubricating pump, fuel oil supplypump, fuel circulating pump, sea water pump, jacket water pump, central water pump and auxiliary blower.
The supplementary equipment that great majority are listed or power-actuated---auxiliary blower for example, perhaps by the bent axle acquisition power of mechanical transmission mechanism (that is, chain or gear) from large-sized two-stroke diesel engine---for example under the situation of high-pressure hydraulic pump or pumping plant.
Electronically controlled large-sized two-stroke diesel engine uses quite a large amount of hydraulic power (about bent axle power 1.5% to 2%) together with its hydraulically operated exhaust valve in the power operation process.
In engine starting process, need a spot of hydraulic pressure.Therefore, in engine starting process, provide hydraulic power than primary hydraulic pump or pumping plant by electronic.Because motor is to start by utilizing pressurized air that cylinder is pressurizeed, so the pneumatic pump of at least a portion is power-actuated.The electric energy that drives the motor of these oil hydraulic pumps and pneumatic pump is provided by generator set.Generator set also at the motor stopping period for large-sized two-stroke diesel engine insulation and provide electric energy with the heavy fuel oil that in fuel channel and reservoir, circulates.Generator set also provides heating power that---cooling system that for example is used for freighter---uses by multiple consumer and the electric power on the ship and is used to throw light on when master motor stops and the electric energy of energy is provided as electrical equipment.
From the viewpoint of fuel efficiency,, be attractive to drive supplementary equipment so obtain mechanical energy from the bent axle of large-sized two-stroke diesel engine because energy produces efficiently at the bent axle place of large-sized two-stroke diesel engine.Yet, obtain mechanical energy from bent axle and only can be used in permission and between supplementary equipment and bent axle, realize simply reaching direct-connected position, and very not useful for the supplementary equipment that consumes the relatively small amount energy.For example, because the position of auxiliary blower needs the complicated mechanical transmission to be connected to bent axle, so help to provide the auxiliary blower of scavenging usually by the motor supplying energy in low load operation (being lower than the 40%-50% of the maximum rated power) process of large-sized two-stroke diesel engine.The power that is consumed by auxiliary blower is very many, typically drops in 1.8% to 2.3% the scope of maximum rated power of large-sized two-stroke diesel engine.Another shortcoming of obtaining energy from bent axle need to be high velocity ratio so that low crankshaft speed (being 100-200 rev/min to the maximum) is increased to the required fair speed of most of supplementary equipment.These high velocity ratios cause the driving mechanism between bent axle and the power consumption device complicated more and therefore expensive more.
The place use motor that the relatively easy degree that flexibility in position between power source and the motor that drives supplementary equipment and forming is connected plays a decisive role for example is used for auxiliary blower.
Maximum two-stroke diesel engine is huge, and single motor can produce the power greater than 100.000kW.The motor of driving supplementary equipment is the sub-fraction of consumption of engine bent axle power only, but is big motor with regard to absolute value.For example, graceful grace diesel engine (the MAN B﹠amp that has the maximum rated power of 68.520kW; W Diesel) 12K98MC-C adopts the motor of four 155kW, four auxiliary blowers of each motoring.This powerful motor is relatively costly equipment.The reason that causes their high prices is because low yield and the cooling problem that is associated with high capacity motor.Motor has structure compact and sealing, and is difficult to cooling because of himself characteristic.The above motor of certain size can't be satisfied by air cooling.Therefore, to be used to the motor of the supplementary equipment supplying energy of large-sized two-stroke diesel engine be oil cooling to majority.In addition, insurance company requires the above motor of 500kW to be subjected to evaluation, causes their market price significantly to rise like this.
The motor of this size is typically asynchronous motor.For controlling required extremely expensive based on silicon controlled frequency conversion AC changer of these electromotor velocities changeably, so these motors typically only are controlled under connection/dissengaged positions.Under the situation of auxiliary blower, this means that fan has to move at full speed, even main motor does not need the full output power of auxiliary blower.Therefore, even owing to motor under the situation that need drive auxiliary blower with the power of much less is still with the full power operation, so this is only at the waste energy.Up to now the method for avoiding this energy dissipation only is by investing above-mentioned very expensive electronic equipment.
The predetermined speed operation of the frequency of the AC current system that asynchronous motor only can be adopted to depend on (50 or 60Hz), and only these rotating speeds can be consistent with the optimum speed of auxiliary blower under rare occasion, thereby in fact auxiliary blower is usually with non-optimum speed operation.
Because higher relatively starting current, between the auxiliary blower in succession with 6 to 10 seconds interval starting.
The cable that is used to connect motor, generator or control apparatus is thick relatively cable, and the layout of these cables is subjected to the restriction of a large amount of main security-related standards, and therefore designs complexity and implementation cost costliness.
Most modern oceangoing boats and ships all have the single motor that drives the large-scale spiral oar.The large-scale oceangoing voyage boats and ships that cause handling owing to the master motor fault are a kind of very unfavorable and unsafe situations.Therefore, the large-sized two-stroke diesel engine that is used for Ship Propeling is configured to machine extremely reliably.Therefore recently yet complete trouble-free structure is non-existent, to redundant or have the requirement of the minimum power that takes home to increase day by day under the situation that master motor may break down.Thereby this purpose can provide suitable redundancy to realize by two less parallel engines of installation rather than a big-block engine in boats and ships.Yet from the viewpoint of fuel efficiency and running cost, two less motors of installation replace a bigger motor and have no attraction in boats and ships.And the propeller efficiency of single large-scale spiral oar is greater than two small propeller.
Summary of the invention
Under this background, the object of the present invention is to provide a kind of large-scale two-stroke marine diesel engine, wherein improved power supply to supplementary equipment.
According to claim 1, this purpose realizes that by a kind of large-scale turbosupercharging multi cylinder two-stroke crosshead diesel engine is provided it comprises: one or more auxiliary blowers, and it is used for discharging the exhaust of described cylinder when hanging down engine loading; One or more oil hydraulic pumps or pumping plant, it is used to hydraulic system and/or lubricated and/or fuel system supplied with pressurised fluid; And one or more motor, it drives described one or more auxiliary blower and described one or more oil hydraulic pump or pumping plant.
Another object of the present invention is to provides more effective power supply for the auxiliary blower of large-sized two-stroke diesel engine.
According to claim 7, this purpose realizes by a kind of large-sized turbo-charging multi cylinder two-stroke crosshead diesel engine is provided, it comprises: one or more auxiliary blowers, it is used for when low engine loading from described inblock cylinder exhaust, and turbocharger is discharged the exhaust of described cylinder when high engine loads; Oil hydraulic pump or pumping plant, it is by motor and/or by the motivational drive of obtaining from bent axle; And one or more oil hydraulic motors, it drives described one or more auxiliary blower.
Another object of the present invention provides the power supply of improvement for the hydraulic valve actuator of large-sized two-stroke diesel engine.
According to claim 16, this purpose realizes that by a kind of propulsion system that is used for large-scale seagoing vessel is provided it comprises: large-scale turbosupercharging multi cylinder two-stroke crosshead diesel engine; One or more generators, it comes supplying power so that electric power to be provided by the power and/or the one or more auxiliary diesel generator set that obtain from described large-scale turbosupercharging multi cylinder two-stroke diesel engine; One or more auxiliary blowers are used for discharging the exhaust of cylinder when hanging down engine loading, described auxiliary blower is by fluid motor-driven; One or more oil hydraulic pumps or high pressure pumping plant, its by the motor supplying power to carry high pressure fuel; Hydraulic valve actuator, it is used to activate described exhaust valve, wherein, one of described hydraulic valve actuator and described oil hydraulic motor or both high pressure fuel operations by carrying by described one or more high-pressure service pumps or high pressure pumping plant.
Another object of the present invention is to provide a kind of large-sized two-stroke marine propuision system with failure-to-safety characteristic of improvement.
According to claim 21, this purpose realizes that by a kind of propulsion system that is used for large-scale seagoing vessel is provided it comprises: large-scale two-stroke crosshead diesel engine, and it is connected to propeller cavitation via live axle; One or more generator set, it comprises motive force and generator, is used to be independent of the serviceability ground generating of described large-sized two-stroke diesel engine; High-pressure and hydraulic pumping plant or pump, it is by one or more motoring; And the hydraulic piston motor, it can be connected to described live axle or described propeller cavitation so that the power that takes home to be provided when described large-sized two-stroke diesel engine breaks down.
Another object of the present invention is to provide a kind of flexibility and propulsion system that is used for large-scale seagoing vessel efficient, that have fluid pressure supply system with improvement.
According to claim 29, this purpose realizes that by a kind of propulsion system that is used for large-scale seagoing vessel is provided it comprises: large-scale two-stroke crosshead diesel engine, and it is connected to propeller cavitation via live axle; One or more generator set, it comprises motive force and generator, is used to be independent of the serviceability ground generating of described large-scale two-stroke diesel engine; One or more high-pressure and hydraulic pumping plants or pump, it is driven by auxiliary diesel engine, is used for the high pressure hydraulic fluid of the high pressure hydraulic fluid consumer that is associated with the large-sized two-stroke motor with generation.
By using auxiliary diesel engine to drive high-pressure service pump or pumping plant, can directly produce hydraulic power and needn't be from motive force via generator and motor, still can be independent of simultaneously described large-sized two-stroke diesel engine serviceability hydraulic power is provided.
Another object of the present invention is to provide a kind of propulsion system that is used for large-scale seagoing vessel, it has the system that is used to drive the supplementary equipment that is associated with large-sized two-stroke diesel engine of improvement.
According to claim 33, this purpose realizes that by a kind of propulsion system that is used for large-scale seagoing vessel is provided it comprises: large-sized two-stroke single current crosshead diesel engine, and it is connected to propeller cavitation via live axle; High-pressure service pump or pumping plant, it supplies high pressure hydraulic fluid; A plurality of cylinders, the hydraulic valve actuator that each cylinder is provided with at least one exhaust valve and is used to activate described at least one exhaust valve; A plurality of supplementary equipment, it is associated with described large-sized two-stroke diesel engine, is driven by rotating power, at least one in wherein said a plurality of supplementary equipment or a plurality of by driving by the power-producing positive displacement motor of high pressure hydraulic fluid
By using oil hydraulic motor rather than motor, can raise the efficiency, because compare, can more accurately and control amount of power and the transporting velocity of using by oil hydraulic motor thereof neatly with motor.
By concrete description, will become obvious according to other purpose, feature, advantage and the characteristic of marine propuision system of the present invention and motor.
Description of drawings
In the following detailed part of this specification, the example embodiment shown in is more specifically explained the present invention with reference to the accompanying drawings, wherein:
Fig. 1 is the side view of large-scale traditional 8 cylinder two-stroke diesel engine, and shows 9 length to twelve-cylinder engine,
Fig. 2 is the front view of the motor among Fig. 1,
Fig. 3 is the view of the marine propuision system in the seagoing vessel, and two stroke engine wherein shown in Figure 1 is connected to propeller cavitation via jack shaft,
Fig. 4 a is the general illustration that connects between the parts of marine propuision system of first embodiment of the invention and parts,
Fig. 4 b is the general illustration that connects between the parts of marine propuision system second embodiment of the invention and parts,
Fig. 5 is the figure that illustrates as the hydraulic power consumption of engine loading function,
Fig. 6 is the cross-sectional view of oil hydraulic motor according to the embodiment of the present invention, and described oil hydraulic motor can be used as the urgent motor or the motor that takes home,
Fig. 7 is the general illustration that connects according between the parts of the marine propuision system of the 3rd mode of execution of the present invention and parts,
Fig. 8 is the figure that illustrates as the power consumption of the hydraulic pump motor of engine loading function and generator,
Fig. 9 is the general illustration that connects according between the parts of the marine propuision system of the 4th mode of execution of the present invention and parts,
Figure 10 is the general illustration that connects according between the parts of the marine propuision system of the 5th mode of execution of the present invention and parts,
Figure 11 is the general illustration that connects according between the parts of the marine propuision system of the 6th mode of execution of the present invention and parts.
Embodiment
In the concrete below description, will the propulsion system that is used for seagoing vessel that comprise the large-sized two-stroke crosshead diesel engine be described by preferred implementation.
Fig. 1 and Fig. 2 illustrate the diesel engine 10 in upright arrangement of the large-sized low-speed two-stroke crosshead with 98cm piston diameter, and it is the core of propulsion system.These typical of engines ground have the cylinder of 6 to 16 arrays.Described the side view of 8 Cylinder engines 10 among Fig. 1, the extra lines of profile of 9,10,11 and 12 cylinder patterns of this motor have been shown simultaneously in addition.Illustrating below motor 10 with rice is the scale of unit, to point out about 18 meters the absolute dimensions to 28 meters machine of 14 cylinder models of these length ranges from 8 cylinder models.
Motor makes up from base 11, and base 11 has the main bearing that is used for bent axle 1 (Fig. 2).Base 11 is divided into the section that is fit to size according to available manufacturing mechanism.
Reference is by the feature that is shown in dotted line among Fig. 2, and motor comprises the piston 28 that is connected to crosshead 24 via piston rod 29.Crosshead 24 is by guide plate 23 guiding.Connecting rod 30 is connected the crankpin of crosshead 24 with bent axle 1.
The A shape crankcase frame 12 of Welding Design is installed on the base 11.Cylinder frame 13 is installed on the top of crankcase frame 12.The stretching screw (not shown) is connected to cylinder frame 13 with base 11 and structure is kept together.Cylinder 14 is by cylinder frame 13 carryings.Exhaust valve assemblies 15 is installed on the top of each cylinder 14.Cylinder frame 13 also carries fuel injection system 19, exhaust manifold 16, turbocharger 17 and scavenging manifold 18.Turbocharger 17 is delivered to air pump in the scavenging manifold.Cooler (not shown) and auxiliary blower 18a are arranged between each turbocharger 17 and the scavenging manifold 18.In the operating process of motor, in case engine loading drops to 30%-40%, auxiliary blower 18a will start automatically and will operate constantly, surpasses about 40%-50% once more up to load.Come from the actuating of the SC sigmal control auxiliary blower of pressure switch (not shown).When engine loading surpassed the continuous maximum rated 30%-50% of motor, turbocharger 17 was transported to scavenging manifold 18 with enough air independently.Under the situation of low load, auxiliary blower 18a provides all or part of of required swept volume to scavenging manifold 18.
Between each cylinder, crankcase frame 12 is provided with and is the stiffening plate that connects transverse slat 21 forms, and this stiffening plate interconnects the outer wall 22 of the longitudinal extension of crankcase frame 12 and extends to the bottom from the top of A shape crankcase frame 12, to increase its lateral stiffness.
Be used to bear the vertical guide plate 23 that acts on the transverse force on the crosshead 24 (Fig. 2) and for example be installed to transverse slat 21 by the mode of welding.The rear side of each guide plate 23 supports by the additional walls 25 of connection guide plate 23 with the vertical extension of transverse slat 21.Guide plate 23, additional walls 25 and transverse slat wall 21 form the hollow profile of high torsional stiffness, wherein hold stretching screw 26.
Fig. 3 illustrates the afterbody of the boats and ships 1 with the typical cargo hold 2 that is provided with and cabin 3.Large-sized two-stroke motor 10 just is arranged on the rear of the wall of separating cabin 3 and cargo hold 2.Live axle 5 (being also referred to as jack shaft) connects the output shaft and the screw shaft 6 that drives propeller cavitation 7 of motor 4.Live axle 5 is comparable illustratedly will lack.
Propulsion system and large-sized two-stroke motor need a series of auxiliary system, for example
Electrical system
The hydraulic power supply system,
The heavy fuel oil system,
The lubricated cold oil system that reaches,
Cylinder lubricating system,
Cooling water system,
Central authorities' cooling water system,
Starting and control air system,
Scavenging system,
Vent systems, and
Control system.
These systems only explain and understand detailed degree required for the present invention.Especially, power consumption and/or transporting system will more specifically be described.All these systems all comprise electric controling part---valve and the motor for example controlled by one or more electronic controllers or computer (not shown).
Inferior to the power that is used to advance, generating is a fuel consumption maximum on the ship, next is the high-pressure hydraulic in the motor of electrical control.
In Fig. 4 a, first mode of execution according to marine propuision system of the present invention is shown by the overall pattern that connects between parts and parts.Propulsion system comprises the two stroke engine 10 of electrical control.Electric power is produced by two generator set 40.Generator set comprises the four-cycle diesel engine that is coupled to generator.Two generator set 40 shown in Figure 4, but can be a Generator Set or more than two less generator set.---for example when boats and ships berth---generator set 40 does not provide electric power yet when large-sized two-stroke motor 10 does not operate.When large-sized two-stroke motor 10 did not operate, generator set provided the heavy fuel oil of avoiding in the oil-fired system to solidify (heavy fuel oil be not fluid form below 40 ℃) required heat.
High pressure pumping plant 44 (represented by single variable delivery pump, still can comprise the pump more than) is transported to common rail 45 via pipeline 47 with high pressure fuel.Pumping plant 44 is driven by the motor 43 that receives electric power from generator set 40.Accumulator 48 (illustrate with single accumulator, but can be formed by several accumulators) is connected to pipeline 47 with leveling pressure.
In the mode of execution that illustrates, heavy fuel oil in the rail 45 not only is transported to and injects fuel into cylinder 14 (Fig. 1 altogether, 2) the sparger (not shown) in, but also be transported in exhaust valve assemblies 15 (Fig. 1,2) thus in the hydraulic actuator (not shown) be its supplying energy.The hydraulic actuator (not shown) is provided for the breaking force of exhaust valve (not shown equally), and comes operate actuator by utilizing heavy fuel oil to replace dedicated hydraulic liquid, can avoid independent hydraulic system.Yet be to be understood that, the mode of execution of all descriptions can easily be retrofit into and comprise independently high-pressure hydraulic---its for example be used for for exhaust valve actuator supplying energy---and high-pressure fuel system independently, and each system all has its oneself pump and electric motor.
The pipeline that comprises electronic control valve (not shown) separately is connected to common rail 45 with fuel injector and exhaust valve actuator.The fluid that returns from valve actuator causes fuel tank 42 via pipeline 46.
The clutch 59 that comprises cod is arranged between the output shaft of live axle 5 and large-sized two-stroke diesel engine 10.Clutch 59 engages when large-sized two-stroke diesel engine is operated, and clutch 59 separates when large-sized two-stroke diesel engine breaks down, thereby oil hydraulic motor 53 needn't rotate large-sized two-stroke diesel engine 10 when driving propeller cavitation 7.The size of the cod in the clutch 59 is set for and can bear in the instant operation process axial force that propelling force caused that produced by propeller cavitation 7 (these axial forces are far below the axial force that is produced, handled by the cod in the large-sized two-stroke diesel engine 10) in the normal operation process.
Because the hydraulic power unit of electric power operation can operate when the inoperation of large-sized two-stroke motor, according to the propulsion system of present embodiment not needs generally include in traditional propulsion system primer pump system with sap pressure supply power during engine start.
Example:
A kind of propulsion system that is used for the van container boats and ships.
The large-sized two-stroke motor is graceful grace diesel engine (MAN B﹠amp; W Diesel) 12K98ME-C, it has 12 cylinders, has the cylinder diameter of 98cm, short stroke (about 2.8) and be subjected to electronic control (being not camshaft control).This motor has the maximum-continuous rating (MCR) of 68.520kW in the time of 104 rev/mins.
Inferior to promotion energy, generating is a fuel consumption maximum on the ship.Required electric power depends on the concrete condition of boats and ships, for example relevant with the required electric power of cooled freight, and typically be positioned at 4% to 10% scope, traditional bulk carrier required electric power be positioned at this scope than downside and modern Container ship and refrigeration boats and ships required electric power are positioned at the upper side of this scope.Therefore in the present embodiment, be used to produce the amount of power of electric power between 2740kW and 6850kW.
The hydraulic power supply system needs to carry 1360kW when 110% load.In order to form a safety zone, the maximum of pumping plant 44 is output as 1500kW.
Fig. 4 b illustrates second embodiment of the invention, it is identical with first mode of execution except oil hydraulic motor 53 is the low cruise oil hydraulic motor (hereinafter more specifically describing with reference to Fig. 6) that has directly with the hollow output shaft 54 of main driving axle 5 cooperations, thereby can avoid gear-box and clutch.
The chart of Fig. 5 with continuous lines illustrate exhaust valve actuator hydraulic power consumption, the power consumption of the oil hydraulic motor 49 that drives auxiliary blower 18a is shown and altogether power consumption is shown with dashed line with dot and dash line.When 45% load, the power demand that is used for auxiliary blower reaches peak value 620kW.Under higher load, turbocharger 17 is taken over job and oil hydraulic motor stops, perhaps by discharge capacity being adjusted to zero or flow the stop solution pressure motor by cutting off the pressurization heavy fuel oil toward oil hydraulic motor 49.Be lower than under 45% the load, the discharge capacity of control oil hydraulic motor 49 makes oil hydraulic motor 49 that required amount of power is transported to auxiliary blower 18a exactly.
Under 45% load, valve actuator consumes 716kW, and altogether consumption reaches peak value 1336kW under 45% load, and reaches peak value 1336kW once more under 110% load.
Instant operation
When large-sized two-stroke diesel engine 10 broke down, control valve 51 (Fig. 4 a and 4b) changed to open position, and needed urgent power or " taking home " power to advance boats and ships.In fact, so the full output power of pump or pumping plant 44 is delivered to oil hydraulic motor 53.Clutch 56 engages and clutch 59 separates the engaged/disengaged of clutch (in according to the mode of execution of Fig. 4 b without any).
According to second mode of execution, as shown in Figure 6, oil hydraulic motor 53 is the low cruise Stirling engines that have a plurality of cylinders of star or fan-shaped setting.Yet should be appreciated that the oil hydraulic motor that can adopt other type.Hydraulic piston motor 53 comprises roller cage piston 71, and described roller cage piston 71 is formed integrally as roller cage part 72 and piston portion 73.Operation in the cylinder 75 of roller cage piston 71 in being arranged at cylinder block 76.Each roller cage piston 71 urges roller 77 against inner cam curve 78, thereby is formed on the moment of torsion on cylinder block 76 and the cam curve 78.In cylinder block 76, have the sliding device 79 that can rotate, be used for high pressure fuel 80 is assigned to cylinder.The motor of the type can provide high moment of torsion under low speed, the moment of torsion (2055kW) of 636000Nm for example is provided in the time of about 30 rev/mins.
The boats and ships that have the 12K98ME-C motor typically need about 30 rev/mins propeller speed that minimum speed of the ship in metres per second (4 to 5 miles/hour) and marine maneuvering capability in case of emergency is provided.The required moment of torsion of propeller cavitation that is equipped with the boats and ships of 12K98ME-C with 30 rev/mins of drivings is about 636000Nm (2055kW).
Required propeller speed depends on the type of boats and ships.For the Container ship that maximum cruise 104 rev/mins the time is about 25 to 26 miles/hour, under about 26 rev/mins propeller speed, will realize 4 to 5 miles/hour speed, and cruising speed is that 14 to 15 miles/hour bulk carrier or oil tanker will need about 34 rev/mins propeller speed to keep 4 to 5 miles/hour speed (yet, wave or can reduce ship's speed against the wind) in the time of 104 rev/mins.
According to not shown mode of execution, by utilize the fluid motor-driven turbocharger under low engine loading, the function of auxiliary blower can be replaced by turbocharger or a plurality of turbocharger.The extra power of being added to turbocharger by oil hydraulic motor makes that turbocharger also can produce enough scavengings when hanging down engine loading.Therefore, auxiliary blower can all omit.During high engine loads, according to a preferred implementation, by operating the oil hydraulic motor that is connected to turbocharger as oil hydraulic pump, energy superfluous in the turbocharger can change into the hydraulic pressure energy.So under the situation of large-sized two-stroke equipment high capacity, the excess energy of turbocharger can be recycled and be used in when high engine loads in the hydraulic system that needs the highest input.
In Fig. 7, the 3rd preferred implementation according to marine propuision system of the present invention is shown by the overall pattern that connects between parts and parts.This propulsion system comprises the two stroke engine 10 of electrical control.Produce electric power by generator set 40 and by generator 61, drive generator 61 by the power that obtains from bent axle via mechanical transmission 63.Cluster engine 40 comprises the be coupled to generator four-cycle diesel engine of---its power is lower than generator 61---.---for example when boats and ships berth---do not provide electric power when generator set 40 does not move at large-sized two-stroke motor 10, and under the situation of peak load, assist high-rating generator 61.When large-sized two-stroke motor 10 did not move, cluster engine also provided the heavy fuel oil of avoiding in the oil-fired system to solidify required heat (heavy fuel oil is not flowing below 40 ℃).
High pressure pumping plant 65 (be depicted as single variable delivery pump, but can comprise more than a pump) is transported to common rail 45 via pipeline 47 with high pressure fuel.Pumping plant 65 is by electric drive motor 64 drivings that receive from the electric power of generator set 40.Accumulator 48 (be depicted as single accumulator, but can be formed by several accumulators) is connected to pipeline 47 in order to leveling pressure.
The required amount of power of auxiliary blower 18a changes, and just being lower than large-sized two-stroke diesel engine 10 middle load level places is the highest, and is zero when the load level of the continuous maximum rated 40%-45% that is higher than large-sized two-stroke diesel engine 10.Auxiliary blower 18a (only illustrating one for easy) also drives by electric drive motor 64.Electric drive motor 64 is connected to auxiliary blower 18a via clutch 67 or other separable connection set, is used for when substituting the supply scavenging by turbocharger 17 auxiliary blower 18a being disconnected from electric drive motor 64 under the situation that is higher than about 40%-50% engine loading.Electric drive motor 64 is connected to pumping plant 65 via clutch 66 or other separable connection set, can disconnect oil hydraulic pump 65 when auxiliary blower 18a is driven by motor 64.
The chart of Fig. 8 with continuous lines illustrate oil hydraulic pump hydraulic power consumption, the power consumption of auxiliary blower 18a is shown and altogether power consumption (numeral is corresponding to graceful grace 12K98ME-C diesel engine) is shown with dashed line with dot and dash line.When 45% load, the power demand that is used for auxiliary blower reaches peak value 620kW.When higher load, turbocharger 17 is taken over and by cut-off clutch 67 auxiliary blower 18a is disconnected from electric drive motor 64.
In the 3rd mode of execution, heavy fuel oil in the rail 45 not only is transported to and injects fuel into cylinder 14 (Fig. 1 altogether, 2) the sparger (not shown) in but also be transported to hydraulic actuator (not shown) in exhaust valve assemblies 15 (Fig. 1,2) is used to their supplying energies.The hydraulic actuator (not shown) provides the breaking force of exhaust valve (not shown equally), and comes operate actuator and can avoid hydraulic system greatly by utilizing heavy fuel oil to replace dedicated hydraulic liquid.Yet should be appreciated that this mode of execution can easily be retrofit into comprises and for example independently is used for being the high-pressure hydraulic of exhaust valve actuator supplying energy and high-pressure fuel system independently, and each all has its oneself pump and electric drive motor.
The pipeline that comprises electronic control valve (not shown) separately is connected to common rail 45 with fuel injector and exhaust valve actuator.The fluid that returns from valve actuator causes fuel tank 42 via pipeline 46.
Because provide the hydraulic power unit of energy to operate when 10 inoperation of large-sized two-stroke motor by electric power, thus according to the propulsion system of the 3rd mode of execution not needs generally include in traditional propulsion system primer pump system in order to sap pressure supply power during engine start.
In Fig. 9, the 4th preferred implementation according to marine propuision system of the present invention is shown by the overall pattern that connects between parts and parts.This propulsion system comprises the two stroke engine 10 of electrical control.Produce electric power by generator set 40 and generator 61, drive generator 61 by the power that obtains from bent axle by mechanical transmission 63.---for example when boats and ships berth---do not supply electric power and can under peak load, assist high-rating generator 61 when cluster engine 40 does not move at large-sized two-stroke motor 10.
High pressure pumping plant 44 (it is depicted as single variable delivery pump, but can comprise the pump more than) is transported to common rail 45 via pipeline 47 with high pressure fuel.Drive pumping plant 44 by the power that obtains from bent axle by mechanical transmission 41.Mechanical transmission 41 can comprise gear and/or chain.Accumulator 48 (be depicted as single accumulator, but can be formed by several accumulators) is connected to pipeline 47 with leveling pressure.
The hydraulic power that variable delivery pump 69 is carried and is used for oil hydraulic motor 49---it drives auxiliary blower 18a---.Variable delivery pump 69 is driven by electric drive motor 68.Pipeline 50 is fed to high pressure fuel in the change displacement volume formula motor 49 that drives auxiliary blower 18a.The required amount of power of auxiliary blower 18a changes, and is the highest at the low load level place of large-sized two-stroke diesel engine 10, and is zero when the load level of the continuous maximum rated 40%-50% that is higher than large-sized two-stroke diesel engine 10.The demand of the volume of variable delivery pump 71 and oil hydraulic motor 49 is complementary.
The pipeline 70 that has control valve 74 is connected to fuel common rail 45 with variable delivery pump, to be used under the situation of hydraulic power unit 45 faults urgent hydraulic power being fed to fuel common rail 45 and oil hydraulic motor 49.Typically, the volume of variable delivery pump 69 is corresponding to be fed to aggregate demand common rail 45 and oil hydraulic motor 49, that be used for the hydraulic power of valve actuator and sparger under 15% engine loading.If main pumping station 44 faults, then control valve 74 is opened and variable delivery pump 69 is transported to common rail 45 and oil hydraulic motor 49 with high pressure fuel.
In the 4th mode of execution, the heavy fuel oil in the rail not only is transported to the sparger that injects fuel in the cylinder 14 (Fig. 1,2) altogether, but also is transported to the hydraulic actuator (not shown) in the exhaust valve assemblies 15 (Fig. 1,2), to give their supplying energies.The hydraulic actuator (not shown) provides the breaking force of exhaust valve (not shown equally), and comes operate actuator by utilizing heavy fuel oil to replace dedicated hydraulic liquid, makes it possible to avoid hydraulic system greatly.Yet be to be understood that, the mode of execution of all descriptions can easily be retrofit into and comprise independently high-pressure hydraulic---its for example be used for for exhaust valve actuator supplying energy---and high-pressure fuel system independently, and each all has its oneself pump and electric drive motor.
The pipeline that comprises electronic control valve (not shown) separately is connected to common rail 45 with fuel injector and exhaust valve actuator.The fluid that returns from valve actuator causes fuel tank 42 via pipeline 46.
Because provide the valve 74 of the oil hydraulic pump 69 of energy to be similar to during instant operation ground is shown in an open position during engine start by electric power, thus according to the propulsion system of the 4th mode of execution not needs generally include in traditional propulsion system primer pump system with sap pressure supply power during engine start.
Figure 10 illustrates the 5th mode of execution of the present invention.This large-sized two-stroke diesel engine 10 attaches one or more generator set 40 (only illustrating) to be arranged and attach one or more pump groups 106 (only illustrating).Pump group 106 comprises the large-scale variable delivery pump 107 of the driving that directly---is preferably 4 stroke diesel engines---by the auxiliary diesel engine 108 much smaller than large-sized two-stroke diesel engine 10.The major part that is used for the high-pressure liquid of hydraulic system is formed by pump group 106.The small part that is used for the high-pressure liquid of hydraulic system is formed by the high pressure variable delivery pump 44 that drives by motor 43.(not shown) alternately, pump 44 can be by the motivational drive of obtaining from bent axle.There are two high-pressure service pumps or pumping plant provide redundancy, guarantee to have enough hydraulic powers---for example the 50%-60% of maximum load---operation large-sized two-stroke diesel engine with under the motivation level that takes home for hydraulic system with different driving unit.In the present embodiment, in normal power operation process, hydraulic system drives hydraulic exhaust valve actuator and auxiliary blower.Therefore, the hydraulic power of installation is mounted in the twice at least (that is, be about maximum master motor output 3.6% to 5%) of typical hydraulic power in traditional propulsion system (be about maximum master motor output 1.8% to 2.3%).Oil hydraulic pump 44 and 107 can both be independent of the running state ground of large-sized two-stroke diesel engine to be operated.
The structure of the 5th mode of execution allows the hydraulic power of large-scale installation can finally be used to the oil hydraulic motor supplying power of the advancing means that takes home.Thereby if the large-sized two-stroke motor breaks down unexpectedly, then hydraulic power can produce by pump group 108 and electric driven pump 44.In this case, electrical control valve 51 is opened, and hydraulic power supply is to two low cruise oil hydraulic motors 53 that are preferably the type of describing with reference to Fig. 6.Oil hydraulic motor 53 disposes the live axle 54 of band through hole, and this live axle 54 preferably cooperates and is connected to live axle 5.Oil hydraulic motor 53 can drive live axle with about 25% to 33% of the maximum service speed of large-sized two-stroke motor, and maximum power be output as large-sized two-stroke diesel engine maximum output about 2% to 5%.The boats and ships maintenance that this sufficient to guarantee wherein is equipped with propulsion system is steerable.
Therefore, oil hydraulic motor 53 will always rotate with live axle, that is, also rotate together when 10 operations of large-sized two-stroke motor.In order to reduce the resistance/frictional loss in the oil hydraulic motor 53 during just along with live axle 5 passive rotation at oil hydraulic motor 53,, it is not contacted with cam curve 78 by hydraulic operation lifting roller cage piston 71.
If oil hydraulic motor 53 is to bear type of moving under large-sized two-stroke motor top speed or the type that can't reverse, then clutch or separable connection set (not shown) are arranged between the output shaft 54 of hollow (many large-sized two-stroke diesel engines can reverse, and this is at having the demand of fixed knot apart from the propulsion system of propeller cavitation).
Figure 11 illustrates the 6th mode of execution of the present invention.This large-sized two-stroke diesel engine 10 attaches two generator set 40.Motor 43 drives the large hydraulic high-pressure service pump 44 of variable displacement type.High-pressure liquid from high-pressure service pump 44 supplies in the common rail 45.Except auxiliary blower motor 49 and exhaust valve actuator, hydraulic system also via pipeline 52 for driving two oil hydraulic motor 81 supplying power of centrifugal sea water pump 82 (for the purpose of redundancy is provided with two pumps).Sea water pump 82 is from seawater inlet 83 suction seawater, via central cooler 84 and turn back to seawer outlet 85.Central cooler 84 is shell-type, tubular type or plate type heat exchanger of being made by the sea water resistance material.
Via pipeline 52, hydraulic system is also for driving two oil hydraulic motor 86 supplying power of central centrifugal cooling waterpump 87.Central authorities' cooling waterpump 87 pumping fresh water return then through a plurality of parts (not shown) of central cooler 84, process lube oil cooler 88, process jacket water cooler 89, process large-sized two-stroke motor 10.
In addition, hydraulic system also via pipeline 52 for driving two oil hydraulic motor 90 supplying power of lubricating pump 91 (for the purpose of redundancy is provided with two pumps).A plurality of part and assemblies of lubricating pump 91 pumping lubricant oil process oil cooler 88, process large-sized two-stroke motor 10 also return.
Drive two centrifugal jacket water pumps 93 via pipeline 52 power-producing two oil hydraulic motors 92.Jacket water pump 93 pumps water are through jacket water cooler 89, via cylinder liner, cylinder head and exhaust valve and return.Jacket-cooling water also is used for the insulation of fuel emission pipe.
One or more oil hydraulic motors 95 (only illustrating one) are one or more ballast pumps 94 (only illustrating) supplying power via pipeline 52.Ballast pump 94 is from around each ballast box (not shown) withdrawn fluid of boats and ships setting and be pumped into each ballast box, so that the boats and ships level.
One or more oil hydraulic motors 97 (only illustrating one) are one or more via pipeline 52 as are used for for example loading and unloading pump 96 of oil tanker (only illustrating) supplying power.
One or more oil hydraulic motors 98 (only illustrating one) are one or more compressors 99 (only illustrating) supplying power via pipeline 52, thereby produce the pressurized air that is used for for example controlling and starting air system.
One or more oil hydraulic motors 100 (only illustrating one) are that one or more windlass 101 (only illustrating) supplying power is to weigh anchor and to cast anchor via pipeline 52.Windlass can be used for loosening or drawing in other chain or the cable that is arranged in boats and ships diverse location all around, perhaps can be the rope rail of hoist.
The oil hydraulic motor of supplying with high-pressure liquid in the direct hydraulic system from large-sized two-stroke diesel engine of the diverse location use of boats and ships has the effect that can avoid many high power cables, connection set, switch and motor at boats and ships, simultaneously owing in hydraulic system, there not being the spark production part, so also have the advantage that improves fire-proof function---especially true on the boats and ships of delivery flammable cargo.
Hydraulic pressure in the conventional push motion device of the large-sized two-stroke diesel engine that has electrical control typically be about large-sized two-stroke diesel engine peak output 1.5%.By using oil hydraulic motor to replace motor in the above-described embodiment in a large number, hydraulic pressure can the peak output of large-sized two-stroke diesel engine about 3% to about 6% scope.
Any pressure that is higher than 8 crust contained in the term " high pressure " that uses in above-mentioned " high-pressure service pump " and " high pressure hydraulic fluid ".
Although described the present invention for illustrative purposes in detail, should be appreciated that these specific descriptions only are used for illustrative purposes, and those of skill in the art can make multiple remodeling and not deviate from category of the present invention.
Claims (36)
1. one kind large-scale turbosupercharging multi cylinder two-stroke crosshead diesel engine comprises: one or more auxiliary blowers, and it is used for discharging the exhaust of described cylinder when low engine loading; One or more oil hydraulic pumps or pumping plant, it is used to hydraulic system and/or lubricated and/or fuel system supplied with pressurised fluid; And one or more motor, it drives described one or more auxiliary blower and described one or more oil hydraulic pump or pumping plant.
2. motor according to claim 1, wherein, each described auxiliary blower is connected to corresponding motor via clutch.
3. motor according to claim 2 also comprises being configured in order to engage and to separate the controller of described clutch.
4. motor according to claim 3, wherein, described controller is configured to engage described clutch when being lower than first threshold when described engine loading drops to, and separates described clutch when being higher than second threshold value when described engine loading rises to.
5. want each described motor in 1 to 4 according to right, wherein, described one or more oil hydraulic pump or pumping plant belong to the type that becomes discharge capacity, the discharge capacity of described oil hydraulic pump or pumping plant is controlled by described controller, and described controller is configured to control described pump delivery and is no more than predetermined threshold value to guarantee the required moment of torsion of described one or more motor.
6. want each described motor in 1 to 5 according to right, wherein, described one or more motor drives described one or more oil hydraulic pumps or pumping plant under all engine operation state, thereby allows described motor not need engine start pumping plant ground to start.
7. one kind large-scale turbosupercharging multi cylinder two-stroke crosshead diesel engine, comprise: one or more auxiliary blowers, it is used for when low engine loading from described inblock cylinder exhaust, and one or more turbochargers are discharged the exhaust of described cylinder when high engine loads; Oil hydraulic pump or pumping plant, it is by motor and/or by the power that obtains from bent axle and/or by diesel engine drives independently; And one or more oil hydraulic motors, it drives described one or more auxiliary blower.
8. large-scale turbosupercharging multi cylinder two-stroke diesel engine according to claim 7, wherein, discharging the exhaust of described cylinder when the low engine loading, and described one or more turbochargers do not need described oil hydraulic motor to assist ground to discharge the exhaust of described cylinder to described one or more turbochargers when higher engine loading by described fluid motor-driven when low engine loading.
9. large-scale turbosupercharging multi cylinder two-stroke diesel engine according to claim 7, comprise: main pumping station, it is used for hydraulic power is fed to exhaust valve actuator, and described main pumping station drives by the power that obtains from bent axle or by one or more electric drive motors; And second pumping plant, it is by one or more motoring, described second pumping plant is fed to hydraulic power the described oil hydraulic motor that drives described one or more auxiliary blowers and/or fuel injector, and when one of described main pumping station or described second pumping plant broke down, another pumping plant hydraulic power of will meeting an urgent need was fed to oil hydraulic motor and the described exhaust valve actuator that drives described one or more auxiliary blowers.
10. large-scale turbosupercharging multi cylinder two-stroke diesel engine according to claim 7 also comprises: generator set, and it has the motive force that is used to produce electric power of self; Hydraulic power station, it is driven by one or more electric drive motors, and can both sap pressure supply power when described large-sized two-stroke diesel engine inoperation and operation.
11. large-scale turbosupercharging multi cylinder two-stroke diesel engine according to claim 7, also comprise emergency hydraulic system, described emergency hydraulic system is formed by the pump that drives described auxiliary blower motor and comprises that the pump with the described auxiliary blower motor of described driving is connected to the pipeline of the other parts of described hydraulic system.
12. large-scale turbosupercharging multi cylinder two-stroke diesel engine according to claim 7 also comprises: live axle, it is connected to propeller cavitation with described large-scale turbosupercharging multi cylinder two-stroke diesel engine; One or more auxiliary diesel generator set are used to supply electric power; At least one described pumping plant is used to carry compression fluid by motoring; At least one oil hydraulic motor, it is configured to when described large-scale turbosupercharging multi cylinder two-stroke diesel engine breaks down to drive jack shaft or described screw shaft, with the supply power that takes home.
13. large-scale turbosupercharging multi cylinder two-stroke diesel engine according to claim 7, wherein, described is the low cruise oil hydraulic motor for the described oil hydraulic motor that takes home power and drive described bent axle is provided.
14. large-scale turbosupercharging multi cylinder two-stroke diesel engine according to claim 7, wherein, described low cruise oil hydraulic motor directly is coupled to described live axle or screw shaft, perhaps shows 1 to 1 gear ratio engagement greatly with described live axle or described screw shaft.
15. according to claim 13 or 14 described large-scale turbosupercharging multi cylinder two-stroke diesel engines, wherein the clutch connection set that maybe can separate is arranged between described bent axle and the described live axle.
16. a propulsion system that is used for large-scale seagoing vessel comprises:
Large-scale turbosupercharging multi cylinder two-stroke crosshead diesel engine;
One or more generators, it comes supplying power so that electric power to be provided by the power and/or the one or more auxiliary diesel generator set that obtain from described large-scale turbosupercharging multi cylinder two-stroke diesel engine;
One or more auxiliary blowers are used for discharging the exhaust of cylinder when hanging down engine loading, described auxiliary blower is by fluid motor-driven;
One or more high-pressure service pumps or high pressure pumping plant, its by the motor supplying power to carry high pressure fuel;
Hydraulic valve actuator, it is used to activate described exhaust valve,
Wherein, one of described hydraulic valve actuator and described oil hydraulic motor or both high pressure fuel operations by carrying by described one or more high-pressure service pumps or high pressure pumping plant.
17. propulsion system according to claim 16, wherein, described high-pressure service pump or the high pressure pumping plant that is supplied with electric power has enough big power, in order to satisfy described hydraulic valve actuator all under various load-up conditions and/or all oil hydraulic motor demand to high-pressure liquid.
18. propulsion system according to claim 16, wherein, directly or indirectly from the described power of obtaining of described bent axle and/or described turbocharger.
19. propulsion system according to claim 16, wherein said generator comprises:
Live axle, it is arranged between the propeller cavitation of the bent axle of described large-sized two-stroke motor and described seagoing vessel;
Oil hydraulic motor, it is connected to and maybe can be connected to described live axle to drive described live axle;
Thus, be used to drive described live axle described oil hydraulic motor power and be supplied power with the described high-pressure service pump of electric power or high pressure pumping plant even as big as the power that takes home as boats and ships under the situation about breaking down at described large-sized two-stroke motor.
20. propulsion system according to claim 16, wherein, when described large-sized two-stroke diesel engine inoperation and operation, described high pressure pumping plant can both sap pressure supply power.
21. be used for the propulsion system of large-scale seagoing vessel, comprise: large-scale two-stroke crosshead diesel engine, it is connected to propeller cavitation via live axle; One or more generator set, it comprises motive force and generator, is used to be independent of the serviceability ground generating of described large-sized two-stroke diesel engine; High-pressure and hydraulic pumping plant or pump, it is by one or more motoring; And the hydraulic piston motor, it can be connected to described live axle or described propeller cavitation so that the power that takes home to be provided when described large-sized two-stroke diesel engine breaks down.
22. propulsion system according to claim 21, wherein, described oil hydraulic motor is a low cruise discharge capacity mechanical system.
23. propulsion system according to claim 22, wherein, described low cruise hydraulic piston motor has the hollow actuating shaft that is coupled to described live axle or described screw shaft, and or directly be connected to described live axle or screw shaft or be connected to described screw shaft via clutch, described clutch makes described oil hydraulic motor can optionally join described live axle or screw shaft to and separates with described live axle or screw shaft.
24. propulsion system according to claim 23, wherein, described oil hydraulic motor is included in the roller cage piston that moves on the cam with projection, and described roller cage piston is lifted when described oil hydraulic motor inoperation.
25. the application of low cruise oil hydraulic motor, when the master motor of large-scale seagoing vessel broke down, application can be connected to the live axle of described large-scale seagoing vessel or the described low cruise oil hydraulic motor of propeller cavitation is supplied the power that takes home.
26. application according to claim 25, wherein, described live axle can separate with master motor.
27. application according to claim 25, wherein, described low cruise oil hydraulic motor is to have a plurality of displacement machine systems that are the cylinder of star or fan-shaped layout.
28. application according to claim 27, wherein, described hydraulic piston motor comprises: housing; At least one has the cam disk of cam ring curve; At least one cylinder block, the piston that it has a plurality of cylinders and moves in these cylinders; The roller cage that has hydrostatic bearing; Roller, it moves between described cam curve and described roller cage, and described retainer holds described roller with certain around the angle; And the guiding elements that is used for described roller.
29. a propulsion system that is used for large-scale seagoing vessel comprises: large-scale two-stroke crosshead diesel engine, it is connected to propeller cavitation via live axle; One or more generator set, it comprises motive force and generator, is used to be independent of the serviceability ground generating of described large-scale two-stroke diesel engine; One or more high-pressure and hydraulic pumping plants or pump, it is driven by auxiliary diesel engine, is used for the high pressure hydraulic fluid of the high pressure hydraulic fluid consumer that is associated with the large-sized two-stroke motor with generation.
30. propulsion system according to claim 29, wherein, described propulsion system also comprises by motor or the power-actuated high-pressure hydraulic pump or the pumping plant that obtain from bent axle.
31. propulsion system according to claim 29, wherein, described consumer comprises one or more groups that comprise oil hydraulic motor, fuel injector and hydraulic actuator.
32. according to claim 29 or 31 described propulsion systems, wherein, the one or more groups that comprise coolant pump, loading and unloading pump, windlass, lubricating pump and auxiliary blower of described fluid motor-driven.
33. a propulsion system that is used for large-scale seagoing vessel comprises:
Large-sized two-stroke single current crosshead diesel engine, it is connected to propeller cavitation via live axle;
High-pressure service pump or pumping plant, it supplies high pressure hydraulic fluid;
The hydraulic valve actuator (9) that a plurality of cylinders, each cylinder are provided with at least one exhaust valve and are used to activate described at least one exhaust valve (4);
A plurality of supplementary equipment, it is associated with described large-sized two-stroke diesel engine, is driven by rotating power,
It is characterized in that at least one in described a plurality of supplementary equipment or a plurality of by driving by the power-producing positive displacement motor of high pressure hydraulic fluid.
34. propulsion system according to claim 33, wherein, described supplementary equipment comprises one or more groups that comprise cooling waterpump, lubricating pump, auxiliary blower, take home motor and compressor.
35. according to claim 33 or 34 described propulsion systems, wherein, described boats and ships comprise a plurality of rotating power driving arrangements that are not associated with described large-sized two-stroke diesel engine, and described unconnected equipment is driven by the positive displacement motor that drives by the high pressure hydraulic fluid that comes from the output of described high-pressure service pump or pumping plant.
36. propulsion system according to claim 33, wherein, the described equipment on board that is not associated with described large-sized two-stroke motor comprises one or more groups that comprise ballast pump, loading and unloading pump, windlass and rope rail.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110185638.3A CN102320368B (en) | 2005-10-05 | 2005-10-05 | Marine propuision system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/EP2005/010690 WO2007038962A1 (en) | 2005-10-05 | 2005-10-05 | Marine propulsion systems |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110185638.3A Division CN102320368B (en) | 2005-10-05 | 2005-10-05 | Marine propuision system |
| CN2009102247775A Division CN101713328B (en) | 2005-10-05 | 2005-10-05 | Vessel propulsion system |
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| CN101283171A true CN101283171A (en) | 2008-10-08 |
| CN101283171B CN101283171B (en) | 2010-08-11 |
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| CN200580051784XA Active CN101283171B (en) | 2005-10-05 | 2005-10-05 | Propulsion system of ship |
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| Country | Link |
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| JP (1) | JP4723645B2 (en) |
| KR (1) | KR100978034B1 (en) |
| CN (1) | CN101283171B (en) |
| WO (1) | WO2007038962A1 (en) |
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| CN105599888A (en) * | 2014-11-14 | 2016-05-25 | 株式会社神户制钢所 | Ship propulsion system, and operation method of the same |
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| WO2016148318A1 (en) * | 2015-03-16 | 2016-09-22 | Daewoo Shipbuilding & Marine Engineering Co., Ltd. | System for supplying fuel to engine of ship |
| DK179645B1 (en) * | 2017-06-15 | 2019-03-08 | MAN Energy Solutions | Internal combustion engine |
| CN111038663A (en) * | 2019-12-18 | 2020-04-21 | 北京海兰信数据科技股份有限公司 | Standby hydraulic pressure providing device and method for ship steering engine |
| WO2021178044A2 (en) * | 2020-01-09 | 2021-09-10 | Thayermahan, Inc. | Multi-hull unmanned water vehicle |
| KR102632422B1 (en) * | 2022-02-10 | 2024-02-02 | 주식회사 제이엠피네트웍스 | Offset drive unit for marine hybrid propulsion |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2324670A1 (en) * | 1973-05-16 | 1974-12-05 | Joost Basen Hasselo Smits | ENERGY CONSUMER FOR DRIVE SYSTEMS, IN PARTICULAR FOR SHIPS |
| NO800935L (en) | 1980-03-31 | 1981-10-01 | Moss Rosenberg Verft As | LNG SHIP PROGRAMMING MACHINE. |
| CH667495A5 (en) | 1985-04-25 | 1988-10-14 | Bbc Brown Boveri & Cie | Booted MARINE DIESEL ENGINE. |
| DK172984B1 (en) * | 1986-08-21 | 1999-11-01 | Sulzer Ag | Power plants for ships with electricity generator supplying the ship's grid |
| DE3711863A1 (en) * | 1987-04-08 | 1988-10-27 | Man B & W Diesel Gmbh | Multiple-engine installation for ships |
| JPH0479937A (en) * | 1990-07-20 | 1992-03-13 | Toshiba Corp | Magnetic resonance imaging device |
| JP2794522B2 (en) * | 1993-09-24 | 1998-09-10 | 株式会社クボタ | Two-stroke engine air supply system |
| DE4432483A1 (en) * | 1994-09-13 | 1996-03-14 | Blohm Voss Ag | Auxiliary drive for marine ship with diesel main engine driving propeller via shaft system |
| CN1308577C (en) * | 2001-06-22 | 2007-04-04 | 曼B与W狄赛尔公司 | Turbocharge arrangement for diesel engine |
| JP4306483B2 (en) * | 2004-02-10 | 2009-08-05 | トヨタ自動車株式会社 | Control device for internal combustion engine having supercharger with electric motor |
-
2005
- 2005-10-05 WO PCT/EP2005/010690 patent/WO2007038962A1/en active Application Filing
- 2005-10-05 JP JP2008528350A patent/JP4723645B2/en active Active
- 2005-10-05 KR KR1020087008124A patent/KR100978034B1/en active IP Right Grant
- 2005-10-05 CN CN200580051784XA patent/CN101283171B/en active Active
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105228895A (en) * | 2013-05-17 | 2016-01-06 | 珀金斯发动机有限公司 | Propulsion system |
| US10113617B2 (en) | 2013-05-17 | 2018-10-30 | Perkins Engines Company Limited | Propulsion system |
| CN105599888A (en) * | 2014-11-14 | 2016-05-25 | 株式会社神户制钢所 | Ship propulsion system, and operation method of the same |
| CN105564623A (en) * | 2016-01-21 | 2016-05-11 | 北京工业大学 | Bidirectional clutch spindle system for ships and warships |
| CN105564623B (en) * | 2016-01-21 | 2017-11-07 | 北京工业大学 | Naval vessel bidirectional clutch axis system |
| CN112977848A (en) * | 2021-03-30 | 2021-06-18 | 上海尚实能源科技有限公司 | Power system of hybrid turboprop engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101283171B (en) | 2010-08-11 |
| KR20080042928A (en) | 2008-05-15 |
| JP2009507161A (en) | 2009-02-19 |
| WO2007038962A1 (en) | 2007-04-12 |
| KR100978034B1 (en) | 2010-08-25 |
| JP4723645B2 (en) | 2011-07-13 |
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