CN101970812B - Large two-stroke diesel engine with electronically controlled exhaust valve actuation system - Google Patents

Large two-stroke diesel engine with electronically controlled exhaust valve actuation system Download PDF

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Publication number
CN101970812B
CN101970812B CN2008801105554A CN200880110555A CN101970812B CN 101970812 B CN101970812 B CN 101970812B CN 2008801105554 A CN2008801105554 A CN 2008801105554A CN 200880110555 A CN200880110555 A CN 200880110555A CN 101970812 B CN101970812 B CN 101970812B
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CN
China
Prior art keywords
exhaust valve
valve
electronic control
stroke
control valve
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CN2008801105554A
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CN101970812A (en
Inventor
埃里克·罗森隆德
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Mannone Solutions Mannone Solutions Germany Branch
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Mann Diesel & Turbine An Associate Co Of Mann Diesel & Turbine Europe AG
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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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F01L1/462—Valve return spring arrangements
    • F01L1/465—Pneumatic arrangements
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C5/00—Crossheads; Constructions of connecting-rod heads or piston-rod connections rigid with crossheads
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/22—Internal combustion engines

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

A large two-stroke diesel engine with an electronically controlled exhaust valve actuation system includes for each cylinder an exhaust valve with a valve stem and a valve disc, an air spring operably connected to the valve stem and urging the exhaust valve towards the closed position, a hydraulic actuator operably connected to the exhaust valve, an electronically controlled hydraulic system that selectively connects the hydraulic actuator to a source of high pressure hydraulic fluid for a first short period at the start of the opening stroke of the exhaust valve, and an intermediate pressure hydraulic accumulator for a period immediately following the first short period until the exhaust valve has reached it open position, the intermediate pressure hydraulic accumulator from the start of the closing stroke of the exhaust valve until the start of a last short period at the end of the closing stroke of the exhaust valve, and to tank during the last short period of the closing stroke of the exhaust valve.

Description

Large-sized two-stroke diesel engine with electronically controlled exhaust valve actuating system
Technical field
The present invention relates to a kind of cross hair style large-sized two-stroke diesel engine with electronically controlled exhaust valve actuating system, particularly relate to a kind of cross hair style large-sized two-stroke diesel engine with energy-conservation electronically controlled exhaust valve actuating system.
Background technique
Usually be used in the propulsion system of large vessel or becoming electronically controlled motor from the development of engine of camshaft control recently as the cross hair style large-sized two-stroke diesel engine of the prime mover in power station.Timing and the formation that electronic control is sprayed at fuel and instant flexibility is being provided aspect the timing of exhaust valve.Control combustion process better thus realizes more effective burning and lower discharge value, the fuel consumption when reducing sub load when full speed running and reduces minimum motion speed.
JP2004-084670 discloses a kind of two-stroke diesel engine of electronic control.In this motor, exhaust valve activates by hydraulic actuator, utilizes high pressure hydraulic fluid to provide power for this hydraulic actuator.This actuator forces the counter-force of gas force in the exhaust valve opposing firing chamber and air spring and opens.Exhaust valve open stroke during, the most of energy by the hydraulic actuator transmission is stored in the air spring as potential energy.Different from the motor of camshaft actuated because there is not device to re-use the energy of storage, so that the energy that is stored in the air spring can't be re-used in shutoff stroke, but be wasted (having dissipated).The energy of this storage is converted to heat, enters into the fuel tank of hydraulic system along with oil return.The total amount that is used for opening the hydraulic energy of the exhaust valve on the large-sized two-stroke diesel engine is considerable, and the major part of the conservation of fuel that obtains of the burning of the increase by electronically controlled motor control is lost in exhaust valve actuation.
DK 148664B discloses a kind of large-sized two-stroke diesel engine with electronics-hydraulic valve actuation system, wherein utilizes hydraulic actuator to apply two kinds of different hydraulic pressures and opens exhaust valve.During opening the starting stage of stroke, use higher stress level, and during the remainder of opening stroke of exhaust valve, use lower pressure.
WO2006108629 discloses a kind of exhaust valve assemblies for large-sized two-stroke diesel engine, and this assembly comprises can be along the exhaust valve of two opposite directions movement between closed position and open position.The double-acting spring assembly is operably connected to exhaust valve, and together with exhaust valve and with exhaust valve together the quality of mobile any other parts formed quality-spring system.When exhaust valve between closed position and the open position back and forth during the translation, this double-acting spring assembly stored energy is to be used for subsequently in the opposite direction the promotion of exhaust valve.Hydraulic pressure installation according to the instruction that comes self-controller exhaust valve is maintained in its closed position or open position in.The physical location of this system requirements exhaust valve is known, and electronic controller is all wanted transmitted signal when valve need to stop in its one of them extreme positions.This hydraulic system relative complex, and the structure of the air spring of locating at the top of valve stem and hydraulic actuator obviously is different from the corresponding structure in traditional cam axle engine.Therefore, the structure of this prior art is relatively costly and complicated.
Summary of the invention
Based on this background, the purpose of this invention is to provide a kind of large-sized two-stroke diesel engine with flexible, energy-conservation, simple and reliable exhaust valve actuating system.
This purpose can be according to claim 1 by providing a kind of large-scale multi cylinder two-stroke diesel engine of cross hair style with exhaust valve actuating system to realize, described exhaust valve actuating system comprises for each cylinder: exhaust valve, this exhaust valve has valve stem and valve head, described exhaust valve can be mobile between closed position and open position along two opposite directions, and wherein valve head places on the valve seat in closed position; Air spring, this air spring has the spring piston that is contained in the air spring cylinder body, and described air spring is operably connected to valve stem and exhaust valve is urged towards closed position; Hydraulic actuator, this hydraulic actuator has the pressure chamber, and described hydraulic actuator is operably connected to the bar of exhaust valve, and described hydraulic actuator urges exhaust valve along opening direction when the pressure chamber is pressurized; Electronically controlled hydraulic system, this electronically controlled hydraulic system can be optionally the first short-term when the opening stroke and begin of exhaust valve the pressure chamber of hydraulic actuator is connected in source of high pressure hydraulic fluid, after described the first short-term until the period that exhaust valve has arrived its open position the pressure chamber of hydraulic actuator is connected in the intermediate pressure hydraulic accumulator, begin until the last short-term of the shutoff stroke of exhaust valve when finishing begins the pressure chamber of hydraulic actuator is connected in the intermediate pressure hydraulic accumulator from the shutoff stroke of exhaust valve, and during the described last short-term of the shutoff stroke of exhaust valve, the pressure chamber of hydraulic actuator is connected in fuel tank.
By after opening stroke and beginning soon until open stroke and finish the pressure chamber of hydraulic actuator is connected in the intermediate pressure hydraulic accumulator, and by beginning from return stroke until nearly return stroke finish the pressure chamber is connected in same intermediate pressure accumulator can be regained and be used to the next one and opened stroke so that be used for opening the major part of the energy of exhaust valve.Therefore, in the situation that can not have the high energy losses that usually is associated with electronically controlled exhaust valve actuating system, this exhaust valve actuating system has the flexibility of electronically controlled exhaust valve actuating system.
Hydraulic system can comprise the first electronic control valve, and this first electronic control valve is arranged to: the short-term when the opening stroke and begin of exhaust valve, the pressure chamber of hydraulic actuator is connected in source of high pressure hydraulic fluid.
Hydraulic system can comprise the second electronic control valve, this second electronic control valve is arranged to: until exhaust valve has arrived the period of its open position, the pressure chamber of hydraulic actuator is connected in the intermediate pressure hydraulic accumulator after the short-term of opening of the first electronic control valve.
Hydraulic system can comprise the 3rd electronic control valve, the 3rd electronic control valve is arranged to: begin until the last short-term the during end of the shutoff stroke of exhaust valve from the shutoff stroke of exhaust valve, the pressure chamber of hydraulic actuator is connected in the intermediate pressure hydraulic accumulator.
Hydraulic system can comprise quadrielectron control valve, and this quadrielectron control valve is arranged to: during the described last short-term of the shutoff stroke of exhaust valve, the pressure chamber of hydraulic actuator is connected in fuel tank.
Because the stages of circulation is controlled by hydraulic flow, so safety check can be used for the smooth transition between the stages of guaranteeing to circulate.
Described the first electronic control valve and described quadrielectron control valve can be formed by single Twoway valves.
Described the second electronic control valve and described the 3rd electronic control valve can be formed by single Twoway valves.
This large-sized two-stroke diesel engine can be provided with: the first safety check that only allows to flow to described intermediate pressure hydraulic accumulator that is associated with described the second electronic control valve; And the second safety check of flowing out from described intermediate pressure hydraulic accumulator of only allowing of being associated with described the 3rd electronic control valve.
The first safety check and the second safety check are provided so that allow for the opening of the opening of the first electronic control valve, the second electronic control valve, the 3rd electronic control valve open and quadrielectron control valve open exist sizable overlapping.
This large-sized two-stroke diesel engine also can comprise electronic control unit, and this electronic control unit is arranged to be controlled at the hydraulic connecting between pressure chamber and source of high pressure hydraulic fluid, intermediate pressure hydraulic accumulator and the fuel tank.
From following detailed description, will become obvious according to other purpose, feature, advantage and the characteristic of large-sized two-stroke diesel engine of the present invention.
Description of drawings
In the detailed part below this specification, the illustrative embodiments shown in is with reference to the accompanying drawings described the present invention in further detail, wherein:
Fig. 1 is the cross-sectional view according to motor of the present invention,
Fig. 2 is the longitudinal section of a cylinder portion of the motor shown in Fig. 1,
Fig. 3 is the symbol table diagram according to first mode of execution of exhaust valve actuating system of the present invention,
Fig. 4 is the order diagram of timing of opening and closing of electronic control valve that illustrates the exhaust valve actuating system of Fig. 3,
Fig. 5 is the alternately order diagram of Fig. 4 of opening time that illustrates electronic control valve, has wherein utilized the effect of safety check, and
Fig. 6 is the symbol table diagram according to the second mode of execution of exhaust valve actuating system of the present invention.
Embodiment
Fig. 1 and Fig. 2 show motor 1 (for a cylinder) according to preferred implementation of the present invention with cross-sectional view and longitudinal section respectively.Motor 1 is cross hair style single current low speed two-stroke cross head diesel engine, and this motor can be propulsion system in the ship or the prime mover in the power station.These motors have into four to 14 cylinders of delegation usually.Motor 1 is set up from base 2, and base 2 has the main bearing for camshaft 3.
Camshaft 3 is semi-built-up.This semi-built-up is to be made by the forged steel or the cast steel throw that are connected in main journal by shrink-fit.
Base 2 can be according to manufacturing mechanism with the single type manufacturing or be divided into a plurality of parts with suitable dimension and make.The crossbeam that this base comprises sidewall and has the welding of bearing spider.This crossbeam is also referred to as " transverse beam " in this field.Food tray 58 is welded in the bottom of base 2 and collects from the oil return of pressure lubrication and cold oil system.
Connecting rod 8 is connected in crosshead 22 with camshaft 3.Crosshead 22 is directed between vertical guide plate 23.
The frame shell 4 of the A shape of welding design is installed on the base 2.This frame shell 4 is welding designs.On exhaust side, frame shell 4 is provided with reduction valve for each cylinder, and on an opposite side, this frame shell 4 is provided with large hinge door for each cylinder.Crosshead guide plate 23 is incorporated in the frame shell 4.
Cylinder frame 5 is installed on the top of frame shell 4.Stay bolt 27 connects base 2, frame shell 4 and cylinder framework 5 and this structure is kept together.Stay bolt 27 utilizes the hydraulic jack tension.
Cylinder framework 5 can be cast or it also can be welding design in one or more modes.
Cylinder frame 5 provides for the cleaning gas-swept space and for the access cover that checks scavenging port and piston ring.Cylinder frame has formed gas-swept space together with cylinder liner 6.Scavenging air box 9 is bolted to cylinder frame 5 in its opening side.There is piston rod stuffing box (stuffing box) in the bottom of cylinder frame; this piston rod stuffing box provides for the seal ring of scavenging and provides scraper ring; this scraper ring can prevent that the products of combustion of discharging from entering into the space of frame shell 4 and base 2, and has protected thus all bearings that exist in this space.
Piston 13 comprises piston head and piston skirt.Piston head is made by refractory steel and is had four annular grooves, and described annular groove is covered with hard chrome (hard-chrome) at upper surface and the lower surface of groove.
Utilize four bolts that piston rod 14 is connected in crosshead 22.Piston rod 14 has two coaxial apertures (not shown in the accompanying drawing), and described coaxial aperture has formed the entrance and exit that is used for the cold oil of piston 13 together with oil cooling service pipe.
Cylinder liner 6 is by cylinder frame 5 supportings.This cylinder liner 6 is made by alloy cast iron, and is suspended on cylinder frame 5 by means of the flange that is arranged in lower.The uppermost part of described cylinder liner by cast iron cooling sleeve ring around.Cylinder liner 6 has the boring (not shown) for cylinder lubricating oil.
Described cylinder is single current, and has the scavenging port 7 that is arranged in gas tank, and this gas tank has formed scavenging air box 9 (Fig. 1), is the scavenging (Fig. 1) of scavenging air box supplied with pressurized by turbosupercharger 10.
Motor is equipped with one or more turbosupercharger 10, turbosupercharger is arranged in the rear end of motor for the motor of four to nine cylinders, then is arranged in exhaust side for the motor of ten or more cylinders.
It is that intake silencer (not shown) by turbosupercharger directly comes from engine compartment that the air of turbosupercharger 10 enters.To guide to from the air of turbosupercharger 10 scavenging port 7 of cylinder liner 6 via pressurizing air tracheae (not shown), air-cooler (not shown) and scavenging air box 9.
Motor provides power-actuated scavenge blower (not shown).The suction side of blower is connected in and is located at air-cooler gas-swept space afterwards.The one-way valve (not shown) is installed, this one-way valve autoshutdown when the auxiliary blower air supply between air-cooler and scavenging air box.This auxiliary blower assisted turbocharger compressor under the condition of low-load and moderate duty.
Fuel valve 40 is installed in the cylinder head 12 concentrically.When compression stroke finished, injection valve 40 was ejected in the firing chamber 15 with the fuel that high pressure will become mist by their jet nozzles.Exhaust valve 11 is installed in the cylinder head 12 in the mode in the center of top of cylinder.When expansion stroke finishes, open through exhaust valve 11 before the scavenging port 7 downwards at engine piston 13, thus, the combustion gas that are positioned at above the piston 13 in firing chamber 15 flow out through the exhaust passage 16 that leads to waste heat box 17, and the pressure decreased in the firing chamber 15.Exhaust valve 11 cuts out again in the process that piston 13 moves upward.Exhaust valve 11 is hydraulic startings.
Fig. 3 shows the first mode of execution according to exhaust valve actuating system of the present invention.This exhaust valve actuating system is for all mode of executions that describe for single cylinder.In multiple cylinder engine, has identical structure for each cylinder.
This exhaust valve actuating system comprises the exhaust valve 11 with valve stem 31 and valve head 32.In closed position shown in Figure 3, valve head 32 places on the valve seat, and this valve seat is arranged in the top of cylinder 6.In Fig. 6, illustrate the open position of exhaust valve 11.
Air spring 34 forces exhaust valve 11 towards its closed position.This air spring 34 provides the pneumatic piston 35 that is connected in valve stem 31, thereby makes air spring 34 be operably connected to exhaust valve 11.
Position transducer 33 is measured the position of exhaust valve 11 with analog form or digital form.The signal of position transducer 33 is transferred into control unit of engine 42 (for example computer) via signal cable.Control unit of engine 42 also receives the camshaft-position signal that comes from the camshaft-signal sensor (not shown).
Exhaust valve actuator 37 is positioned at the top of valve stem 31 and comprises the columnar valve chest with hydraulic piston 38, it is inboard that this hydraulic piston is contained in columnar housing, and this hydraulic piston 38 is connected in valve stem 31, thereby makes hydraulic actuator 37 be operably connected to exhaust valve 11.Pressure chamber 39 is limited to the top of hydraulic piston 38.
Pressure piping 40 is connected in the pressure chamber 39 of hydraulic actuator 38 hydraulic system of exhaust valve actuating system.
The hydraulic system of exhaust valve actuating system comprises the source of high pressure hydraulic fluid such as the pumping plant (not shown), this pumping plant can be for the special-purpose pumping plant of exhaust valve actuating system or can be the pumping plant that also is used for other purpose (system pressure), for example provides pressure for fuel injection system or for cylinder lubricating system.Usually, system pressure will be several hectobars (bar).In the application of reality, hydraulic system and hydraulic actuator 37 will be opened by pressurized machine or similar device separates usually, thereby avoid the pollution between the system.
The first electronic control valve 44 authorized pressure pipelines 40 such as hydraulic switching valve optionally are connected in source of high pressure hydraulic fluid.
Pressure piping 40 also is connected in lateral 41.
Lateral 41 is connected in intermediate pressure hydraulic accumulator 43 via the first safety check 45 and the second electronic control valve 46 (for example hydraulic switching valve).
Intermediate pressure hydraulic accumulator 43 is following type preferably, that is: it provides elastic membrane, the part that this elastic membrane is divided into accumulator the part of the hydraulic fluid that is filled with pressurization and is filled with the gas of pressurization.
Lateral 41 also is connected in hydraulic accumulator 43 via the second safety check 47 and the 3rd electronic control valve 48 (for example hydraulic switching valve).
Lateral 41 also is connected in fuel tank via quadrielectron control valve 50 (for example hydraulic switching valve).
The first safety check 45 and the second safety check 47 have the opposite flow direction.
The first electronic control valve 44, the second electronic control valve 46, the 3rd electronic control valve 48 and quadrielectron control valve 50 are coupled to control unit of engine 42 via signal cable, and these valves open and cut out according to the instruction of control unit of engine 42.
Electronic control unit 42 time-baseds are determined the end of period " 1 ", still determine the length of " 1 " in valve stroke and the next circulation of correction by the signal that is used to autobiography sensor 33, so that the valve stroke that acquisition needs.
The operation of electronics-hydraulic valve actuation system is now described with reference to the order diagram shown in Fig. 4.
In this order diagram, the operation of exhaust valve 11 is divided into six continuous periods.In the first period " 0 ", exhaust valve 11 cuts out, and first to fourth electronic control valve 44,46,48,50 is also closed.
When electronic control unit 42 based on camshaft signal and also may determine to open the time of exhaust valve 11 based on other operating conditions of motor the time, finish period " 0 " and beginning in period " 1 ".When exhaust valve 11 open this short-term that stroke begins when beginning, the first electronic control valve 44 is opened and is allowed high pressure hydraulic fluid to flow in the pressure chamber 39.High pressure hydraulic fluid in the pressure chamber 39 so that exhaust valve 11 can resist the pressure of the combustion gas in the firing chamber 15 and open.Because the high pressure of the gas in the firing chamber is pressed onto exhaust valve 11 in its seat, so need hydraulic actuator 37 to provide very high breaking force when stroke has just begun opening of exhaust valve 11.
When exhaust valve 11 was opened a little, combustion gas just no longer forced exhaust valve 11 towards its seat, and hydraulic actuator 37 need not the power that provides again very high.Therefore, when exhaust valve 11 open the first short-term " 1 " that stroke begins when finishing, stroke electronic control unit 42 orders the first electronic control valve 44 is closed and is ordered the second electronic control valve 46 to be opened.Electronic control unit 42 utilizes the signal that comes from position transducer 33 to determine the end of period " 1 ", and corrects regularly based on the result of a upper circulation.
The residue of opening stroke of exhaust valve 11 refers to the period " 2 " in the order diagram of Fig. 4 period.
The hydraulic fluid that hydraulic accumulator 43 holds the pressure that mediates---for example 10 to 30 bar---.Therefore, when the second electronic control valve 46 was opened, the hydraulic fluid of the pressure that mediates flowed to pressure chamber 39 and allows exhaust valve 11 to finish its stroke of opening.By intermediate pressure is used for opening the major part of stroke, so that it is relatively low to be used for opening the total amount of energy of exhaust valve 11, and because power is less, therefore opens motion and being easier to control and very steady.When opening stroke and finish, mobile valve and the inertia of actuator are reduced to zero together with active force, and the power that acts on the air on the pneumatic piston 35 in air spring 34 spring housing begins to urge exhaust valve 11 and retracts.But, prevented this return movement by safety check 45, and exhaust valve 11 stops in its open position.Be used for opening that some are stored in the air spring 34 now in the hydraulic energy of exhaust valve 11.
At this some place, finish period " 2 " one, then beginning in period " 3 ".Electronic control unit 42 orders the second electronic control valve 46 is closed, and exhaust valve 11 stays open state during period " 3 ".Electronic control unit 42 can be based on the end of determining period " 2 " from the signal of position transducer 33.
Based on from the signal of camshaft-signal sensor (and selectively based on other operating parameter), electronic control unit 42 determines when that finish period " 3 " and beginning in period " 4 ".Comprise beginning and the major part of the shutoff stroke of exhaust valve 11 period " 4 ".
When began period " 4 ", electronic control unit 42 orders the 3rd electronic control valve 48 was opened.Thus, hydraulic pressure chamber 39 is connected in hydraulic accumulator 43 again.Air spring 34 urges exhaust valve 11 at closing direction, and 39 hydraulic fluids of discharging cause hydraulic accumulator 43 to fill and store thus the energy that is stored in before the air spring 34 from the hydraulic pressure chamber.The energy that is stored in now in the hydraulic accumulator 43 can be opened stroke for the next one of exhaust valve 11.When finished period " 4 " and begin period " 5 ", electronic control unit 42 orders the 3rd electronic control valve 48 was closed, and orders quadrielectron control valve 50 to be opened.Comprise the last short-term of the shutoff stroke of exhaust valve 11 period " 5 ", and during this period, pressure chamber 39 is connected in fuel tank, therefore allows exhaust valve 11 to be forced on its seat by the residual pressure in the air spring 34.Beginning of period " 5 " is based on determining from the signal of position transducer 33 and based on the pressure in the accumulator 43 by electronic control unit 42.About this point, send the signal that is connected in the pressure transducer of accumulator 43 to control unit of engine 42.Control as follows, that is: come the timing of the beginning of adjustment period " 5 " in the mode of keeping the predetermined pressure in the accumulator 43 based on the result in the previous circulation.Therefore, if the pressure in the accumulator 43 increases, then with the beginning in advance of period " 5 ", and if the pressure decreased in the accumulator 43, then with period " 5 " begin postpone.
When finished period " 5 ", exhaust valve 11 placed its seat upper (being fully closed), and electronic control unit 42 order quadrielectron control valves 50 are closed.Beginning of the end in period " 5 " and period " 0 " is based on determining from the signal of sensor 33 by electronic control unit 42.During period " 0 ", exhaust valve 11 cuts out, until next circulation beginning.
Utilize this valve actuation system, a part that is stored in the energy in the air spring 34 can be utilized again in next cycle period.Therefore, when with traditional electro-hydraulic valve actuation system---energy that wherein is stored in the air spring 34 is dissipated during return stroke---when comparing, whole energy consumption of this exhaust valve actuating system can significantly reduce.
Fig. 5 illustrates the order diagram of Fig. 4 of the shadow region with increase, described shadow region pointed out each electronic control valve 46,48 and 50 other may open period.Because the first safety check 45 and the second safety check 47 being provided, thus these overlapping be possible.This is overlapping so that be easier to guarantee just be opened when each electronic control valve 46,48 and 50 valve does not formerly also cut out.For example, the second electronic control valve 46 can be opened during period " 1 ", and need not thus just in time to open during the transition of " 2 " from period " 1 " to period.Therefore, the period that relevant valve can open or cut out has been pointed out in the shadow region in the diagram.
Fig. 6 illustrates another mode of execution of electro-mechanical valve actuation system, and wherein the first electronic control valve 44 and quadrielectron control valve 50 are merged into single three-way valve.The second electronic control valve 46 and the 3rd electronic control valve 48 are merged into single Twoway valves (cartridge valve).Variant (not shown) according to this mode of execution, the first safety check 45, the second electronic control valve 46, the second safety check 47 and the 3rd electronic control valve 48 are merged into the single three-way valve with neutral position, in this neutral position, the connection between pipeline 41 and the hydraulic accumulator 43 is cut off.This mode of execution needs less control signal, because the switching between the first valve and the 4th valve can be used to realize from a signal of electronic control unit, and the switching between second valve and the 3rd valve can be used to realize from a signal of electronic control unit.
According to the mode of execution (not shown), a hydraulic accumulator 43 can be shared by several or whole cylinders of motor.
Instruction of the present invention has a plurality of advantages.Different embodiments or executive mode can produce one or more in the following advantage.Should be pointed out that this is not exhaustive tabulation, can also have other advantage of not describing herein.An advantage of the application's teaching is, it provides the electronics-hydraulic valve actuation system of the relatively less energy of a kind of use for large-sized two-stroke diesel engine.Another advantage of the application's teaching is, it provides a kind of electronics-hydraulic valve actuation system that can be installed on the large-sized two-stroke diesel engine with fully traditional exhaust valve layout, and its use acts on simple (stepless) hydraulic actuator on the valve stem and utilizes traditional air spring to urge exhaust valve at closing direction.The another advantage of the application's teaching is, it provides a kind of reliable electronics-hydraulic valve actuation system.Another advantage of the present invention is that it has reduced energy loss.
Although described for illustrative purposes the application's teaching in detail, but be to be understood that this details only is the purpose for explanation, and those skilled in the art can make multiple variant therein in the situation of the teaching scope that does not deviate from the application.
Should be pointed out that the mode that also has the plurality of replaceable that realizes the device in the teaching of the present invention.
" comprise " element or the step of not getting rid of other such as employed term in the claims.As employed term " " or " a kind of " do not get rid of a plurality of situations in the claims.The function of a plurality of devices described in the claim can be realized in single processor or other unit.

Claims (11)

1. large-scale multi cylinder two-stroke diesel engine of cross hair style with exhaust valve actuating system, described exhaust valve actuating system comprises for each cylinder:
Exhaust valve, described exhaust valve has valve stem and valve head, and described exhaust valve can be mobile between closed position and open position along two opposite directions, wherein places on the valve seat at valve head described in the described closed position,
Air spring, described air spring has the spring piston that is contained in the air spring cylinder body, and described air spring is operably connected to described valve stem and described exhaust valve is urged towards described closed position,
Hydraulic actuator, described hydraulic actuator has the pressure chamber, and described hydraulic actuator is operably connected to the bar of described exhaust valve, and described hydraulic actuator urges described exhaust valve along opening direction when described pressure chamber is pressurized,
The intermediate pressure hydraulic accumulator, described intermediate pressure hydraulic accumulator is used for time durations last short-term when the finishing except return stroke of the return stroke of described exhaust valve and stores by the energy of described air spring release and for the time durations first short-term when opening stroke and begin of opening stroke of described exhaust valve and transmit its energy to described hydraulic actuator
Electronically controlled hydraulic system, described electronically controlled hydraulic system be optionally:
The first short-term when the opening stroke and begin of described exhaust valve, be connected in source of high pressure hydraulic fluid with the pressure chamber of described hydraulic actuator,
After described the first short-term, until described exhaust valve has arrived the period of exhaust valve open position, the pressure chamber of described hydraulic actuator is connected in described intermediate pressure hydraulic accumulator,
Begin until the last short-term of the shutoff stroke of described exhaust valve when finishing from the shutoff stroke of described exhaust valve, the pressure chamber of described hydraulic actuator is connected in described intermediate pressure hydraulic accumulator, and
During the described last short-term of the shutoff stroke of described exhaust valve, the pressure chamber of described hydraulic actuator is connected in fuel tank.
2. large-sized two-stroke diesel engine according to claim 1, wherein, described hydraulic system comprises the first electronic control valve, this first electronic control valve is arranged to: the short-term when the opening stroke and begin of described exhaust valve, the pressure chamber of described hydraulic actuator is connected in source of high pressure hydraulic fluid.
3. large-sized two-stroke diesel engine according to claim 2, wherein, described hydraulic system comprises the second electronic control valve, this second electronic control valve is arranged to: until described exhaust valve has arrived the period of exhaust valve open position, the pressure chamber of described hydraulic actuator is connected in described intermediate pressure hydraulic accumulator after the short-term that described the first electronic control valve is opened.
4. large-sized two-stroke diesel engine according to claim 3, wherein, described hydraulic system comprises the 3rd electronic control valve, the 3rd electronic control valve is arranged to: begin until the last short-term of the shutoff stroke of described exhaust valve when finishing from the shutoff stroke of described exhaust valve, the pressure chamber of described hydraulic actuator is connected in described intermediate pressure hydraulic accumulator.
5. large-sized two-stroke diesel engine according to claim 4, wherein, described hydraulic system comprises quadrielectron control valve, this quadrielectron control valve is arranged to: during the described last short-term of the shutoff stroke of described exhaust valve, the pressure chamber of described hydraulic actuator is connected in fuel tank.
6. large-sized two-stroke diesel engine according to claim 5, wherein, described the first electronic control valve and described quadrielectron control valve are formed by single Twoway valves.
7. large-sized two-stroke diesel engine according to claim 4, wherein, described the second electronic control valve and described the 3rd electronic control valve are formed by single Twoway valves.
8. large-sized two-stroke diesel engine according to claim 4, wherein, only allow to be associated with described the second electronic control valve towards the first safety check that described intermediate pressure hydraulic accumulator flows, and only allow to be associated with described the 3rd electronic control valve from the second safety check that described intermediate pressure hydraulic accumulator flows out.
9. large-sized two-stroke diesel engine according to claim 5, wherein, only allow to be associated with described the second electronic control valve towards the first safety check that described intermediate pressure hydraulic accumulator flows, and only allow to be associated with described the 3rd electronic control valve from the second safety check that described intermediate pressure hydraulic accumulator flows out.
10. large-sized two-stroke diesel engine according to claim 9, wherein, by the existence of described the first safety check and described the second safety check so that for the opening of the opening of described the first electronic control valve, described the second electronic control valve, described the 3rd electronic control valve open and described quadrielectron control valve open can exist sizable overlapping.
11. each described large-sized two-stroke diesel engine in 10 according to claim 1, also comprise electronic control unit, this electronic control unit is arranged to control the hydraulic connecting between described pressure chamber and described source of high pressure hydraulic fluid, described intermediate pressure hydraulic accumulator and the fuel tank.
CN2008801105554A 2008-11-11 2008-11-11 Large two-stroke diesel engine with electronically controlled exhaust valve actuation system Expired - Fee Related CN101970812B (en)

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JP2011505521A (en) 2011-02-24
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JP4657386B2 (en) 2011-03-23
CN101970812A (en) 2011-02-09

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