CN101111665A - Macrotype double ram stroke diesel engine with hydraulic actuating exhaust valve - Google Patents

Macrotype double ram stroke diesel engine with hydraulic actuating exhaust valve Download PDF

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Publication number
CN101111665A
CN101111665A CNA2005800475866A CN200580047586A CN101111665A CN 101111665 A CN101111665 A CN 101111665A CN A2005800475866 A CNA2005800475866 A CN A2005800475866A CN 200580047586 A CN200580047586 A CN 200580047586A CN 101111665 A CN101111665 A CN 101111665A
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China
Prior art keywords
fuel
valve
motor
actuator
pressure
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Granted
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CNA2005800475866A
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Chinese (zh)
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CN100554652C (en
Inventor
芬·考助普·延森
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Man Diesel & Turbo Deutschland
Mann Diesel & Turbine An Associate Co Of Mann Diesel & Turbine Europe AG
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MANDIESEL Corp DK
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • F02M39/02—Arrangements of fuel-injection apparatus to facilitate the driving of pumps; Arrangements of fuel-injection pumps; Pump drives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
    • F02M53/02—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means with fuel-heating means, e.g. for vaporising
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/04—Fuel-injectors combined or associated with other devices the devices being combustion-air intake or exhaust valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves

Abstract

The present invention relates to a large two-stroke diesel engine (1) of the cross-head type in which the exhaust valves (11) are hydraulically actuated by providing hydraulic actuators (19) associated with each of the exhaust valves (11) with high pressure hydraulic fluid. Fuel oil or heavy fuel oil can be used as hydraulic fluid. The invention also relates to a control valve (25) for use in such an engine (1) , to a hydraulic system for such an engine (1) and to an hydraulic actuator (19) for such an engine (1).

Description

Large-scale two-stroke diesel engine with hydraulic actuating exhaust valve
Technical field
The present invention relates to the large-scale two-stroke diesel engine of crosshead, wherein by high pressure hydraulic fluid being provided and hydraulically activating described exhaust valve to the hydraulic actuator that is associated with each exhaust valve.
Background technique
Prime mover that the large-scale two-stroke diesel engine of crosshead is generally used for marine propulsion and is used as the power station.These internal-combustion engines are not only constructed differently with any other internal-combustion engine because of its overall dimensions.Two stroke principle and use in the time of 50 ℃ viscosity to be lower than the heavy fuel oil (this fuel oil in room temperature time do not flow) of 700cSt make them constitute a class by itself in engine art.
In many such conventional engines, exhaust valve and fuel injection system are driven by the rotating cam that directly is coupled to engine crankshaft.The air inlet that two-cycle engine uses scavenge port to come control cylinder, thereby the air inlet timing is relevant with degree in crank angle rigidly.This control that just makes exhaust valve and fuel spray is more flexible.
For the fuel consumption of this motor, reliability and power output require high.Recently, environmental requirement has caused requirement to reduce toxic emission.In order to satisfy these conflicting sometimes requirements, with respect to traditional rotating cam drive-type exhaust valve and fuel injector, need carry out comprehensively and flexibly controlling to fuel injection timing and emitted dose, and need carry out comprehensively and control flexibly the aperture that opens and closes timing and exhaust valve.
Because the size of this motor, electric actuator can not be used to handle exhaust valve.In this motor of maximum, this exhaust valve 450Kg that can weigh.
MAN B﹠amp; The ME power team of W Diesel company is the crosshead type large two-stroke diesel engine with electrichydraulic control formula exhaust valve and electric liquid actuating type fuel injection system.Since the hydraulic system from the oil work of motor lubrication system.Lubricating oil system is by the low pressure pump operation of 3-4 crust.The pump of another high pressure type is transported to common rail with the pressure of about 200 crust with lubricant oil.The lubricant oil that comes from common rail is directed into the fuel pressurization device by hydrovalve, and 200 bar pressures that the fuel pressurization device is heavy with common rail are increased to needed 1000 bar pressures in the burning line.Burning line is heated to 90-150 ℃ to guarantee that fuel oil can flow and have suitable viscosity.The lubricant oil that comes from common rail is directed into hydraulic exhaust valve actuator with operations platoon's valve by the timing valve.
Yet the lubricant oil that comes from the lubrication system of these motors is not clean must being enough to be used in the common rail hydraulic system.Thereby need filtering lubricant oil, to remove any particle on the 5-10 μ before common rail can being pumped at it.
W  rtsil /Sulzer RT-flex Engine Series is the crosshead type large two-stroke diesel engine with electrichydraulic control formula exhaust valve and electric liquid startup formula fuel injection system.The hydraulic system that is used for valve actuation is operated with specific hydraulic fluid.Lubrication system is separated with hydraulic system fully.
Summary of the invention
Based on above-mentioned background, the purpose of this invention is to provide a kind of at the crosshead type large two-stroke diesel engine that has the control of improvement aspect the fuel injection.
This purpose realizes by a kind of crosshead type large two-stroke diesel engine is provided according to claim 1, described crosshead type large two-stroke diesel engine comprises: the crankcase support, and it supports bent axle and the cylinder support that is installed on the described crankcase support; A plurality of cylinders, it is by described cylinder bracket supports, and each cylinder is provided with at least one fuel injector and at least one exhaust valve; The hydrovalve actuator that each described exhaust valve is associated; Common fuel rail, it has one or more accumulators that are connected thereto (accumulator); High pressure fuel pump, it under high pressure supplies fuel to described common fuel rail, and each described sparger is to come from the operating fuel of described common rail; With and the Proportional valve that is associated with each cylinder, described thus proportional valve control fuel flowing from described common fuel rail to each sparger.
The use of proportional control valve allows more accurately and neatly to control the characteristic curve of fuel injection timing, consumption.And the use of proportional control valve allows to realize rule shaping (rate shaping) and pre-spray and need not extra equipment that for example the rule shaping realizes by the control signal that is sent to Proportional valve basically fully.
Another object of the present invention provides a kind of crosshead type large two-stroke diesel engine that has the control of improvement aspect exhaust valve actuation.
This purpose realizes by a kind of crosshead type large two-stroke diesel engine is provided according to claim 10, described crosshead type large two-stroke diesel engine comprises: the crankcase support, and it supports bent axle and the cylinder support that is installed on the described crankcase support; A plurality of cylinders, it is by described cylinder bracket supports, and each cylinder is provided with at least one fuel injector and at least one exhaust valve; The hydrovalve actuator that is associated with each described exhaust valve; Common fuel rail, it has one or more accumulators that are connected thereto; High pressure fuel pump, it under high pressure supplies fuel to described common fuel rail, and each described sparger is to come from the operating fuel of described common rail; And the proportional control valve that is associated with each cylinder, described thus proportional control valve control fuel flowing from described common fuel rail to each hydrovalve actuator.
The use of proportional control valve is providing aspect the opening degree that opens and closes timing and exhaust valve fully and control flexibly.And, control the position of the exhaust valve of each cylinder with flexible way, thereby for example allow the exhaust valve of certain specific cylinder during its compression stroke, to open a little so that engine start.
Another object of the present invention provides a kind ofly to be had more simple on the whole and the crosshead type large two-stroke diesel engine of hydraulic system flexibly.
This purpose realizes by a kind of crosshead type large two-stroke diesel engine is provided according to claim 18, described crosshead type large two-stroke diesel engine comprises: the crankcase support, and it supports bent axle and the cylinder support that is installed on the described crankcase support; A plurality of cylinders, it is by described cylinder bracket supports, and each cylinder is provided with at least one fuel injector and at least one exhaust valve; The hydrovalve actuator that is associated with each described exhaust valve; Common fuel rail, it has one or more accumulators that are connected thereto; High pressure fuel pump, it under high pressure supplies fuel to described common fuel rail, each described sparger is to come from the operating fuel of described common rail, described hydrovalve actuator is connected to described common rail via corresponding supply line, and wherein said supply line is provided with heating equipment.
Thereby, at heavy fuel oil---when being also referred to as HFO etc. as hydraulic medium, this HFO remains on suitable viscosity.
Another object of the present invention provides a kind of crosshead type large two-stroke diesel engine, and it has the hydraulic pressure exhaust valve actuating system that can move in big temperature range.
This purpose realizes by a kind of crosshead type large two-stroke diesel engine is provided according to claim 30, described crosshead type large two-stroke diesel engine comprises: the crankcase support, and it supports bent axle and the cylinder support that is installed on the described crankcase support; A plurality of cylinders, it is by described cylinder bracket supports, and each cylinder is provided with at least one fuel injector and at least one exhaust valve; The hydrovalve actuator that is associated with each described exhaust valve; Common fuel rail, it has one or more accumulators that are connected thereto; High pressure fuel pump, it under high pressure supplies fuel to described common fuel rail, each described sparger is to come from the operating fuel of described common rail, each described hydrovalve actuator is to come from the operating fuel of described common rail, and wherein said hydrovalve actuator is provided with the device that is used to compensate the size change that is caused by underlying cause:
Under different temperatures, move,
Finishing, for example grinding of valve seat, and
Manufacturing tolerances.
Thereby the hydrovalve actuator will occupy suitable position and guarantee and correctly arrive valve seat at the free internal valve head of institute in big temperature range.
Another object of the present invention provide a kind of to the fuel temperature in the supply line of crosshead type large two-stroke diesel engine control method.
This purpose realizes by the method for temperature that fuel in a kind of pressure piping of controlling crosshead type large two-stroke diesel engine is provided according to claim 35, described pressure piping is connected to hydraulic exhaust valve actuator with common fuel rail, and this method running temperature of being included in fuel change during the control temperature that enters into the fuel of pressure piping maintain step under the predetermined threshold with temperature gradient with described fuel.
Thereby fuel can be used as hydraulic medium, is used to operate the exhaust valve actuator for the variation sensitivity of running temperature.
Another object of the present invention provides a kind of crosshead type large two-stroke diesel engine, and it has can be with the hydraulic pressure exhaust valve actuating system of multiple hydraulic fluid operation.
This purpose realizes by a kind of crosshead type large two-stroke diesel engine is provided according to claim 40, described crosshead type large two-stroke diesel engine comprises: the crankcase support, and it supports bent axle and the cylinder support that is installed on the described crankcase support; A plurality of cylinders, it is by described cylinder bracket supports, and each cylinder is provided with at least one fuel injector and at least one exhaust valve; The hydrovalve actuator that is associated with each described exhaust valve; Common fuel rail, it has one or more accumulators that are connected thereto; High pressure fuel pump, it under high pressure supplies fuel to described common fuel rail, each described sparger is to come from the operating fuel of described common rail, described hydrovalve actuator is connected to described common rail by corresponding hydraulic line, and finally be connected to for example other hydraulic unit of valve, it is characterized in that static gasket that pipeline and the connection between other hydraulic unit to described motor seal and the dynamic packing ring in the described valve actuator made by following material: cast iron, steel, polytetrafluoroethylene (PTFE), fluorine rubber, (FPM), copolymer (NBR), nitrite rubber, poly-(dimethyl siloxane) (SI) or its composition and/or mixture.
From these materials selected packing ring allow non-dedicated hydraulic fluid for example fuel can be used in the hydraulic system, described fuel can not cause damage to packing ring.
Another object of the present invention provides a kind of crosshead type large two-stroke diesel engine, and described crosshead type large two-stroke diesel engine has can be with the hydraulic pressure exhaust valve actuating system of multiple hydraulic fluid operation.
This purpose realizes by a kind of crosshead type large two-stroke diesel engine is provided according to claim 41, described crosshead type large two-stroke diesel engine comprises: the crankcase support, and it supports bent axle and the cylinder support that is installed on the described crankcase support; A plurality of cylinders, it is by described cylinder bracket supports, and each cylinder is provided with at least one fuel injector and at least one exhaust valve; The hydrovalve actuator that is associated with each described exhaust valve; Common fuel rail, it has one or more accumulators that are connected thereto; High pressure fuel pump, it under high pressure supplies fuel to described common fuel rail; Be used for fuel is transported to supply line and control valve unit respective injectors, that be associated with each cylinder from described common rail; Be used for fuel is transported to supply line and control valve unit the respective hydraulic valves actuator, that be associated with each cylinder from described common rail; With the heating reflux line, be used for fuel is sent to fuel tank or is sent to the pipeline of the inlet that leads to described high-pressure service pump from described hydrovalve actuator.
Thereby, have low viscous HFO and can be used as hydraulic medium.
Another object of the present invention provides a kind of crosshead type large two-stroke diesel engine, and described crosshead type large two-stroke diesel engine has the hydraulic pressure exhaust valve actuating system that can move in big temperature range.
This purpose realizes by a kind of crosshead type large two-stroke diesel engine is provided according to claim 48, described crosshead type large two-stroke diesel engine comprises: the crankcase support, and it supports bent axle and the cylinder support that is installed on the described crankcase support; A plurality of cylinders, it is by described cylinder bracket supports, and each cylinder is provided with at least one fuel injector and at least one exhaust valve; The hydrovalve actuator that is associated with each described exhaust valve; Common fuel rail, it has one or more accumulators that are connected thereto; High pressure fuel pump, it under high pressure supplies fuel to described common fuel rail; Be associated with each cylinder, be used for fuel is transported to corresponding injector pressure pipeline and control valve unit from described common rail; The supply line and the control valve unit that are used for fuel is transported to from described common rail the respective hydraulic valves actuator that are associated with each cylinder; And reflux line, be used for fuel is sent to fuel tank or is sent to the pipeline of the inlet that leads to described high-pressure service pump from described hydrovalve actuator, wherein at least one described pipeline comprises the device that is used to eliminate the influence that line size that the variation owing to running temperature produces changes.
Thereby described hydraulic system can be moved and guarantee can not produce mechanical stress owing to the dimensional changes that temperature causes in big temperature range.
Another object of the present invention provides a kind of new purposes of Proportional valve.
This purpose realizes that by a kind of purposes that Proportional valve is provided according to claim 51 it is used for controlling common fuel pipeline the flowing to fuel injector and/or operating fuel parts of fuel from crosshead type large two-stroke diesel engine.
Another object of the present invention provides a kind of electrical control valve, is used to control common fuel pipeline the flowing to one or more operating fuels or fuel consumption engine components of fuel from crosshead type large two-stroke diesel engine.
This purpose realizes by a kind of electrical control valve is provided according to claim 54, described electrical control valve is used to control common fuel pipeline the flowing to one or more operating fuels or fuel consumption engine components of fuel from crosshead type large two-stroke diesel engine, this electrical control valve comprises valve body and electromagnet (solenoid), described thus electromagnet and described valve body thermal insulation.
Another object of the present invention provides a kind of crosshead type large two-stroke diesel engine, and described crosshead type large two-stroke diesel engine has improved hydraulic system circulation when motor stops.
This purpose realizes by a kind of crosshead type large two-stroke diesel engine is provided according to claim 58, described crosshead type large two-stroke diesel engine comprises: the crankcase support, and it supports bent axle and the cylinder support that is installed on the described crankcase support; A plurality of cylinders, it is by described cylinder bracket supports, and each cylinder is provided with at least one fuel injector and at least one exhaust valve; Common fuel rail; And high pressure fuel pump, it under high pressure supplies fuel to described common fuel rail at the motor run duration; The supply line and the control valve unit that are associated with each cylinder, be used for fuel is transported to from described common rail respective injectors; Described high pressure fuel pump is mechanically driven by described bent axle and is electrically driven by electric motor at the motor stopping period at the motor run duration, circulates under low pressure to make fuel pass described supply line and/or described common rail and/or pass with other engine components of operating fuel.
By using high-pressure service pump to provide circulation as high-voltage power supply and low pressure source at the motor stopping period, part count is reduced, thereby makes unitary construction and maintenance cost have more competitiveness.
Another object of the present invention provides a kind of hydraulic actuating scavenging air valve, and it is used to have the internal-combustion engine of the pneumatic spring of improvement.
This purpose realizes that by a kind of hydraulic actuating scavenging air valve that is used for internal-combustion engine is provided according to claim 63 described hydraulic actuating scavenging air valve comprises: static valve body; Scavenging air valve, it can move between the position take one's seat position and non-taking one's seat, and comprises microscler valve rod, and this microscler valve rod one end has valve head, has free terminal on the opposite end; Hydraulic actuator, described hydraulic actuator comprises the piston on the free terminal that acts on described valve rod, is used for when described hydraulic actuator is supplied with pressurized hydraulic fluid described valve urged the non-position of taking one's seat; Pneumatic spring, it urges the described position of taking one's seat with described valve, and described pneumatic spring comprises: cylinder, it is fixed to described valve rod, and described cylinder is sealing on the direction of the free terminal of described valve rod, is opening wide on the direction of described valve head; And the stationary piston of coupling, it is contained in the described cylinder, and described piston is fixed to described valve body and is formed for the spring housing of described pneumatic spring with described cylinder.
The structure of described pneumatic spring has reduced the chance that the hydraulic medium that comes from described actuator enters described spring housing.
Another object of the present invention provides a kind of improvement hydraulic actuating scavenging air valve that is used for internal-combustion engine.
This purpose realizes that by a kind of hydraulic actuating scavenging air valve that is used for internal-combustion engine is provided according to claim 66 described hydraulic actuating scavenging air valve comprises: static valve body; Scavenging air valve, it can move between the position non-the taking one's seat that take one's seat position and described valve that described valve cuts out are opened, and comprises microscler valve rod, and this microscler valve rod one end has valve head, has free terminal on the opposite end; Hydraulic actuator, described hydraulic actuator comprises the piston on the free terminal that acts on described valve rod, is used for when described hydraulic actuator is supplied with pressurized hydraulic fluid described valve urged the non-position of taking one's seat; Pneumatic spring, it urges the described position of taking one's seat with described valve, and wherein said valve is determined by the reverse equilibrium of forces of described hydraulic actuator and described pneumatic spring in the described running length of opening on the direction.
Thereby described actuator need not be provided with the end of travel snubber at the described end of opening stroke, and need be in the described terminal supply of cutoff high hydraulic fluid suddenly of opening stroke.The end of travel snubber is not set has reduced mechanical load and vibration, not rapid simultaneously cutoff high hydraulic fluid has been avoided the potential destructive hydraulic shock ripple that has.
Another object of the present invention provides a kind of hydraulic actuator that is used for the Gas Exchange Process of Internal Combustion Engine valve, and it can accurately operation in big temperature range.
This purpose realizes by a kind of hydraulic actuator that is used for the Gas Exchange Process of Internal Combustion Engine valve is provided according to claim 69, described hydraulic actuator comprises: static cylinder, the far-end that it has near-end and opens wide, and comprise and can alternately be connected to source of high pressure hydraulic fluid or be connected to the pressure chamber of reflux pipeline via control valve unit; Piston, it has the near-end that is contained in the described main pressure chamber and acts on far-end on the free terminal of valve rod of described valve, when being used for being connected to described source of high pressure hydraulic fluid described valve is urged the non-position of taking one's seat in described pressure chamber, described piston comprises first portion and second portion, described first portion from described far-end towards described proximal extension, and described second portion is arranged on described proximal end, described second portion slidably engages described first portion, thereby forms the compensated chamber between described first portion and the described second portion; Spring assembly, it urges described first portion and second portion makes it away from each other, thereby described compensated chamber is enlarged; First flow path, it is between described compensated chamber and described pressure chamber, described first flow path is only opened when described second portion is positioned at the little axial range of being scheduled in the proximal end of described cylinder, discharges from described compensated chamber to allow excessive hydraulic fluid; Second flow path, it is between described compensated chamber and described pressure chamber, and described second flow path allows described compensated chamber to refill under the effect of described spring assembly.
Described compensated chamber guarantees that described actuator piston always starts the position in axial range, and this causes turning back to suitable position, and wherein said valve head accurately is positioned on the described valve seat.Position in the axial range depends on that described compensated chamber is during opening or in the Volume Changes of down periods.These Volume Changes can be positive or negative during two parts of described circuit.
Another object of the present invention provides a kind of hydraulic actuator that is used for the Gas Exchange Process of Internal Combustion Engine valve, described hydraulic actuator can overcome the big reaction force when beginning in the opening procedure, and, the in check power of conveying on the direction will opened in case described scavenging air valve is opened.
This purpose realizes by a kind of hydraulic actuator that is used for the Gas Exchange Process of Internal Combustion Engine valve is provided according to claim 74, described hydraulic actuator comprises: static cylinder, and it comprises the pressure chamber that can alternately be connected to source of high pressure hydraulic fluid via first opening in the described cylinder or be connected to reflux pipeline; Piston, it is contained in the described pressure chamber and the valve rod that acts on described valve freely on the end, when being used for being connected to described source of high pressure hydraulic fluid described valve is urged the non-position of taking one's seat in described pressure chamber, described piston can axially move between the extended position that extended position that described valve is taken one's seat and described valve are opened, described piston has first useful area, when described piston is between described retracted position and predetermined neutral position, described pressurized hydraulic fluid in the described pressure chamber acts on described first useful area and urges described piston towards described extended position, described piston has second useful area less than described first useful area, when described piston was between described neutral position and described extended position, the described pressurized hydraulic fluid in the described pressure chamber acted on described second useful area and urges described piston towards described extended position.
The acting in conjunction of described first and second effective piston areas, be that the total area by the effect of described high pressure pressure fluid of described piston makes the big actuation force of generation during the first portion that opens motion of described scavenging air valve, and the effect of described second effective piston area has been carried out good control at the remaining part of opening motion of described scavenging air valve individually.
By following detailed description, other purpose, feature, advantage and the characteristic of described large-scale two-stroke diesel engine and operating method thereof will become more obvious.
Description of drawings
In following detailed description part of the present invention, the illustrative embodiments that illustrates with reference to the accompanying drawings illustrates in greater detail the present invention, wherein
Fig. 1 illustrates the plan view of cylinder profile in two stroke crosshead engines with cylinder head,
Fig. 2 illustrates the cross-sectional view of the cylinder profile in the motor shown in Figure 1,
Fig. 3 is the schematic representation of hydraulic pressure shown in Fig. 1 and lubrication system,
Fig. 4 is another mode of execution of the schematic representation of hydraulic pressure shown in Fig. 3 and lubrication system,
Fig. 5 illustrates the cross-sectional view of pressure tube used herein,
Fig. 6 is another cross-sectional view, and alternative pressure tube used herein is shown,
Fig. 7 is the longitdinal cross-section diagram of first mode of execution of the hydraulic braking formula exhaust valve of cylinder among Fig. 2, wherein valve take one's seat and piston at its retracted position,
Fig. 8 illustrates the typical opening curves according to exhaust valve actuator of the present invention,
Fig. 9 illustrates the cross-sectional view of actuator shown in Figure 7 with bigger ratio, and wherein piston is positioned at the position that part is extended,
Figure 10 illustrates the view same with Fig. 9, and wherein piston is positioned at the extreme higher position at retracted position and piston cap in its axial range,
Figure 11 is the detailed view on the top of actuator, and wherein piston roughly is in a retracted position and piston cap roughly is in the extreme higher position of its axial range,
Figure 12 is the detailed view on the top of actuator, wherein piston be in a retracted position and piston cap roughly be in its axial range extreme lower position and
Figure 13 is the detailed view on the top of actuator, and wherein piston is in a retracted position and piston cap roughly is in the neutral position of its axial range.
Embodiment
Fig. 1 illustrates according to motor 1 of the present invention.This motor is low speed two stroke cross-head diesel engines, and it can be propelling motor in the boats and ships or the prime mover in the power plant.These motors have 6 to 16 cylinder in lines usually.This motor is made the base 2 with the main bearing that is used for bent axle 3.This base is divided into the part with suitable dimension according to available manufacturing equipment.The A type crankcase support 4 of Welding Design formula is installed on the described base.Cylinder support 5 is installed on the top of crankcase support 5.The stretching screw (not shown) is connected to the cylinder support with base and described structure is kept together.Cylinder 6 is by 5 carryings of cylinder support.
Fig. 2 illustrates the cylinder 6 of internal-combustion engine.Cylinder 6 is for the type of one-way flow and have the relief opening 7 that is arranged in air tank 8, and this air tank is provided with waste gas by turbosupercharger 10 (Fig. 1) supercharging from waste gas reception unit 9 (Fig. 1).Unshowned crosshead couples together piston rod 14 and bent axle 3 (Fig. 1).
Exhaust valve 11 medially is installed on the top of cylinder in cylinder head 12.In the latter stage of expansion stroke, exhaust valve 11 is opened through before the exhaust outlet 7 downwards at engine piston 13, thus, the combustion gas in the firing chamber on the piston 13 flow out by the exhaust passage 16 of leading to waste gas reception unit 17, and the pressure in the firing chamber 15 discharges.Exhaust valve 11 cuts out once more in adjustable moment during piston 13 moves upward, and this moment can for example be depended on the needed effective compression ratio of burning subsequently.During this closing movement, exhaust valve is upwards driven by pneumatic spring 18.
Consider the durability of valve 11 and consider favourable, accurate control, and then consider the efficient of motor, can advantageously very accurately control exhaust valve 11 state in the firing chamber.
Exhaust valve 11 is opened by hydraulic driving actuator 19.Hydraulic fluid (fuel) is by pressure piping 20 supply, and this pressure piping is connected to the inlet on the actuator 19 in the control mouth on the upper surface of the allocation block 21 that is supported by operating console 22.Reflux line 43 is connected to the outlet on the actuator 19 refluxing opening on the upper surface of allocation block 21.
Each cylinder 6 is provided with two or three spargers 23 (only illustrating) that connected by the circulating line (not shown).Fuel is fed to sparger 23 from allocation block 21 via service 24.Sparger 23 is connected to refluxing opening on the allocation block 21 via reflux line 49.
Operating console 22 is connected to the reflux line that leads to supply line and is connected to common fuel rail (being 40 among Fig. 3, not shown among Fig. 2).
Being connected of common fuel rail 40 (Fig. 3) (not shown) in the allocation block 21 carrying proportional control valves 25, the mouth on proportional control valve 25 control allocation blocks 21 tops and reflux line (being 43 among Fig. 3) and operating console 22.
In operating console 22, pressurized hydraulic fluid is sent to inlet on the proportional control valve 25 from the passage 41 (Fig. 3) of common fuel rail 40 branches.
Fuel in the common fuel rail 40 (Fig. 3) comes driven valve actuators 19 and gives sparger 23 fuel supplying as hydraulic fluid.Pressure in the common rail 40 changes according to the running state of the motor 1 of for example motion speed and loading condition.Typically, the pressure in the common fuel rail 40 clings between 2000 crust 600 and changes.
Each cylinder 5 of motor 1 is associated with electronic control unit 26, and this electronic control unit receives total synchronous and control signal by cable 27, in addition, also by cable 28 electronic control signal is sent to proportional control valve 25.Can be provided with a control unit 26 for each cylinder, perhaps several cylinders are associated with same control unit (not shown).Control unit 26 also can be from the shared overall control unit (not shown) received signal of all cylinders.
With reference to Fig. 3, show the hydraulic system and the lubrication system of motor 1 with the form of block diagram.Hydraulic system is as fuel injection system and as exhaust valve actuating system.
Lubrication system comprises lubricating oil tank, filter and electric driving low pressure pump.Lubrication system is separated fully with hydraulic system.
Hydraulic system is with operating fuel, typically is HFO (water and milkization with not emulsification of water).The frequent emulsification of water is in HFO, to reduce the NOx discharging.This emulsification occurs in (not shown) in the independent emulsification unit.The fuel reservoir that is used for the motor operation is at heating cabinet 29.The fuel that uses is commonly called heavy fuel oil (HFO), and its viscosity in the time of 50 ℃ is 500-700cSt, and at room temperature can not flow.HFO in the case is maintained at about 50 ℃ if having time in institute basically, also is like this at the motor stopping period promptly.Typically, the steamer with such motor is provided with generator set (Genset), and the miniature diesel engine of electric power and heat promptly is provided to steamer and master motor at the master motor stopping period.
HFO leads to filter or centrifuge 30 from heating cabinet, and leads to preheater 31.The temperature of controlling the HFO that leaves preheater 31 according to running state and the grade of HFO.At the motor stopping period, when HFO circulated with low pressure in hydraulic system, the temperature of HFO remained in 45-60 ℃ the scope.At the motor run duration,, the temperature of leaving the HFO of preheater 31 is remained between 90-150 ℃ according to the viscosity of HFO.The measurement of sensor (not shown) is close to the viscosity of HFO of the downstream part (or other correct position) of preheater 31.The temperature of leaving the HFO of preheater 31 typically is controlled as and makes in the scope of viscosity at 10-20cSt of measurement point.
Shape intermediate conduit 32 is connected to high pressure fuel pump 33 and auxiliary low pressure circulation pump 34 with preheater again.Pipe downstream at each pump is provided with safety check 35, to prevent back suction.
At the motor run duration, high pressure fuel pump 33 is driven via gear 37 by the gear on the bent axle 3 33.Thereby high pressure fuel pump 33 produces the rated pressure of 1000-1500 crust, but this pressure can be according to operating conditions fluctuation between the 600-2000 crust.
At the motor stopping period, auxiliary low pressure circulation pump 34 is driven by electric motor 38.Thus, transmit the pressure of about 3-10 crust, in hydraulic system, to circulate at motor withholding period chien shih HFO.
Common fuel rail 40 is extended along all cylinders, and with Fig. 3 in represent being connected of unshowned cylinder 6 by the short vertical curve that stretches out from this common rail.
Cylinder 6 shown in Fig. 3 is provided with HFO by supply line 41, and supply line 41 is from common rail 40 branches and lead to the inlet of proportional control valve 25.Supply line 41 is provided with a plurality of fluidic accumulators 42, and it carries most of fluid when proportional control valve 25 is opened, and supplies with (post-feed) from common rail 40 backs when proportional control valve 25 cuts out.
Pressure piping 20 is with an inlet that is connected to hydraulic actuator 19 in two outlets of proportional control valve 25.Service 24 is connected to sparger 23 with in these two outlets another.Two control mouthful is connected to corresponding exhaust port on the upper surface of allocation block by the passage in the allocation block on the proportional control valve 25.Proportional control valve 25 also has two outlets, is connected to the reflux line 43 of the hydraulic fluid (HFO) that was used for.
Proportional control valve 25 is the Electromagnetic Drive servovalves with three positions.Electromagnet 44 receives control signal via electric wire 28 from control unit 26 (Fig. 2).Electromagnet 44 is installed to the housing of proportional control valve 25, is provided with ceramic plate 45 therebetween, so that electromagnet 44 and proportional control valve 25 thermal insulation, proportional control valve 25 may reach at the motor run duration and surpass 150 ℃ temperature.This structure prevents that responsive electromagnet 44 is overheated.According to another mode of execution (not shown), electromagnet 44 is connected to valve body by heat insulating washer.
At middle position, wherein electromagnet 44 is inoperative, two inlet sealings of proportional control valve 25, and two outlets of proportional control valve 25 are connected to reflux line 43.When shifting left side (left side among Fig. 3) onto when the electromagnet startup and with guiding valve (valve spool), the inlet of proportional control valve is connected to pressure piping 20, and high pressure HFO is sent to this pressure piping 20, makes actuator 19 open exhaust valve 11.In this position, service 24 is connected to reflux line 43.When shifting right side (right side among Fig. 3) onto when electromagnet 44 startups and with guiding valve, the inlet of proportional control valve 25 is connected to service 24, and high pressure HFO is sent to this service 24, makes sparger 23 inject fuel in the firing chamber 15.In this position, pressure piping 20 is connected to reflux line 43.The shape of the volume of fuel injection timing, institute's burner oil and injection scheme (injectionpattern) is by proportional valve control.According to another preferred implementation, (unshowned) fuel flowing from the common fuel rail to the sparger controlled by close/open valve.This close/open valve can be the mobile valve of the controlling valve independently mutually that goes out hydraulic actuator with the convection current influent stream.
The mobile independently valve of controlling that the convection current influent stream goes out actuator can also be a close/open valve.
Traditional fuel limiter 46 is placed in the pressure piping 24, when long-time, avoids excessive HFO to enter cylinder to open mistakenly at proportional control valve.
Pressure in the reflux pipeline 43 keeps the several crust of overvoltage, avoiding air penetration in hydraulic system, and prevents that the water among the water transfer emulsification HFO from forming steam bubble.Guarantee that at the pressure controlled valve 47 at reflux line 43 downstream end places the minimized overvoltage of being scheduled to remains in the reflux line 43.Overvoltage in the reflux line 43 is preferably the 3-10 crust.Accumulator or expansion tank 48 are connected to reflux line 43, to be absorbed in the pressure surge that may occur when proportional control valve 25 changes the position.
Second reflux line 49 is connected to reflux line 43 with the outlet of sparger 23.At the downstream part of pressure controlled valve 47, reflux line 43 will supply to preheater 31 with the HFO that crosses, to finish this circulation.
HFO is sent to common rail 40 and is provided with the heating equipment of being represented by the heating coil shown in Fig. 3 from common rail 40 via the pipeline that proportional control valve 25 is sent to hydrovalve actuator 19 and sparger 23 from the outlet of preheater 31.This pipeline can for example be heated by steam tracing or by electrical heating elements on its total length.The HFO that the heating of these pipelines is used to reduce heat is the heat loss when mobile downstream from preheater.At the motor run duration, remain near 150 ℃ towards the temperature of the ducted HFO of sparger and hydrovalve actuator, yet this depends on the viscosity of the HFO that uses.The adjacent channel that extends in parallel on the part of its length for example pressure piping 20 and service 24 can be provided with shared heating equipment (not shown).
Reflux pipeline 43 and 49 also is provided with the heating equipment of same-type as mentioned above.The temperature of HFO is so crucial in reflux pipeline, and heating equipment is adjusted to the temperature of guaranteeing HFO and can be lower than 50 ℃.
At the motor stopping period, HFO enters hydraulic system to avoid air, and avoids local cooling of HFO and sclerosis under the effect of recycle pump 34 and pass hydraulic system circulation (with the lower pressure of 3-10 crust).At the motor stopping period, the temperature of leaving the oil of preheater 31 is set in and is about 50 ℃, solidifies to avoid HFO.
At circulation period, in order not only to arrive sparger 23 but also arrive hydraulic actuator 19, proportional control valve periodic variation position.According to another mode of execution, this proportional control valve is provided with the 4th bypass position (not shown).In this position, proportional control valve leads to sparger and hydrovalve actuator simultaneously.According to another one mode of execution (not shown), independent by-pass valve is set, it allows HFO side by side to flow to sparger and hydrovalve actuator from common rail.
Heated pressure pipeline 20 is provided with device, so that this pipeline can move in about 150 ℃ temperature range of motor run duration from 50 ℃ of circulation period.Stop and after the temperature of HFO was elevated to about 150 ℃ from about 50 ℃, thermal expansion made the length of pressure piping 20 increase at motor, vice versa.
As shown in Figure 5, pressure piping 20 is provided with one or more U-shaped parts 50, the difference of length when it can be absorbed in different running temperature by the flexibility of U-shaped part.Alternately, perhaps combine, need can between two carriages 51 and 52, axially freely overhang in the part of the pressure piping 20 that moves under low temperature and the high temperature and other pipeline, as shown in Figure 6.Each carriage comprises lining 53, holds an end of pressure piping 20 in the lining 53, makes that pressure piping 20 is fixing diametrically but is removable in the axial direction.By cast iron, steel, polytetrafluoroethylene (PTFE), fluorine rubber, (FPM), copolymer (NBR), nitrite rubber, poly-(dimethyl siloxane) (SI) or similar material O shape circle 54 or the similar packing ring made guarantee sealing airtight basically between pipe end and the lining.The pressure that is applied on two relative free ends of pipeline 20 balances each other.The axial variation of pipeline 20 length is absorbed by its axial pipe end that freely overhangs.
Packing ring in the hydraulic system from cast iron, steel, polytetrafluoroethylene (PTFE), fluorine rubber, (FPM), copolymer (NBR), nitrite rubber, poly-(dimethyl siloxane) (SI), select its mixture or the similar material, with sealing airtight basically between the parts of guaranteeing hydraulic system.Concrete packing ring is described with reference to Fig. 9 below.
Fig. 4 shows another preferred implementation of hydraulic system.This mode of execution is identical with the mode of execution shown in Fig. 3 basically, yet high-pressure service pump 33 also is used as the low pressure pump that makes the HFO circulation at the motor stopping period.Here, the clutch 56 by central unit control is arranged between gear 37 and the high-pressure service pump 33.At the motor run duration, clutch 56 engages, and high-pressure service pump 33 is driven by bent axle 3.At the motor stopping period, clutch 56 is disengaged.Another clutch 55 by central unit control is arranged between high-pressure service pump 33 and the electric motor 38 '.Clutch 55 is disengaged at the motor run duration, engages at the motor stopping period.Electric motor 38 ' drives high-pressure service pump 33 at the motor stopping period, but more much lower than its motion speed at the motor run duration, is used for the pressure circulation of HFO with the 3-10 crust so that enough hydraulic pressures to be provided.
Describe the preferred implementation of actuator 19 and pneumatic spring 18 below in detail with reference to Fig. 7-11.
Exhaust valve 11 has the bar 57 that extends straight up from valve head 58, and the upper end of bar 57 supports the cylinder 59 that firmly is installed on the valve rod 57, thereby forms wiper seal and vertically can move on stationary piston 60.Stationary piston 60 is parts of spring housing 61.Have the spring housing 62 that is connected to forced air feeding mechanism (not shown) on stationary piston 60, this forced air feeding mechanism keeps spring housing 62 to fill with for example forced air of the predetermined minimum pressure of 4.5 crust overvoltages.Also can use other air pressure, for example the 3-10 crust.Pressure minimum is selected according to the required elastic characteristic of pneumatic spring.Can the spring housing on a plurality of different cylinders is interconnected, but preferably, each spring housing is cut off individually by the safety check 63 at forced air feeding mechanism place.Forced air in the spring housing 62 produces the power that makes progress that continues on cylinder 59.Should power upwards when moving down, cylinder 59 increase, and the air in the extrusion spring chamber 62, safety check 63 prevents that the air in the spring housing 62 from flowing out.
Spring housing 61 defines around pneumatic spring 18 and chamber 64 thereon, position.Chamber 64 is connected to discharge portion 65, makes this chamber have barometric pressure.Any oil that leaks from actuator 19 will enter chamber 64, and discharge via discharge portion 65.This spring is configured such that leaking oil is difficult to enter spring housing 62, because cylinder 59 forms umbrella, it forces and leaks the bottom that oil flows through and arrive chamber 64 thereon downwards, and can not have the risk that enters spring housing 62.This is very important, because when leakage oil is attempted to pass even further entered pneumatic system, leaks oily (HFO) and can assemble and sclerosis or obstruction Pneumatic pipe in spring housing.
With reference to Fig. 7 and 9, hydrovalve actuator 19 is by cylinder 66 structures, and this cylinder is by the top braces of housing 61.Piston 67 is contained in the central hole of cylinder 66.This central hole seals at the place, top of cylinder 66, and opens wide at the place, bottom of cylinder 66.Hole 68 in this central hole and the housing 61 is provided with coaxially.(closely) end of going up of piston 67 is contained in this central hole, and the far-end of piston 67 acts on the top of valve rod 57.
Main pressure chamber 69 limits between the top of cylinder 66 and piston 67.Hydraulic fluid (HFO) is supplied to the hydrovalve actuator via opening 70 and discharges from the hydrovalve actuator.Opening 70 is passed into intermediate pressure chamber 71, this intermediate pressure chamber be arranged under the main pressure chamber 69 and be defined in cylinder 66 and the intermediate portion of piston 67 between.Opening 70 is by proportional control valve control and alternately be connected to pressure piping 20 and reflux line 43, and this proportional control valve is exemplarily illustrated as close/open valve 25 ' in this view, although also usage ratio valve alternatively.Aux. pressure chamber 73 is defined between the respective diameters enlarged portion of the enlarged diameter part 74 of piston 67 and central hole.Alternatively, packing ring 68 ' can be arranged between enlarged diameter part 74 and the cylinder 66, with the amount of the leakage oil that reduces to enter chamber 64.During the first portion that opens stroke of hydraulic actuator 19, the axial passage 75 that aux. pressure chamber 73 forms through the recess 75 by piston 67 is provided with the high pressure HFO from medial compartment 71.During opening stroke, close by the control flange 76 on the cylinder 67 at predetermined neutral position axial passage 75.Simultaneously, opening 77 is connected to reflux pipeline 43 with aux. pressure chamber 73, because the top edge of enlarged diameter part 74 is positioned under the top edge of opening 77 now.Thereby enlarged diameter part 74 helps to overcome during the first portion that opens stroke of hydraulic actuator 19 by the pressure in the firing chamber 15 and is applied to bigger power on the valve head 58.In the predetermined neutral position of piston 67, the supply discontinuity of arriving the high-pressure liquid of ancillary chamber 73, and this aux. pressure chamber is via opening 77 emptyings.Pressure in the firing chamber 15 descends now, and no longer needs the effect of enlarged diameter part 74.
Fig. 8 shows the typical opening curves figure of exhaust valve.In Phase I, the beginning section of opening motion need obtain bigger power from hydraulic actuator 19, overcoming the pressure in the firing chamber 15, and is used to make heavier exhaust valve 11 to quicken.In this stage, hydraulic actuator 19 must provide maximum power.Yet, should avoid the hydraulic shock ripple that produces owing to opening fast of control valve 25 or 25 '.In Phase, exhaust valve 11 arrives the position of opening fully, and in this stage, and exhaust valve 11 should be little by little slack-off and stop, and preferably, can not abut against each other with other object.In Phase I, the return movement of exhaust valve 11 should gently begin, the hydraulic pressure ripple that should avoid the rapid opening and closing owing to control valve 25 or 25 ' to cause.In Phase IV latter stage, it is the most key that valve head 58 drops on the valve seat gradually and accurately, because metal object will abut against each other.Thereby crucial is that exhaust valve 11 and piston 67 are little by little slack-off, thereby huge accelerating force is minimized, and avoid valve head to impinge upon on the valve seat.Exhaust valve 11 suitable opening curves can obtain in many ways according to the present invention.A kind of mode is the simple hydraulic actuator that is used for exhaust valve by use, for example the oil hydraulic cylinder (not shown) combines with the suitable control of proportional control valve, thereby makes the opening degree of exclusiveness basically of proportional control valve guarantee to be used to obtain suitable opening curves by suitable power and resistance that actuator is applied on the exhaust valve.Another kind method is by using hydraulic actuator described herein and valve spring, and it has inherent characteristic, makes the suitable opening curves that is used for exhaust valve to obtain by the ON/OFF control valve.Actuator with inherent characteristic also can combine with Proportional valve.
When exhaust valve will be opened and proportional control valve 25 when high-pressure liquid is fed to opening 70, and make winner pressurized chamber, middle pressurized chamber and the pressurization of auxiliary pressurized chamber.The high pressure hydraulic fluid of main pressurized chamber and auxiliary pressurized chamber makes piston be pressed downward.
Piston 67 (first piston part) is provided with piston cap 78 (second piston portion).The top of piston 67 (near-end) slidably engages piston cap 78, thereby forms compensated chamber 79 between piston 67 and piston cap 78.According to preferred implementation, piston cap 78 is enclosed within on the top of piston 67.Yet piston cap 78 also can be arranged to be engaged in (not shown) in the top of piston 67.Spring 80 urges piston 67 and piston cap 78 makes it away from each other, thereby enlarges compensated chamber 79.First flow path is arranged between compensated chamber 79 and the main pressure chamber 69.First flow path comprises valve member 81, and valve member 81 is engaged in the receiving bore in the top of piston cap 78.Spring 80 upwards urges valve member 81 towards piston cap 78.According to another mode of execution (not shown), independent spring can be set be used for upwards urging piston cap 78 and valve member 81.This power that allows to be applied on arbitrary element can be regulated independently of one another.
Valve member 81 is provided with axial bore 82 and two radial holes 83 and 84, and these holes connect compensated chamber 79 and main pressure chamber 69, unless valve member 81 is positioned at its upper position in receiving bore.At this upper position (Fig. 9 and 12), the wall of opening by receiving bore in hole 84 is stoped, thereby first flow path is closed.First flow path is used for when piston 67 is positioned at its upper position allowing excessive hydraulic fluid 79 to overflow from the compensated chamber, and piston cap 78 is because the amount of hydraulic fluid in the compensated chamber 79 too much is set to the top than needed such more close main pressure chamber 69.(Figure 10 and 11) in this case, valve member 81 be against the end surface of cylinder 66, and valve member 81 moves down with respect to piston cap 78, thereby open first flow path, makes that compensated chamber 79 can emptying, leans against on the valve seat up to valve head 58.Thereby first flow path is only just opened when (closely) end place is positioned at little predetermined axial range on cylinder 66 at piston element.
Second flow path is between compensated chamber 79 and intermediate pressure chamber 71.According to preferred implementation, second flow path is formed by the annulus 85 between piston 67 and the piston cap 78.Because annulus 85 is narrower, second flow path has high relatively flow resistance.Second flow path allows compensated chamber 79 to be filled under the effect of spring 80.The suitable characteristics of the power by selecting to be used for spring 80 and the resistance of flow path 85 obtains the suitable filling rule of compensated chamber.
Air refreshing tube 86 with high flow capacity restriction (flow restriction) is arranged on the top of cylinder 66, and the top of the main pressure chamber 69 that will be formed by dampening chamber 87 is connected to reflux line 43.
Piston cap 78 has the periphery of axial taper, and its diameter increases gradually towards piston head.Tapering part cooperates with inwardly outstanding annular flange flange 88, and annular flange flange 88 is led to the position of central hole at opening 70 and located above lucky and extend from central hole.Tapering part forms narrow annulus 89 with annular flange flange 88, and the size of annulus 89 changes along with position of piston.Hydraulic fluid must pass this annulus 89 and be compressed, thereby flow to main pressure chamber 69 from middle pressure chamber 71.This makes and produces pressure drop between intermediate pressure chamber 71 and the main pressure chamber 69.This pressure drop raises during 89 size decreases in the annulus, and along with flow rate increases and increases gradually, thereby prevent that effectively piston 67 from arriving at a high speed.The size of tapering part makes annulus 89 towards the end of opening stroke and less.Towards the end of described stroke, thereby the speed of piston 67 is restricted effectively, even the supply pressure of hydraulic fluid is than higher.Tapering part is shown in Fig. 9-11, and it has bandy slightly profile, but for example frustum of a cone, aduncate slightly profile, both combining form or the predetermined profile of any needs also are possible to other profile.This profile can pass through test method, computer emulation method or analytical method to be determined, described method representation should have much in each position and flow restriction of stroke, so that valve actuator has optimum dynamic property.Then, can correspondingly construct tapering part.
The downward power of actuator 19 and the power that makes progress of pneumatic spring 18 reach balance at the end to outer stroke, and promptly piston 67 and exhaust valve 11 will self stop owing to them, shown in the Phase of Fig. 8.Neither need the supply of cutoff high HFO, also do not need stroke limiting stop to stop piston and exhaust valve.Because the supply of HFO does not need unexpected cut-out, thereby does not have the hydraulic shock ripple, otherwise, described hydraulic shock ripple will be oppressed whole hydraulic system.Do not have stroke limiting stop, thereby make mechanical load lower with impact.
Being fed to the pressure of HFO of hydraulic actuator 19 and the pressure that is fed to the air of pneumatic spring 18 is controlled as and guarantees that exhaust valve 11 arrives suitable open position.The size of actuator 19 and pneumatic spring 18 is arranged so that they are in the open position reverse power of balance easily.
During near the fully open position, the flow path between the tapering part of flange 88 and piston cap 78 narrows down at piston 67.Narrow slit has damping effect for the motion of piston 67, thereby piston stops at open position, and does not almost have or do not have at all to impact and vibration subsequently.
Piston 67 turns back to retracted position under the effect of pneumatic spring 18.Form with dampening chamber 87 is provided with the end of travel damping to hydraulic actuator 19 at the top of cylinder 66 (at near-end).The size at piston cap 78 tops forms with dampening chamber 87 and cooperates with micro-gap, and when the top of second piston portion 78 is inserted in the dampening chamber, in return stroke, the micro-gap outflow dampening chamber 87 that forms by annulus 90 by forcing hydraulic fluid to pass, thereby absorb most of kinetic energy of piston 67 and exhaust valve 11, and valve head 58 is located on the valve seat gently.
By changing the flow resistance that the flow path between opening 70 and the main pressure chamber 69 is regulated in the design of tapering part at the needed pressure in each position of piston 67 according to main pressure chamber 69.Thereby hydrovalve actuator 19 can cooperate well with the high-voltage power supply with change pressure.Low relatively supply pressure will cause lower valve acceleration.Therefore, electronic control unit 26 changes the timing and the length of valve open continuously, with the variation in pressure in the supply of compensation high pressure hydraulic fluid.When supply pressure is low, electronic control unit 26 will indicate proportional control valve 25 to open and stay open longer a period of time earlier, open long enough to guarantee exhaust valve, to discharge the gas in the firing chamber suitably, and when supply pressure was higher, vice versa.
Cylinder 66 comprises ventilation and recirculation conduit 86, and warm thus hydraulic fluid can pass actuator and circulate and turn back in the reflux line 43.This helps when motor does not move valve being remained on running temperature, and this can also remove air effectively.
The operation of hydrovalve
In the closed position of exhaust valve 11, piston cap 78 residing positions are: its top is positioned at dampening chamber 87 inboards and is positioned at the position range that valve member 81 is allowed.Figure 10 shows the highest possible position of piston cap 87, and wherein first flow path is opened, and Figure 12 shows the minimum possible position of piston cap 78, and wherein valve member 81 is closed.In position range, between the wall of the top of piston cap 78 and dampening chamber 87, always there is a narrow annulus 90.
Exhaust valve 11 is by opening to opening 70 (Figure 10) supply high-pressure medium (HFO or fuel oil) from proportional control valve 25 (according to another mode of execution, for example the valve of other type of close/open valve 25 ' or servovalve can be used in alternative Proportional valve).Thus, hydraulic medium is flowed through annulus 89 and annulus 90 and is entered into main pressure chamber 69 and dampening chamber 87, and forms pressure and urge piston 67 downwards.The hydraulic fluid that flows out from opening 70 also flow into medial compartment 71, and enters into aux. pressure chamber 73 via axial passage 75.Thereby the pressure that acts on the enlarged diameter part 74 has increased the power that urges piston 67 downwards.
When on the piston 67 make a concerted effort to surpass the reaction force of pressure in pneumatic spring 18 and the firing chamber time, exhaust valve 11 begins to open.In the incipient stage of opening motion, pass annulus 90 and enter the restricted mobile low pressure that is formed in the dampening chamber 87 that produced in the dampening chamber 87, thereby the incipient stage of guaranteeing to open motion is level and smooth, does not have rapid acceleration and does not have the hydraulic shock ripple, referring to the Phase I of Fig. 8.
When exhaust valve 11 partially opens, the pressure in the firing chamber 15 and finish exhaust valve 11 and open needed power and obviously descend.In this stage, flowing of hydraulic fluid by being cut to aux. pressure chamber 73 by control flange 76, and simultaneously aux. pressure chamber 73 is connected to reflux line 43 via opening 77 and reduces to act on downward power on the piston 67, to allow to supply to aux. pressure chamber 73 in all the other stages of opening stroke from the hydraulic fluid of reflux line 43, allow the further expansion of aux. pressure chamber 73, thereby avoid in axial passage 75 and in aux. pressure chamber 73, air pocket occurring.
When the opening degree of exhaust valve 11 increased, the circulation area in slit 89 reduced.Thereby the pressure in main pressure chamber 69 and the aux. pressure chamber 79 reduces gradually.Pressure in the pneumatic spring 18 increases gradually simultaneously, thereby the velocity-stabilization ground of exhaust valve 11 reduces, up to form good balance between the power that gentle moving medium applies by hydraulic pressure.Because relative hydrodynamic pressure little by little changes, exhaust valve 11 and piston are decelerated to fully smoothly and stop, and do not have any hydraulic shock ripple and Mechanical Contact, with reference to Fig. 8 Phase.The damping function of the circulation area that sharply reduces by slit 89 reduces near any oscillating movement of exhaust valve 11 fully open position.
During the opening stage of exhaust valve 11, valve member 81 is closed owing to the effect of spring 80 and against the downside of living piston cap 78.The amount that flows into the hydraulic fluid of compensated chamber 79 has guaranteed the predefine position of piston cap 78.The pressure difference between intermediate pressure chamber 71 and the main pressure chamber 69 and the power of spring 80 upwards urge piston cap 78, thereby a spot of hydraulic fluid is inhaled between the compensated chamber 79 via the annulus between piston cap and the piston 85.In the fully open position of exhaust valve 11, the pressure of main pressure chamber 69 and intermediate pressure chamber 71 equates, and has only spring 80 upwards to urge piston cap 78.Exhaust valve 11 open and fully during the opening stage, refilling of compensated chamber 79 makes piston cap 78 upwards move lentamente with respect to piston 67.
Exhaust valve 11 cuts out once more when coupling together in proportional control valve 25 change positions and with opening 70 and reflux line 43.The thrust of pneumatic spring 18 makes hydraulic fluid enter the reflux line 43 via annulus 89 from main pressure chamber 69.Little circulation area in the annulus 89 is guaranteed the soft start of return stroke, and during piston 67 moved upward, it had the stable speed that increases, and this speed is controlled by the stable increase of the circulation area of annulus 89, with reference to Fig. 8 Phase I.Because the pressure in the main pressure chamber 69 is higher than intermediate pressure chamber 71, will make compensated chamber 79 dwindle a little via the discharge of annulus 85.Hydraulic fluid in the aux. pressure chamber 73 is via opening 77 emptyings, and when opening 77 is blocked by enlarged diameter part 74, via axial passage 75, medial compartment 71, opening 70 and Returning pipe 43 emptyings.
In the closing movement final stage, piston cap 78 is inserted in the dampening chamber 87, thereby formed annulus 90 has obviously reduced the available circulation area of hydraulic fluid in the dampening chamber.Hydraulic fluid in the dampening chamber 87 flows out dampening chamber via annulus 90, thereby it is used as braking force on piston 67 by the corresponding increase of pressure in the compensated chamber 79, thereby makes its deceleration, with reference to Fig. 8 Phase IV.In the compensated chamber 79 increase of pressure will make some wherein fluid discharge via annulus 85.Thereby before exhaust valve 11 cut out, the speed that valve head 58 lands on valve seat went up by the circulation area of annulus 90 definite largely.Air refreshing tube 86 and annulus 85 more or less help fluid to flow out from dampening chamber 87.
If it is big that compensated chamber 79 has become during the opening stage of exhaust valve 11 fully, piston cap 78 will occupy to be inserted into it compares higher a little position in the dampening chamber 87.Thus, valve member 81 will be against the end (bottom of dampening chamber) of cylinder 66, and opens first flow path, with emptying compensated chamber 79 (Figure 11), makes piston cap 78 can occupy correct position (Figure 10).
If shrink fully the return stroke compensating during chamber 79 at exhaust valve 11, piston cap 78 will occupy to be inserted into it compares lower a little position in the dampening chamber 87, and valve member 81 will be not against the end (Figure 12) of cylinder.Up to next opening stage; spring 80 just can upwards urge piston cap 78; thereby compensated chamber 79 will admit the amount of hydraulic fluid that flows out via annulus 85, up to the end (Figure 13) of valve member 81 against cylinder 66, and guarantee that piston cap 78 occupies position roughly placed in the middle in its axial range.
Piston cap 78 makes hydraulic actuator 19 automatically compensate owing to move under different temperatures, repair with the operation of compensated chamber's 79 combinations---be the grinding of valve seat and the dimensional changes that foozle produced.Thereby valve head 58 will always softly and accurately land on valve seat.
According to an embodiment of the invention, hydraulic actuator 19 also can be embodied as does not have the compensated chamber as shown in Figure 7.It is not too important motor that this mode of execution can be used for dimensional changes compensation, for example when as the general hydraulic fluid of hydraulic fluid when moving for 30-60 ℃.
Although detailed for illustrative purposes description the present invention, it will be appreciated that these details only are the purposes that is used to explain, those skilled in the art can make version under the situation that does not depart from scope of the present invention.

Claims (79)

1. a crosshead type large two-stroke diesel engine (1), it comprises:
Crankcase support (4), it supports bent axle (3) and is installed in cylinder support (5) on the described crankcase support (4);
A plurality of cylinders (6), it is by described cylinder support (5) supporting, and each cylinder is provided with at least one fuel injector (23) and at least one exhaust valve (11);
The hydrovalve actuator (19) that is associated with each described exhaust valve (11);
Common fuel rail (40), it has one or more accumulators that are connected thereto (42);
High pressure fuel pump (33), it under high pressure supplies fuel to described common fuel rail (40),
Each described sparger (23) is to come from the operating fuel of described common rail (40); And
The Proportional valve (25) that is associated with each cylinder (6),
Described thus Proportional valve (25) control fuel flowing from described common fuel rail (40) to respective injectors (23).
2. motor as claimed in claim 1, wherein the shape of the volume of fuel injection timing, institute's burner oil and injection scheme is controlled by described Proportional valve (25).
3. motor as claimed in claim 1 or 2, wherein said actuator (19) is operatively connected to described common fuel rail (40).
4. motor as claimed in claim 3, wherein control valve (25 is arranged for each described cylinder (6), 25 ') associated, described control valve (25,25 ') control fuel flowing from described common fuel rail (40) to respective hydraulic valves actuator (19).
5. motor as claimed in claim 4, wherein said control valve (25 ') are close/open valve.
6. motor as claimed in claim 4, wherein said control valve are Proportional valve (25).
7. as claim 5 or 6 described motors, wherein said Proportional valve and described control valve are combined into an integral valve with single guiding valve (25).
8. motor as claimed in claim 7, wherein said integral valve (25) comprise valve body and are used to control the electromagnet (44) of described guiding valve, described thus electromagnet (44) and described valve body thermal insulation.
9. motor as claimed in claim 8 wherein is provided with layer of insulation material (45) between described electromagnet (44) and described valve body.
10. a crosshead type large two-stroke diesel engine (1), it comprises:
Crankcase support (4), it supports bent axle (3) and is installed in cylinder support (5) on the described crankcase support;
A plurality of cylinders (6), it is by described cylinder support (5) supporting, and each cylinder is provided with at least one fuel injector (23) and at least one exhaust valve (11);
The hydrovalve actuator (19) that is associated with each described exhaust valve (11);
Common fuel rail (40), it has one or more accumulators that are connected thereto (42);
High pressure fuel pump (33), it under high pressure supplies fuel to described common fuel rail (40),
Each described sparger (23) is to come from the operating fuel of described common rail (40); And
The proportional control valve (25) that is associated with each cylinder (6),
Described thus proportional control valve (25) control fuel flowing from described common fuel rail (40) to respective hydraulic valves actuator (19).
11. motor as claimed in claim 10, the opening degree of the opening and closing timing of wherein said exhaust valve (11) and described exhaust valve (11) is controlled by corresponding proportion control valve (25).
12. as claim 10 or 11 described motors, the opening and closing curve of wherein said exhaust valve (11) is determined by the characteristic of described hydrovalve actuator (19) substantially.
13. as claim 10 or 11 described motors, the opening and closing curve of wherein said exhaust valve (11) is determined by described Proportional valve (25) substantially.
14. as each described motor in the claim 10 to 12, wherein described proportional control valve (25) operates to as close/open valve when the described hydrovalve actuator of control (19).
15. as each described motor in the claim 10 to 14, wherein fuel flowing from described common fuel rail (40) to described sparger (23) controlled by close/open valve (25 ').
16. as each described motor in the claim 10 to 14, wherein fuel flowing from described common fuel rail (40) to described sparger (23) controlled by Proportional valve (25).
17. as claim 15 or 16 described motors, wherein said proportional control valve (25) and being used to is controlled fuel to the described valve that flows of described sparger (23) and is combined into the integral valve (25) that has single guiding valve.
18. a crosshead type large two-stroke diesel engine (1), it comprises:
Crankcase support (4), it supports bent axle (3) and is installed in cylinder support (5) on the described crankcase support;
A plurality of cylinders (6), it is by described cylinder support (5) supporting, and each cylinder is provided with at least one fuel injector (23) and at least one exhaust valve (11);
The hydrovalve actuator (19) that is associated with each described exhaust valve (11);
Common fuel rail (40), it has one or more accumulators that are connected thereto (42);
High pressure fuel pump (33), it under high pressure supplies fuel to described common fuel rail,
Each described sparger (23) to be coming from the operating fuel of described common rail (40),
Described hydrovalve actuator (19) is connected to described common rail (40) via corresponding pressure piping (20), and wherein said pressure piping is provided with heating equipment.
19. motor as claimed in claim 18, wherein, when described motor (1) moves, enter in the scope of temperature between 90 ℃ and 150 ℃ of fuel of the supply line that leads to described common rail (40), and described heating equipment reduces the thermal losses of described fuel in described supply line at least.
20. as claim 18 or 19 described motors, wherein, when fuel at described motor stopping period circulation time, enter in the scope of temperature between 40 ℃ and 70 ℃ of fuel of described supply line, and described heating equipment reduces the thermal losses of described fuel in described pressure piping (20) at least.
21. as each described motor in the claim 18 to 20, wherein said motor also comprises reflux line (43), be used for fuel is sent to fuel tank (29) or is sent to the pipeline that leads to described high-pressure service pump (33) inlet side from described hydrovalve actuator (19), wherein said reflux line (43) is provided with heating equipment.
22. as each described motor in the claim 18 to 21, wherein said heating equipment is an electric.
23. as each described motor in the claim 18 to 22, wherein said heating equipment is a steam-type.
24. as each described motor in the claim 18 to 23, wherein said heating equipment is configured to also move when described motor stops.
25., also be arranged on described motor (1) and make described fuel pass described supply line and/or reflux line and/or pressure piping when stopping and the device (34,38 ', 55,56) that circulating as each described motor in the claim 18 to 24.
26. motor as claimed in claim 25, also be provided with described motor (1) make when stopping described fuel pass described pipeline (24) and with described common fuel rail (40) be connected to described sparger (23) other hydraulic unit (25,25 ') and the circulation device.
27. motor as claimed in claim 26, wherein said motor (1) comprises whole Proportional valve (25), this proportional valve control fuel is to described hydrovalve actuator (19) with to the flowing of described sparger (23), and wherein said fuel is in the one or more realizations in the following step of flowing through of motor stopping period:
Periodically open flowing to described sparger (23) or described hydrovalve actuator (19), or
Proportional valve (25) for described integral body provides bypass position, and wherein said Proportional valve (19) side by side leads to described sparger (23) and described hydrovalve actuator (19), or
Independent by-pass valve is provided, and described by-pass valve allows fuel side by side to flow to described sparger (23) and described hydrovalve actuator (19) from described common rail (40).
28. as each described motor in the claim 25 to 27, wherein said circulation is carried out with low pressure, preferably carries out with the 3-10 bar pressure.
29. as each described motor in the claim 18 to 28, wherein described reflux line is pressurized when using the water transfer emulsion fuel.
30. a crosshead type large two-stroke diesel engine (1), it comprises:
Crankcase support (4), it supports bent axle (3) and is installed in cylinder support (5) on the described crankcase support;
A plurality of cylinders (6), it is by described cylinder support (5) supporting, and each cylinder is provided with at least one fuel injector (23) and at least one exhaust valve (11);
The hydrovalve actuator (19) that is associated with each described exhaust valve (11);
Common fuel rail (40), it has one or more accumulators that are connected thereto (42);
High pressure fuel pump (33), it under high pressure supplies fuel to described common fuel rail (40),
Each described sparger (23) to be coming from the operating fuel of described common rail (40),
Each described hydrovalve actuator (19) to be coming from the operating fuel of described common rail (40),
Wherein said hydrovalve actuator (19) is provided with and is used for changing the device that compensates by move caused size with different temperatures.
31. motor as claimed in claim 30, the wherein said device that is used to compensate comprises the piston (67) of have first portion (67) and second portion (78), described second portion (78) slidably engages described first portion (67), thereby forms compensated chamber (79) between described first portion (67) and described second portion (78).
32. motor as claimed in claim 31 also comprises spring assembly (80), described spring assembly drives described first portion (67) and described second portion (78) and makes it away from each other, thereby makes described compensated chamber (79) enlarge.
33. motor as claimed in claim 32 also comprises:
Be positioned at first flow path between described compensated chamber (79) and the pressure chamber (69,87), described first flow path is only just opened when described second portion (78) is positioned at little predetermined axial range at the place, top of described hydraulic actuator (19), with allow excessive hydraulic fluid from described compensated chamber (79) discharge and
Be positioned at second flow path between described compensated chamber (79) and the pressure chamber (69,87), described second flow path allows described compensated chamber (79) to refill under the effect of described spring assembly (80).
34. motor as claimed in claim 33, wherein, before described piston (67) arrived retracted position, described second portion (78) was inserted in the cecum of stroke dampening chamber (87) just, and in described retracted position, described exhaust valve (11) is taken one's seat.
35. the method for temperature of fuel in the pressure piping (20) of a control crosshead type large two-stroke diesel engine (1), described pressure piping (20) is connected to hydrovalve actuator (19) with common fuel rail (40), and described method comprises the steps: during the running temperature of described fuel changes, control enters into the temperature of the fuel of described pressure piping (20), maintains under the predetermined threshold with the temperature gradient with described fuel.
36. method as claimed in claim 35, wherein, the running temperature of described fuel from the fuel temperature of motor run duration to being used for during changing the fuel temperature of the described fuel circulation of motor withholding period chien shih, the temperature gradient of described fuel remains between 0 ℃/minute to-2 ℃/minute.
37. as claim 35 or 36 described methods, wherein, from being used at the fuel temperature of the described fuel circulation of motor withholding period chien shih during change the fuel temperature of motor run duration, the temperature gradient of described fuel remains between 0 ℃/minute to 2 ℃/minute in the running temperature of described fuel.
38. as claim 36 or 37 described methods, wherein the fuel temperature of motor run duration is between 90-150 ℃, the fuel temperature that the motor stopping period is used to circulate is between 40-70 ℃.
39. as each described method among the claim 35-38, wherein said fuel temperature is basically by the control of the preheater (31) in the fluid circuit of the upstream that is arranged on described high pressure fuel pump (33).
40. a crosshead type large two-stroke diesel engine (1), it comprises:
Crankcase support (4), it supports bent axle (3) and is installed in cylinder support (5) on the described crankcase support;
A plurality of cylinders (6), it is by described cylinder support (5) supporting, and each cylinder is provided with at least one fuel injector (23) and at least one exhaust valve (11);
The hydrovalve actuator (19) that is associated with each described exhaust valve (11);
Common fuel rail (40), it has one or more accumulators that are connected thereto (42);
High pressure fuel pump (33), it under high pressure supplies fuel to described common fuel rail (40),
Each described sparger (22) to be coming from the operating fuel of described common rail (40),
Described hydrovalve actuator (19) is connected to described common rail (40) by corresponding hydraulic line, and finally be connected to for example other hydraulic unit of valve, it is characterized in that static gasket (68 ') that the pipeline and the connection between other hydraulic unit of described motor sealed and the dynamic packing ring in the described valve actuator are made by following material: cast iron, steel, polytetrafluoroethylene (PTFE), fluorine rubber, (FPM), copolymer (NBR), nitrite rubber, poly-(dimethyl siloxane) are (SI) or its composition and/or mixture.
41. a crosshead type large two-stroke diesel engine (1), it comprises:
Crankcase support (4), it supports bent axle (3) and is installed in cylinder support (5) on the described crankcase support;
A plurality of cylinders (6), it is by described cylinder support (5) supporting, and each cylinder is provided with at least one fuel injector (23) and at least one exhaust valve (11);
The hydrovalve actuator (19) that is associated with each described exhaust valve (11);
Common fuel rail (40), it has one or more accumulators that are connected thereto (42);
High pressure fuel pump (33), it under high pressure supplies fuel to described common fuel rail (40);
Supply line (24) that is associated with each cylinder (6) and control valve unit (25), it is used for fuel is transported to corresponding sparger (23) from described common rail (40);
Pressure piping (20) that is associated with each cylinder (6) and control valve unit (25,25 '), it is used for fuel is transported to corresponding hydrovalve actuator (19) from described common rail (40); With
Heating reflux line (43) is used for fuel is sent to fuel tank (29) or is sent to the pipeline of the inlet side that leads to described high-pressure service pump (33) from described hydrovalve actuator (19).
42. motor as claimed in claim 41, wherein said heating reflux line (43) is pressurized.
43. motor as claimed in claim 42, wherein said heating reflux line (43) comprises pressure controlled valve (47), is preferably used for keeping in described heating reflux line the pressure controlled valve of given pressure minimum.
44. as each described motor among the claim 41-43, wherein one or more accumulators (48) are connected to described pressurization and heating reflux line (43).
45. as each described motor among the claim 41-44, wherein said heating reflux line (43) comprises heating equipment, to reduce wherein to be held the heat loss of fuel.
46. the fuel that motor as claimed in claim 45, wherein said heating equipment are suitable for being contained in described heating reflux line (43) is maintained and is higher than 50 ℃.
47. as each described motor among the claim 43-46, wherein said given pressure minimum is about 3-10 crust.
48. a crosshead type large two-stroke diesel engine (1), it comprises:
Crankcase support (4), it supports bent axle (3) and is installed in cylinder support (5) on the described crankcase support;
A plurality of cylinders (6), it is by described cylinder support (5) supporting, and each cylinder is provided with at least one fuel injector (23) and at least one exhaust valve (11);
The hydrovalve actuator (19) that is associated with each described exhaust valve (11);
Common fuel rail (40), it has one or more accumulators that are connected thereto (42);
High pressure fuel pump (33), it under high pressure supplies fuel to described common fuel rail (40);
Supply line (24) that is associated with each cylinder (6) and control valve unit (25), it is used for fuel is transported to corresponding sparger (23) from described common rail (40);
Pressure piping (20) that is associated with each cylinder (6) and control valve unit (25,25 '), it is used for fuel is transported to corresponding hydrovalve actuator (19) from described common rail (40); With
Reflux line (43) is used for fuel is sent to fuel tank (29) or is sent to the pipeline of the inlet that leads to described high-pressure service pump (33) from described hydrovalve actuator (19),
Wherein at least one described pipeline (20,24,40,43) comprises the device (50,53,54) that is used to eliminate the influence that described line size that the variation owing to running temperature produces changes.
49. motor as claimed in claim 48, the wherein said device that is used to eliminate the effects of the act (50,53,54) comprises pipe section, and described pipe section vertically freely overhangs between the supporting member (51,52,53,54) that is being oppositely arranged in its tail end.
50. as claim 48 or 49 described motors, the wherein said device that is used to eliminate the effects of the act comprises one or more U-shaped pipe sections (50).
51. the purposes of Proportional valve (25), it is used for controlling common fuel pipeline (40) the flowing to fuel injector (23) and/or operating fuel parts (19) of fuel from crosshead type large two-stroke diesel engine (1).
52. Proportional valve purposes as claimed in claim 51, wherein said operating fuel parts are hydrovalve actuator (19).
53. Proportional valve purposes as claimed in claim 52, wherein said Proportional valve (25) moves as close/open valve.
A 54. electrical control valve (25,25 '), its be used to control fuel from the common fuel pipeline (40) of crosshead type large two-stroke diesel engine (1) to one or more operating fuels or fuel consumption engine components (19, flowing 23), described electrical control valve (25,25 ') comprise valve body and electromagnet (44), it is characterized in that described electromagnet (44) and described valve body thermal insulation.
55. valve as claimed in claim 54, wherein said valve are Proportional valve (25).
56. as claim 54 or 55 described valves, wherein said valve (25,25 ') has at least three positions: middle position, it is connected to reflux line (43) with two hydraulic pressure operating fuels or fuel consumption engine components (19,23); The first non-middle position, in wherein said two hydraulic pressure operating fuels or the fuel consumption engine components first is connected with high-pressure fuel source (41), in described two hydraulic pressure operating fuels or the fuel consumption engine components (19,23) second is connected with described reflux line (43); And the second non-middle position, described second in wherein said two hydraulic pressure operating fuels or the fuel consumption engine components is connected with described high-pressure fuel source (41), described first in described two hydraulic pressure operating fuels or the fuel consumption engine components (19,23) is connected with described reflux line (43).
57. as each described valve among the claim 54-56, wherein said electromagnet (44) by one deck insulating material (45) and with described housing thermal insulation, preferably described insulating material (45) is a stupalith.
58. a crosshead type large two-stroke diesel engine (1), it comprises:
Crankcase support (4), it supports bent axle (3) and is installed in cylinder support (5) on the described crankcase support;
A plurality of cylinders (6), it is by described cylinder support (5) supporting, and each cylinder is provided with at least one fuel injector (23) and at least one exhaust valve (11);
Common fuel rail (40); With
High pressure fuel pump (33), it under high pressure supplies fuel to described common fuel rail (40) at the motor run duration;
Supply line (24) that is associated with each cylinder (6) and control valve unit (25), it is used for fuel is transported to corresponding sparger (23) from described common rail (40);
Described high pressure fuel pump (33) is mechanically driven by described bent axle (3) and is electrically driven by electric motor (38 ') at the motor stopping period at the motor run duration, circulates under low pressure to make fuel pass described supply line (24) and/or described common rail (40) and/or pass with other engine components of operating fuel.
59. motor as claimed in claim 58 also comprises clutch (56), is used for described high pressure fuel pump (33) being connected to described bent axle (3) or described high pressure fuel pump (33) being broken away from from described bent axle (3).
60. as claim 58 or 59 described motors, also comprise clutch (55), be used for described high pressure fuel pump (33) being connected to described electric motor (38 ') or described high pressure fuel pump (33) being broken away from from described electric motor (38 ').
61. as each described motor among the claim 58-60, also comprise gear (36,37), be used for described bent axle (3) is connected to described high pressure fuel pump (33).
62. as each described motor among the claim 58-61, wherein said high pressure fuel pump (33) is at the pressure transfer the fuel of motor run duration with the 600-2000 crust, at the pressure transfer the fuel of motor stopping period with the 3-10 crust.
63. a hydraulic actuating type ventilation valve (11) that is used for internal-combustion engine (1), it comprises:
Static valve body (61);
Scavenging air valve (11), it can move between the position take one's seat position and non-taking one's seat, and comprises microscler valve rod (57), and this microscler valve rod one end has valve head (58), has terminal freely on the opposite end;
Hydraulic actuator (19), described hydraulic actuator comprises the piston (67) on the end freely that acts on described valve rod (57), is used for when described hydraulic actuator (19) is supplied with pressurized hydraulic fluid described scavenging air valve (11) being urged the non-position of taking one's seat;
Pneumatic spring (18), it urges the described position of taking one's seat with described valve,
Described pneumatic spring (18) comprising:
Cylinder (59), it is fixed to described valve rod (57), and described cylinder is sealing on the direction of the free terminal of described valve rod (57), is opening wide on the direction of described valve head (58); With
The stationary piston (60) of coupling, it is contained in the described cylinder (59), and described piston is fixed to described valve body (61) and is formed for the spring housing (62) of described pneumatic spring (18) with described cylinder (59).
64., wherein be used for forced air is fed to the pipeline of described spring housing (62) through described piston (60) as the described hydraulic actuating type ventilation valve of claim 63 (11).
65. as claim 63 or 64 described hydraulic actuating type ventilation valves (11), wherein valve rod (57) with slidably and airtight basically mode pass hole in the described piston (60).
66. a hydraulic actuating type ventilation valve component that is used for internal-combustion engine (1), it comprises:
Static valve body (61);
Scavenging air valve (11), it can move between the position non-the taking one's seat that take one's seat position and described valve that described valve cuts out are opened, and comprises microscler valve rod (57), and this microscler valve rod one end has valve head (58), has terminal freely on the opposite end;
Hydraulic actuator (19), described hydraulic actuator (19) comprises the piston (67) on the end freely that acts on described valve rod (57), is used for when described hydraulic actuator (19) is supplied with pressurized hydraulic fluid described valve (11) being urged the non-position of taking one's seat;
Pneumatic spring (18), it urges the described position of taking one's seat with described valve (11),
Wherein said scavenging air valve (11) is determined by the relative equilibrium of forces of described hydraulic actuator (19) and described pneumatic spring (18) in the described running length of opening on the direction.
67. as the described ventilation valve component of claim 66, wherein said hydrovalve actuator (19) comprising:
Piston (67), it is arranged in the cylinder (66) and acts on the free end of described valve rod (57), when described scavenging air valve (11) when taking one's seat, described piston (67) is in a retracted position, when described scavenging air valve (11) when not taking one's seat, described piston (67) is in extended position
Main pressure chamber (69,87), wherein pressure fluid is applied on the surface area of described piston (67) it being driven into described extended position,
Opening (70), it can alternately be connected to hydraulic fluid high-voltage power supply (40) or reflux pipeline (43), and
Flow path, it is positioned between described opening (70) and the described main pressure chamber (69,87), and the flow resistance of wherein said flow path when described extended position substantially is higher than the flow resistance when described retracted position.
68. as the described scavenging air valve of claim 65, wherein when described piston (67) when being in extended position, the flow path of described fluid from high-pressure fluid source (20) to described actuator made described piston (67) be cushioned in the motion of described extended position by throttling.
69. a hydraulic actuator (19) that is used for the scavenging air valve (18) of internal-combustion engine (1), it comprises:
Static cylinder (66), the far-end that it has near-end and opens wide, and comprise and can alternately be connected to source of high pressure hydraulic fluid (40) or be connected to the pressure chamber (69,87) of reflux pipeline (43) via control valve unit (25,25 ');
Piston (67), it has and is contained in described main pressure chamber (69, far-end on the free terminal of near-end 87) and the valve rod (57) that acts on described scavenging air valve (11), when being used in described pressure chamber that (69,87) are connected to described source of high pressure hydraulic fluid (40) described valve is urged the non-position of taking one's seat
Described piston (67) comprises first portion (67) and second portion (78), and towards described proximal extension, and described second portion (78) is arranged on described proximal end from described far-end in described first portion (67),
Described second portion (78) slidably engages described first portion (67), thereby forms compensated chamber (79) between described first portion (67) and described second portion (78);
Spring assembly (80), it urges described first portion (67) and second portion (78) makes it away from each other, thereby described compensated chamber (79) is enlarged;
Be positioned at described compensated chamber (79) and described pressure chamber (69,87) first flow path between, described first flow path is only opened when described second portion (78) is positioned at the little axial range of being scheduled in the proximal end of described static cylinder (66), discharges from described compensated chamber (79) to allow excessive hydraulic fluid;
Be positioned at second flow path between described compensated chamber (79) and described pressure chamber (69,87), described second flow path allows described compensated chamber (79) to refill under the effect of described spring assembly (80).
70. as the described actuator of claim 67, wherein said second portion (78) was inserted in the cecum of stroke dampening chamber (87) before described piston (67) arrives described retracted position just.
71. as claim 69 or 70 described actuators, the stroke dampening chamber (87) of wherein said band cecum is the part of described pressure chamber (69).
72. as the described actuator of claim 71, the diameter of wherein said second portion (78) is slightly less than the diameter of described stroke dampening chamber (87) cecum, thereby, when described second portion (78) is contained in the cecum of described stroke dampening chamber, allow between the remaining part of the cecum of described stroke dampening chamber (87) and described pressure chamber (69), to carry out restricted hydraulic fluid flows.
73. as each described actuator among the claim 69-72, wherein in the upper end of described second portion (78) at its axial range and described scavenging air valve (11) when taking one's seat, described first flow path is opened.
74. a hydraulic actuator (19) that is used for the scavenging air valve (11) of internal-combustion engine (1), it comprises:
Static cylinder (66), it comprises the pressure chamber (69,73,87) that can alternately be connected to source of high pressure hydraulic fluid (40) via the opening (70) in the described static cylinder (66) or be connected to reflux pipeline (43);
Piston (67), it is contained in the described pressure chamber (69,73,87) and acts on the free terminal of valve rod (57) of described scavenging air valve (11), when being used in described pressure chamber that (69,73,87) are connected to described source of high pressure hydraulic fluid (40) described scavenging air valve (11) is urged the non-position of taking one's seat
Axially move between the extended position that retracted position that described piston (67) can be taken one's seat in described scavenging air valve (11) and described scavenging air valve (11) are opened,
Described piston (67) has first useful area, when described piston (67) is between described retracted position and predetermined neutral position, the described pressurized hydraulic fluid that is arranged in described pressure chamber (69,73,87) acts on described first useful area and urges described piston (67) towards described extended position
Described piston (67) has second useful area less than described first useful area, when described piston (67) was between described neutral position and described extended position, the described pressurized hydraulic fluid in described pressure chamber (69,87) acted on described second useful area and urges described piston (67) towards described extended position.
75. as the described actuator of claim 74, wherein said piston (67) comprises the oversize piston part (74) with first predetermined diameter, this first predetermined diameter is greater than the diameter of the remaining part of described piston, described static cylinder (66) is provided with a part with increased diameter, the diameter of the described increasing of this part is corresponding to the piston portion (74) of described increasing, the cylinder of piston portion of described increasing (74) and described increasing partly forms aux. pressure chamber (73), when described piston (67) is between described retracted position and described predetermined intermediate position, described aux. pressure chamber is communicated with described opening (70) fluid, when described piston (67) was between described neutral position and described extended position, described aux. pressure chamber (73) was connected to reflux opening (77) and is not communicated with described first opening (70) fluid.
76. as claim 74 or 75 described actuators, wherein said static cylinder (66) comprises the part that otch (75) or diameter reduce, when described piston (67) was between described retracted position and described predetermined neutral position, the part that described diameter reduces provided the flow path from described first opening (70) to described aux. pressure chamber (73).
77. as each described actuator among the claim 74-76, wherein said pressure chamber (69,87) comprises the main pressure chamber (69,87) that is communicated with described first opening (70) fluid via main flow path, and described actuator also comprises and is used for about the position of described piston (67) and changes the device (78,88,89) of the flow resistance of described main flow path.
78. as the described actuator of claim 77, wherein when described piston (67) from described retracted position when described extended position moves, the flow resistance of described main flow path increases, vice versa.
79. as the described actuator of claim 78, wherein said piston (67) comprises tapering part, described tapering part is with forming flow restriction (89) from the inwardly outstanding flange (88) of described cylinder, when described piston (67) from described retracted position when described extended position moves, described flow restriction increases, and vice versa.
CNB2005800475866A 2005-02-02 2005-02-02 Crosshead type large two-stroke diesel engine and control valve thereof and purposes Expired - Fee Related CN100554652C (en)

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PCT/EP2005/001040 WO2006081829A1 (en) 2005-02-02 2005-02-02 A large two-stroke diesel engine with hydraulically actuated exhaust gas valves

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CN2009100085812A Division CN101482041B (en) 2005-02-02 2005-02-02 Crosshead type large two-stroke diesel engine
CN200910008585.0A Division CN101509403B (en) 2005-02-02 2005-02-02 Method for controlling temperature of fuel in engine pressure conduit
CN2009100085846A Division CN101487406B (en) 2005-02-02 2005-02-02 Crosshead type large two-stroke diesel engine
CN2009100085831A Division CN101487405B (en) 2005-02-02 2005-02-02 Crosshead type large two-stroke diesel engine
CN2009100085827A Division CN101476497B (en) 2005-02-02 2005-02-02 Hydraulic actuating type ventilation valve component used for internal combustion engine and its actuator
CN2009100085795A Division CN101482040B (en) 2005-02-02 2005-02-02 Crosshead type large two-stroke diesel engine

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KR20070100388A (en) 2007-10-10
KR100960647B1 (en) 2010-06-07
WO2006081829A1 (en) 2006-08-10
JP2008527239A (en) 2008-07-24

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