CN107975432B - dual-fuel engine and control method thereof - Google Patents

dual-fuel engine and control method thereof Download PDF

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Publication number
CN107975432B
CN107975432B CN201710985731.XA CN201710985731A CN107975432B CN 107975432 B CN107975432 B CN 107975432B CN 201710985731 A CN201710985731 A CN 201710985731A CN 107975432 B CN107975432 B CN 107975432B
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fuel
engine
ignition
throttle valve
dual
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CN107975432A (en
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滑海宁
谢斌
贺晶晶
韩斌
刘生全
李阳阳
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Changan University
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Changan University
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/08—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels
    • F02D19/081—Adjusting the fuel composition or mixing ratio; Transitioning from one fuel to the other
    • 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
    • F02B11/00—Engines characterised by both fuel-air mixture compression and air compression, or characterised by both positive ignition and compression ignition, e.g. in different cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D35/00—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for
    • F02D35/02—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions
    • F02D35/027—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions using knock sensors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/02—Circuit arrangements for generating control signals
    • F02D41/14—Introducing closed-loop corrections
    • F02D41/1438—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor
    • F02D41/1444—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases
    • F02D41/1454—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being an oxygen content or concentration or the air-fuel ratio
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/40—Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/40—Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
    • F02D41/401—Controlling injection timing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/04—Engine intake system parameters
    • F02D2200/0404—Throttle position
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/10—Parameters related to the engine output, e.g. engine torque or engine speed
    • F02D2200/101—Engine speed

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Combined Controls Of Internal Combustion Engines (AREA)

Abstract

The invention discloses a dual-fuel engine and a control method thereof, wherein the dual-fuel engine comprises an ignition device and a throttle device, wherein the ignition device and the throttle device are both connected with an engine ECU (electronic control Unit); the spark plug of the ignition device is arranged on a cylinder cover of the engine; the throttle valve device is arranged on an air inlet manifold of the engine; a control method for the dual fuel engine is also disclosed; the method solves the problem that the existing dual-fuel engine cannot use the ignition type fuel under the small-load working condition, realizes the full substitution (substitution rate of 100%) of the ignition type fuel to the compression type fuel under the small-load working condition, improves the economical efficiency and the emission performance of the existing dual-fuel engine under the small-load working condition, and fully exerts the performance advantages of the dual-fuel engine.

Description

Dual-fuel engine and control method thereof
Technical Field
the invention belongs to the field of engine technology and control methods, and relates to a dual-fuel engine and a control method thereof.
background
due to the difference of physical and chemical properties, the application modes of the ignition type fuel on the compression ignition engine mainly include an emulsification method, a combustion-supporting method, a direct compression ignition method and a dual-fuel method. The dual-fuel method is characterized in that in the working process of an engine, partial ignition type fuel is input into a cylinder of the compression ignition type engine through an air inlet system or an oil supply system, partial premixed combustible mixed gas is formed in the cylinder, then a small amount of compression ignition type fuel is injected into the cylinder near a compression top dead center, and the compression ignition type fuel is subjected to compression ignition to further ignite the premixed combustible mixed gas formed by the ignition type fuel and air, so that the engine can simultaneously burn the ignition type fuel and the compression ignition type fuel. The dual-fuel method is adopted to apply some ignition fuels (such as natural gas, methanol and the like) to the compression-ignition engine, which is not only beneficial to improving the effective thermal efficiency of the original compression-ignition engine and reducing the consumption rate of equivalent effective fuel oil, but also beneficial to reducing the exhaust emission of the original compression-ignition engine. Therefore, part of ignition type fuels (such as natural gas, methanol and the like) are applied to the compression ignition engine by adopting a dual-fuel method, and the method has important theoretical significance and practical value for relieving the energy safety problem caused by the shortage of the traditional compression ignition type fuel-diesel oil supply and improving the environmental problem caused by the tail gas emission of the original compression ignition type engine.
Due to the advantages of the dual-fuel method, a large amount of manpower and material resources are input by a plurality of scientific research institutions and colleges at home and abroad, related researches are carried out, a series of technical achievements are obtained, but some outstanding problems are found and are not solved so far. Researches of Tianjin university Yaochun, Sigan traffic university Liushenghua, Changan university Chunshua and Liusheng safety and the like find that under the working condition of small load, the injection of ignition type fuel (with a small substitution rate) causes combustion lag, the combustion temperature is reduced, the combustion cycle change is large, the economy is deteriorated, and simultaneously, the high CO and HC emission is accompanied; if the supply quantity of the ignition type fuel is continuously increased (the substitution rate of the ignition type fuel is increased) or the working load of the engine is reduced, the compression ignition type fuel quantity which plays a role in igniting is too small, the cooling effect of vaporization of a large quantity of the ignition type fuel on a fresh charging is obvious, and the inhibition effect of the ignition type fuel on ignition is obvious when the ignition type fuel is added, so that the engine is easy to catch fire, and the engine cannot work.
because the dual-fuel engine adopts the ignition type fuel and the compression ignition type fuel to operate under the working condition of small load, the performance is poor, and the dual-fuel engine mainly adopts the ignition type fuel and the compression ignition type fuel to operate under the working condition of medium and large load in the current practical application, so that the substitution rate of the ignition type fuel (such as natural gas, methanol and the like) to the compression ignition type fuel is relatively low. Therefore, a novel dual-fuel engine and a system control method thereof are urgently needed to be developed, so that the dual-fuel engine can burn the ignition type fuel under a small-load working condition, the substitution rate of the ignition type fuel for the compression ignition type fuel is greatly improved, and the performance advantages of the dual-fuel engine are fully exerted.
Disclosure of Invention
aiming at the problems in the prior art, the invention aims to provide a dual-fuel engine and a control method thereof, solve the problem that the existing dual-fuel engine cannot use ignition fuel under a small-load working condition, realize the full substitution (substitution rate of 100%) of the ignition fuel of the dual-fuel engine on compression ignition fuel under the small-load working condition, improve the economy and the emission performance of the existing dual-fuel engine under the small-load working condition, and fully play the performance advantages of the dual-fuel engine.
in order to achieve the purpose, the invention adopts the following technical scheme:
a control method of a dual fuel engine comprising the steps of:
The dual-fuel engine is under the working conditions of cold start, warm-up or idling
(1) The opening degree of the throttle valve is kept fully closed;
(2) stopping the compression ignition fuel injector;
(3) determining the injection quantity of the ignition fuel according to the required value of the excess air coefficient lambda of the mixture under the working conditions of cold starting, warm-up and idling;
(4) igniting when the piston moves to 5 CA degrees before the compression top dead center, and igniting combustible mixed gas formed by ignition fuel and air;
(5) the method comprises the following steps that a throttle position sensor measures an opening signal of a throttle, and an engine ECU performs closed-loop correction on the throttle opening psi according to the opening signal of the throttle, so that the throttle of the dual-fuel engine is in a completely closed state under the working conditions of cold start, warm-up and idling;
And the ECU of the engine performs closed-loop correction on the oil injection pulse width of the ignition type fuel oil injector according to the oxygen content in an exhaust pipe of the engine, so that the value of the mixed gas excess air coefficient lambda is always the required value of the mixed gas excess air coefficient lambda under the working conditions of cold starting, warm-up and idling.
The (II) dual-fuel engine is under the working condition of idling-30% load, namely small load
(1) the accelerator opening phi is increased from 0% to 30%;
(2) The engine ECU adjusts the opening psi of the throttle valve according to a relational expression of the change of the throttle valve opening psi along with the accelerator opening phi; determining the quantity of the ignition fuel according to the required value of the excess air coefficient lambda of the mixed gas under the condition of small load; stopping the compression ignition fuel injector;
(3) igniting when the piston moves to 10 CA degrees before the compression top dead center, and igniting combustible mixed gas formed by ignition fuel and air;
(4) the method comprises the following steps that a throttle position sensor measures an opening signal of a throttle, and an engine ECU performs closed-loop correction on a throttle opening psi according to the opening signal of the throttle, so that the opening of the throttle conforms to a relational expression of the change of the throttle opening psi with an accelerator opening phi;
and the ECU of the engine performs closed-loop correction on the oil injection pulse width of the ignition type fuel oil injector according to the oxygen content, so that the excess air coefficient lambda of the mixed gas is the required value of the excess air coefficient lambda of the mixed gas under the condition of small load.
(III) the dual-fuel engine is under the working condition of 30-100% load
(1) The accelerator opening phi is increased from 30% to 100%;
(2) determining an engine speed n;
(3) the opening psi of the throttle valve is rapidly adjusted to full opening;
(4) the spark plug stops sparking;
(5) Determining the value of the excess air coefficient lambda of the mixer and the value of the substitution rate L under the current accelerator opening phi and the engine speed n, and determining the fuel injection quantity of the ignition type fuel and the fuel injection quantity of the compression ignition type fuel according to the value of the excess air coefficient lambda of the mixer and the value of the substitution rate L;
(6) And the engine ECU performs closed-loop correction on the injection pulse width of the compression ignition fuel injector and the ignition fuel injector.
optionally, the closed-loop correction of the injection pulse width of the compression ignition fuel injector and the ignition fuel injector specifically includes the following processes:
detecting the oxygen concentration in an exhaust pipe of the engine, comparing the detected oxygen concentration with a target range by an engine ECU, and if the oxygen concentration in the exhaust pipe is lower than the minimum value of the target range, sending a control instruction by the engine ECU, and simultaneously reducing the oil injection pulse width of a compression ignition fuel oil injector and an ignition fuel oil injector;
If the oxygen concentration in the exhaust pipe is higher than the maximum value of the target range, the engine ECU sends out a control instruction, and simultaneously increases the oil injection pulse width of the compression ignition fuel oil injector and the ignition fuel oil injector;
if the oxygen concentration in the exhaust pipe is in the target range, adjusting the oil injection pulse width of the compression ignition fuel oil injector and the ignition fuel oil injector, and the specific process comprises the following steps: if a knock signal is detected, the engine ECU sends a control command to reduce the oil injection pulse width of the ignition type fuel oil injector and correspondingly increase the oil injection pulse width of the compression ignition type fuel oil injector, and the excess air coefficient lambda is kept unchanged; if the knock signal is not detected, the engine ECU sends out a control command, the oil injection pulse width of the ignition type fuel oil injector is increased, the oil injection pulse width of the compression ignition type fuel oil injector is reduced, and the excess air coefficient lambda is kept unchanged.
The present disclosure also provides a dual fuel engine, further comprising an ignition device and a throttle device, both connected to the engine ECU; the spark plug of the ignition device is arranged on a cylinder cover of the engine; the throttle valve device is arranged on an air inlet manifold of the engine;
The ignition device is used for igniting when a spark plug of the ignition device ignites when a piston moves to 5 degrees CA before a compression top dead center under the working conditions of cold starting, warming up or idling of the dual-fuel engine, and igniting combustible mixed gas formed by ignition fuel and air; when the dual-fuel engine is in the working condition of idling-30% load, namely small load, the spark plug ignites when the piston moves to 10 CA degrees before the compression top dead center, and combustible mixed gas formed by ignition fuel and air is ignited; the dual-fuel engine is under the working condition of 30% -100% load, and the spark plug stops sparking;
the throttle valve device keeps fully closed under the working conditions of cold starting, warming or idling of the dual-fuel engine; under the working condition that the dual-fuel engine is at idle speed of-30% load, namely small load, the opening psi of the throttle valve is changed along with the opening phi of the accelerator; and under the working condition that the dual-fuel engine is at 30% -100% of load, the throttle valve opening psi is fully opened.
optionally, the throttle device comprises a throttle valve and a throttle position sensor, the throttle valve is of a circular structure, and when the axis of the throttle valve is consistent with the axis of the intake manifold, a gap is left between the edge of the throttle valve and the intake manifold.
Compared with the prior art, the invention has the following technical effects:
1. The ignition system is arranged on the traditional dual-fuel engine, so that the engine can work in an ignition mode under the working conditions of cold start, warm-up, idling and small load, and the defect that the ignition type fuel cannot be normally used under the working condition of small load of the traditional dual-fuel engine is overcome.
2. Under the working conditions of cold starting, warm-up, idling and small load, the relative compression ratio of the mixed gas in the cylinder under the actual work can be effectively controlled by adjusting the opening degree of the throttle valve, and the detonation phenomenon in the combustion process of the ignition type fuel mixed gas is prevented.
3. The dual-fuel engine controls the excess air coefficient of the mixed gas under each working condition, adopts the concentrated mixed gas under the working conditions of cold start, warm-up and idling, and is convenient for the cold start, warm-up and idling of the engine; the economic mixed gas is combusted under the working condition of small load, so that the economy of the ignition type fuel for the dual-fuel engine is improved; the lean mixed gas is combusted under the working conditions of medium and large loads, the combustion quality of the mixed gas of the dual-fuel engine is improved, good economical efficiency is obtained, and the emission of tail gas is reduced.
4. the load regulation mode of the dual-fuel engine is as follows: the method is characterized in that the method adopts quantity adjustment (the size of the load is adjusted by adjusting the quantity of the mixed gas) under the working condition of small load, and adopts quality adjustment (the size of the load is adjusted by adjusting the quantity of the working medium, namely the size of the load is adjusted by adjusting the concentration of the mixed gas) under the working condition of large load.
5. the invention updates the ECU control strategy of the traditional dual-fuel engine, realizes single combustion of the ignition type fuel under the working conditions of cold start, warm-up, idling and small load, and simultaneously combusts the ignition type fuel and the compression ignition type fuel under the working conditions of medium and large load.
drawings
fig. 1 is a schematic diagram of a structure of a dual fuel engine in which ignition type fuel cylinder injection is performed;
FIG. 2 is a schematic diagram of a dual fuel engine with port injection of spark ignited fuel;
FIG. 3 is a graph of throttle opening of a dual fuel engine as a function of throttle opening;
FIG. 4 is a graph of the concentration of a mixture of a dual-fuel engine as a function of operating conditions;
FIG. 5 is a graph of spark-ignition fuel substitution rate as a function of operating conditions;
description of reference numerals: 1, a silencer; 2 reducing the catalytic converter; 3 an oxidation catalytic converter; 4 an oxygen sensor; 5, an exhaust valve; 6 compression ignition type fuel supply oil path; 7 compression ignition fuel injector; 8 a spark plug; 9 an air inlet valve; 10 ignition type fuel injectors; 11 a throttle valve; 12 a throttle position sensor; 13 an air cleaner; 14 an engine ECU; 15 engine cylinder walls; 16 an engine piston; 17, an accelerator; an 18 throttle position sensor; 19 a knock sensor; 20 revolution speed sensor.
the embodiments of the invention will be explained and explained in further detail with reference to the figures and the detailed description.
Detailed Description
The invention provides a control method of a dual-fuel engine, which realizes the work in a mode of ignition and ignition under the working conditions of cold start, warm-up, idling and small load, and works in a mode of compression ignition and ignition under the working conditions of medium and large loads, and specifically comprises the following steps:
one, the dual-fuel engine is in the working condition of cold start, warm-up or idling
(1) the engine ECU14 controls the opening degree of the throttle valve 11 to remain fully closed, while air still enters;
(2) The engine ECU14 controls the compression ignition fuel injector 7 to stop operating;
(3) the engine ECU14 controls the ignition fuel injector 10 to determine the amount of ignition fuel according to the mixture concentration requirement under the cold start, warm-up and idle conditions, that is, the excess air coefficient λ < 1, in the embodiment, the excess air coefficient λ is 0.85; mixture concentration requirement referring to fig. 4, the excess air ratio λ is the amount of air actually supplied/the amount of air required for complete combustion of the fuel;
Wherein, according to the excess air coefficient lambda, the quantity of the injection ignition fuel is determined, and the specific process is as follows: under the working condition that the dual-fuel engine is in cold starting, warm-up or idling, the air quantity entering the engine through a throttle valve is known, the air quantity required by complete combustion of fuel can be known according to an excess air coefficient lambda, and the quantity of the injection ignition fuel can be determined according to the corresponding relation between the air quantity required by complete combustion of the fuel and the quantity of the injection ignition fuel;
(4) The engine ECU14 controls the ignition plug 8 of the ignition device to ignite when the piston moves to 5 ° CA before compression top dead center, igniting a combustible mixture of ignition fuel and air;
(5) The throttle position sensor 12 measures an opening signal of the throttle valve 11, and the engine ECU14 performs closed-loop correction on the throttle opening psi according to the opening signal of the throttle valve 11 to make the throttle valve 11 in a fully closed state under the working conditions of cold start, warm-up and idling;
the oxygen sensor 4 measures the oxygen content in an exhaust pipe of the engine, and the engine ECU14 carries out closed-loop correction on the oil injection pulse width of the spark-ignition fuel oil injector 10 according to the oxygen content, so that the mixed gas excess air coefficient lambda of the dual-fuel engine is controlled to be 0.85 under the working conditions of cold start, warm-up and idling. Specifically, the oxygen sensor 4 measures the oxygen content in the exhaust pipe, and the engine ECU14 controls the injection pulsewidth of the spark-ignition fuel injector 10 to increase when the measured oxygen content is greater than a threshold value corresponding to λ 0.85, and the engine ECU14 controls the injection pulsewidth of the spark-ignition fuel injector 10 to decrease when the measured oxygen content is less than the threshold value corresponding to λ 0.85.
(II) the dual-fuel engine is in the working condition of idling-30% load, namely small load
(1) An accelerator pedal is stepped, and the opening phi of the accelerator is increased from 0% to 30%;
(2) the engine ECU14 adjusts the opening ψ (0-45%) of the throttle valve 11 as shown in fig. 3 in accordance with the variation of the throttle opening ψ with the accelerator opening Φ; in the present embodiment, in the case of a small load, the slope k of the straight line in fig. 3 is 1.5; meanwhile, the engine ECU14 determines the quantity of the injection ignition type fuel according to the requirement of the concentration of the mixed gas under the small-load working condition, wherein the excess air coefficient lambda of the mixed gas is 1.05-1.15, in the embodiment, the excess air coefficient lambda of the mixed gas is 1.10, the injection pulse width of the ignition type fuel injector 10 is adjusted, and the compression ignition type fuel injector 7 still stops working under the control of the engine ECU 14;
(3) the engine ECU14 controls the spark plug 8 to ignite when the piston moves to 10 CA degrees before the compression top dead center, and ignites the combustible mixture formed by the ignition fuel and the air;
(4) The throttle position sensor 12 measures an opening signal of the throttle valve 11, and the engine ECU14 performs closed-loop correction on the throttle opening ψ based on the opening signal of the throttle valve 11 so that the throttle valve 11 is maintained at the opening size of the throttle valve obtained from fig. 3;
the oxygen sensor 4 measures the oxygen content in the exhaust pipe, and the engine ECU14 performs closed-loop correction on the oil injection pulse width of the ignition type fuel oil injector 10 according to the oxygen content, so that the excess air coefficient of the mixed gas of the dual-fuel engine is controlled to be 1.10 under the low-load working condition. Specifically, the oxygen sensor 4 measures the oxygen content in the exhaust pipe, and the engine ECU14 controls the injection pulsewidth of the spark-ignition fuel injector 10 to increase when the measured oxygen content is greater than a threshold value corresponding to λ 1.10, and the engine ECU14 controls the injection pulsewidth of the spark-ignition fuel injector 10 to decrease when the measured oxygen content is less than a threshold value corresponding to λ 1.10.
(III) the dual-fuel engine is in the working condition of 30% -100% load
(1) The accelerator pedal is stepped, and the opening phi of the accelerator is increased from 30% to 100%;
(2) the engine ECU14 analyzes and processes the accelerator opening degree signal acquired by the accelerator position sensor 18 and the rotation speed signal acquired by the rotation speed sensor 20, and determines the accelerator opening degree Φ (30% -100%) and the engine rotation speed n;
(3) The engine ECU14 controls the throttle opening ψ to be quickly adjusted to full opening;
(4) The engine ECU14 controls the ignition plug 8 to stop the spark-over;
(5) The engine ECU14 determines the value of the mixer excess air coefficient lambda under the current accelerator opening phi (30% -100%) and the engine speed n according to a curve graph (figure 4) of the concentration of the mixed gas along with the change of the working conditions, and determines the total amount of two fuels according to the excess air coefficient lambda; under the condition of determining the total amount of the two fuels, solving the oil injection quantity of the ignition type fuel oil injector 10 and the oil injection quantity of the compression ignition type fuel oil injector 7 according to a curve graph (shown in figure 5) of the substitution rate along with the change of the working conditions, and adjusting the oil injection pulse width of the ignition type fuel oil injector 10 and the oil injection pulse width of the compression ignition type fuel oil injector 7 according to the solved oil injection quantity;
wherein the substitution rate
Note: m isDIgnition fuel mass consumption rate
HμDLow heating value of ignition fuel
mY-compression ignition fuel mass rate of consumption
HμYLow heating value of compression ignition fuel
Wherein HμDlow heating value and H of ignition fuelμYThe lower heating value of the compression ignition fuel is constant, and the mass consumption rate m of the ignition fuel can be obtained according to the formula under the condition that the total amount of the two fuels is knownDand compression ignition type fuel quality eliminationspecific power consumption mY。
in the present embodiment, the curve equation shown in fig. 4 shows that, when the rotation speed n is 1550r/min, the corresponding relationship between the excess air ratio and the accelerator opening degree is as follows:
when n is 1850r/min, the corresponding relation between the excess air coefficient and the accelerator opening degree is as follows:
Wherein y is the excess air factor; x is the opening degree of the accelerator
fig. 5 shows a curve equation in which, when n is 1550r/min, the correspondence between the substitution rate and the accelerator opening is as follows:
When n is 1850r/min, the corresponding relation between the substitution rate and the accelerator opening degree is as follows:
Wherein z is substitution rate; and x is the opening degree of the accelerator.
(6) the engine ECU14 performs closed-loop correction on the injection pulse width of the compression ignition fuel injector 7 and the ignition fuel injector 10 according to the feedback signals of the oxygen sensor 4 and the knock sensor 19, thereby realizing accurate adjustment of the engine load. The specific process is as follows:
The oxygen sensor 4 detects the oxygen concentration in the engine exhaust pipe, and feeds back the detection result to the engine ECU 14. The engine ECU14 compares the detection result with the target range, and if the oxygen concentration in the exhaust pipe is lower than the minimum value of the target range, the engine ECU14 issues a control command while reducing the injection pulse width of the compression ignition fuel injector 7 and the ignition fuel injector 10;
if the oxygen concentration in the exhaust pipe is higher than the maximum value of the target range, the engine ECU14 issues a control command while increasing the injection pulse widths of the compression ignition fuel injector 7 and the ignition fuel injector 10;
If the oxygen concentration in the exhaust pipe is in a target range, adjusting the fuel injection pulse width of the compression ignition fuel injector 7 and the ignition fuel injector 10 according to a feedback signal of the knock sensor 19, if the knock sensor 19 detects a knock signal, sending a control command by the engine ECU14, reducing the fuel injection pulse width of the ignition fuel injector 10, correspondingly increasing the fuel injection pulse width of the compression ignition fuel injector 7, and keeping the excess air coefficient lambda unchanged; if the knock sensor 19 does not detect a knock signal, the engine ECU14 issues control commands to increase the pulse width for injection by the spark-ignition fuel injector 10 and decrease the pulse width for injection by the compression-ignition fuel injector 7, while maintaining the excess air ratio λ constant.
(IV) Dual Fuel Engine load reduction Process
and in the process of reducing the load, reversely returning to an idle state or stopping the engine according to the control route of the original process of increasing the load.
the invention controls the concentration of the mixed gas under each working condition of the dual-fuel engine, and adopts the concentrated mixed gas (the excess air coefficient lambda is 0.85) under the working conditions of cold start, warm-up and idling, so that the engine is easy to cold start, and the warm-up acceleration and the idling are stable; the economical mixed gas is combusted under the working condition of small load (the excess air coefficient lambda is 1.10), so that the economy of the ignition type fuel for the dual-fuel engine is improved; the lean mixed gas is combusted under the working conditions of medium and large loads, the combustion quality of the mixed gas of the dual-fuel engine is improved, good economical efficiency is obtained, and the emission of tail gas is reduced.
the dual-fuel engine combines the characteristic of pollutant emission of self tail gas, and adopts an oxidation catalytic converter and a reduction catalytic converter simultaneously, so that the carbon smoke, NOx, CO and HC in the tail gas can be reduced better.
the invention controls the amount adjustment under the small load working condition of the dual-fuel engine, and solves the defect of narrow ignition limit of the ignition type fuel. The ignition type fuel can ensure good service performance under the whole small load working range.
the invention realizes the full substitution (substitution rate of 100%) of the ignition type fuel for the compression ignition type fuel under the working conditions of cold start, warm-up, idling and small load of the dual-fuel engine, which greatly improves the substitution rate of the ignition type fuel (such as natural gas, methanol and the like) of the dual-fuel engine for the compression ignition type fuel, thereby further relieving the problem of the shortage of the traditional compression ignition type fuel-diesel supply in China. Meanwhile, the ignition type fuel is combusted under a higher relative compression ratio, so that the characteristic of high octane number of partial ignition type fuel (such as natural gas, methanol and the like) is fully exerted, and the dynamic property, the economical efficiency and the emission property of the novel dual-fuel engine are improved, thereby not only being beneficial to further reducing the oil consumption and improving the energy safety problem, but also being beneficial to reducing the pollutant emission and improving the environmental usability of the fuel.
another aspect of the present disclosure provides a dual fuel engine, see fig. 1 and 2, comprising an ignition device and a throttle device, a spark plug 8 of the ignition device being mounted on a cylinder head of the dual fuel engine and operating under the control of an engine ECU 14; the throttle valve device is arranged on an air inlet manifold and is connected with an engine ECU 14; the throttle device includes a throttle valve 11 and a throttle position sensor 12.
the ignition system is arranged on the traditional dual-fuel engine, so that the engine can work in an ignition mode under the working conditions of cold starting, warming, idling and small load, and the defect that ignition type fuel cannot be combusted under the working condition of small load of the traditional dual-fuel engine is overcome. Under the working conditions of cold starting, warm-up, idling and small load, the throttle position sensor 12 can collect the opening information of the throttle valve 11 and transmit the information to the engine ECU14, the engine ECU14 adjusts the opening of the throttle valve 11 according to the opening information of the throttle valve 11, and the relative compression ratio of the mixed gas in the cylinder under the actual working state can be effectively controlled by adjusting the opening of the throttle valve 11, so that the detonation phenomenon in the combustion process of the ignition type fuel mixed gas is prevented.
In the embodiment, the ignition fuel may be injected by air inlet channel injection or direct in-cylinder injection. The dual-fuel engine is also provided with an oxygen sensor 4, a rotating speed sensor 20 and a knock sensor 19, wherein the oxygen sensor 4 is arranged on an exhaust pipe, the rotating speed sensor 20 is arranged at the tail end of a crankshaft, and the knock sensor 19 is arranged on the engine body of the dual-fuel engine.
in the embodiment, the throttle valve 11 is of a circular structure, when the axis of the throttle valve 11 is consistent with the axis of the intake manifold, a gap is left between the edge of the throttle valve 11 and the intake manifold, so that when the throttle valve 11 is in a full-closed state, air still enters the cylinder of the engine from the intake manifold. The engine burns combustible materials and converts heat energy released by combustion into mechanical energy so as to do work to the outside. Oxygen (air) is necessary for combustible combustion. Under the conditions of cold starting, warm-up and idling, the throttle valve is fully closed (namely the throttle valve opening is minimum), and in order to ensure that the engine can normally run under the conditions, an air inlet cylinder is required, otherwise, combustion cannot be carried out.
the ignition device is used for igniting when a spark plug 8 of the ignition device is ignited when a piston moves to 5 CA degrees before a compression top dead center under the working conditions of cold starting, warming up or idling of the dual-fuel engine, and igniting combustible mixed gas formed by ignition fuel and air; when the dual-fuel engine is in the working condition of idling-30% load, namely small load, the spark plug 8 ignites when the piston moves to 10 CA degrees before the compression top dead center, and the combustible mixed gas formed by ignition fuel and air is ignited; the dual-fuel engine is in the working condition of 30% -100% load, and the spark plug 8 stops sparking.
the throttle valve device keeps fully closed under the working conditions of cold starting, warming or idling of the dual-fuel engine; under the working condition that the dual-fuel engine is at idle speed of-30% load, namely small load, the opening psi of the throttle valve is changed along with the opening phi of the accelerator; and under the working condition that the dual-fuel engine is at 30% -100% of load, the throttle valve opening psi is fully opened.
the engine of the invention changes the relative compression ratio of the dual-fuel engine under the working conditions of cold start, warm-up, idling and small load by adopting an air inlet throttling mode, and avoids the phenomenon that the detonation happens to the ignition fuel for the dual-fuel engine due to the overlarge compression ratio of the dual-fuel engine.
by additionally arranging the ignition system, the dual-fuel engine can work in a mode of ignition and ignition under the working conditions of cold start, warm-up, idling and small load, and the defect that ignition is difficult to realize compression ignition due to low cetane number of ignition type fuel is overcome.
In a third aspect of the present disclosure, a control method of a dual fuel engine is provided, including the steps of:
the dual-fuel engine is under the working conditions of cold start, warm-up or idling
(1) the opening degree of the throttle valve (11) is kept fully closed;
(2) The compression ignition fuel injector 7 stops working;
(3) Determining the injection quantity of the ignition fuel according to the required value of the excess air coefficient lambda of the mixture under the working conditions of cold starting, warm-up and idling;
(4) Igniting when the piston moves to 5 CA degrees before the compression top dead center, and igniting combustible mixed gas formed by ignition fuel and air;
(5) The throttle position sensor 12 measures an opening signal of the throttle valve 11, and the engine ECU14 performs closed-loop correction on the throttle opening psi according to the opening signal of the throttle valve 11 to enable the throttle valve 11 of the dual-fuel engine to be in a fully closed state under the working conditions of cold start, warm-up and idling;
the engine ECU14 performs closed-loop correction of the fuel injection pulsewidth of the spark-ignition fuel injector 10 based on the oxygen content in the exhaust pipe of the engine so that the value of the mixture air excess factor λ is always the desired value of the mixture air excess factor λ under cold start, warm-up, and idle conditions.
The (II) dual-fuel engine is under the working condition of idling-30% load, namely small load
(1) The accelerator opening phi is increased from 0% to 30%;
(2) the engine ECU14 adjusts the opening ψ of the throttle valve 11 in accordance with a relational expression of the change of the throttle valve opening ψ with the accelerator opening Φ; determining the quantity of the ignition fuel according to the required value of the excess air coefficient lambda of the mixed gas under the condition of small load; the compression ignition fuel injector 7 stops working;
(3) Igniting when the piston moves to 10 CA degrees before the compression top dead center, and igniting combustible mixed gas formed by ignition fuel and air;
(4) the throttle position sensor 12 measures an opening signal of the throttle valve 11, and the engine ECU14 performs closed-loop correction on the throttle opening ψ according to the opening signal of the throttle valve 11 so that the opening of the throttle valve 11 conforms to a relational expression of the change of the throttle opening ψ with the accelerator opening Φ;
the engine ECU14 performs closed-loop correction of the injection pulsewidth of the ignition-type fuel injector 10 based on the oxygen content so that the mixture air excess factor λ is a required value of the mixture air excess factor λ under a small load condition.
(III) the dual-fuel engine is under the working condition of 30-100% load
(1) The accelerator opening phi is increased from 30% to 100%;
(2) Determining an engine speed n;
(3) The opening psi of the throttle valve is rapidly adjusted to full opening;
(4) the spark plug 8 stops the spark-over;
(5) Determining the value of the excess air coefficient lambda of the mixer and the value of the substitution rate under the current accelerator opening phi and the engine speed n, and determining the fuel injection quantity of the ignition type fuel and the fuel injection quantity of the compression ignition type fuel according to the value of the excess air coefficient lambda of the mixer and the value of the substitution rate;
(6) the engine ECU14 performs closed-loop correction of the injection pulse width of the compression ignition fuel injector 7 and the ignition fuel injector 10.

Claims (3)

1. a control method of a dual fuel engine, characterized by comprising the steps of:
The dual-fuel engine is under the working conditions of cold start, warm-up or idling
(1) The opening of the throttle valve (11) is kept fully closed, and when the axis of the throttle valve (11) is consistent with the axis of an intake manifold, a gap is reserved between the edge of the throttle valve (11) and the intake manifold;
(2) the compression ignition fuel injector (7) stops working;
(3) determining the injection quantity of the ignition fuel according to the required value of the excess air coefficient lambda of the mixture under the working conditions of cold starting, warm-up or idling;
(4) Igniting when the piston moves to 5 CA degrees before the compression top dead center, and igniting combustible mixed gas formed by ignition fuel and air;
(5) The method comprises the following steps that a throttle valve position sensor (12) measures an opening signal of a throttle valve (11), and an engine ECU (14) performs closed-loop correction on the throttle valve opening psi according to the opening signal of the throttle valve (11) to enable the throttle valve (11) of the dual-fuel engine to be in a completely closed state under the working conditions of cold start, warm-up or idling;
The method comprises the following steps that an engine ECU (14) carries out closed-loop correction on the oil injection pulse width of a spark-ignition fuel oil injector (10) according to the oxygen content in an exhaust pipe of the engine, so that the value of the excess air coefficient lambda of mixed gas is always the required value of the excess air coefficient lambda of the mixed gas under the working conditions of cold starting, warm-up or idling;
the (II) dual-fuel engine is under the working condition of idling-30% load, namely small load
(1) The accelerator opening phi is increased from 0% to 30%;
(2) The engine ECU (14) adjusts the opening psi of the throttle valve (11) according to a relational expression of the change of the throttle valve opening psi with the accelerator opening phi; determining the quantity of the ignition fuel according to the required value of the excess air coefficient lambda of the mixed gas under the condition of small load; the compression ignition fuel injector (7) stops working;
(3) Igniting when the piston moves to 10 CA degrees before the compression top dead center, and igniting combustible mixed gas formed by ignition fuel and air;
(4) the throttle position sensor (12) measures an opening signal of the throttle valve (11), and the engine ECU (14) performs closed-loop correction on the throttle opening psi according to the opening signal of the throttle valve (11) so that the opening of the throttle valve (11) conforms to a relational expression of the change of the throttle opening psi with the accelerator opening phi;
The engine ECU (14) performs closed-loop correction on the oil injection pulse width of the ignition type fuel oil injector (10) according to the oxygen content, so that the mixed gas excess air coefficient lambda is a required value of the mixed gas excess air coefficient lambda under the condition of small load;
(III) the dual-fuel engine is under the working condition of 30-100% load
(1) the accelerator opening phi is increased from 30% to 100%;
(2) Determining an engine speed n;
(3) The opening psi of the throttle valve is rapidly adjusted to full opening;
(4) the spark plug (8) stops sparking;
(5) determining the value of the excess air coefficient lambda of the mixer and the value of the substitution rate L under the current accelerator opening phi and the engine speed n, and determining the fuel injection quantity of the ignition type fuel and the fuel injection quantity of the compression ignition type fuel according to the value of the excess air coefficient lambda of the mixer and the value of the substitution rate L;
(6) The engine ECU (14) performs closed-loop correction on the injection pulse width of the compression ignition fuel injector (7) and the ignition fuel injector (10).
2. the control method of a dual fuel engine as claimed in claim 1, characterized in that the closed loop correction of the pulse width of injection of the compression ignition fuel injector (7) and the ignition fuel injector (10) comprises the following steps:
Detecting the oxygen concentration in an exhaust pipe of the engine, comparing the detected oxygen concentration with a target range by an engine ECU (14), and if the oxygen concentration in the exhaust pipe is lower than the minimum value of the target range, sending a control command by the engine ECU (14) and simultaneously reducing the injection pulse width of a compression ignition fuel injector (7) and an ignition fuel injector (10);
if the oxygen concentration in the exhaust pipe is higher than the maximum value of the target range, the engine ECU (14) sends out a control command, and simultaneously increases the injection pulse width of the compression ignition fuel injector (7) and the ignition fuel injector (10);
if the oxygen concentration in the exhaust pipe is in the target range, adjusting the oil injection pulse width of the compression ignition fuel oil injector (7) and the ignition fuel oil injector (10), and the specific process is as follows: if the knock signal is detected, the engine ECU (14) sends a control command to reduce the oil injection pulse width of the ignition type fuel oil injector (10) and correspondingly increase the oil injection pulse width of the compression ignition type fuel oil injector (7), and the excess air coefficient lambda is kept unchanged; if the knock signal is not detected, the engine ECU (14) sends out a control command to increase the injection pulse width of the ignition type fuel injector (10) and reduce the injection pulse width of the compression ignition type fuel injector (7), and the excess air coefficient lambda is kept unchanged.
3. a dual fuel engine comprising an engine, characterized in that it further comprises an ignition device and a throttle device, both connected to the engine ECU (14); a spark plug (8) of an ignition device is arranged on a cylinder cover of the engine; the throttle valve device is arranged on an air inlet manifold of the engine;
The ignition device is characterized in that under the working condition that the dual-fuel engine is in cold starting, warming or idling, a spark plug (8) of the ignition device ignites when the piston moves to 5 degrees CA before a compression top dead center, and ignitable mixed gas formed by ignition fuel and air is ignited; under the working condition that the dual-fuel engine is at an idle speed of-30% load, namely a small load, a spark plug (8) ignites when the piston moves to 10 degrees CA before a compression top dead center, and a combustible mixture formed by ignition fuel and air is ignited; the dual-fuel engine is under the working condition of 30% -100% load, and the spark plug stops sparking;
the throttle valve device keeps fully closed under the working conditions of cold starting, warming or idling of the dual-fuel engine; under the working condition that the dual-fuel engine is at idle speed of-30% load, namely small load, the opening psi of the throttle valve is changed along with the opening phi of the accelerator; under the working condition that the dual-fuel engine is at 30% -100% load, the opening psi of the throttle valve is fully opened;
The throttle valve device comprises a throttle valve (11) and a throttle valve position sensor (12), wherein the throttle valve (11) is of a circular structure, and when the axis of the throttle valve (11) is consistent with the axis of the intake manifold, a gap is reserved between the edge of the throttle valve (11) and the intake manifold.
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