CN102251895B - Crosshead-shaped large uniflow-type dual-stroke diesel engine - Google Patents
Crosshead-shaped large uniflow-type dual-stroke diesel engine Download PDFInfo
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- CN102251895B CN102251895B CN201110207797.9A CN201110207797A CN102251895B CN 102251895 B CN102251895 B CN 102251895B CN 201110207797 A CN201110207797 A CN 201110207797A CN 102251895 B CN102251895 B CN 102251895B
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Abstract
The invention relates to a crosshead-shaped large uniflow-type dual-stroke diesel engine which is provided with a plurality of air cylinders, and each of the cylinder is provided with at least one exhaust valve and one or more fuel injectors; the fuel injection is performed under the influence of a high-pressure fluid source; potential energy is accumulated by compression in a container of the high-pressure fluid; electro-hydraulic valves control the fuel injection which is primarily driven by energy accumulated in a high pressure container; the engine is provided with a camshaft for actuation of the exhaust valves; hydraulic piston pumps are driven by the cams on the camshaft; and hydraulic actuators move the exhaust valves in the opening direction with hydraulic fluid received via conduits from the hydraulic piston pumps.
Description
The application is that international filing date is the dividing an application of No. 200680054192.8, the Chinese invention patent application that is entitled as " large-sized uniflow type two-stroke diesel motor of crosshead " on April 12nd, 2006.
Technical field
The present invention relates to a kind of large-sized low-speed uniflow type two-stroke diesel motor of crosshead, and be particularly related to the engine components relevant with exhaust valve actuation with the fuel injection.
Background technique
The large two-stroke diesel engine of crosshead is generally used for that the naval vessel advances and as the prime mover in the power plant.Not only because its enormous size, and the structure of these burning type engines is also different from other burning type engine.Viscosity constitutes a class by itself this motor up to the use (at room temperature this fuel oil does not flow) of the reduced fuel oil of 700cSt when two-stroke principle and 50 ℃ in the motor world.
In a lot of such conventional engines, exhaust valve and fuel injection system are driven by the rotating cam that is attached directly to engine crankshaft.Two-stroke engine is controlled air with scavenging port and is entered cylinder, and therefore, air inlet timing and crank angle are closely related.
Requirement for fuel consumption, reliability and the power stage of this type of engine is all high.Recently, environmental requirement causes reducing the demand of toxic emission.In order to satisfy these sometimes mutual conflicting requirements, compare with fuel injector with the exhaust valve that the rotating cam of routine drives, it is believed that to be necessary fuel injection timing and emitted dose are controlled flexibly, and opening and closing timing and the aperture of exhaust valve are carried out comprehensively and flexibly control.
A kind of large-sized uniflow type two-stroke diesel motor of known crosshead is the MC-C power team form of Man Enbiwei diesel engine company.This motor is provided with the camshaft that extends along the length of motor in camshaft case.Camshaft is provided with the cam that sprays for fuel and the cam that is used for exhaust valve actuation.
On camshaft, each cylinder there is a fuel cam.Each fuel cam acts on has (each cylinder is furnished with a reciprocating pump) on the variable-displacement piston type fuel pump, is used for being adjusted in the fuel quantity that each cycle of engine sprays.The piston delivery side of pump is connected to the entrance of the sparger that is associated with associated cylinder by pressure duct.Jet law (for example the emitted dose of the one-period time of cycle of engine fuel injection or curve and the timing of jet pressure) only has by cam profile and ejector characteristics and just might control, but the two all can not easily change after the motor manufacturing is finished.
On camshaft, each cylinder there is an exhaust cam.On exhaust cam acts on so-called " hydraulic push rod ".The open timing of the open nature of exhaust valve such as exhaust valve, the aperture of closing timing and exhaust valve of exhaust valve etc. all has been fixed in the motor manufacture process, and can not easily change after manufacturing is finished.
The emission request that the large two-stroke diesel engine of working in ocean going vessel uses is determined by the international organization that is named as IMO.And local government also can stipulate local requirement.It is more and more stricter that these emission requests just progressively become, and these variations are not always carried out in complete predictable mode.The permissible discharge level can be depending on and the port between distance.Therefore compare when near the shore line, working, when the off-lying sea, require motor under higher emission level, to work.
In order to satisfy at present and emission level in the future, the electric-controlled type motor is grown up during the eighties in 20th century and the nineties.
The ME power team of Man Enbiwei diesel engine company is the large two-stroke diesel engine with electricity-hydraulic control exhaust valve processed and electricity-crosshead that liquid actuating fuel sprays.Hydraulic system uses the oil from engine lubrication system to carry out work.The low pressure pump of lubricating oil system use 3 to 4bar carries out work.Another kind of high pressure type pump is delivered to shared rail with lubricant oil pump under the pressure of 200bar.Be introduced to the fuel pressurization device from the lubricant oil that shares rail by hydrovalve, pressurized machine will share in the rail pressure of 200bar and be increased in the fuel conduit desired 800 to 1000bar.Fuel conduit is heated to guarantee that fuel oil can flow and have suitable viscosity.Be introduced to the exhaust valve actuator of hydraulic pressure by time-delay valve from the lubricant oil that shares rail, with operations platoon's valve.
Fuel system uses the hydraulic fluid identical with lubricant oil in motor from hydraulic power system to drive the pressurized machine that sparger is provided fuel under high pressure (reduced fuel oil).Each cylinder is provided with a pressurized machine.The high pressure side of pressurized machine is forced into desired 800 to 1000bar level with fuel.The electric-controlled hydraulic proportional control valve is allowed for jet law and the injection timing that fuel metering sprays.Therefore, finish long after in the motor manufacturing and also can change at an easy rate jet law and injection timing, and even can for example load in response to working state or the change of motion speed and directly changing at the motor run duration.
The cylinder type actuator is installed on each exhaust valve and the high-pressure and hydraulic medium that is provided by the high-pressure and hydraulic supply system by electrically-controlled valve is provided.Exhaust valve is pushed at closing direction by gas spring.Timing and the exhaust valve aperture of exhaust valve opening action and exhaust valve closing action can both be controlled with electrically-controlled valve.Therefore finish timing and the aperture that also is easy to long after change exhaust valve in the motor manufacturing.
Fuel sprays and exhaust valve actuation is all controlled by the programmable controller that appropriate software is installed.
Therefore, the motor of automatically controlled type arranges at it has larger degrees of freedom, and this is so that more easily satisfy a lot of often mutual conflicting requirements that motor is proposed.The operator of these motors need to hang down the specific high output under the manufacture cost, high fuel efficiency and high reliability.Emission request often can limit maximum combustion pressure and temperature and other increase the aspect of fuel efficiency and power stage.This is just so that determine to require very high for the task of the optimized operation setting of this motor to the engineer who researches and develops this type of engine.At the motor run duration or at service life of aeroengine phase intrinsic motivation the increase of degrees of freedom is set, and the raising that changes the flexibility of these motors settings, the electric-controlled type motor is compared with camshaft type engine had significant advantage.
But the installation cost of the injection of electric-controlled type fuel and exhaust valve actuation is relatively high, and is relatively independent of the size of motor.The normal mode that this cost of not following the most of miscellaneous parts that usually are applicable to these motors with regard to the cost that means these parts increases with the increase of size of engine.In practice, this just mean utilize automatically controlled fuel to spray and vent systems more cheap when making up piston diameter in these motors and surpassing the largest motor of about 90cm, but piston diameter is then held high more expensive less than comparing with the operated motor of camshaft than mini engine of about 60cm in these motors when the equipment power fuel sprays with exhaust valve actuating system.
The competitive low manufacture cost of small-bore gas Cylinder engine is very important to its success on market.Therefore, existence to piston diameter that necessary degrees of freedom and flexibility are provided in operation arranges less than the about demand of the large two-stroke diesel engine of 60cm, to compare the requirement that competitive cost level satisfies output, fuel consumption, reliability and emission limit set with the camshaft type engine of routine.
To this, also there are cost and the complexity that reduces the hydraulic system that is associated with the electronic fuel control system that is used for large two-stroke diesel engine and the demand that improves its reliability.
Summary of the invention
Under this background, the purpose of this invention is to provide a kind of large-sized uniflow type two-stroke diesel motor that can satisfy the crosshead of above-mentioned requirements.
This purpose is by providing a kind of large-sized uniflow type two-stroke diesel motor to realize, this large-sized uniflow type two-stroke diesel motor comprises: turbosupercharger; Crosshead; A plurality of cylinders, each cylinder are furnished with cylinder liner and at least one exhaust valve; Fuel injector, each cylinder is furnished with one or more fuel injectors; High-pressure fluid source; Gather by compression potential energy described high-pressure liquid container or gather the accumulator of potential energy by compression; At least one automatically controlled ratio hydrovalve, wherein, described cylinder liner is provided with for the scavenging port that receives from the pressurized air of described turbosupercharger, wherein, fuel sprays and is mainly driven by the potential energy that gathers, wherein, fuel sprays to be controlled by described at least one automatically controlled ratio hydrovalve, wherein, described large-sized uniflow type two-stroke diesel motor further comprises: be provided with at least one camshaft of cam, described cam is for the actuating of described at least one exhaust valve that is associated with each cylinder; Hydraulic piston pump, described hydraulic piston pump is by the described actuated by cams on the described camshaft; Be located at the hydraulic actuator of each exhaust valve, described hydraulic actuator is used for moving described exhaust valve along opening direction; Be located at the hydraulic pipe line of each exhaust valve, described hydraulic pipe line is used for described hydraulic piston pump is linked to each other with described hydraulic actuator; And the pneumatic spring that is associated with each exhaust valve, described pneumatic spring is used for along the relevant described exhaust valve of closing direction pushing.
The present inventor has realized that the directional preponderance of electric-controlled type motor is in fuel injection aspect.For the optimum running parameter of determining motor, and consider the emission request that satisfies the future that present emission request and the later stage of flexible adaptation motor in its lifetime may needs follow, electronic fuel-injection system provides a large amount of flexibilities.The selection of hydraulic pressure and exhaust valve actuating system being separated the fueling injection pressure that makes is freer, has therefore improved the possibility that obtains in all cases desirable jet pressure.In addition, available electric control exhaust door actuation system has used a large amount of hydraulic powers at present, therefore makes the overall fuel efficiency variation of motor.
Because exhaust valve by the camshaft operation, is therefore compared with the motor that valve activates with having electric-controlled injection, has reduced total hydraulic power demand.This becomes possibility so that satisfy the hydraulic power demand with the less pump of the motor-drive pump form that can be used as industrial standard.Compare with the installation cost of the power-actuated large hydraulic pump that is discharged by engine crankshaft, the cost of this motor-drive pump significantly reduces.
Preferably, described high-pressure liquid is medium different from fuel and that separate with fuel.In the case, high-pressure liquid and fuel by at least one piston of each cylinder separately, and described high-pressure liquid is at fuel mobile described piston apparatus between injection period, and described piston apparatus is sent into fuel in the firing chamber in the associated cylinder then.
Piston apparatus can be pressurized machine, and described piston apparatus preferably includes and has towards the large effective area of high pressure hydraulic fluid with towards the piston of the less useful area of fuel.This makes it possible to use the hydraulic medium of working under the pressure of jet pressure being starkly lower than.
Preferably, the container of described high-pressure liquid is accommodated in along in the delivery line of motor length extension.This delivery line can comprise a plurality of pressing chambers that distribute along motor length; Described pressing chamber is provided with the expansion capacity for described high pressure hydraulic fluid, in order to can gather a large amount of potential energy by the compression of hydraulic fluid self.Utilize this feature, can avoid using the membrane type accumulator, this is an advantage, and reason is that the membrane type accumulator easily breaks down.
Preferably, a pressing chamber is set to be used to a pair of adjacent cylinder that high pressure hydraulic fluid is provided.
Motor comprises camshaft case, has camshaft and described delivery line in camshaft case.Therefore, delivery line is accommodated in the protected position of avoiding damaging, and near the people the camshaft case protection delivery line avoids being full of the danger of the delivery line explosion of high-pressure liquid.
Preferably, pressing chamber is positioned at described camshaft case at least in part.Like this, pressing chamber can not disturb motor.
Pressing chamber can share at least one wall with described camshaft case, to reduce for the manufacture of the used quantity of material of motor.
Preferably, form pressing chamber by machining recess part in solid metal block, can keep out the high pressure of the fluctuation that in its lifetime, will stand to guarantee pressing chamber.
High-pressure fluid source can be one or more electric high pressure pumps.Owing to do not need the independent priming pump for fuel system, so the use of these electric high pressure pumps helping the starting of motor.
Preferably, hydrovalve fuel of controlling two or more cylinders sprays.Therefore, reduced the quantity of making the required electro hydraulic valve of motor.The reduction of required control capacity for size independence cost sensitivity than relevant especially for the mini engine.
According to a preferred embodiment, described high pressure hydraulic fluid is fuel.In this embodiment, the container of high pressure hydraulic fluid preferably is accommodated in and shares in the rail.
The hydrovalve that is used for the control injection is preferably Proportional valve.These hydrovalves are by described one or more computer control.Described one or more computer is configured to make the timing of fuel injection and/or the working state that jet law is adapted to motor.This feature is so that more easy to the optimization about the engine performance of the aspects such as power stage, reliability, responsiveness and discharging.
Described one or more computer can be provided in when engine load reduces and make the fuel injection timing in advance.Like this, can under low load condition, maximum combustion pressure be remained on high level.
Preferably, for the spray characteristic that obtains to expect, can regulate fuel injection rate between injection period at fuel.This feature makes it possible to middle increase degrees of freedom is set and thus so that more easy to the optimization about the engine performance of the aspects such as power stage, reliability, responsiveness and discharging at motor.
Motor may further include also by described one or more computer-controlled cylinder lubricating systems.In the case, high pressure hydraulic fluid provides power also can for described cylinder lubricating system.The electronic control cylinder lubrication system can be carried out quick adjustment according to the variation of employed fuel quality.Therefore, can (for example very low fuel of Sulpher content) save a large amount of cylinder lubricating oils when motor uses the operating fuel of higher quality, cylinder lubricating oil occupies second largest variable operation cost after coming fuel consumption.
Preferably, the pressure duct that hydraulic piston pump is connected to valve actuator can reduce pressure by the electrically-controlled valve device, to allow exhaust valve its backhaul of beginning before the backhaul timing that corresponding cam on the camshaft is limited.Like this, can obtain and show certain flexibility of exhaust valve actuation, thereby the increase motor moves the degrees of freedom in arranging.
Preferably, the pressure duct that hydraulic piston pump is connected to valve actuator can optionally be blocked by electronic valve device, backhaul is deferred on the camshaft after the backhaul timing that corresponding cam limited always.Like this, can obtain certain flexibility of exhaust valve actuation, thereby the increase motor moves the degrees of freedom in arranging.Described one or more computer can be configured to control shifting to an earlier date or delay of the exhaust valve closing timing relevant with engine behavior.
Can be provided with on the camshaft for the mechanism of adjustment cam axle with respect to the angular orientation of crank angle position, described mechanism is preferably by the opening and closing timing of described one or more computer control with the change exhaust valve.Like this, can obtain certain flexibility of exhaust valve actuation, thereby the increase motor moves the degrees of freedom in arranging.
More purposes, feature, advantage and character according to the large-sized uniflow type two-stroke diesel motor of crosshead of the present invention will become apparent from following detailed description.
Description of drawings
Below this specification in the detailed description, the exemplary embodiment shown in reference to the accompanying drawings is described in more details the present invention, in the accompanying drawings:
Fig. 1 is the sectional view during according to motor of the present invention when seeing from the motor front,
Fig. 2 is the sectional view of a cylinder portion of motor shown in Fig. 1 when seeing from the motor side,
Fig. 3 is the view of a thin section among Fig. 1,
Fig. 4 is the view of a thin section among Fig. 2,
Fig. 5 is the front perspective view of motor among Fig. 1,
Fig. 6 is the view of a thin section among Fig. 5,
The detailed sectional view of the exhaust valve actuating system that Fig. 7 shows motor among Fig. 1 along the primary importance of camshaft the time,
The detailed sectional view of the valve actuation system that Fig. 7 A shows motor among Fig. 1 along the second place of camshaft the time,
Fig. 7 B is camshaft case along the sectional view on the plane of the longitudinal axis that is parallel to camshaft,
Fig. 7 C is the perspective view of a thin section of camshaft case,
Fig. 8 is the unify schematic diagram of valve actuation system of the fuel injection systems of motor among Fig. 1,
Fig. 9 shows the chart according to the jet law curve of the fuel injection of the motor of Fig. 1,
Figure 10 is the front perspective view of the motor of Fig. 1 in another embodiment,
Figure 11 shows the thin section of Figure 10, and
Figure 12 is the schematic diagram according to the embodiment's of Figure 10 fuel injection system.
Embodiment
Fig. 1 and Fig. 2 show the sectional view of seeing motor 1 according to the preferred embodiment of the invention from the motor front and seeing a cylinder from the motor side.Motor 1 is the single current low speed two-stroke cross-head diesel engine of crosshead.Motor 1 can be propelling motor in the naval vessel or the prime mover in the power plant.These motors have 3 to 14 single-row cylinder arrangements usually.Motor 1 builds from the base plate 2 that has for the main bearing of bent axle 3.
Bent axle 3 is half combined.Half combined bent axle is made by forged steel crank throw or cast steel crank throw that the mode that is connected by hot jacket links to each other with main journal.
Bearing cap (being used for cross head bearing and crank pin bearing) is made and be provided with to connecting rod 8 by forged steel or cast steel.Crosshead and crank pin bearing cover bolt and fastening nuts are used the hydraulic jack fastening nut to connecting rod 8.Cross head bearing 22 is made of one group of thin-walled box hat that is lined with the supporting metal.Crank pin bearing is provided with the thin-walled box hat that is lined with the supporting metal.Lubricant oil is admitted to crosshead 22 and connecting rod 8 by the pipeline (not shown).
Main bearing is made of the thin-walled box hat that is lined with the supporting metal.Drain pan can utilize special tool(s) and produce and change over to for the Hydraulic power tools that promotes bent axle.Box hat is held in place by the bearing cap (not shown).
The A shape structure case 4 of welding procedure is installed on the base plate.This structure case can be finished by casting or welding procedure.At exhaust side, each cylinder is provided with reduction valve, and in camshaft side, each cylinder is provided with large hinge door.Cross guide plate is integrated in this structure case.
Four bolts of piston rod 14 usefulness are connected to crosshead 22.Piston rod 14 has center hole (invisible among the figure), and this center hole is formed for the entrance and exit of the cold oil of piston 13 together with oil cooling service pipe.
The air of turbosupercharger 10 enters directly and carries out from the admission air silencer (not shown) of engine compartment by turbosupercharger.Via pressurizing air tracheae (not shown), intercooler (not shown) and scavenging receiver 9 are introduced into the scavenging port 7 of cylinder liner 6 to air from turbosupercharger 10.
Motor is equipped with one or more turbosupercharger, and for 4 motors to 9 cylinders, described pressurized machine is arranged in the tail end of motor, for 10 or then be arranged in exhaust side more than the motor of 10 cylinders.
Motor is equipped with electronic scavenge blower (not shown).The side of bleeding of this blower is connected to the gas-swept space behind the intercooler.Between intercooler and scavenging receiver, the safety check (not shown) is installed with autoshutdown when the auxiliary blower air feed.Auxiliary blower low carry and middle carrier strip spare under assist the compressor of turbosupercharger.
The exhaust valve 11 that is shown in further detail among Fig. 3 is medially installed in the cylinder head 12 at the top of cylinder.In expansion stroke latter stage, exhaust valve 11 is opened through before the scavenging port 7 downwards at engine piston 13, therefore the combustion gas in the firing chamber 15 of piston 13 tops flow out by the exhaust passage 16 at exhaust receiver 17 split sheds, and the pressure relieve in the firing chamber 15.Exhaust valve 11 cuts out during the moving upward of piston 13 again.Exhaust valve 11 is upwards driven by pneumatic spring 20.
Fig. 3 and Fig. 4 show top, cylinder head 12 and the exhaust valve housing of cylinder liner 6.Cylinder head 12 is made single-piece by forged steel, and has the hole for cooling water.Cylinder head 12 has for the center hole of exhaust valve 11 and is used for some holes of two or three fuel injectors 23, safety valve (not shown), starting valve (not shown) and indicator valve (not shown).Each cylinder head 12 is equipped with two or three fuel injectors 23, a starting valve, a safety valve and an indicator valve.Fuel injector 23 open the fuel oil high voltage control that is produced by fuel booster (being explained in more detail hereinafter), and close fuel injector 23 by spring.Automatic vent slide bar (not shown) allows fuel oil to circulate by fuel injector and by the high-voltage tube that fuel injector 23 is connected to fuel booster, and prevents that the situation lower combustion chamber 15 of the main shaft generation adhesion of sparger 23 when motor 1 is shut down is full of fuel oil.Fuel oil from exhaust slide bar and other outlets is introduced in the system of sealing.
The exhaust valve housing is made of cast iron and is arranged to carry out water-cooled.This housing is provided with the bottom steel member, and this bottom steel member has the deposited metal that is welded on the base.This bottom steel member is water-cooled.Self is made valve rod by refractory steel, and has the deposited metal that is welded on the base.The exhaust valve housing is provided with the valve rod guide.The exhaust valve housing is secured to cylinder head 12 with screw bolt and nut.Hydraulic exhaust valve actuator 21 is installed in the top of exhaust valve housing.When pressurized, hydraulic actuator 21 is along the exhaust valve of (opening) direction pushing downwards.Hydraulic actuator 21 comprises the piston in the cylinder, has the pressure chamber in the cylinder above piston.The exhaust valve housing also comprises the pneumatic spring 20 that upwards pushes exhaust valve rod 11 (along closing direction).Pneumatic spring 20 comprises spring piston, in the cylinder portion in the exhaust valve housing, is provided with spring housing below spring piston.
The hydraulic exhaust valve actuator 21 of each exhaust valve is connected to reciprocating pump 37 (Fig. 6) by pressure tube 35.Each cylinder is furnished with a reciprocating pump 37 and an exhaust valve 11 in the present embodiment, but each cylinder can be furnished with more than a reciprocating pump or more than an exhaust valve (not shown).
As shown in Figure 7, reciprocating pump 37 is installed on the deflector roll housing 46.Roller 42 rotates with corresponding cam 29 on the camshaft 28.Therefore reciprocating pump 37 starts excitation by camshaft 28.
Fig. 5 is the perspective view that has removed the motor of some parts in order to illustrate purpose.Camshaft 28 is driven by the chain driver 26 that camshaft 28 is connected to bent axle 3.Chain driver 26 is provided with chain tensioning device (not shown) and guide rod (not shown), to support long chain length.According to the modification of the present embodiment, chain driver provides power to be used for the high hydraulic pressure of motor to the oil hydraulic pump (not shown).Chain can also be used to drive the secondary counterweight.As substituting of chain driver, can come drive cam shaft by the gear drive (not shown).
Fig. 6 illustrates in greater detail the part of the Fig. 5 with camshaft case 25 and cylinder 6.Can see that in the figure pipeline 31 branches out from delivery line 30.Pipeline 31 is connected to pressurized machine 39 by the distributor chunk 40 with hydraulic control valve 41 with delivery line 30.Distributor chunk 40 is installed on the top board of camshaft case 25.
The reciprocating pump 37 that is activated by the cam 29 of camshaft 28 also be located at the top board 25 of camshaft case 25 ' on.Reciprocating pump 37 is connected to hydraulic exhaust valve actuator 21 by pressure tube 35.
Each cylinder 6 is furnished with two or three spargers 23, and each sparger pipeline (not shown among Fig. 6, but have reference character 51 in Fig. 8) is connected to the port of pressurized machine 39.
Each distributor chunk 40 is with two proportional control valves 41, being connected of the delivery line 30 in the port at these two proportional control valves, 41 control dispenser chunks, 40 tops and return line (65 among Fig. 8) and the camshaft case 25.Pressurized machine 39 is installed in the top of each distributor chunk 40 and is connected with the port at distributor chunk 40 tops.Like this, distributor chunk 40 namely is used as the mechanical support of hydraulic actuating fuel booster 39.
Fig. 7 A, 7C show in detail pressing chamber housing 68 with 7C with different viewgraph of cross-section and perspective view.Pressing chamber 67 provides the expansion volume that is used for the potential energy of stores hydraulic pressure fluid, can use to guarantee the hydraulic oil peak flow that is necessary during whole fuel injecting step.
In the present embodiment, for a pair of adjacent cylinder 6 a pressing chamber housing 68 with two pressing chambers 67 is set.But, also can for each cylinder setting still less or more pressing chamber.
Pressing chamber 68 injects high pressure hydraulic fluid by localized branches pipeline 31 from delivery line 30.Connection between pipeline 31 and the pipeline 30 is by the contiguous block 30 on the bottom that is installed in camshaft case 25 ' realization.
Pressing chamber 68 forms the top board part of the whole of camshaft case 25.The top board of camshaft case 25 vertically is divided into some parts.One type of these parts is the sheet metal that wherein is formed with two cylindrical shape pressing chambers 67, and therefore this plate also forms pressing chamber housing 68.This top board is placed with pressurized machine 39 also with distributor chunk 40 on this distributor chunk 40.The longitudinal shaft of cylindrical shape pressing chamber 67 is to the longitudinal axis that is set to be parallel to camshaft 28.Pressing chamber 67 is made by two parallel holes of machining in solid sheet metal.Pressing chamber 67 is bolted circular jam plate 69 sealings to pressing chamber housing 68.The hole (not shown) that passes in the sensing of pressing chamber housing 68 is connected to distributor chunk 40 with pressing chamber 67.Because the distributor chunk is directly installed on the top of pressing chamber housing 68, thus high pressure hydraulic fluid from pressing chamber 67 to distributor chunk 40 must through the path very short.
Two types top board of camshaft case alternately distributes along the length of camshaft case 25.Transition position between this top board of two types has longitudinal overlap, and top board is bolted together at this overlapping.
Fig. 8 schematically shows fuel injection system.Fuel is transported to pressurized machine 39 from fuel delivery means 73.Fuel delivery means 73 is not shown specifically in the drawings.
Fuel delivery means 73 is arranged to make diesel oil and heavy fuel oil to be used.Fuel is introduced electronic oil feed pump from fuel tank, utilize this electronic oil feed pump can in the low-pressure section of fuel circulating system, keep the pressure of about 4bar, thereby avoided fuel in applied temperature range, in ventilated box, to gasify.Fuel oil is transported to electric circulating pump from the low-pressure section of fuel system, and this electric circulating pump pumping fuel is by the full flow filtration device before heater and next-door neighbour's motor 1 entrance, this with fuel distribution to each pressurized machine 39.
Fuel sprays and is undertaken by the automatically controlled pressurized machine 39 that each cylinder is configured.(fuel-side) increases by fixed ratio pressurized machine to the high pressure side from low voltage side (using the flow of pressurized side) with pressure.
For every pair of cylinder arranges pressing chamber 67 (in the situation that the cylinder number is odd number, one of them cylinder can use single pressing chamber).Pipeline 69 is connected to two proportional control valves 41 and two close/open valves 55 with pressing chamber 67.According to a modification (not shown) of the present embodiment, use inflation membrane type accumulator replaces pressing chamber or uses in conjunction with pressing chamber.
Each cylinder 6 of motor 1 is associated with ECU (Electrical Control Unit) 99, and wherein ECU (Electrical Control Unit) 99 receives synchronously conventional by circuit 59 and control signal and electronic signal is delivered to proportional control valve 41.Each cylinder can be furnished with a control unit 99, and perhaps a plurality of cylinders can be associated with same control unit (not shown).Control unit 99 also can receive signal from the master control unit (not shown) that all cylinders share.
Timing, jet law and emitted dose that control unit 99 comes computing fuel to spray according to the working state of motor.At this, control unit receives the information about the temperature of crankshaft rotating position, speed of crankshaft (can obtain from rotating position signal by control unit 99), ambient temperature, load and various engine fluid.Control unit also changes be used to the fuel injection timing that makes engine inversion.The movement of proportional control valve 41 inner valve stem is by control unit 99 controls in the feedback control circuit.Alternately, feedback control circuit can be included in the proportional control valve 41 self.The opening characteristic of Proportional valve 41 is complementary corresponding to optimum jet law and the expectation opening characteristic that is stored in the control unit 99 with predetermined.
In its position of rest, proportional control valve 41 is connected to fuel tank with the pressure chamber of pressurized machine low voltage side.When control unit 99 sends when beginning that given cylinder carried out signal that fuel sprays, proportional control valve 41 is opened to specific aperture and therefore the low voltage side of pressurized machine 39 is connected to pressing chamber 67 by pipeline 69.
Pressure in the pressurized machine low voltage side is increased the jet pressure between about 400 to 1500bar usually.Delivery line 51 is delivered to fuel injector 23 with fuel under high pressure, and fuel injector 23 is by spraying into firing chamber 15 and atomized fuel with its nozzle with fuel.
Fig. 9 shows the exemplary jet law curve of fuel injecting step.Make wittingly the rising of pressure level and smooth and slow, to obtain long-time substantially average and high firing pressure, under loading fully, this firing pressure is set to approach maximum permission firing pressure.
Figure 10 and Figure 11 show an alternative embodiment of the invention, and electronic fuel-injection system wherein is so-called common-rail type.In this system, do not have independent hydraulic fluid, but fuel is kept under high pressure and by compressed fuel coming the store injection energy.Shared rail is divided into and each some part 95 that are associated in two cylinders.The advantage of this set is share rail far better aspect the twist motion of motor run duration adaptation motor 1, otherwise described twist motion will make very long sharing continuously the distortion of rail pipe and make its fatigue.
Figure 12 schematically shows common-rail injection system.Usually use (water emulsification and non-water emulsification) heavy fuel oil (HFO) during the motor operation.Be emulsified in the independent emulsification unit (not shown) and carry out.The fuel that is used for the motor operation is stored in the heating tank 129.Heavy fuel oil has 500 to 700cSt viscosity and at room temperature can't flow under 50 ℃.Heavy fuel oil remains at approximately 50 ℃ in the tank, that is to say at during engine shutdown like this equally.Boats and ships with the type motor all are provided with generator set (Genset) usually, and the less diesel engine of electric power and heat supply namely is provided for boats and ships and master motor between the master motor down period.Heavy fuel oil is transported to filter or centrifuge 130 from heating tank 129, and is transported to preheater 131.Control the temperature of the heavy fuel oil that leaves preheater 131 according to the grade of working state and heavy fuel oil.At during engine shutdown, when heavy fuel oil under low pressure cycled through hydraulic system, the temperature of heavy fuel oil was maintained in 45 ℃ to 60 ℃ the scope.At the motor run duration, the temperature of leaving the heavy fuel oil of preheater 131 depends on restrikes oil viscosity and is maintained between 90 ℃ to 150 ℃.The sensor (not shown) is just in time measured the oil viscosity of restriking in the downstream (or another suitable position) of preheater 131.The temperature of leaving the heavy fuel oil of preheater 131 is controlled so as to the viscosity in measuring point produces 10 to 20cSt scopes usually.
The intermediate duct 132 of branch is connected to high pressure fuel pump 133 and auxiliary low pressure recycle pump 134 with preheater.The downstream part of each pump arranges safety check 135 to prevent back suction in pipeline.
At the motor run duration, high pressure fuel pump 133 is driven by gear 137 by the gear 136 on the camshaft 3.Thus, high pressure fuel pump 133 produces 1000 to 1500bar nominal pressure, but this pressure can fluctuate between 600 to 2000bar according to working state.
At during engine shutdown, auxiliary low pressure recycle pump 134 is driven by motor 138.Thus, provide about pressure of 3 to 10bar to be used for making heavy fuel oil cycle through hydraulic system at during engine shutdown.
By rail 140 branches out and the oil feed line 141 that leads to proportional control valve 125 entrances provides heavy fuel oil to a pair of adjacent cylinder from sharing.Oil feed line 141 is provided with a plurality of fluidic accumulators 142, and fluidic accumulator 142 is carried most fluids when proportional control valve 125 is opened, and when proportional control valve 125 cuts out after share rail 140 and carry out fuel feeding.
In coil 144 inoperative central positions, the entrance of proportional control valve 125 is closed, and two outlets of proportional control valve 125 are connected to return line 143.
When solenoid is energized and shifts spool onto left side when (left side among Figure 12), the entrance of proportional control valve is connected to delivery line 120, so that sparger 23 sprays into fuel in the firing chamber 15 of the described cylinder in two cylinders that are associated with control valve 125.In this position, pressure piping 124 is connected to return line 143.
When solenoid 44 is energized and shifts spool onto right side (right side among Figure 12), the entrance of proportional control valve 125 is connected to delivery line 124, the high pressure heavy fuel oil is through delivery line 124, so that sparger 23 sprays into fuel in the firing chamber 15 of described another cylinder in two cylinders that are associated with proportional control valve 125.In this position, pressure piping 120 is connected to return line 143.
The form of fuel injection timing, fuel injection amount and jet mode is by Proportional valve 125 controls.
The unshowned modification according to the present invention, with have less port and only the proportional control valve of two positions control the fuel injection of a cylinder.In this modification, proportional control valve is connected to low pressure line in its position of rest with delivery line, and another position in two position is connected to shared rail with delivery line.
According to another unshowned modification of the present embodiment, share rail and do not have Inflated film accumulator 142 and 148 at its end.
According to further preferred embodiment (not shown), controlled by the on/off-type valve to the fuel flow rate of sparger from sharing rail.
In two delivery lines 120,124, all be provided with conventional fuel limiter 146, to avoid too much heavy fuel oil enters cylinder in the situation just in case proportional control valve 125 was opened for a long time mistakenly.
Pressure in the return line 143 are held the overvoltage of several bar, to avoid air penetration in hydraulic system and to prevent that water contained in the water emulsification heavy fuel oil from forming steam bubble.The pressure controlled valve 147 that is positioned at return line 143 downstream is guaranteed in the predetermined minimum overvoltage of return line 143 maintenances.Overvoltage in the return line 143 is preferably 3 to 10bar.Accumulator or expansion tank 148 are connected to return line 143, contingent pressure surge when changing the position with assimilation ratio control valve 125.
The second return line 149 is connected to return line 43 with the outlet of sparger 23.In pressure controlled valve 147 downstreams, return line 143 is sent into preheater 131 to finish circulation with used heavy fuel oil.
Heavy fuel oil is delivered to the pipeline that shares rail 140 and be delivered to sparger 23 from sharing rail 40 passing ratio control valves 125 from the outlet of preheater 131 is provided with the heating equipment that represents with heating coil.These pipelines can be heated by for example steam line or electric heating part along its whole length.Heat these pipelines and play the effect of thermogravimetric fuel oil heat loss when reducing heavy fuel oil from the preheater flow further downstream.At the motor run duration, the temperature of the heavy fuel oil that flows to sparger and hydrovalve actuator in the pipeline is retained as near 150 ℃, but this depends on the employed oil viscosity of restriking.Along the contiguous pipeline that its partial-length extends in parallel, for example delivery line 120 and delivery line 124 can be provided with and share the heating equipment (not shown).
At during engine shutdown, heavy fuel oil cycles through hydraulic system (under 3 to 10bar relatively low pressure) under recycle pump 134 effect, to avoid air capture in hydraulic system and to avoid Local cooling and the sclerosis of heavy fuel oil.
A kind of modification (not shown) according to above-described embodiment, the pressure duct 35 that hydraulic piston pump 37 is connected to valve actuator 21 can carry out step-down by electrically-controlled valve device (by control unit 99 controls), to allow exhaust valve its backhaul of beginning before the backhaul timing that corresponding cam on the camshaft is limited.
Further modification (not shown) according to above-described embodiment, the pressure duct 35 that hydraulic piston pump 37 is connected to valve actuator 21 can optionally be blocked by electronic valve device (by control unit 99 control), backhaul is deferred to after the backhaul timing that corresponding cam is limited on the camshaft always.
Described one or more control unit 99 can be configured to control shifting to an earlier date or delay of the exhaust valve closing timing relevant with engine behavior.
According to another modification (not shown) of above-described embodiment, camshaft 28 is provided with for the electric liquid mechanism of adjustment cam axle 28 with respect to the angular orientation of bent axle 3 angular orientations.This mechanism is controlled by described one or more control units 99, to change the opening and closing timing of exhaust valve.
Although preferred embodiment only shows the motor with cylinder of arranging in upright arrangement, the present invention also can be used for other cylinder arrangement form, for example v-shaped structure or U-shaped structure.
The term that uses in the claim " comprises " element or the step of not getting rid of other.The term that uses in the claim " one " is not got rid of a plurality of.
The reference character that uses in the claim should not be construed as the restriction to protection domain.
Although for illustrative purposes the present invention is had been described in detail, be to be understood that these detailed descriptions only are used for the example purpose, and those of ordinary skills can carry out various modification in the situation that do not deviate from protection domain of the present invention.
Claims (12)
1. the large-sized uniflow type two-stroke diesel motor of a crosshead (1) comprising:
Turbosupercharger (10);
A plurality of cylinders, each cylinder are furnished with cylinder liner and at least one exhaust valve (11);
Fuel injector (23), each cylinder are furnished with one or more described fuel injectors (23);
High-pressure fluid source (60);
Gather the container (67) of the described high-pressure liquid of potential energy or gather the accumulator of potential energy by compression by compression;
At least one automatically controlled ratio hydrovalve (41,145),
Wherein, described cylinder liner is provided with for the scavenging port (7) that receives from the pressurized air of described turbosupercharger (10),
Wherein, fuel sprays and is mainly driven by the potential energy that gathers,
Wherein, fuel sprays to be controlled by described at least one automatically controlled ratio hydrovalve (41,125),
Wherein, described large-sized uniflow type two-stroke diesel motor (1) further comprises:
Be provided with at least one camshaft (28) of cam (29), described cam (29) is for the actuating of described at least one exhaust valve (11) that is associated with each cylinder;
Hydraulic piston pump (37), described hydraulic piston pump (37) is driven by the described cam (29) on the described camshaft (28);
Be located at the hydraulic actuator (21) of each exhaust valve (11), described hydraulic actuator (21) is used for moving described exhaust valve (11) along opening direction;
Be located at the hydraulic pipe line (35) of each exhaust valve (11), described hydraulic pipe line (35) is used for described hydraulic piston pump (37) is linked to each other with described hydraulic actuator (21); And
With the pneumatic spring that each exhaust valve (11) is associated, described pneumatic spring is used for along the relevant described exhaust valve (11) of closing direction pushing.
2. the large-sized uniflow type two-stroke diesel motor of crosshead as claimed in claim 1 (1), wherein, the described container of high-pressure liquid is contained in the delivery line (30) that extends along the length of motor.
3. the large-sized uniflow type two-stroke diesel motor of crosshead as claimed in claim 2 (1), wherein, described delivery line (30) comprises a plurality of pressing chambers (67) along the distribution of lengths of motor (1), and wherein said pressing chamber (67) is provided with the expansion capacity for described high pressure hydraulic fluid, in order to can gather a large amount of potential energy by the compression of hydraulic fluid self.
4. the large-sized uniflow type two-stroke diesel motor of crosshead as claimed in claim 3 (1) wherein, arranges a pressing chamber (67) or a pair of pressing chamber (67) and is used to a pair of adjacent cylinder that described high pressure hydraulic fluid is provided.
5. such as the large-sized uniflow type two-stroke diesel motor (1) of each described crosshead in the claim 1 to 4, also comprise camshaft case (25), described camshaft (28) and described delivery line (30) are contained in the described camshaft case (25).
6. the large-sized uniflow type two-stroke diesel motor of crosshead as claimed in claim 5 (1), wherein, described pressing chamber (67) is at least partially disposed in the described camshaft case (25).
7. the large-sized uniflow type two-stroke diesel motor of crosshead as claimed in claim 5 (1), wherein, described pressing chamber (67) and described camshaft case (25) share at least a portion of a wall.
8. the large-sized uniflow type two-stroke diesel motor of crosshead as claimed in claim 3 (1), described pressing chamber (67) forms by machining recess part in solid metal block.
9. such as the large-sized uniflow type two-stroke diesel motor (1) of each described crosshead in the claim 1 to 4, wherein, described high-pressure fluid source comprises one or more electric high pressure pumps (60).
10. such as the large-sized uniflow type two-stroke diesel motor (1) of each described crosshead in the claim 1 to 4, wherein, automatically controlled ratio hydrovalve control is sprayed the fuel of two or more cylinders.
11. the large-sized uniflow type two-stroke diesel motor of crosshead as claimed in claim 1 (1), wherein, the described container of high pressure hydraulic fluid is contained in and shares in the rail.
12. the large-sized uniflow type two-stroke diesel motor of crosshead as claimed in claim 7 (1), wherein, described pressing chamber (67) shares or forms the part of the top board (68) of described camshaft case (25).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110207797.9A CN102251895B (en) | 2006-04-12 | 2006-04-12 | Crosshead-shaped large uniflow-type dual-stroke diesel engine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110207797.9A CN102251895B (en) | 2006-04-12 | 2006-04-12 | Crosshead-shaped large uniflow-type dual-stroke diesel engine |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006800541928A Division CN101415936B (en) | 2006-04-12 | 2006-04-12 | Crosshead type large-sized uniflow type two-stroke diesel motor |
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| Publication Number | Publication Date |
|---|---|
| CN102251895A CN102251895A (en) | 2011-11-23 |
| CN102251895B true CN102251895B (en) | 2013-03-27 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201110207797.9A Active CN102251895B (en) | 2006-04-12 | 2006-04-12 | Crosshead-shaped large uniflow-type dual-stroke diesel engine |
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| US9739180B2 (en) * | 2015-08-07 | 2017-08-22 | GM Global Technology Operations LLC | Variable tensioning for engine camshaft drive |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1503096A (en) * | 1975-05-16 | 1978-03-08 | Karl Marx Stadt Automobilbau | Fuel injection pumping apparatus |
| FR2496170A1 (en) * | 1980-12-16 | 1982-06-18 | Sulzer Ag | DEVICE FOR CONTROLLING THE FUEL SUPPLY OF AN INTERNAL COMBUSTION ENGINE |
| CN1214408A (en) * | 1997-10-14 | 1999-04-21 | 瓦特西拉Nsd施韦兹公司 | Arrangement and method for valve control of reversible diesel combustion engine |
| WO2004013487A1 (en) * | 2002-08-02 | 2004-02-12 | Wärtsilä Finland Oy | Fuel supply system |
-
2006
- 2006-04-12 CN CN201110207797.9A patent/CN102251895B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1503096A (en) * | 1975-05-16 | 1978-03-08 | Karl Marx Stadt Automobilbau | Fuel injection pumping apparatus |
| FR2496170A1 (en) * | 1980-12-16 | 1982-06-18 | Sulzer Ag | DEVICE FOR CONTROLLING THE FUEL SUPPLY OF AN INTERNAL COMBUSTION ENGINE |
| CN1214408A (en) * | 1997-10-14 | 1999-04-21 | 瓦特西拉Nsd施韦兹公司 | Arrangement and method for valve control of reversible diesel combustion engine |
| WO2004013487A1 (en) * | 2002-08-02 | 2004-02-12 | Wärtsilä Finland Oy | Fuel supply system |
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| CN102251895A (en) | 2011-11-23 |
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Address after: Copenhagen, Denmark Patentee after: Mannone solutions (mannone solutions Germany) branch Address before: Copenhagen, Denmark Patentee before: Mann Diesel & Turbine, an associate company of Mann Diesel & Turbine Europe AG |