CN110821661B - Dual-fuel compression-ignition four-stroke engine based on reformed gas and combustion control method - Google Patents
Dual-fuel compression-ignition four-stroke engine based on reformed gas and combustion control method Download PDFInfo
- Publication number
- CN110821661B CN110821661B CN201810936677.4A CN201810936677A CN110821661B CN 110821661 B CN110821661 B CN 110821661B CN 201810936677 A CN201810936677 A CN 201810936677A CN 110821661 B CN110821661 B CN 110821661B
- Authority
- CN
- China
- Prior art keywords
- fuel
- cylinder
- nozzle
- reformed gas
- combustion
- 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.)
- Active
Links
Images
Classifications
-
- 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
- F02B69/00—Internal-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
- F02B69/02—Internal-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
- F02B69/04—Internal-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
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/004—Cylinder liners
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/242—Arrangement of spark plugs or injectors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
Abstract
The invention provides a dual-fuel compression ignition type four-stroke engine based on reformed gas and a combustion control method, and belongs to the field of combustion of internal combustion engines. The cylinder head is provided with a first fuel nozzle for direct injection in the cylinder and/or the intake passage is provided with a first fuel nozzle for intake passage, the cylinder head is provided with a second fuel nozzle for direct injection in the cylinder, and the cylinder head is provided with a reformed gas nozzle for direct injection in the cylinder and/or the intake passage is provided with a reformed gas nozzle for intake passage. 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. The efficient clean combustion in all working condition ranges is realized, and the energy structure is optimized.
Description
Technical Field
The invention relates to a dual-fuel compression-ignition four-stroke engine based on reformed gas and a combustion control method, belonging to the field of combustion of internal combustion engines.
Background
The application of hydrogen-adding to engine can improve the performance and emission of engine, mainly its combustion flame propagation speed is fast, promote the abundant combustion of fuel, raise the thermal efficiency, reduce the unburned product, and the ignition temperature is low, can improve the cold start of the engine. The production cost and storage of hydrogen is one difficulty currently applied to engines.
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 based on reformed gas. The method utilizes the waste heat of the engine exhaust gas to carry out on-line catalytic reforming on the fuel which is easy to reform and produce hydrogen, adjusts the injection strategy and other measures, realizes the high-efficiency clean combustion in all working condition ranges of the compression ignition four-stroke engine, and optimizes the energy structure.
The technical scheme adopted by the invention is as follows: the utility model provides a double fuel compression ignition formula four-stroke engine based on reformed gas, includes intake duct, exhaust passage and combustion chamber, sets up the first fuel nozzle of direct injection in the jar and/or be in on the cylinder cap set up the first fuel nozzle of intake duct on the intake duct, set up the second fuel nozzle of direct injection in the jar on the cylinder cap, set up the reforming gas nozzle of direct injection in the jar and/or set up intake duct reforming gas nozzle on the intake duct on the cylinder cap. 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 air 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 heat insulation coatings and/or heat insulation materials are selected at the top of the piston.
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 and/or exhaust gas recirculation technology is employed.
Further, the reformed gas is obtained by modifying carbohydrates, alcohols, ethers or hydrocarbons by utilizing waste heat energy of engine exhaust gas and/or an electric heating device and/or directly electrolyzing to prepare or fill pure hydrogen.
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 double-fuel compression-ignition four-stroke engine based on reformed gas 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, a second fuel nozzle is directly injected into the cylinder cover, under the condition that the air inlet channel and/or the cylinder cover is provided with the reformed gas nozzle, the compression ratio is set to be the critical compression ratio that main fuel cannot be directly compressed and ignited, and a pre-mixing 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, the first fuel nozzle is directly injected in the cylinder, and the second fuel nozzle and the reformed gas nozzle are directly injected in the cylinder to supply fuel;
at the time of medium load, the first fuel nozzle of the air inlet passage, the second fuel nozzle of direct injection in the cylinder and the reformed gas nozzle are used for supplying fuel;
at high load, fuel is supplied using the first fuel injector of the intake port, the first fuel injector of direct in-cylinder injection, the second fuel injector of direct in-cylinder injection, and the reformed gas injector.
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 based on reformed gas utilizes the waste heat of the exhaust gas of the engine to carry out on-line catalytic reforming on the fuel which is easy to reform and produce hydrogen, thereby not only effectively carrying out the heat management of the engine, but also solving the difficulty of storing hydrogen. The cylinder cover is provided with a cylinder head and a cylinder inlet channel, the cylinder head is provided with a first fuel nozzle which is easy to atomize, the cylinder head is provided with a second fuel nozzle which is directly injected into the cylinder, under the state that the cylinder head and/or the cylinder inlet channel are provided with reformed gas nozzles, the compression ratio is set to be the critical compression ratio that the main fuel can not 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 injection strategies under different working conditions are carried out to realize different combustion modes. Therefore, efficient clean combustion in all working condition ranges 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 is a block diagram of a dual fuel compression ignition four-stroke engine based on reformate gas in accordance with the present invention.
In the figure: 1. intake port, 2, exhaust port, 3, combustion chamber, 4, intake port reformed gas nozzle, 5, intake port first fuel nozzle, 6, in-cylinder direct injection first fuel nozzle, 7, in-cylinder direct injection second fuel nozzle, 8, in-cylinder direct injection reformed gas 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 a first fuel injector 6 for direct injection in the cylinder head and/or a first fuel injector 5 for an intake passage is provided in the intake passage 1, a second fuel injector 7 for direct injection in the cylinder head is provided in the cylinder head, a reformate injector 8 for direct injection in the cylinder head is provided in the intake passage 1, and/or a reformate injector 4 for an intake passage is provided in the intake passage 1. The engine ignition mode is such that the jet flow of the second fuel injection nozzle 7 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 is injected for multiple times 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 reformed gas is obtained by modifying carbohydrate, alcohol, ether or hydrocarbon by utilizing the waste heat energy of the engine exhaust gas and/or an electric heating device and/or directly electrolyzing to prepare or fill pure hydrogen. 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 based on reformed gas is characterized in that a first fuel nozzle which is easy to atomize is arranged on an air inlet channel and a cylinder cover of the engine at the same time, a second fuel nozzle 7 which is directly injected into a cylinder is arranged on the cylinder cover, and the following control is carried out according to the working condition under the state that the reformed gas nozzle is arranged on the air inlet channel and/or the cylinder cover:
at the time of low load, in the intake stroke, fuel is supplied by using the reforming gas nozzle 4 of the air inlet channel, the fuel and the air are mixed and then flow into the cylinder to form hydrogen-containing mixed gas, in the compression stroke, the first fuel nozzle 6 is directly injected for multiple times by using the cylinder to form layered mixed gas, the layered mixed gas rich in the reforming gas is ignited by the jet flow of the second fuel near the top dead center, layered combustion is realized, and the emission of HC and CO is reduced;
during medium load, in an intake stroke, fuel is supplied by using the air inlet channel reformed gas nozzle 4 and the air inlet channel first fuel nozzle 5, the fuel and air are mixed and then flow into a cylinder, relatively homogeneous lean mixed gas containing the reformed gas is formed in the cylinder, the mixed gas is in a critical state which cannot be directly compression-ignited and is close to compression-ignited by adopting variable compression ratio and EGR introduction, the mixed gas in the combustion chamber 3 is triggered by jet flow of second fuel to be close to the critical state, 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, fuel is supplied by using the intake passage reformed gas nozzle 4 and the intake passage first fuel nozzle 5, the fuel and the air are mixed and flow into the cylinder to form hydrogen-containing mixed gas, the fuel is supplied by using the compression top dead center and auxiliary in-cylinder direct injection second fuel nozzle 7, and the fuel is supplied by using the in-cylinder direct injection first fuel nozzle 6, so that premixed-diffusion synergistic combustion is realized, knocking is inhibited, and stable and efficient clean combustion is completed.
Preferably, the reformed gas nozzle may be provided in the intake port 1, or may be provided in the cylinder head in order to avoid backfire.
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 15%, the nitrogen oxide is reduced by 60%, the particulate matter emission is reduced by 95%, the hydrocarbon emission is reduced by 50%, and the carbon monoxide emission is reduced by 45%. Other embodiments of the invention can also achieve the effect of efficient clean combustion.
Embodiment 3 differs from embodiment 1 in that the number of in-cylinder direct injection first fuel injection nozzles 6 is reduced, and the first fuel is injected through the intake port first fuel injection nozzle 5 and mixed with the reformed gas for combustion, thereby achieving efficient clean combustion.
Example 4: different from the embodiments 1-3, the method adopts the variable valve technology and the exhaust gas recirculation technology, sets the critical compression ratio, enables the mixed gas to be in the critical state which can not be directly compressed and is close to compressed and ignited, and adopts the premixing compression ignition mode of direct injection of the second fuel jet to ignite to carry out high-efficiency clean combustion.
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 (6)
1. The combustion control method of the dual-fuel compression-ignition four-stroke engine based on the reformed gas 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 (6) for direct injection in a cylinder, the air inlet channel (1) is provided with a first fuel nozzle (5) for the air inlet channel, the cylinder cover is provided with a second fuel nozzle (7) for direct injection in the cylinder, the air inlet channel (1) is provided with a reformed gas nozzle (4), and the ignition mode of the engine is that the jet flow of the second fuel nozzle (7) for direct injection in the cylinder triggers the combustion of the fuel in the cylinder;
the reformed gas is prepared by carrying out catalytic reforming on the easily-reformed fuel by using the waste heat of the exhaust gas of the engine;
the combustion control method includes the steps of:
at the time of low load, in the intake stroke, fuel is supplied by using an air inlet channel reformed gas nozzle (4), the fuel is mixed with air and then flows into a cylinder to form a hydrogen-containing mixed gas, in the compression stroke, a first fuel nozzle (6) is directly injected for multiple times to form a layered mixed gas, and the layered mixed gas rich in the reformed gas is ignited by the jet flow of second fuel near a top dead center, so that layered combustion is realized, and the emission of HC and CO is reduced;
during medium load, in an intake stroke, fuel is supplied by using an intake passage reformed gas nozzle (4) and an intake passage first fuel nozzle (5), the fuel and air are mixed and then flow into a cylinder, homogeneous lean mixed gas containing the reformed gas is formed in the cylinder, the mixed gas is in a critical state which cannot be directly compression-ignited and is close to compression-ignited by adopting variable compression ratio and EGR introduction, the mixed gas in a combustion chamber (3) is triggered by jet flow of second fuel, the direct control of ignition phase is realized, stable premixed compression ignition is completed, and NOx emission is reduced;
at high load, in an intake stroke, fuel is supplied by using an intake passage reformed gas nozzle (4) and an intake passage first fuel nozzle (5), the fuel and the air are mixed and flow into a cylinder to form a hydrogen-containing mixed gas, the fuel is supplied by using an auxiliary cylinder direct injection second fuel nozzle (7) near a compression top dead center, and the fuel is supplied by using a cylinder direct injection first fuel nozzle (6), so that premixed-diffused synergic combustion is realized, knocking is inhibited, and stable and efficient clean combustion is completed.
2. A combustion control method of a reformed gas based 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 combustion control method of a reformed gas based 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 combustion control method of a reformed gas based 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 combustion control method of a reformed gas based dual fuel compression ignition four-stroke engine as claimed in claim 1, wherein: using variable valve technology and/or using exhaust gas recirculation technology.
6. The combustion control method of a reformed-gas-based dual-fuel compression-ignition four-stroke engine as claimed in claim 5, wherein: during cold start, the variable valve technology is adopted to improve the compression ratio.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810887785 | 2018-08-07 | ||
| CN2018108877857 | 2018-08-07 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110821661A CN110821661A (en) | 2020-02-21 |
| CN110821661B true CN110821661B (en) | 2022-04-01 |
Family
ID=69547363
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810936677.4A Active CN110821661B (en) | 2018-08-07 | 2018-08-16 | Dual-fuel compression-ignition four-stroke engine based on reformed gas and combustion control method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN110821661B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111305968B (en) * | 2020-03-12 | 2021-11-12 | 上海交通大学 | Fuel injection method and device for multi-fuel charge compression combustion engine |
| CN111336006B (en) * | 2020-03-12 | 2022-01-07 | 上海交通大学 | Multi-fuel intelligent charge compression combustion engine |
| CN111365133B (en) * | 2020-03-12 | 2022-03-04 | 上海交通大学 | Multi-fuel charging-quantity compression combustion engine combustion system and control method |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102278240A (en) * | 2011-06-08 | 2011-12-14 | 清华大学 | Method and device for reducing oil consumption of diesel engine by utilizing catalytic decomposition of oxygen-containing fuels |
| CN102472177A (en) * | 2009-09-30 | 2012-05-23 | 株式会社日立制作所 | Engine system with reformer |
| CN102635437A (en) * | 2011-02-10 | 2012-08-15 | 曼柴油机和涡轮机欧洲股份公司 | A two-stroke internal combustion engine and a method for making the engine work |
| CN103511104A (en) * | 2012-06-29 | 2014-01-15 | 曼恩柴油机涡轮股份公司曼恩柴油机涡轮德国分公司 | An internal combustion engine with control of fuel gas injection pressure |
| CN103748334A (en) * | 2011-07-08 | 2014-04-23 | 瓦锡兰瑞士有限公司 | Two-stroke internal combustion engine, method of operating two-stroke internal combustion engine and method of converting two-stroke engine |
| CN104854323A (en) * | 2013-01-28 | 2015-08-19 | 株式会社Ihi | Uniflow-scavenged two-cycle engine and fuel injection method for uniflow-scavenged two-cycle engine |
| CN105317573A (en) * | 2014-06-16 | 2016-02-10 | 上海汽车集团股份有限公司 | Fuel injection method for direct injection combustion system |
| CN106499531A (en) * | 2016-10-16 | 2017-03-15 | 北京工业大学 | A kind of twin-jet nozzle gas/liquid double fuel in-cylinder direct-jet internal combustion engine and control method |
| CN106640428A (en) * | 2015-10-29 | 2017-05-10 | 意法半导体股份有限公司 | Engine group comprising a mixed fuel engine and fuel supplying method therof |
| CN106677930A (en) * | 2017-03-09 | 2017-05-17 | 宽城天宇鹿业有限公司 | Internal combustion engine and vehicle |
| CN106870186A (en) * | 2016-02-04 | 2017-06-20 | 大连理工大学 | Dual fuel engine fuel injection manner |
| CN107781026A (en) * | 2017-09-22 | 2018-03-09 | 大连理工大学 | Spark ignitor formula internal combustion engine homogeneous charge compression ignition system |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9915235B2 (en) * | 2015-10-02 | 2018-03-13 | Wisconsin Alumni Research Foundation | Engine combustion control at high loads via fuel reactivity stratification |
-
2018
- 2018-08-16 CN CN201810936677.4A patent/CN110821661B/en active Active
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102472177A (en) * | 2009-09-30 | 2012-05-23 | 株式会社日立制作所 | Engine system with reformer |
| CN102635437A (en) * | 2011-02-10 | 2012-08-15 | 曼柴油机和涡轮机欧洲股份公司 | A two-stroke internal combustion engine and a method for making the engine work |
| CN102278240A (en) * | 2011-06-08 | 2011-12-14 | 清华大学 | Method and device for reducing oil consumption of diesel engine by utilizing catalytic decomposition of oxygen-containing fuels |
| CN103748334A (en) * | 2011-07-08 | 2014-04-23 | 瓦锡兰瑞士有限公司 | Two-stroke internal combustion engine, method of operating two-stroke internal combustion engine and method of converting two-stroke engine |
| CN103511104A (en) * | 2012-06-29 | 2014-01-15 | 曼恩柴油机涡轮股份公司曼恩柴油机涡轮德国分公司 | An internal combustion engine with control of fuel gas injection pressure |
| CN104854323A (en) * | 2013-01-28 | 2015-08-19 | 株式会社Ihi | Uniflow-scavenged two-cycle engine and fuel injection method for uniflow-scavenged two-cycle engine |
| CN105317573A (en) * | 2014-06-16 | 2016-02-10 | 上海汽车集团股份有限公司 | Fuel injection method for direct injection combustion system |
| CN106640428A (en) * | 2015-10-29 | 2017-05-10 | 意法半导体股份有限公司 | Engine group comprising a mixed fuel engine and fuel supplying method therof |
| CN106870186A (en) * | 2016-02-04 | 2017-06-20 | 大连理工大学 | Dual fuel engine fuel injection manner |
| CN106499531A (en) * | 2016-10-16 | 2017-03-15 | 北京工业大学 | A kind of twin-jet nozzle gas/liquid double fuel in-cylinder direct-jet internal combustion engine and control method |
| CN106677930A (en) * | 2017-03-09 | 2017-05-17 | 宽城天宇鹿业有限公司 | Internal combustion engine and vehicle |
| CN107781026A (en) * | 2017-09-22 | 2018-03-09 | 大连理工大学 | Spark ignitor formula internal combustion engine homogeneous charge compression ignition system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110821661A (en) | 2020-02-21 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP2606215B1 (en) | Internal combustion engine provided with a stoichiometric mixture of two fuels with a compression ignition | |
| CN114320572B (en) | Multi-combustion-mode ammonia fuel engine and control method thereof | |
| CN109441626B (en) | Dual-fuel engine combustion organization method adopting main and auxiliary fuel injectors and manifold for multiple injection | |
| US20140299105A1 (en) | Methods for Low Temperature Combustion and Engines Using the Same | |
| CN110821661B (en) | Dual-fuel compression-ignition four-stroke engine based on reformed gas and combustion control method | |
| CN105673281B (en) | In a kind of gas/liquid double fuel cylinder/cylinder outer pair of injection apparatus and control method | |
| CN101907030A (en) | Composite homogeneity compression-ignition engine based on fuel real-time design and jet management | |
| CN108571392A (en) | Lean-burn systems and method for spark-ignition engine | |
| CN111219269A (en) | Partial premixing combustion system based on liquid hydrogen fuel piston engine and engine | |
| CN110145405A (en) | The double injected petrol lean-combustion engines of perforated plate type atomizer | |
| CN110821662A (en) | Dual-fuel compression-ignition two-stroke engine based on reformed gas and combustion control method | |
| CN111305968B (en) | Fuel injection method and device for multi-fuel charge compression combustion engine | |
| CN110821653A (en) | Dual-fuel ignition chamber type four-stroke engine based on reformed gas and combustion control method | |
| CN110821638B (en) | Ignition chamber type engine with high-energy ignition fuel and control method thereof | |
| CN103216316B (en) | Low-temperature combustion method of internal-combustion engine with fuel reformation inside cylinders and system | |
| CN105736165A (en) | Engine intelligent combustion system capable of regulating mixed gas components in cylinder and combustion modes at will | |
| CN110821652A (en) | Dual-fuel ignition chamber type two-stroke engine based on reformed gas and combustion control method | |
| CN110821658A (en) | Single-fuel ignition chamber type four-stroke engine based on reformed gas and combustion control method | |
| CN110821654B (en) | Dual-fuel spark plug type four-stroke engine based on reformed gas and combustion control method | |
| CN110821655B (en) | Reformed gas-based single-fuel plasma nozzle type two-stroke engine and combustion control method | |
| CN110821664A (en) | Dual-fuel ignition chamber type four-stroke engine and combustion control method | |
| CN101929364A (en) | Diffusion combustion method for knock-resisting compression ignition of equivalence-ratio gasoline direct injection engine | |
| CN110821639B (en) | Multi-mode engine with high-energy ignition fuel and control method thereof | |
| CN110067638A (en) | A kind of fuel jet ignition type premixed combustion of IC engine system | |
| CN110821641A (en) | Ignition chamber type engine with high-energy ignition fuel and control method thereof |
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 | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |