CN110821657A - Dual-fuel compression ignition type four-stroke engine and combustion control method - Google Patents

Dual-fuel compression ignition type four-stroke engine and combustion control method Download PDF

Info

Publication number
CN110821657A
CN110821657A CN201810935886.7A CN201810935886A CN110821657A CN 110821657 A CN110821657 A CN 110821657A CN 201810935886 A CN201810935886 A CN 201810935886A CN 110821657 A CN110821657 A CN 110821657A
Authority
CN
China
Prior art keywords
fuel
cylinder
nozzle
dual
injection
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN201810935886.7A
Other languages
Chinese (zh)
Inventor
隆武强
崔靖晨
田华
王洋
张恒
曹建林
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dalian University of Technology
Original Assignee
Dalian University of Technology
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to CN201810887288 priority Critical
Priority to CN2018108872887 priority
Application filed by Dalian University of Technology filed Critical Dalian University of Technology
Publication of CN110821657A publication Critical patent/CN110821657A/en
Pending legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B69/00Internal-combustion engines convertible into other combustion-engine type, not provided for in F02B11/00; Internal-combustion engines of different types characterised by constructions facilitating use of same main engine-parts in different types
    • F02B69/02Internal-combustion engines convertible into other combustion-engine type, not provided for in F02B11/00; Internal-combustion engines of different types characterised by constructions facilitating use of same main engine-parts in different types for different fuel types, other than engines indifferent to fuel consumed, e.g. convertible from light to heavy fuel
    • F02B69/04Internal-combustion engines convertible into other combustion-engine type, not provided for in F02B11/00; Internal-combustion engines of different types characterised by constructions facilitating use of same main engine-parts in different types for different fuel types, other than engines indifferent to fuel consumed, e.g. convertible from light to heavy fuel for gaseous and non-gaseous fuels
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D19/00Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06Controlling 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
    • F02D19/08Controlling 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02FCYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00Cylinders; Cylinder heads 
    • F02F1/004Cylinder liners
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02FCYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00Cylinders; Cylinder heads 
    • F02F1/24Cylinder heads
    • F02F1/242Arrangement of spark plugs or injectors
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M39/00Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00Other engines
    • F02B75/02Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four

Abstract

The invention provides a dual-fuel compression-ignition four-stroke engine and a combustion control method, and belongs to the field of combustion of internal combustion engines. The cylinder cover is provided with a first fuel nozzle for direct injection in the cylinder and/or the air inlet channel is provided with a first fuel nozzle for air inlet channel, and the cylinder cover is provided with a second fuel nozzle for direct injection in the cylinder. Under the condition that all types of nozzles are arranged, the first fuel and the second fuel are supplied to the fuel through the direct injection nozzle in the cylinder at the time of low load, and the heat efficiency is improved; during medium load, the first fuel nozzle of the air inlet channel and the second fuel nozzle of direct injection in the cylinder supply fuel to reduce the generation of NOx; at high load, all the injectors of the first fuel and the second fuel are supplied with fuel, and knocking is controlled. High-efficiency clean combustion in the whole working condition range is realized, and the energy structure is optimized.

Description

Dual-fuel compression ignition type four-stroke engine and combustion control method
Technical Field
The invention relates to a dual-fuel compression-ignition four-stroke engine and a combustion control method, and belongs to the field of combustion of internal combustion engines.
Background
Energy and environmental issues are becoming more prominent, and low temperature combustion of premixed compression ignition can improve the thermal efficiency of the engine and reduce NOx emissions. However, the ignition timing of premixed compression ignition is affected by environmental conditions and engine operating conditions and is difficult to control reliably. In addition, the working condition range is small, excessive HC and CO can be generated in cold start and low load, and knocking can be generated in high load.
The engine with single fuel is difficult to meet the requirement of energy diversification, and the combustion characteristic of the single fuel has limitation, so that the performance improvement of the engine is limited.
Disclosure of Invention
The invention discloses a dual-fuel compression ignition type four-stroke engine and a combustion control method. The method is characterized in that measures such as direct injection in a cylinder and air inlet channel injection nozzles are arranged, injection strategies are adjusted, efficient clean combustion in the full working condition range of the compression-ignition four-stroke engine is achieved, and an energy structure is optimized.
The technical scheme adopted by the invention is as follows: a dual-fuel compression ignition type four-stroke engine comprises an air inlet channel, an air outlet channel and a combustion chamber, wherein a cylinder cover is provided with a first fuel nozzle for direct injection in a cylinder and/or the air inlet channel is provided with a first fuel nozzle for the air inlet channel, and the cylinder cover is provided with a second fuel nozzle for direct injection in the cylinder; the engine ignition mode is to trigger the combustion of the fuel in the cylinder by the jet flow of the second fuel nozzle.
Further, the bottom of the cylinder cover, the bottom of the exhaust valve, the top surface of the piston, a fire bank and the upper part of the cylinder sleeve which can not be contacted by the piston ring are sprayed with a heat insulation coating and/or the top of the piston is selected from a heat insulation material.
Further, the in-cylinder direct injection fuel nozzle employs a high-disturbance nozzle.
Further, the in-cylinder direct injection fuel employs multiple injections.
Further, variable valve technology is employed.
Further, exhaust gas recirculation technology is employed.
Further, the second fuel is easily compression-ignited hydrocarbon, ether and mixture thereof; when the first fuel is diesel oil, ether, or mixed fuel containing diesel oil or mixed fuel containing ether, the fuel nozzle can only select an in-cylinder direct injection nozzle, the compression ratio is set to a critical compression ratio at which the main fuel cannot be directly compression-ignited, and the premixed compression ignition is performed.
A combustion control method of a dual-fuel compression-ignition four-stroke engine is characterized in that a first fuel nozzle easy to atomize is simultaneously arranged on an air inlet channel and a cylinder cover of the engine, under the condition that a second fuel nozzle is directly injected into the cylinder cover, the compression ratio is set to be the critical compression ratio that main fuel cannot be directly compressed and ignited, and a premixed compression ignition mode that the second fuel nozzle is directly injected into the cylinder to ignite is adopted; or a premixing-diffusion collaborative combustion mode is adopted under all working conditions; or the following control is carried out according to the working condition:
at the time of low load, supplying fuel by using a first fuel injection nozzle of direct in-cylinder injection and a second fuel injection nozzle of direct in-cylinder injection;
at the time of medium load, supplying fuel by using a first fuel nozzle of an air inlet channel and a second fuel nozzle of direct injection in a cylinder;
at high load, fuel is supplied using the first fuel injector of the intake passage, the first fuel injector of direct in-cylinder injection, and the second fuel injector of direct in-cylinder injection.
During cold start, the variable valve technology is adopted to improve the compression ratio.
The invention has the beneficial effects that: the dual-fuel compression-ignition four-stroke engine is characterized in that a first fuel nozzle easy to atomize is simultaneously arranged on an air inlet channel and a cylinder cover, under the condition that a second fuel nozzle is directly injected into the cylinder cover, the compression ratio is set to be the critical compression ratio that main fuel cannot be directly compressed and ignited, and a premixed compression ignition mode of directly injecting the second fuel into the cylinder to ignite is adopted; or a premixing-diffusion collaborative combustion mode is adopted under all working conditions; or the injection strategies under different working conditions are carried out to realize different combustion modes. Therefore, efficient clean combustion in the whole working condition range is realized, and the energy structure is optimized.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings needed to be used in the description of the embodiments or the prior art will be briefly introduced below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.
Fig. 1 shows a block diagram of a dual fuel compression ignition four stroke engine.
In the figure: 1. an air inlet channel, 2, an air outlet channel, 3, a combustion chamber, 4, an air inlet channel first fuel nozzle, 5, an in-cylinder direct injection first fuel nozzle, and 6, an in-cylinder direct injection second fuel nozzle.
Detailed Description
It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict. The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the invention, its application, or uses. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the invention. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, and it should be understood that when the terms "comprises" and/or "comprising" are used in this specification, they specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof, unless the context clearly indicates otherwise.
The relative arrangement of the components and steps, the numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present invention unless specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective portions shown in the drawings are not drawn in an actual proportional relationship for the convenience of description. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate. In all examples shown and discussed herein, any particular value should be construed as merely illustrative, and not limiting. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, further discussion thereof is not required in subsequent figures.
In the description of the present invention, it is to be understood that the orientation or positional relationship indicated by the directional terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal" and "top, bottom", etc., are generally based on the orientation or positional relationship shown in the drawings, and are used for convenience of description and simplicity of description only, and in the absence of any contrary indication, these directional terms are not intended to indicate and imply that the device or element so referred to must have a particular orientation or be constructed and operated in a particular orientation, and therefore should not be considered as limiting the scope of the present invention: the terms "inner and outer" refer to the inner and outer relative to the profile of the respective component itself.
Spatially relative terms, such as "above … …," "above … …," "above … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial relationship to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if a device in the figures is turned over, devices described as "above" or "on" other devices or configurations would then be oriented "below" or "under" the other devices or configurations. Thus, the exemplary term "above … …" can include both an orientation of "above … …" and "below … …". The device may be otherwise variously oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
It should be noted that the terms "first", "second", and the like are used to define the components, and are only used for convenience of distinguishing the corresponding components, and the terms have no special meanings unless otherwise stated, and therefore, the scope of the present invention should not be construed as being limited.
For a further understanding of the invention, reference should be made to the following detailed description taken in conjunction with the accompanying drawings in which:
embodiment 1, as shown in fig. 1, the engine includes an intake passage 1, an exhaust passage 2, and a combustion chamber 3, and in-cylinder direct injection first fuel injection nozzles 5 are provided in a cylinder head and/or intake passage first fuel injection nozzles 4 are provided in the intake passage, and in-cylinder direct injection second fuel injection nozzles 6 are provided in the cylinder head; the engine ignition mode is such that the jet flow of the second fuel injection nozzle 6 triggers in-cylinder fuel combustion.
The bottom of the cylinder cover, the bottom of the air valve, the top surface of the piston, the firepower bank and the upper part of the cylinder sleeve which can not be contacted by the piston ring are sprayed with a heat insulation coating and/or a piston selection ceramic material, so that the heat transfer loss in the cylinder is reduced, and the heat efficiency of the engine is improved; the in-cylinder direct injection fuel nozzle adopts a high-disturbance nozzle, so that the fuel oil spray atomization quality is enhanced; in-cylinder direct injection fuel injection adopts multiple times of injection to form layered mixed gas or relatively homogeneous premixed gas; variable valve technology is adopted to realize variable compression ratio. And the combustion speed of the fuel in the cylinder is controlled by adopting an exhaust gas recirculation technology. The second fuel is easily compression-ignited hydrocarbon, ether and mixture thereof; when the first fuel is diesel oil, ether, or mixed fuel containing diesel oil or mixed fuel containing ether, the fuel nozzle can only select an in-cylinder direct injection nozzle, the compression ratio is set to a critical compression ratio at which the main fuel cannot be directly compression-ignited, and the premixed compression ignition is performed.
A combustion control method of a dual-fuel compression ignition type four-stroke engine is characterized in that a first fuel nozzle which is easy to atomize is simultaneously arranged on an air inlet channel and a cylinder cover of the engine, and the engine is controlled as follows according to working conditions under the condition that a second fuel nozzle is directly injected into the cylinder cover:
at the time of low load, in a compression stroke, fuel is supplied by using the in-cylinder direct injection first fuel nozzle 5 for multiple injection to form stratified mixture, and the stratified mixture is ignited by the jet flow of the second fuel near the top dead center, so that stratified combustion is realized, and the emission of HC and CO is reduced.
During medium load, in an intake stroke, the first fuel nozzle 4 of the air inlet channel is used for supplying fuel, the fuel is mixed with air and flows into a cylinder, relatively homogeneous lean air-fuel mixture is formed in the cylinder, the air-fuel mixture is in a critical state which cannot be directly compressed and is close to compressed ignition by adopting variable compression ratio and introducing EGR, the air-fuel mixture close to the critical state in the combustion chamber 3 is triggered by jet flow of second fuel, direct control over ignition phase is realized, stable premixed compression ignition is completed, and NOx emission is reduced.
At high load, in the intake stroke, the first fuel nozzle 4 of the air inlet channel is used for supplying fuel, the fuel is mixed with air and flows into the cylinder to form relatively homogeneous mixed gas, the second fuel nozzle 6 of direct injection in the cylinder is assisted to supply fuel near a compression top dead center, and the first fuel nozzle 5 of direct injection in the cylinder is used for supplying fuel, so that premixed-diffusion synergistic combustion is realized, knocking is inhibited, and stable and efficient clean combustion is completed.
During cold start, the variable valve technology is adopted to improve the compression ratio.
In the embodiment, the main fuels are dimethyl ether and methanol, and the research is carried out on a four-stroke engine, compared with the original engine, the thermal efficiency is improved by 10%, the nitrogen oxide is reduced by 70%, the particulate matter emission is reduced by 95%, the hydrocarbon emission is reduced by 45%, and the carbon monoxide emission is reduced by 40%. Other embodiments of the invention can also achieve the effect of efficient clean combustion.
Embodiment 2 is different from embodiment 1 in that the number of main fuel nozzles 4 in the air inlet channel is reduced, and the efficient and clean split-operating-condition combustion is realized by mixing and combusting with reformed gas by changing the injection time, the injection times and other strategies of the main fuel nozzle 5 for direct injection in the cylinder.
Embodiment 3 differs from embodiment 1 in that the number of direct-injection main fuel injectors 5 is reduced, and the main fuel is injected through the intake main fuel injector 4 and mixed with the reformed gas for combustion, thereby achieving efficient clean combustion.
Embodiment 4 is different from embodiments 1 to 3 in that a variable valve technology and an exhaust gas recirculation technology are adopted, a critical compression ratio is set, so that the mixed gas is in a critical state which can not be directly compressed and is close to compressed, and efficient clean combustion is carried out by adopting a premixed compression ignition mode of flame jet ignition of an ignition chamber.
Example 5 differs from examples 1-4 in that premixed-diffusion co-combustion was used under all conditions.
Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; while the invention has been described in detail and with reference to the foregoing embodiments, it will be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and the modifications or the substitutions do not make the essence of the corresponding technical solutions depart from the scope of the technical solutions of the embodiments of the present invention.

Claims (9)

1. A dual-fuel compression ignition type four-stroke engine comprises an air inlet channel (1), an air outlet channel (2) and a combustion chamber (3), and is characterized in that a cylinder cover is provided with a first fuel nozzle (5) for direct injection in a cylinder and/or the air inlet channel (1) is provided with a first fuel nozzle (4) for the air inlet channel, and the cylinder cover is provided with a second fuel nozzle (6) for direct injection in the cylinder; the ignition mode of the engine is that the jet flow of the second fuel nozzle (6) directly injects in-cylinder fuel to trigger the combustion of the in-cylinder fuel.
2. A dual fuel compression ignition four stroke engine as claimed in claim 1 wherein: the bottom of the cylinder cover, the bottom of the air valve, the top surface of the piston, the fire bank and the upper part of the cylinder sleeve which can not be contacted by the piston ring are sprayed with heat insulation coatings and/or heat insulation materials selected from the top of the piston.
3. A dual fuel compression ignition four stroke engine as claimed in claim 1 wherein: the in-cylinder direct injection fuel nozzle adopts a high-disturbance nozzle.
4. A dual fuel compression ignition four stroke engine as claimed in claim 1 wherein: the direct injection fuel in the cylinder adopts multiple injections.
5. A dual fuel compression ignition four stroke engine as claimed in claim 1 wherein: variable valve technology is employed.
6. A dual fuel compression ignition four stroke engine as claimed in claim 1 wherein: exhaust gas recirculation technology is used.
7. A dual fuel compression ignition four stroke engine as claimed in claim 1 wherein: the second fuel is easily compression-ignited hydrocarbon, ether and mixture thereof; when the first fuel is diesel oil, ether, or mixed fuel containing diesel oil or mixed fuel containing ether, the fuel nozzle can only select an in-cylinder direct injection nozzle, the compression ratio is set to a critical compression ratio at which the main fuel cannot be directly compression-ignited, and the premixed compression ignition is performed.
8. A combustion control method of a dual-fuel compression ignition type four-stroke engine is characterized in that: the engine is provided with a first fuel nozzle which is easy to atomize on an air inlet channel and a cylinder cover at the same time, under the condition that a second fuel nozzle is directly injected into the cylinder cover, the compression ratio is set to be the critical compression ratio that the main fuel can not be directly compressed and ignited, and a premixing compression ignition mode that the second fuel nozzle is directly injected into the cylinder to ignite is adopted; or a premixing-diffusion collaborative combustion mode is adopted under all working conditions; or the following control is carried out according to the working condition:
at the time of low load, fuel is supplied by using a first fuel injection nozzle (5) for direct in-cylinder injection and a second fuel injection nozzle (6) for direct in-cylinder injection;
at the time of medium load, fuel is supplied by using a first fuel nozzle (4) of an air inlet channel and a second fuel nozzle (6) of direct injection in a cylinder;
at high load, fuel is supplied from the first fuel injector (4) of the intake passage, the first fuel injector (5) of direct in-cylinder injection, and the second fuel injector (6) of direct in-cylinder injection.
9. The combustion control method of a dual fuel compression ignition four-stroke engine as claimed in claim 8, wherein: during cold start, the variable valve technology is adopted to improve the compression ratio.
CN201810935886.7A 2018-08-07 2018-08-16 Dual-fuel compression ignition type four-stroke engine and combustion control method Pending CN110821657A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201810887288 2018-08-07
CN2018108872887 2018-08-07

Publications (1)

Publication Number Publication Date
CN110821657A true CN110821657A (en) 2020-02-21

Family

ID=69547366

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201810935886.7A Pending CN110821657A (en) 2018-08-07 2018-08-16 Dual-fuel compression ignition type four-stroke engine and combustion control method

Country Status (1)

Country Link
CN (1) CN110821657A (en)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106870186A (en) * 2016-02-04 2017-06-20 大连理工大学 Dual fuel engine fuel injection manner

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106870186A (en) * 2016-02-04 2017-06-20 大连理工大学 Dual fuel engine fuel injection manner

Similar Documents

Publication Publication Date Title
Alvarez et al. A review of prechamber ignition systems as lean combustion technology for SI engines
Li et al. Experimental and theoretical analysis of the combustion process at low loads of a diesel natural gas dual-fuel engine
Karim Combustion in Gas‐fueled Compression Ignition Engines of the Dual Fuel Type
US20170198629A1 (en) Internally cooled internal combustion engine and method thereof
Dec Advanced compression-ignition engines—understanding the in-cylinder processes
Zeng et al. Combustion characteristics of a direct-injection natural gas engine under various fuel injection timings
CA2767247C (en) Apparatus and method for igniting a gaseous fuel in a direct injection internal combustion engine
Park et al. Stratified lean combustion characteristics of a spray-guided combustion system in a gasoline direct injection engine
Gan et al. Homogeneous charge compression ignition (HCCI) combustion: implementation and effects on pollutants in direct injection diesel engines
Zheng et al. Effect of equivalence ratio on combustion and emissions of a dual-fuel natural gas engine ignited with diesel
US10450975B2 (en) Skip-fire fuel injection system and method
JP3964387B2 (en) Control device for compression ignition type internal combustion engine
CN104995392B (en) The fuel injection strategy of middle of cycle
RU2342543C2 (en) Internal combustion engine with gas fuel injection
US7171953B2 (en) Method for operating an internal combustion engine with direct fuel injection
Toulson et al. A review of pre-chamber initiated jet ignition combustion systems
CN103061908B (en) Flexible double fuel HPCC engine combustion, discharge control method and device
CN106870186A (en) Dual fuel engine fuel injection manner
US20150300296A1 (en) Internally cooled exhaust gas recirculation system for internal combustion engine and method thereof
Kanda et al. PCCI operation with early injection of conventional diesel fuel
Stanglmaier et al. Homogeneous charge compression ignition (HCCI): benefits, compromises, and future engine applications
US7270108B2 (en) Opposed piston, homogeneous charge pilot ignition engine
CN101443540B (en) Method of injecting a gaseous fuel into an internal combustion engine
CN103154474B (en) The method of the stoichiometric explosive motor of vaporized fuel and operation explosive motor
JP4214586B2 (en) Fuel supply method for gasoline internal combustion engine

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination