CN109247022A - The control method and engine system of engine - Google Patents

The control method and engine system of engine Download PDF

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Publication number
CN109247022A
CN109247022A CN201780025208.0A CN201780025208A CN109247022A CN 109247022 A CN109247022 A CN 109247022A CN 201780025208 A CN201780025208 A CN 201780025208A CN 109247022 A CN109247022 A CN 109247022A
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CN
China
Prior art keywords
engine
valve
fuel gas
output
rotation speed
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Granted
Application number
CN201780025208.0A
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Chinese (zh)
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CN109247022B (en
Inventor
黑岩隆典
桥本彻
渡边孝
渡边孝一
结城和广
山泽美和子
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Niigata Engineering Co Ltd
Niigata Power Systems Co Ltd
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Niigata Engineering Co Ltd
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D43/00—Conjoint electrical control of two or more functions, e.g. ignition, fuel-air mixture, recirculation, supercharging or exhaust-gas treatment
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02P—IGNITION, OTHER THAN COMPRESSION IGNITION, FOR INTERNAL-COMBUSTION ENGINES; TESTING OF IGNITION TIMING IN COMPRESSION-IGNITION ENGINES
    • F02P5/00—Advancing or retarding ignition; Control therefor
    • F02P5/04—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions
    • F02P5/145—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions using electrical means
    • F02P5/15—Digital data processing
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/30—Use of alternative fuels, e.g. biofuels
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/40—Engine management systems

Abstract

Under the combustion gas mode for the dual fuel engine of ship (1), make the mixed gas of fuel gas and air in combustion chambers burn.It include: control unit (22), it is when the output of the output shaft (2) of engine (1) increases, the time advance for closing the inlet valve (8) of engine, and correspondingly shift to an earlier date the duration of valve opening of fuel gas supply valve (15) with the variation of the advance angle；Variable inlet valve timing mechanism (30), the time advance for closing inlet valve (8) according to the shut-in time of the inlet valve (8) of control unit setting；And fuel gas supply valve timing mechanism (45), correspondingly shift to an earlier date the duration of valve opening of fuel gas supply valve (15) with the variation of the advance angle of the inlet valve (8) of control unit setting.Output with the output shaft of engine (1) increases, and by can be changed inlet valve timing mechanism (30), further decreases the control of the compression ratio of the mixed gas of in-engine combustion gas and air.

Description

The control method and engine system of engine
Technical field
The present invention relates to the control method for the engine for using the fuel gas such as natural gas and engine systems, and in particular to One kind have variable inlet valve timing (Variable Intake Valve timing, VIVT) mechanism using fuel gas The control method and engine system of engine.
Background technique
The specific composition example of VVT gear has recorded in following Patent Documents 1 to 3.
As shown in Figure 20 and Figure 21, the driving mechanism of VVT gear 100 described in Patent Document 1 has connecting rod Mechanism 101 and actuator 102.Exhaust in link mechanism 101, with push rod (the プ ッ シ ュ ロ ッ De) connection of engine exhaust valve Valve rocker arm 103 is supported by pitman shaft 104, and the air-breathing valve rocker arm 105 that links with the push rod of inlet valve from pitman shaft 104 by deviateing The tappet axis (タ ペ ッ ト axis) 106 of eccentric axial portion supports.
After exhaust valve rocker arm 103 and air-breathing valve rocker arm 105 can be advanced by the eccentric cam 108a of camshaft 108 respectively It moves back.In addition, pitman shaft 104 links with the piston rod 109 for being set to actuator 102.
If before using position shown in Figure 21 as the pop-up action of piston rod 109, making piston rod by actuator 102 109 progress pop-up actions (fly び and go out movement), so that all rocker arms 105,103 of connection are rotated to a side.Therefore, Ke Yili With actuator 102, the rotation angle of all rocker arms 105,103 is controlled by link mechanism 101.
In addition, Figure 22, Figure 23 describe VVT gear described in patent document 2,3 as other examples. Identical symbol is used in part identical with VVT gear 100 shown in above-mentioned Figure 20, Figure 21 about these mechanisms It number is illustrated.
VVT gear shown in Figure 22, in the range of the teeth portion of the sector gear 120 linked with actuator 102 Interior, the rotating range of pitman shaft 104 is restricted, and (is equivalent to tappet relative to the eccentric fixed eccentric disc 123 of pitman shaft 104 Axis) it is kept by the base portion of exhaust valve rocker arm 103 and air-breathing valve rocker arm 105.
Therefore, the offset of the rotation position for the rotary angle position of each eccentric disc 123 relative to pitman shaft 104, it is convex The position that the eccentric cam 108a of wheel shaft 108 is abutted and pressed upwards on exhaust valve rocker arm 103 and air-breathing valve rocker arm 105 can occur Variation.
In example shown in Figure 23, the exhaust valve rocker arm 103 and air-breathing valve rocker arm that link via push rod 128 and rocking bar 127 105, it is connect with the tappet axis 106 (position of the fulcrum of rocker arm) of the pitman shaft 104 of crank-like.By being changed using actuator 102 The phase of the pitman shaft 104 of (rotation) crank-like, so that the position of the fulcrum of air-breathing valve rocker arm 105 and exhaust valve rocker arm 103 occurs Variation, as a result can make the cusp position to camshaft 108 change.
As a result, the eccentric cam 108a of camshaft 108 pushes exhaust valve rocker arm 103 or air-breathing by camshaft 108 Valve rocker arm 105 makes the temporally variable of its forward-reverse.
Patent document 4 discloses a kind of control device applied to internal combustion engine, comprising: be set to each combustion chamber first inhales Air valve and the second inlet valve；It is set to air entry, respectively to the fuel injection of the first inlet valve and the second inlet valve injection fuel Device；And the valve timing of the valve timing of the first inlet valve and the second inlet valve can be changed to valve different from each other just When variable actuation valve mechanism.The internal combustion engine includes: valve timing setting unit, variable actuation valve mechanism is controlled, by the first air-breathing The opening period of valve is set as before top dead center, after setting top dead-centre for the opening period of the second inlet valve, by the first air-breathing The closing period of valve and the closing period of the second inlet valve are set as after bottom dead centre；And injection timing setting unit, Under the setting state of the valve timing of valve timing setting unit, by fuel injection device rising to the first inlet valve injection fuel Time of beginning is set as via the first inlet valve more, the period more postponed from top dead-centre to air entry side-blown time gas flow.
Patent document 4 is related to the device for realizing stratified combustion in the internal EGR of mobile engine, fuel injection Device is to the fuel that the first inlet valve sprays can be in the liquid fuel for completing injection in a flash.
Patent document 5 discloses: by the negative change rate of target EGR rate and defined threshold comparison, when the negative change rate is When more than above-mentioned threshold value, the response of the middle EGR gas that there is the closing motion with EGR valve during detecting the valve opening of EGR valve Delay；When detecting the operating lag of EGR gas, the closing period of inlet valve is corrected, so that actual compression ratio increases, and Correction fuel injection timing, to be close to compression top dead center.
Patent document 5 in the external EGR of diesel engine for coping with the operating lag of EGR gas.Via injector to each The fuel of in-cylinder injection is can be filled into the liquid fuel of combustion chamber in moment.
Patent document 6 is the pre-mixing pression ingiter motor of self-ignition combustion type, and the setting for detecting engine is defeated Out, with the increase of setting output, increase the equivalent proportion (setting according to the supply amount of fuel) of pre-mixed gas, and reduce reality Border compression ratio.The setting of engine exports, and in other words the output of required engine is with manual, or detection is applied to hair The load of the crankshaft of motivation and be arranged.Being somebody's turn to do " load for being applied to crankshaft " is that " in other words setting output is then starting for requirement The output of machine ", therefore the output of the output shaft of not instead of engine reality output, the output to engine setting, requirement.
Patent document 7 describes the fuel gas engine (ガ ス fuel エ Application ジ Application) in divided chamber gas engine Output is provided by revolving speed and torque.
Existing technical literature
Patent document
Patent document 1: International Publication No. 2015/060117
Patent document 2: European Patent Publication the 2136054th
Patent document 3:(Japan) tekiaki 62-99606
Patent document 4:(Japan) patent the 5502033rd
Patent document 5:(Japan) patent the 5338977th
Patent document 6:(Japan) special open 2002-21608
Patent document 7:(Japan) special open 2013-185515
Summary of the invention
Problems to be solved by the invention
Current fuel gas engine, even if increasing the supply of fuel gas earlier in order to quickly improve output Amount, booster can not also follow up, so that required air capacity cannot be supplied.This is because booster be by exhaust gas driven, because This is promoted when the output of fuel gas engine, when exhaust gas is not supplied to booster sufficiently, just can not effectively be worked.Work as air capacity When insufficient, air-fuel ratio will combustion gas it is superfluous, so that pinking occur, lead to plant failure.When the speed that can be followed up with booster When promoting output to inhibit this pinking, the promotion (Load lifting) of output needs 10 minutes or so time.It needs to illustrate It is that in this specification, the power of engine reality output uses " output " word in principle, to the function of engine setting, requirement Rate uses " load " word in principle, but " exports "=" load " in most cases, can also use " negative out of habit sometimes A lotus " word replaces " exporting " (or opposite).
On the other hand, it in ship device, since the discharge limitation of harmful exhaust is stringent year by year, also wishes to introduce into The discharge amount of the harmful exhaust from fuel can be reduced, the dual fuel engine of discharge limitation is met.But to introduce This dual fuel engine needs to foreshorten to the Load lifting time into 20 seconds or so the operational modes to meet ship device.
The present invention is the invention completed in view of the above subject, and it is an object of the present invention to provide one kind is able to suppress in promotion fuel gas The pinking that generates when the output of engine simultaneously shortens the Load lifting time, and the unburned fuel gas in apneustic overlapping The control method and engine system of the engine of deterioration in fuel consumption caused by gas blowby.
The means to solve the problem
That is, the inventors of the present invention have found: by with the valve opening of each VIVT angulation change fuel gas supply valve (supply starts) Time determines optimal value according to THC concentration, combustion state, and the duration of valve opening of fuel gas supply valve is arranged according to VIVT angle, It is possible thereby to inhibit the pinking occurred when the output for promoting fuel gas engine and shorten the Load lifting time, and then can change Fuel gas supply valve opens in kind torque excess areas (field ト Le Network リ ッ チ), torque shortage region (field ト Le Network プ ア) Combustion fluctuation caused by the valve time, rotation speed fluctuation, until completing the present invention.
The control method of engine of the invention is using combustion gas as the control method of the engine of fuel, which is characterized in that With the increase that engine exports, by adjusting the advance angle that air-breathing valve closing time shifts to an earlier date from sucking bottom dead centre, to be dropped Low burn burns the control of the compression ratio of indoor mixed gas, also, correspondingly supplies fuel gas with the variation of advance angle The duration of valve opening of valve shifts to an earlier date.
As the pinking suppression technology of engine, variable inlet valve timing (Variable Intake Valve can be used Timing；VIVT) mechanism reduces effective compression ratio.About this point, will by Figure 19 A, 19B come to pinking suppression technology into Row explanation.The step of Figure 19 A indicates the step of common four-stroke cycle, and Figure 19 B indicates Miller cycle.
Such as in fuel gas engine, inlet valve usually closes in the bottom dead centre of piston and (refers to Figure 19 A).Another party Face, as shown in Figure 19 B, upon closing between earlier than bottom dead centre when, inlet valve close valve after mixed gas also will continue to expand, therefore Cylinder temperature Ts is declined (Ts* < Ts) compared to Figure 19 A.Highest compression temperature when top dead-centre also only decline it is so more (Tc* < Tc), it thus it can be prevented that self-ignition, pinking are inhibited.
The shortcomings that Miller cycle, is that compression temperature can decline, and deteriorates so as to cause the ignition quality of low load region, therefore It needs to be restored to the duration of valve opening of common inlet valve shown in Figure 19 A when starting and when underload, will only be inhaled in high load capacity The duration of valve opening of air valve shifts to an earlier date.
In the control method of engine of the invention, is increasing the supply amount of fuel gas and increasing the fuel gas of output In engine, (advance angle) is shifted to an earlier date from sucking bottom dead centre by the time for closing inlet valve, is carried out in the combustion chamber of engine The control of the interior compression ratio for reducing mixed gas.By reducing compression ratio, so that the indoor temperature of burning when compression reduces, because This can inhibit pinking.
In addition, can be disliked with ignition quality when low output on startup when reducing the compression ratio of mixed gas in the combustion chamber The shortcomings that changing, and advantage can be deviateed in terms of efficiency of combustion, generating deterioration in fuel consumption.Therefore, the present invention is being easier to It generates in the higher operation area of output of pinking and more drastically change the time that inlet valve is closed, with bigger ratio Reduce the control of compression ratio.Thus, it is possible to inhibit pinking according to the variation of output, prevent deterioration in fuel consumption and shorten load Promote the time.Moreover, correspondingly mentioning the duration of valve opening of fuel gas supply valve by the variation with the advance angle of inlet valve Before, the gas blowby of unburned fuel gas can be reduced in the valve overlap of inlet valve and exhaust valve.
Preferably, with the progress of the advance angle of air-breathing valve closing time, the duration of valve opening of fuel gas supply valve is mentioned The degree of anterior angle is bigger.
Thus, it is possible to be further reduced the unburned fuel gas of combustion chamber in the valve overlap of inlet valve and exhaust valve Gas blowby.
Furthermore it is preferred that the closing valve time of fuel gas supply valve determines in the following manner: according to target rotational speed During calculating valve opening with the deviation of actual rotation speed, using the duration of valve opening of fuel gas supply valve as starting point, which is set Period.
According to the deviation of the target rotational speed of engine and actual rotation speed, such as pass through the feedbacks control such as PID control During making the valve opening to calculate fuel gas supply valve.By starting point of the duration of valve opening of fuel gas supply valve, the valve opening phase is set Between, it is possible thereby to determine the closing valve time of fuel gas supply valve.
Furthermore it is preferred that improving the supply pressure of fuel gas with the advance angle of air-breathing valve closing time.
The supply pressure that fuel gas is improved according to the advance angle of the closing valve time of inlet valve, it is possible thereby to during valve opening The amount of appropriate fuel gas of the interior supply for maintaining output.
Furthermore it is preferred that the duration of ignition of engine is shifted to an earlier date with the advance angle of air-breathing valve closing time.
According to the advance angle of the closing valve time of inlet valve, shift to an earlier date the duration of ignition in the range of NOx is limited to specified value, by The thermal efficiency can be improved in this.
In addition, the advance angle degree of the duration of ignition can also will be with the output and rotation speed of the engine of measured in advance Parameter and the ship for being provided as the boundary that torque excess areas and torque lack region use cube characteristic line as peak, In torque excess areas, ship cube characteristic line is compared, advance angle degree is reduced.
In this case, compared to making before air-breathing valve closing time shifts to an earlier date, use cube characteristic line as peak ship and The duration of ignition shifts to an earlier date in the forefoot area that torque excess areas and torque lack region, therefore there is entirety to limit NOx inhibition In range processed and the thermal efficiency improves this advantage.It should be noted that " ship cube characteristic " refers to output and rotation speed The characteristic of the proportional ship sustainer of the cube of degree, but in practical ship not necessarily accurately with cube It is proportional, have deviation to a certain degree.
Furthermore it is preferred that (torque sensor measures the torque of the output shaft of engine and obtains according to the output of engine Torque measuring definite value and (rotation speed sensor measures the rotation speed of the output shaft of engine and obtains) rotation speed out) The output valve for the output shaft that measured value is found out.
It is relatively difficult compared with liquid fuel since the combustion gas as fuel is elastomer in engine of the invention To obtain accurate fuel feed.It is therefore preferable that by using the practical progress torque rating of torque sensor, according to rotation The relationship of speed carrys out operation output.Moreover, passing through the rotation of the output shaft obtained from possessed rotation speed sensor The product for the torque measuring definite value that velocity measurement and torque sensor measure, the output that can find out engine output shaft in real time are (negative Lotus).It therefore, can be with the advance angle and fuel gas supply valve of the shut-in time of the inlet valve of good precision setting engine Duration of valve opening advance angle, therefore even if output increase, can also be improved efficiency of combustion, suitably carry out fuel gas engine Operation.
Furthermore it is preferred that the advance angle of air-breathing valve closing time is according to the output of multiple output shafts of measured in advance The value setting for the advance angle that the data of value and rotation speed are arranged for parameter.
The preferred value of the advance angle of the shut-in time of inlet valve can become much larger when exporting big, but also depend in addition to this In rotation speed.Therefore, pre-production includes at least the chart of both parameters, according to the output of engine and rotation speed Change to control the advance angle of the shut-in time of inlet valve, it is possible thereby to further suppress pinking.
Engine system of the invention is to include using combustion gas as the engine system of the four-stroke engine of fuel, feature It is, comprising: control unit, when the output of the output shaft of engine increases, the time for closing the inlet valve of engine is mentioned Before, and correspondingly shift to an earlier date the duration of valve opening of fuel gas supply valve with the variation of the advance angle；Variable inlet valve timing Mechanism changes the time that inlet valve is closed according to the shut-in time of the inlet valve of control unit setting；And fuel gas Supply valve timing mechanism correspondingly makes fuel gas supply valve with the variation of the advance angle of the inlet valve of control unit setting Duration of valve opening shifts to an earlier date, wherein with engine output shaft output increase, by can be changed inlet valve timing mechanism, carry out into One step reduces the control of the compression ratio of the mixed gas of in-engine combustion gas and air.
In the control method of engine system of the invention, when the supply amount increase of fuel gas and the output shaft of engine Output increase when, by make inlet valve close time from sucking bottom dead centre shift to an earlier date, progress dropped in the combustion chamber of engine The control of the compression ratio of low mixed gas.By reducing compression ratio, so that the indoor temperature of burning when compression reduces, therefore can To inhibit pinking.
Moreover, the present invention carries out the time for closing inlet valve more in the higher operation area of output for being more also easy to produce pinking It drastically changes, the control of compression ratio is reduced with bigger ratio.Thus, it is possible to inhibit pinking according to the variation of output, prevent Only deterioration in fuel consumption and shorten the Load lifting time.Moreover, by correspondingly making to fire with the variation of the advance angle of inlet valve The duration of valve opening of material air supply valve shifts to an earlier date, and the crankshaft angles closed for inlet valve can be in the valve of inlet valve and exhaust valve The gas blowby of unburned fuel gas is reduced when overlapping.
Furthermore it is preferred that including: torque sensor, the torque of the output shaft of engine is measured；And rotation speed passes Sensor measures the rotation speed of the output shaft of engine, wherein the torque measuring definite value and rotation measured according to torque sensor The rotation speed measured value that velocity sensor measures, when finding out the output of output shaft, and the closing of inlet valve in control unit being set Between change.
In fuel gas engine of the invention, since the combustion gas as fuel is elastomer, with liquid fuel phase Than being relatively difficult to obtain accurate fuel feed.It is therefore preferable that by using the practical progress torque rating of torque sensor, According to the relationship with rotation speed come operation output.Moreover, as defeated obtained from possessed rotation speed sensor The product for the torque measuring definite value that the rotation speed measured value and torque sensor of shaft measure, can find out engine output shaft in real time Output.
Invention effect
The control method and engine system of engine through the invention, when the output of the output shaft of engine increases When, the compression ratio of in-engine mixed gas can be reduced, therefore pinking when Load lifting can be inhibited and shorten load Promote the time.
Moreover, because being that adjustment with the advance angle of inlet valve correspondingly mentions the duration of valve opening of fuel gas supply valve Before, thus can improve Combustion fluctuation caused by the duration of valve opening of fuel gas supply valve, rotation speed fluctuation, suitably into The operation of row fuel gas engine.
Detailed description of the invention
Fig. 1 is the block diagram for indicating the major part of the ship dual fuel engine of embodiment of the present invention and constituting.
Fig. 2 is the figure for indicating diesel fuel mode and combustion gas mode in dual fuel engine shown in FIG. 1.
Fig. 3 is the three-dimensional chart (3 dimension マ ッ プ) for indicating the relationship of output, rotation speed and VIVT instruction value.
Fig. 4 is the three-dimensional chart for indicating the relationship of closing valve time of output, rotation speed and inlet valve.
Fig. 5 is to indicate that output and optimal VIVT refer in the case where the rotation speed of output shaft is certain situation and variation Enable the curve graph of the relationship of value.
Fig. 6 is the duration of valve opening and THC concentration for indicating the fuel gas supply valve when various differences occurs in VIVT instruction value Relationship curve graph.
Fig. 7 is to indicate in the case where the rotation speed of output shaft is certain situation and variation, output and fuel gas The curve graph of the relationship of the duration of valve opening of supply valve.
Fig. 8 is the curve graph for indicating the supply beginning period of fuel gas corresponding to VIVT instruction value.
Fig. 9 is the figure for indicating to carry out the composition of the control device of the PID control of ship dual fuel engine.
Figure 10 is the figure for indicating to carry out the step of PID control is to become target rotational speed for actual rotation speed.
The timing diagram of the switch motion of inlet valve and fuel gas supply valve when Figure 11 is usual and when advance angle.
Figure 12 be indicate output, fuel gas supply valve valve opening during and fuel gas pressure Δ P relationship figure.
Figure 13 is the three-dimensional chart for indicating the relationship of pressure Δ P of output, rotation speed and fuel gas.
Figure 14 is the variation for indicating NOx corresponding to air-fuel ratio and the curve graph of usable range.
Figure 15 is the three-dimensional chart for indicating the relationship of rotation speed, output and supply gas pressure.
Figure 16 be indicate when air-breathing valve closing time be certain situation and advance angle the case where when output and supply gas pressure Relationship curve graph.
Figure 17 is the three-dimensional chart for indicating rotation speed, output and the relationship of the duration of ignition.
Figure 18 is the curve graph of the relationship of the NOx and the thermal efficiency when indicating duration of ignition change.
The step of Figure 19 A is the ordinary cycle in the burn cycle of engine figure.
The step of Figure 19 B is the Miller cycle in the burn cycle of engine figure.
Figure 20 is the perspective view for indicating an example of existing variable inlet valve timing mechanism.
Figure 21 is the front view for indicating an example of existing variable inlet valve timing mechanism.
Figure 22 is another perspective view for indicating existing variable inlet valve timing mechanism.
Figure 23 is the figure for indicating an example again of existing variable inlet valve timing mechanism.
Figure 24 is the relationship for indicating actuator and pitman shaft in existing variable inlet valve timing mechanism shown in Figure 22 Figure.
Invention embodiment
In the following, the engine as embodiments of the present invention, based on attached drawing to such as four as marine engines Stroke dual-fuel engine 1 is illustrated.
Fig. 1 and ship shown in Fig. 2 have diesel fuel mode D with dual fuel engine 1 (hereinafter sometimes referred to simply as engine 1) With each machine of combustion gas mode G, it can be switched to diesel fuel mode D and combustion gas mode G in operation.Double fuel hair shown in FIG. 1 Motivation 1 has 2 mechanism of crankshaft as the output shaft with the connections such as propeller (プ ロ ペ ラ), crankshaft 2 and is arranged in cylinder block 3 Piston 4 link.Piston 4 in cylinder block 3 is set and engine lid 5 forms combustion chamber 6
Combustion chamber 6 is by the inlet valve 8 and exhaust valve 9 that are mounted in engine lid 5, the combustion used at diesel fuel mode D Expect that injection valve 10 seals.In addition, being provided with micro- light fluid injection valve (the マ イ used under combustion gas mode in engine lid 5 Network ロ パ イ ロ ッ ト oil spurts man's cap used in ancient times) 11.In the air entry for the inlet valve 8 for being provided with engine lid 5, it is connected with air intake duct 13, The exhaust outlet for being provided with exhaust valve 9 is provided with exhaust pipe 14.It is provided in air intake duct 13 by the solenoid valve of control fuel gas injection The fuel gas supply valve 15 of composition is provided with aerial cooler 16, the booster being connected to exhaust pipe 14 17 at upstream side.
Here, the dual fuel engine 1 of present embodiment is as shown in Fig. 2, diesel fuel mode D and combustion gas mode can be switched to G operation.At diesel fuel mode D, such as can pressure by A heavy oil etc. as fuel oil from from fuel injection valve 10 to combustion chamber 6 Spray to contracting aero-mechanical simultaneously ignition.At combustion gas mode G, by the fuel gas such as natural gas fuel gas supply valve 15 supply to air intake duct 13, are pre-mixed, mixed gas are supplied into combustion chamber 6, in the compression shape of mixed gas with air stream From micro- 11 pilot fuel of light fluid injection valve, ignition under state.Micro- light fluid injection valve 11 is few for example by being controlled electronically Measure pilot fuel, the incendiary source as strength.Fuel gas supply valve 15 is to form big opening with small stroke, can be The solenoid valve for flowing bulk gas in short time.
Engine 1 is starting under the diesel fuel mode D of injecting LPG in liquefied condition from fuel injection valve 10 into combustion chamber 6.True After recognizing the gaseous-pressure more than 1 pay standard value of engine, using fuel gas supply valve 15 by fuel gas to air-breathing Pipe 13 supplies, and mixes with air in rear flowing in combustion chamber 6, runs under the combustion gas mode G for making fuel gas burn.
When stopping, stopping after being altered to diesel fuel mode D again.When other than when starting and when stopping, it can changing Diesel fuel mode D and combustion gas mode G.
The dual fuel engine 1 of present embodiment has gas engine system, and the gas engine system is in combustion gas mould It will do it output control when load rises under formula G.The structure of the gas engine system is further detailed below.
In Fig. 1, rotation speed sensor 20 and torque sensor 21 are installed in crankshaft 2, rotation speed sensor 20 is counted The rotation speed (revolving speed) of crankshaft 2 is surveyed, torque sensor 21 measures engine torque.As torque sensor 21, such as can be with Use the sensor that the torque being applied on axis is detected according to deformation.Rotation speed sensor 20 and torque sensor 21 are counted The determination data of survey is output to the control unit 22 of control engine 1 respectively with signal form.
The signal that control unit 22 is sent based on rotation speed sensor 20 and torque sensor 21 etc., detection engine 1 Operating status.That is, the rotation speed (revolving speed) for the crankshaft 2 that rotation speed sensor 20 is measured is set as n, torque sensor 21 The torque measured is set as T, passes through output (load) A of following formula (1) and formula (2) operation engine 1.Wherein, Lt is The rated output of engine 1.
It exports Lo=2 π Tn/60 (1)
It exports (load) A=Lo/Lt × 100 (2)
In addition, asking method, the operation shape of with good grounds fuel feed etc. and engine 1 as the output of engine 1 (load) Torque sensor is arranged the method that is speculated, and in the power-transmission system of 1 output shaft of engine in the relevant information of state 21 and carry out torque rating actually come the method that finds out output.In fuel gas engine, since the combustion gas as fuel is bullet Property body, therefore compared with liquid fuel, it is relatively difficult to obtain accurate fuel feed.It is therefore preferable that by being passed using torque The practical torque rating that carries out of sensor 21 carrys out operation output.
In addition, when mono- timing of rotation speed n, output A and torque measuring definite value T is proportional.Certain in rotation speed n Under the conditions of, output A is bigger, i.e. torque data T is bigger, more hope mentioning with the shut-in time of bigger ratio setting inlet valve 8 Anterior angle.
The first chart 24 of the first electric signal for the determination inlet valve switch time being pre-created is stored in control unit 22, And determine the second chart 25 of switch time corresponding with the first electric signal.Control unit 22 is based on 20 He of rotation speed sensor Rotary speed data n and torque data T corresponding to the output A with engine 1 that torque sensor 21 is measured, by above-mentioned The output A of formula (1) and formula (2) operation engine 1.And it by rotation speed n and output A, is selected in the first chart 24 Select the first electric signal corresponding to the switch time of inlet valve 8.According to first electric signal, determined in the second chart 25 and the The switch time of the corresponding inlet valve 8 of one electric signal.In addition, the creation method about the first chart 24 and the second chart 25, It will will be described later.
The second electric signal of switch time set by control unit 22 is sent to electro-pneumatic converter 27, electro-pneumatic converter 27 The signal of switch time is converted into air pressure.The air pressure is sent to actuator 28, controls variable inlet valve positive opportunity The driving of structure 30.The air for driving and controlling is supplied from the first pressure reducing regulator 34 and electro-pneumatic converter 27 to actuator 28 Pressure P1, P2.
In addition, the air pressure for being supplied to actuator 28 is compressed by air compressor 32, air tank 33 is arrived in storage.Air tank Air pressure in 33 is decompressed to required pressure by the first pressure reducing regulator 34.Pressure at this time is adjusted by changing the first decompression The valve opening of device 34 is saved to adjust, is supplied to actuator 28 as the air pressure P1 for driving.It is measured when pressure gauge 36 When pressure P1 is below specified value, engine 1 can not start.
For driving the air pressure of electro-pneumatic converter 27 further to be adjusted from the first pressure reducing regulator 34 by the second decompression Section device 37 is supplied after depressurizing.Electro-pneumatic converter 27 is by air pressure corresponding with the second electric signal of the switch time of input Power is supplied as the air pressure P2 for adjusting the work of actuator 28 to actuator 28.According to air pressure P1, P2, make The bar 28a of actuator 28 is moved, so that variable inlet valve timing mechanism 30 be made to work.
Actuator 28 is, for example, well known P cylinder (cylinder (Port ジ シ ョ Na リ pays I シ リ Application ダ) in subsidiary site), is based on Pressure P1, P2 inputted from the first pressure reducing regulator 34 and electro-pneumatic converter 27 carrys out the forward-reverse of control-rod 28a.Pass through change The movable length of the bar 28a of actuator 28 controls the driving of variable inlet valve timing mechanism 30, makes the shut-in time of inlet valve 8 Shift to an earlier date (advance angle) or delay (delay angle) from sucking bottom dead centre, to reduce the control of compression ratio.
Time between the duration of valve opening and closing valve time of inlet valve 8 is constant, so if the time of valve opening is under sucking Dead point shifts to an earlier date, then the time for closing valve also can shift to an earlier date same time from sucking top dead-centre.Moreover, the present invention passes through according to engine 1 Output change valve opening and close valve time, to inhibit pinking and shorten the Load lifting time.Output A based on engine 1 and The switch time of inlet valve 8 is arranged by the first chart 24 in control unit 22 and the second chart 25, is passed through by rotation speed n Actuator 28 and variable inlet valve timing mechanism 30 are adjusted to the time of the valve opening of inlet valve 8 and pass valve to be able to suppress pinking.
The composition of variable inlet valve timing mechanism 30 is current known composition, has and constitutes with shown in Figure 20 to Figure 24 Identical composition.That is, for can be changed inlet valve timing mechanism 30, such as pitman shaft is matched with the camshaft of eccentric cam is parallel If rotation angle range is arranged via sector gear by the movable length of the bar 28a of actuator 28 in the pitman shaft.In connecting rod Axis connection has exhaust rocker arm, in the tappet axis for the from deviating from the position for being set to pitman shaft, is connected with air-breathing rocker arm.It is used in air-breathing Rocker arm is connected with inlet valve 8 via push rod and rocking bar；In exhaust rocker arm, exhaust valve 9 is connected with via push rod and rocking bar.
According to the rotation angle of tappet axis corresponding with the rotation of pitman shaft, the distance meeting of camshaft and air-breathing rocker arm It changes, the time that the eccentric cam of camshaft starts touching can change.Thus, it is possible to which closing valve time is changed to mention Anterior angle (or delay angle).Distance from tappet axis to camshaft center is remoter, and the closing valve time of inlet valve 8 is more early.Tappet axis Rotation angle changes according to the movable length of the bar 28a of actuator 28.The movable length of bar 28a is according to being supplied to actuator 28 Control air pressure P1, P2 and arbitrarily change.
The size of advance angle as 8 switch time of inlet valve is according to the air-breathing rocker arm with the connection of the tappet axis of pitman shaft Start the time of touching with the eccentric cam of camshaft and determines.
In addition, servo electricity (not shown) also can be used in the rotating device of the tappet axis in variable inlet valve timing mechanism 30 Machine substitutes actuator 28.At this point, the signal of the switch time issued from the second chart 25 of control unit 22 can be input to servo Motor.Servo motor makes pitman shaft only rotate amount corresponding with the signal received and rotates tappet axis, thus relative to convex Wheel shaft can change the switch time of inlet valve 8 close to separate.In addition, not needing 28 He of actuator when using servo motor The composition of 32~pressure gauge of air compressor 38.In addition, the substitution as electro-pneumatic converter 27, uses controller driving servo electricity Machine.
In addition, just supplying the supply machine of fuel gas to the fuel gas supply valve 15 for controlling air intake duct 13 fuel gas injection Structure is illustrated.In Fig. 1, combustion gas is supplied to gas evaporators 41 from the LNG gas tank 40 for storing the fuel gas such as natural gas Fuel, then gaseous-pressure is depressurized to required air pressure by gas conditioner 42.
Air pressure at this time is shown on fuel gas pressure meter 43, and the valve opening by changing gas conditioner 42 is adjusted It is whole, it is supplied from fuel gas supply valve 15 into air intake duct 13, as fuel gas used for combustion.In air intake duct 13, combustion Gas fuel and the pressurized air mixing cooled down by aerial cooler 16, are supplied to combustion chamber 6.In Load lifting, pass through fuel The movement of air supply valve 15 increases the supply amount of fuel gas.
Moreover, the second electric signal for the switch time that control unit 22 is arranged is via the fuel gas for being different from electro-pneumatic converter 27 Body supply timing unit 44 is sent to fuel gas supply valve 15.Fuel gas supplies timing unit 44 according to inlet valve 8 The advance angle of shut-in time mentions the duration of valve opening opened fuel gas supply valve 15 and supply fuel gas into air intake duct 13 Preceding mode is controlled.The combustion for adjusting the gas conditioner 42 of air pressure and shifting to an earlier date the duration of valve opening of fuel gas supply valve 15 Both material gas supply timing units 44 are comprised in fuel gas supply valve timing mechanism 45.
It should be noted that fuel gas supply timing unit 44 also can be set in the outside of control unit 22.Fuel gas Body supply valve timing mechanism 45 also can receive the second electric signal from the second chart 25, according to the shut-in time of inlet valve 8 Advance angle, shift to an earlier date the duration of valve opening of fuel gas supply valve 15.
The creation method of the first chart 24 and the second chart 25 that store in control unit 22 is illustrated below.Fig. 3 is Indicate that the three-dimensional chart of the first chart 24, first chart 24 pass through the rotation speed of crankshaft 2 and the output of engine 1 in detail (rate of load condensate) determines VIVT instruction value (inlet valve closes crankshaft angles, Intake Valve Closed timing, IVC), i.e., Determine the crankshaft angles when pass valve of inlet valve 8.
In Fig. 3, the region B of common ground (practicably) operation is represented by dashed line.In contrast, relative to carrying out in power generation The variation (advance angle) of the VIVT instruction value of the variation of the output of one timing of rotation speed is indicated with arrow line C；Ship use in into The variation (advance angle) of VIVT instruction value when capable rotation speed and output (rate of load condensate) change simultaneously is indicated with arrow line D. Arrow line D indicates ship cube characteristic.Ship indicates that output is proportional to the cube of rotation speed with cube characteristic Ship sustainer representative characteristic, be the rotation speed determined according to the specified rotation speed of engine, rated output The characteristic curve of degree and output.Moreover, in the region of common operation area B, compared with ship is with cube characteristic line D, Exporting (rate of load condensate) high region indicates that torque excess areas, the low region of output (rate of load condensate) indicate that torque lacks region.
The process of experimental procedure (1)~(18) based on following of first chart 24 and create.
Used same type of dual fuel engine 1 in practice is used in experiment.
(1) start engine 1, rotation speed (revolving speed) n is set as 400min-1, it exports (load) A and is set as 10%, air-breathing The closing valve time of valve 8 is set as 545deg (closing valve time in structure the latest).
(2) then, the abnormal combustion referred to as pinking generated when measurement engine 1 drives and delivery temperature at that time.
The generation of pinking is detected by being installed on the detonation sensor (not shown) of each engine lid 5.Pinking occurs When phenomenon, the waveform for being overlapped high-frequency pressure oscillation on common burning waveform and being formed will become.
In addition, measuring delivery temperature when pinking measurement by the temperature sensor for being installed on exhaust pipe 14.
(3) after delivery temperature when having measured above-mentioned pinking measurement, the closing valve time of inlet valve 8 is reduced into 5deg, again Carry out the measurement of (2).Closing valve time is altered to 500deg (earliest closing valve time in structure) to measure.
(4) after the measurement of above-mentioned (3), every 10% ground A will be exported and be stepped up to 110%, (2) are repeated again (3) measurement.
(5) by the measurement of above-mentioned (1)~(4), by knock intensity be standard value or less and delivery temperature is 500 DEG C or less The case where be judged as that pinking is inhibited and engine 1 can be safely operated.
(6) according to the measurement of above-mentioned (5) as a result, Y-axis is set as rotation speed n, and Z axis is set as out X-axis is set as output A In the solid curve figure for closing Fig. 4 of time, the picture on the measurement point that can be safely operated ● (black circle), in unsafe measurement point Upper picture ×.Thus, it is possible to which the pinking in the relationship of selected output A, revolving speed n and closing valve time inhibits range.
(7) by the every 100min of rotation speed n-1Ground is promoted to 900min-1, carry out the measurement step of above-mentioned (1)~(6), meter Survey the range of each rotation speed n being safely operated.
(8) Fig. 4 is the curve that the measurement result of above-mentioned (7) is indicated with rotation speed n, output A, closing valve time these three axis Figure.It is that pinking is inhibited with the range that straight line surrounds in Fig. 4, the range that engine 1 can be safely operated.
(9) then the experiment by above-mentioned (1)~(8) measure it is shown in Fig. 4 make engine health run It is standard value hereinafter, thermal efficiency highest to pursue nitrogen oxides (hereinafter referred to as NOx) in the range of the solid region that straight line is surrounded Setting for the purpose of, further progress experiment.
Engine rotary speed n is set as 400min-1, export A and be set as 10%, the closing valve time of inlet valve 8 is set as 545deg。
(10) NOx and the thermal efficiency are then measured.NOx is measured by being installed on the heat prover of exhaust pipe 14.Thermal effect Rate is then according to (being installed on what the fuel flow meter of fuel distribution tube was measured) fuel flow rate L and (by the meter of torque sensor 21 Survey result and calculate) output A, (3) calculate according to the following equation.
Thermal efficiency η=360Lo/H/L (3)
Wherein, H: the low heat valve (J/Nm of fuel gas3)
Lo: current output
L: fuel flow rate
(11) after the measurement of above-mentioned (10), the every 5deg of the closing valve time of inlet valve 8 is reduced, carries out (10) again Measurement.Closing valve time is altered to 505deg to be measured (with reference to Fig. 9).
(12) after the measurement of above-mentioned (10) and (11), every 10% ground will be exported and be stepped up to 110%, repeated again Carry out the measurement of (10) and (11).Closing valve time is shown in Fig. 4 be safely operated in the range of change.
(13) by the every 100min of rotation speed n-1Ground is stepped up to 900min-1, the measurement of above-mentioned (9)~(12) is carried out, Determine the optimal measurement point of the performance of each rotation speed.
(14) after, according to each rotation speed n and output A, setting NOx is specified value hereinafter, the highest suction of the thermal efficiency The closing valve time of air valve 8.According to this as a result, the original bill of creation the first chart shown in Fig. 3.
(15) then, rotation speed n and output A are promoted according to arbitrary Load lifting mode, detects pinking.Load lifting Mode refers to the variable condition of output A (rate of load condensate) and the unit time of rotation speed n, according to the spiral of ship propulsion device Paddle specification (shape, revolving speed) and change.
(16) knock intensity for detecting above-mentioned (15) is that the closing valve time of the measurement point of standard value or more reduces 3deg.
(17) after, repeat (15) and (16) the step of, until knock intensity become standard value hereinafter, determination pinking obtain The closing valve time of inhibition.When reducing closing valve time, the thermal efficiency can deteriorate.To obtain NOx, knock intensity be standard value below and The setting of the closing valve time of the highest result of the thermal efficiency, the setting value as rotation speed n, output A.
(18) inhibit the closing valve time of pinking, root by above-mentioned (17) by measuring respectively with each rotation speed n, output A According to this as a result, creation the first final chart 24 shown in Fig. 3.
In Fig. 3, curve graph (the 3 dimension planes of VIVT instruction value 3 D plane corresponding with rotation speed and output グ ラ Off) it indicates, upside is the direction of closing valve time further in advance in figure.On 3 D plane, represented by dotted line Region is operation area practical used in the operation of actual marine propulsion, an example of good Load lifting mode It is indicated with ship with cube characteristic line D.In Load lifting in practical operation area, the output for carrying out engine is bigger, More increase the control of the advance angle of closing valve time.
For ship in an example of the cube characteristic line D good Load lifting mode indicated, rotation speed and output are small Figure in lower right, advance angle is set as minimum, with the increase of rotation speed and output, increases advance angle.Increase mentions Although the ratio of anterior angle be not it is certain, as a whole, output more increase, advance angle sets bigger.It should be noted that by It is to be found out according to the product of torque and rotation speed, therefore the torque that also can be expressed as output shaft is got in output (rate of load condensate) Greatly, more increase advance angle.
Later, the second chart 25 is created by following experiments.
When carrying out rotation control to variable inlet valve timing mechanism 30 by actuator 28, the is created according to the following steps Two charts 25.
(1) closing valve time is changed by actuator 28, measurement is changed to pressure when each closing valve time.
(2) according to the specification of electro-pneumatic converter 27, the second electric signal needed for investigation supplies the pressure of above-mentioned (1).
(3) according to above-mentioned (1) and (2) as a result, the second chart 25 of creation, wherein horizontal axis indicates to pass through above-mentioned first figure The first electric signal that table 24 selects, the longitudinal axis indicate closing valve time (the second electric signal).
In addition, above explained the case where being using actuator 28, when replacing actuator 28 to variable using servo motor It is following to carry out when inlet valve timing mechanism 30 carries out rotation control.
(1) closing valve time is changed based on servo motor, measurement is changed to the second electric signal when each closing valve time.
(2) according to above-mentioned (1) as a result, the second chart 25 of creation, wherein horizontal axis indicates that the first electric signal, the longitudinal axis indicate Closing valve time (the second electric signal).
Second chart 25 is the chart for indicating the relationship of closing valve time (the second electric signal) and the first electric signal.
In three-dimensional chart shown in Fig. 3, in the characteristic line and ship cube characteristic for power generation that solid line C is indicated On line D, optimal VIVT instruction value is different according to output.That is, as shown in an example in Fig. 5, though output phase simultaneously, such as Fruit rotation speed is different, then the inlet valve closing crankshaft angles of optimal VIVT instruction value also can be different.
It is corresponding with the variation of VIVT instruction value in present embodiment, i.e., crankshaft angles are closed relative to various inlet valves, The duration of valve opening that the fuel gas supply valve 15 of fuel gas is supplied to air intake duct 13 is set, to reduce inlet valve 8 and exhaust valve 9 Valve overlap when gas blowby from caused unburned fuel gas to exhaust pipe 14.For this purpose, setting and rotation speed and defeated first Corresponding VIVT instruction value out.Strictly speaking, preferably using the thermal efficiency and NOx as target, in advance also by air-fuel ratio and igniting when Phase is arranged to optimal value, but it is assumed that engine 1 can stable operation, and be not provided with these conditions.
As setting fuel gas supply valve 15 duration of valve opening an example, below explanation with ship cube characteristic Timing unit 44 is supplied by fuel gas under the corresponding engine operational conditions of optimal VIVT instruction value in line D and determines combustion Expect the method for the duration of valve opening of air supply valve 15.
Firstly, being set as 25%, 50%, 75%, 100% each service condition in the output (rate of load condensate) by engine Under, using the opening time of inlet valve 8 as standard, fuel gas is supplied from fuel gas supply valve 15, but due to air intake duct 13 Interior supply fuel gas, therefore fuel gas will not reach inlet valve 8 moment.Therefore, to imagine in view of being supplied from fuel gas To the crank angle position of the duration of valve opening of the fuel gas supply valve 15 of the distance of valve 15 to inlet valve 8.Then, by fuel gas Crank angle position in the duration of valve opening of body supply valve 15 is altered to its front and back 5deg scale, measures booster 17 at this time Unburned gas, that is, total hydrocarbon concentration (THC concentration) in the exhaust gas of gas turbine outlet.It repeats to implement under each service condition The measurement of THC concentration.It is preferable to use hydrogen flame ionization method (JIS B 7956) measurements for THC concentration.
The duration of valve opening for changing fuel gas supply valve 15 according to each condition, by each VIVT instruction value, (inlet valve is closed Crankshaft angles) for example it is set as 40%, 65%, 85%, 100%, there is shown when fuel gas valve opening in each VIVT instruction value Between and measurement THC concentration relationship, as shown in Figure 6.
As shown in fig. 6, the duration of valve opening of fuel gas supply valve 15 is by the gas blowby of unburned fuel gas when valve overlap Few, THC concentration becomes minimum crankshaft angles as benchmark.On the other hand, if output variation leads to fuel gas supply valve 15 duration of valve opening change dramatically, then it is related with above-mentioned Combustion fluctuation and rotation speed variation.Therefore, make and export to be formed The variable quantity of the duration of valve opening of corresponding fuel gas supply valve 15 becomes minimum tendency, from selected benchmark ± The crankshaft angles of the fuel gas duration of valve opening as optimal fuel gas supply valve 15 are selected in the range of 5deg.C.A, and Crankshaft angles corresponding with the optimal duration of valve opening of fuel gas supply valve 15 are determined under the conditions of each.
By so determining optimized fuel air supply valve of the ship in the optimal VIVT instruction value of cube characteristic line D The crankshaft angles of 15 duration of valve opening and the relationship of output (rate of load condensate) are indicated with the broken line of " the rotation speed variation " of Fig. 7.
Similarly, the optimal VIVT in the certain output of the rotation speed indicated with the power generation of Fig. 3 with characteristic line C is instructed " the rotation of relationship Fig. 7 of the crankshaft angles and output (rate of load condensate) of the duration of valve opening of optimized fuel air supply valve 15 in value Rotary speed is certain " broken line indicate.
As shown in fig. 7, the duration of valve opening about optimal fuel gas supply valve 15, even if output phase is same, in rotation speed It, as a result also can be different under conditions of the condition and rotation speed of degree variation are certain.
But about optimal fuel gas supply valve of the ship in the optimal VIVT instruction value of cube characteristic line D The crankshaft angles of 15 duration of valve opening, and generate electricity with optimal in the optimal VIVT instruction value of characteristic line C (rotation speed is certain) Fuel gas supply valve 15 duration of valve opening crankshaft angles, as shown in figure 8, using VIVT instruction value as horizontal axis with replace it is defeated It is adjusted out, then the two shows a consistent line chart characteristic.That is, it follows that optimized fuel air supply valve 15 Duration of valve opening is not dependent on output, but depends on VIVT designated value (inlet valve closing crankshaft angles).
As shown in Figure 8, when changing the pass valve period of inlet valve 8 by can be changed inlet valve timing mechanism 30, then with suction The progress of the advance angle of the shut-in time of air valve 8, the degree of the advance angle of the supply time started of fuel gas supply valve 15 is more Greatly.
Therefore, timing unit 44 is supplied by fuel gas, on the basis of VIVT instruction value, be arranged under the conditions of each really The crankshaft angles of the duration of valve opening of fixed optimal fuel gas supply valve 15, it is possible thereby to realize fuel by VIVT instruction value The optimization of the duration of valve opening of air supply valve 15.It should be noted that in fig. 8, about the VIVT instruction value not measured and combustion Expect gas supply beginning period etc., can be determined by the approximate line of the data before and after connection measuring point.
Then, the time for terminating supply fuel gas to fuel gas supply valve 15 by Fig. 9 and Figure 10, which controls, to carry out Explanation.
Fig. 9 indicates that the major part of engine 1 shown in FIG. 1 is constituted.In Fig. 9, the outside of control unit 22 is provided with mesh Rotational speed command portion 50 is marked, inputs preset target rotational speed to control unit 22.The gas supplying time meter of control unit 22 Calculation portion 51 based on according to the actual rotation speed of the measured value operation of rotation speed sensor 20 and the deviation of target rotational speed, To directly carrying out PID control during the valve opening of fuel gas supply valve 15.
The air supply valve control unit 52 connecting with gas supplying time calculation part 51 carries out feedback control and makes with fuel The duration of valve opening of air supply valve 15 is starting point, and operation answers the time of valve opening and is output to fuel gas supply valve 15, so that combustion Expect the only valve opening within the time for answering valve opening of air supply valve 15.
The closing valve time control of fuel gas supply valve 15 is following to be carried out.That is, as shown in Figure 10, control unit 22 is based on target The deviation of target rotational speed and actual rotation speed that rotational speed command portion 50 is arranged, to opening for fuel gas supply valve 15 PID control is directly carried out during valve.Specifically, the deviation based on target rotational speed and actual rotation speed is controlled by feedback It makes to control the time of each 15 valve opening of fuel gas supply valve, so that actual rotation speed follows target rotational speed.
Air supply valve control unit 52 is based on the valve opening phase calculated using the duration of valve opening of fuel gas supply valve 15 as starting point Between, carry out the control of the closing valve time of each fuel gas supply valve 15.Valve opening phase of the control unit 22 to fuel gas supply valve 15 Between directly carry out PID control, so that actual rotation speed and target is rotated speed with the fuel gas scale of construction without preparatory operation supply Degree is consistent.
The supply pressure control of aftermentioned fuel gas carries out feedback control to the pressure regulator 55 of fuel gas, so that By in pressure Δ P value that the data of the output of engine 1 and rotation speed are parameter setting plus being arranged in air intake duct 13 Supply gas pressure meter 54 detect the obtained value of supply gas pressure and the value of fuel gas pressure meter 43 between there is no deviation.
If indicating, the advance angle of the variable inlet valve timing mechanism 30 of display the above results and fuel gas supply timing list The relationship of the time of the supply beginning and end of the fuel gas supply valve 15 of 44 setting of member, then as shown in figure 11.
The crankshaft angles of engine 1 and the valve stroke (バ Le Block リ Off ト) of inlet valve 8 and exhaust valve 9 are illustrated in Figure 11 Relationship.In the curve of switch motion for indicating inlet valve 8, what solid line indicated is VIVT (variable inlet valve timing) instruction value Switch motion image when being 0%, the switch motion figure of (VIVT instruction value is 100%) when what single dotted broken line indicated is advance angle Picture.Moreover, during the valve opening of the fuel gas supply valve 15 when being 0% relative to VIVT instruction value, (VIVT instruction when advance angle Become longer during valve opening of the value for fuel gas supply valve 15 100%).
Furthermore it is preferred that the advance angle of the closing valve time with inlet valve 8, improves the supply pressure of fuel gas and increasing Big fuel feed.Therefore, in Fig. 9, the supply pressure that fuel gas is supplied into air intake duct 13 is set as being set to suction Plus resulting size after pressure Δ P value in the supply gas pressure that supply gas pressure meter 54 in tracheae 13 detects.Pressure Δ P is as hereinafter It is described, it is using the data of the output of multiple engines 1 of measured in advance and rotation speed as parameter setting.As a result, from combustion Expect the advance angle for the time that the supply pressure for the fuel gas that air supply valve 15 supplies is closed with inlet valve 8 and improves.
It is illustrated below for the setting method of the pressure Δ P of fuel gas.
Figure 12 be indicate output, fuel gas supply valve 15 valve opening during and pressure Δ P relationship figure.It will output (rate of load condensate) and rotation speed change the service condition of engine 1 as parameter, change pressure Δ P in each condition, obtain each Pressure Δ P in output and during the valve opening of fuel gas supply valve 15.It is low when being set pressure Δ P according to output and rotation speed When, it can be elongated during the valve opening of fuel gas supply valve 15, when too long during valve opening, it will be unable to during inlet valve 8 is opened Supply fuel gas appropriate.On the contrary, can shorten during the valve opening of fuel gas supply valve 15 when pressure Δ P is set high, supply It can deteriorate to the controlling of amount.Therefore, pressure Δ P should be set as the pressure for not having baneful influence to the operating status of engine 1 ΔP。
When by spin speed profile, identical step is also repeated, determines pressure Δ P.In Figure 12, about fuel gas The lower limit value of duration of valve opening is arranged by the way that the upper limit of pressure Δ P is arranged in supply valve 15, by be arranged the lower limit of pressure Δ P come Upper limit value during valve opening is set.By during these valve opening upper limit value and lower limit value in the range of fit as changeable amplitude When the setting value of setting pressure Δ P, the median of upper limit value and lower limit value is preferably set as setting value.
In addition, the meeting that is distributed due to mixed gas changes because of the supply pressure of fuel gas, it should also be appreciated that Combustion state.In Figure 12, about the condition not measured, the approximate line of the data of point front and back can be measured by connection to determine.
In this way, describing the Δ P of setting, then as shown in figure 13 using output (rate of load condensate) and rotation speed as parameter.In Figure 13 Shown in using output, rotation speed and pressure Δ P as in the three-dimensional chart of parameter, the range that dotted line indicates is common (practical ) operation area, solid line then indicates ship cube characteristic.
In addition, since fuel gas supply pressure is determined according to pressure Δ P, when supply gas pressure variation, combustion The supply pressure of material gas can also change.That is, being expressed as setting the differential pressure of the upstream and downstream of fuel gas supply valve 15 It sets, the amount of fuel gas even if is worked as air pressure depending on during the front and back differential pressure and valve opening of fuel gas supply valve 15 It, will not relationship during the valve opening to determining herein fuel gas supply pressure and fuel gas supply valve 15 when power changes It affects greatly.
As shown in Figure 13, if the output (rate of load condensate) of engine 1 becomes larger, i.e., as the time that inlet valve 8 is closed mentioning Anterior angle, the supply pressure of the fuel gas comprising pressure Δ P can also increase.
It is illustrated below for the determination method of the supply gas pressure (air-fuel ratio) in engine 1.
It is corresponding with the variation of VIVT instruction value (inlet valve closing crankshaft angles) of above-mentioned present embodiment, about from suction Tracheae 13 is supplied to the supply gas pressure of inlet valve 8, according to using the output of the engine 1 of measured in advance and rotation speed as parameter and The target supply gas pressure of setting controls such as compressor side and turbo-side shown in Fig. 9 in booster 17 and is respectively provided with side The flow control valve on siphunculus road, with control supply gas pressure (such as with reference to Japanese Patent Application 2016-027359 application shown in Hold).It should be noted that the control of supply gas pressure is not limited to the control mode.Existing known supply gas pressure can also be used Control mode.
It is illustrated below for the determination method of above-mentioned supply gas pressure (air-fuel ratio).
The fuel quantity on the basis as air-fuel ratio, is the supply pressure by fuel gas shown in above-mentioned Figure 12, Figure 13 It determines, (rate of load condensate) is exported according to the regulation of engine 1 and revolves with the relationship during the valve opening of fuel gas supply valve 15 Rotary speed determines suitable fuel quantity.Air-fuel ratio is determined according to the ratio between air capacity and the fuel gas scale of construction.Therefore, pass through Change supply gas pressure, thus it is possible to vary the air capacity supplied to combustion chamber 6.That is, air-fuel ratio is adjusted by supply gas pressure.
About the setting method of air-fuel ratio, by output (rate of load condensate) and rotation speed as a parameter to changing engine 1 Service condition, such as output (rate of load condensate) is set as 25%, 50%, 75%, 100% etc., various air-fuel ratios (gas supply can be measured Pressure) in the thermal efficiency and NOx data.Moreover, in arbitrary output and rotation speed, NOx's when will change air-fuel ratio Data instance is shown in Figure 14.
In Figure 14, using the measured value of NOx data corresponding with the variation of air-fuel ratio as " measurement data ", curve table is used Show.From measurement data it has been confirmed that turning and (reduce supply gas pressure) air-fuel ratio down can be such that NOx increases.
Here, the value of NOx is depending on the application, standard value is different.About standard value, according to based on for example in ship revision The IMO NOx of MARPOL pact supplemental provisions VI rule 13 is limited, and the upper limit value and lower limit value in land are prevented method etc. by atmosphere pollution Shown in NOx discharge limitation.
The lower limit value of air-fuel ratio is limited by the upper limit value of the legal provisions based on above-mentioned NOx discharge.Wherein, if The abnormal combustions such as pinking occur before the limits value that NOx data reach the upper limit, then will just be abnormal the air-fuel before burning Than being set as lower limit value.
On the other hand, when increasing air-fuel ratio, NOx can be reduced, but caught fire etc. and be will lead to engine 1 and be unable to operate stably. Therefore, the upper limit for the air-fuel ratio that will should continually and steadily run is set as upper limit value.Thereby determine that the model of settable air-fuel ratio It encloses.
Where it determines that the range of settable air-fuel ratio, using the air-fuel ratio of the centre of settable range as desired value, if Set supply gas pressure at this time.Identical measurement is repeated with any export with rotation speed in the range of being commonly used.In other words, Under the service condition of each output and rotation speed, change supply gas pressure (air-fuel ratio) to obtain meeting the suitable of target capabilities Supply gas pressure (air-fuel ratio).
Figure 15 is to depict the three-dimensional chart for the pressure of inspiration(Pi) being correspondingly arranged with output and rotation speed.It is empty in figure The region that line indicates is the image of common (practical) operation area, is provided with ship indicated by the solid line within its scope and uses Cube characteristic.In addition, about the condition not measured the approximate line of the data of point front and back can be measured by connection to determine.
As shown in Figure 15, if the output of engine 1 becomes larger, i.e., the advance angle for the time closed with inlet valve 8 is required Supply gas pressure can also increase.
As described above, time control, the confession of fuel gas of the supply beginning and end by fuel gas supply valve 15 To pressure control and supply gas pressure control, air-fuel ratio control can be carried out.
In addition, air-fuel ratio can become smaller under same supply gas pressure when the time advance for closing inlet valve 8.Therefore, scheming In the relationship of output and pressure of inspiration(Pi) shown in 16, compared with the shut-in time of inlet valve 8 certain situation, with inlet valve 8 The advance angle of the time of closing becomes larger with the increase ratio (the increased gradient) for exporting increased optimal supply gas pressure.
Later, it needs correspondingly to change fuel with the variation of VIVT designated value (crankshaft angles of air-breathing valve closing time) The duration of ignition.The duration of ignition of engine 1 is, for example, the time of fuel oil of micro- injection of light fluid injection valve 11 for igniting, The duration of ignition is according to Figure 17 that the output valve of engine 1 of measured in advance and the data of rotation speed are arranged as parameter Shown in the value of the duration of ignition be arranged.
It is illustrated below for the determination method of the duration of ignition.
(rate of load condensate) and rotation speed will be exported as a parameter to changing the service condition of engine 1, and obtain such as load The thermal efficiency of the various durations of ignition of rate 25%, 50%, 75%, 100% etc., NOx data.In arbitrary output, rotation speed In, the data instance of the thermal efficiency and NOx when changing the duration of ignition is indicated, then as shown in figure 18.Such as the reality in Figure 18 Shown in line, in the duration of ignition is made, then NOx increases in advance, the relationship that the thermal efficiency improves.Therefore, the thermal efficiency and NOx are in compromise Relationship.
As noted previously, as NOx has a defined standard value, therefore set meeting with the NOx of supply gas pressure identical standard It sets in range, the duration of ignition shifted to an earlier date in such a way that the thermal efficiency becomes highest is arranged to the preferred time.
Wherein, when the abnormal combustions such as pinking take place before NOx data reach defined standard value, by abnormal combustion The duration of ignition before the boiled beginning is set as the preferred duration of ignition.About the duration of ignition of micro- light fluid injection valve 11, often make In the range of, repeat to measure by arbitrarily exporting with rotation speed.In other words, in each " output (rate of load condensate) and rotation Under the service condition of speed ", change the duration of ignition to obtain the duration of ignition for meeting target capabilities.In the range of being commonly used Any rotation speed and output to repeat identical adjustment, thereby determine that the duration of ignition.In addition, about the condition not measured, The approximate line of the data of point front and back can be measured by connection to determine.
As shown in Figure 17, in the range of the common operation area that dotted line indicates, output is lower than expression ship with three times The region of the solid line of the image of square characteristic indicates that torque lacks region.Lack in region in torque, if the output of engine 1 becomes Greatly, i.e., the advance angle for the time closed with inlet valve 8, the duration of ignition of micro- light fluid injection valve 11 of engine 1 also shift to an earlier date.
On the other hand, the ship that output is higher than solid line expression indicates torque excess areas with the region of cube characteristic line. In torque excess areas, the duration of ignition will be used as peak on the dotted line of common operation area, the duration of ignition relative to peak value, Maximum can reduce advance angle degree in the range of 30~50%.Wherein, lack region and torque excess areas if it is torque Interior, then under same rotation speed, the case where not shifting to an earlier date compared to VIVT instruction value, the duration of ignition can maintain state in advance. That is, the duration of ignition is also to indicate that ship cube is special as the inlet valve of VIVT instruction value closes the advance angle of crankshaft angles Property solid line line on for peak and shift to an earlier date.The degree of advance angle is reduced in torque excess areas, but not compared to VIVT instruction value In advance the case where, the fuel injection time (duration of ignition) of micro- light fluid injection valve 11 of engine 1 is also whole to shift to an earlier date.
As described above, the control method and engine 1 of the engine 1 of embodiment through the invention, it can be common The unburned fuel gas of discharge is cut down in operation area, therefore the thermal efficiency can be improved, and obtain cutting for greenhouse gases The superiority to environment such as subtract.
In addition, since the output of engine 1 is higher, for air-fuel ratio can range of operation it is narrower, therefore maintain stable Operating status, the range of operation expansion for being higher than the torque excess areas of ship cube characteristic particularly with output can obtain Effect.
In addition, the compression of the mixed gas in engine 1 can be reduced when the output of the output shaft of engine 1 increases Than, therefore pinking when Load lifting can also be inhibited and shorten the Load lifting time.
It should be noted that the dual fuel engine 1, Ke Yi that engine of the invention is not limited to the above embodiment It does not depart from and carries out change and replacement appropriate etc. in the range of main idea of the present invention.Variation etc. of the invention is said below Bright, with the same or like part such as the component and material that illustrate in above embodiment using same symbol, the description thereof will be omitted.
Engine of the invention is not limited to can be switched using liquid fuel as the diesel fuel mode D of main fuel and based on combustion gas The dual fuel engine 1 for wanting the combustion gas mode D of fuel also can be applied to the fuel gas engine that combustion gas is used as to fuel.
Moreover, be not limited to the Load lifting mode of marine engines, it can also be applied to can operate with vehicle and use and very With the Load lifting mode of generator etc..
In addition, in above embodiment, can be changed inlet valve timing mechanism 30 change duration of valve opening and closing valve time the two Time, the time that inlet valve 8 opens do not change, but also can choose in the closing valve time and duration of valve opening of inlet valve 8 one A or two times change control.
Industrial applicibility
The present invention, which provides, a kind of is able to use fuel gas and the pre-mixed gas of air inhibits pinking in Load lifting And shorten the control method and engine system of the engine of Load lifting time.
Symbol description
1 dual fuel engine
2 crankshafts
8 inlet valves
9 exhaust valves
13 air intake ducts
14 exhaust pipes
15 fuel gas supply valves
17 boosters
20 rotation speed sensors
21 torque sensors
22 control units
24 first charts
25 second charts
27 electro-pneumatic converters
28 actuators
30 variable inlet valve timing mechanisms
42 gas conditioners
44 fuel gas supply timing unit
45 fuel gas supply valve timing mechanisms

Claims (14)

1. a kind of control method of engine, the engine is using combustion gas as fuel, which is characterized in that
As the output of the engine increases, by adjusting the advance angle that air-breathing valve closing time shifts to an earlier date from sucking bottom dead centre, come Reduce the control of the compression ratio for indoor mixed gas of burning,
Also, correspondingly the duration of valve opening of fuel gas supply valve is shifted to an earlier date with the variation of the advance angle.
2. the control method of engine according to claim 1, which is characterized in that with the air-breathing valve closing time The degree of the progress of advance angle, the advance angle of the duration of valve opening of the fuel gas supply valve is bigger.
3. the control method of engine according to claim 1 or 2, which is characterized in that the fuel gas supply valve Closing valve time determines in the following manner: during calculating valve opening according to the deviation of target rotational speed and actual rotation speed, with The duration of valve opening of the fuel gas supply valve is during the valve opening is arranged in starting point.
4. the control method of engine described in any one of claim 1 to 3, which is characterized in that with the air-breathing The advance angle of valve closing time improves the supply pressure of fuel gas.
5. the control method of engine according to any one of claims 1 to 4, which is characterized in that with the air-breathing The advance angle of valve closing time shifts to an earlier date the duration of ignition of the engine.
6. the control method of engine according to claim 5, which is characterized in that
The advance angle degree of the duration of ignition by using the output of the engine of measured in advance and rotation speed as parameter and The ship on boundary being arranged, as torque excess areas and torque shortage region is set as peak with cube characteristic line,
In the torque excess areas, ship cube characteristic line is compared, advance angle degree is reduced.
7. the control method of engine described according to claim 1~any one of 6, which is characterized in that the engine Output is the output valve of the output shaft found out according to torque measuring definite value and rotation speed measured value, and the torque measuring definite value is to pass through Torque sensor measures the torque of the output shaft of the engine and obtains, the rotation speed measured value is by rotation speed Degree sensor measures the rotation speed of the output shaft of the engine and obtains.
8. the control method of engine according to any one of claims 1 to 7, which is characterized in that the inlet valve closes The advance angle for closing the time is that basis is arranged using the output of multiple output shafts of measured in advance and the data of rotation speed as parameter Advance angle value setting.
9. a kind of engine system, including using combustion gas as the four-stroke engine of fuel, which is characterized in that the engine system Include:
Control unit, when the output of the output shaft of the engine increases, by the time of the inlet valve closing of the engine Shifted to an earlier date with advance angle, and correspondingly shifts to an earlier date the duration of valve opening of fuel gas supply valve with the variation of the advance angle；
Variable inlet valve timing mechanism changes the suction according to the shut-in time of the inlet valve of control unit setting The time that air valve is closed；And
Fuel gas supply valve timing mechanism, it is corresponding with the variation of advance angle of the inlet valve of control unit setting Ground shifts to an earlier date the duration of valve opening of the fuel gas supply valve,
Wherein, it as the output of the output shaft of the engine increases, by the variable inlet valve timing mechanism, carries out into one Step reduces the control of the compression ratio of the mixed gas of the in-engine combustion gas and air.
10. engine system according to claim 9, comprising:
Torque sensor measures the torque of the output shaft of the engine；And
Rotation speed sensor measures the rotation speed of the output shaft of the engine,
Wherein, the rotation speed that the torque measuring definite value and the rotation speed sensor measured according to the torque sensor measures Measured value finds out the output of the output shaft, and in the control unit be arranged inlet valve shut-in time change.
11. engine system according to claim 9 or 10, wherein
The closing valve time of the fuel gas supply valve is arranged by following device:
Gas supplying time calculation part, according to the deviation of target rotational speed and actual rotation speed come during calculating valve opening； And
Air supply valve control unit, according to the fuel gas for during the valve opening, indicating that the fuel gas supply valve executes Closing valve time.
12. the engine system according to any one of claim 9~11, setting are as follows:
With the advance angle of the air-breathing valve closing time, the supply pressure of fuel gas is improved.
13. the engine system according to any one of claim 9~12, wherein
With the advance angle of the air-breathing valve closing time, the duration of ignition of the engine is also shifted to an earlier date.
14. the engine system according to any one of claim 9~13, wherein
It will be with pre- along with the advance angle degree of the duration of ignition of the engine of the advance angle of the air-breathing valve closing time The output valve and revolving speed of the engine first measured are provided as torque excess areas for parameter and torque lacks region The ship on boundary be set as peak with cube characteristic line, in the torque excess areas, advance angle degree is reduced.
CN201780025208.0A 2017-05-11 2017-05-11 Control method of engine and engine system Active CN109247022B (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112912607A (en) * 2018-10-22 2021-06-04 纬湃科技有限责任公司 Method and system for controlling vehicle engine speed

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019102887A1 (en) * 2019-02-06 2020-08-06 Man Energy Solutions Se Method for operating a gas engine or a dual-fuel engine operated in a gas fuel operating mode, and corresponding engine

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1094789A (en) * 1993-02-03 1994-11-09 马自达汽车株式会社 The internal-combustion engine of band pressurized machine
JP2002021608A (en) * 2000-07-05 2002-01-23 Osaka Gas Co Ltd Premix compression self ignition engine
JP2006322352A (en) * 2005-05-18 2006-11-30 Nissan Motor Co Ltd Internal combustion engine
CN102265014A (en) * 2008-12-25 2011-11-30 丰田自动车株式会社 Internal combustion engine controller
JP2012021434A (en) * 2010-07-13 2012-02-02 Toyota Motor Corp Control apparatus of internal combustion engine
CN1233313B (en) * 1996-08-23 2013-01-02 卡明斯发动机公司 Premixed charge compression ignition engine with optimal combustion control
CN103726899A (en) * 2012-10-16 2014-04-16 福特环球技术公司 Internal combustion engine which can be operated with liquid and with gaseous fuel and a method for operating an internal combustion engine of this kind
JP2015194080A (en) * 2014-03-31 2015-11-05 株式会社クボタ engine

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08177590A (en) * 1994-12-20 1996-07-09 Nippondenso Co Ltd Fuel supply device for internal combustion engine
JP2004308558A (en) * 2003-04-08 2004-11-04 Honda Motor Co Ltd Controller for compression self-ignition internal combustion engine
JP5895570B2 (en) * 2012-02-09 2016-03-30 株式会社デンソー Gas engine control system
JP5872335B2 (en) * 2012-03-08 2016-03-01 ヤンマー株式会社 Sub-chamber gas engine

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1094789A (en) * 1993-02-03 1994-11-09 马自达汽车株式会社 The internal-combustion engine of band pressurized machine
CN1233313B (en) * 1996-08-23 2013-01-02 卡明斯发动机公司 Premixed charge compression ignition engine with optimal combustion control
JP2002021608A (en) * 2000-07-05 2002-01-23 Osaka Gas Co Ltd Premix compression self ignition engine
JP2006322352A (en) * 2005-05-18 2006-11-30 Nissan Motor Co Ltd Internal combustion engine
CN102265014A (en) * 2008-12-25 2011-11-30 丰田自动车株式会社 Internal combustion engine controller
JP2012021434A (en) * 2010-07-13 2012-02-02 Toyota Motor Corp Control apparatus of internal combustion engine
CN103726899A (en) * 2012-10-16 2014-04-16 福特环球技术公司 Internal combustion engine which can be operated with liquid and with gaseous fuel and a method for operating an internal combustion engine of this kind
JP2015194080A (en) * 2014-03-31 2015-11-05 株式会社クボタ engine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112912607A (en) * 2018-10-22 2021-06-04 纬湃科技有限责任公司 Method and system for controlling vehicle engine speed

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