CN104806382B - It is the automotive fuel carrying method of fuel to use gas-liquid two-phase natural gas - Google Patents
It is the automotive fuel carrying method of fuel to use gas-liquid two-phase natural gas Download PDFInfo
- Publication number
- CN104806382B CN104806382B CN201510153562.4A CN201510153562A CN104806382B CN 104806382 B CN104806382 B CN 104806382B CN 201510153562 A CN201510153562 A CN 201510153562A CN 104806382 B CN104806382 B CN 104806382B
- Authority
- CN
- China
- Prior art keywords
- adiabatic
- natural gas
- common rail
- gas
- liquid
- 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.)
- Expired - Fee Related
Links
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/30—Use of alternative fuels, e.g. biofuels
Landscapes
- Output Control And Ontrol Of Special Type Engine (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
Abstract
It is the automotive fuel carrying method of fuel the invention discloses gas-liquid two-phase natural gas is used, liquid compressed natural gas source and gaseous state compressed natural gas source are delivered to an adiabatic common rail by thermal insulation, cylinder is delivered to through an electric-controlled fuel injector after completing mixing in adiabatic common rail：Fuel into adiabatic common rail (5) has fluid path and gas circuit two-way：Fluid path is delivered to adiabatic common rail (5) by liquid compressed natural gas bottle (1) by adiabatic low-voltage tube (2) and adiabatic pressure pump (10)；Gas circuit enters adiabatic common rail (5) by gaseous compressed natural gas cylinder (7) by corresponding pipe valve.The present invention makes gas-liquid two-phase natural gas that flash distillation boiling to occur when cylinder is entered, and carries out the gas-liquid component real-time design control of two-phase natural gas in different operating modes.Because of burning is gas-liquid two-phase natural gas, therefore CO, CO2, PM discharge it is low, without NMHC；Sprayed using compression process, HC discharges are low；Cylinder temperature is low, NOXDischarge is low；With extremely low emission performance.
Description
Art
The present invention relates to a kind of I. C engine combustion system construction, more particularly to natural gas is used as the burning system of fuel
System.
Background technology
In current natural gas internal combustion engine, either using the central port injection at inlet manifold, at inlet manifold
Multi-point injection or the inner cylinder direct injection by air nozzle on cylinder cap, the fuel of its injection is all gaseous natural gas.Non-straight
In jet natural gas machine, natural gas reduces by 12% with the gaseous mixture of air compared to the heat vale of mixture of diesel oil and air；Meanwhile, day
Right gas is entered in cylinder with gaseous state, to occupy certain volume of cylinder, air inlet amount ratio is reduced about when using liquid fuel
10%.In-cylinder direct-jet natural gas internal combustion engine is that natural gas enters cylinder at the end of induction stroke, though can so increase air inlet
Amount, but natural gas gaseous mixture is relative to liquid fuel gaseous mixture, fuel will not carburation by evaporation absorb heat of evaporation, will not also make air inlet
Temperature reduction.So the intake air temperature of current natural gas engine is higher, the thermic load of combustion chamber component is higher, and NOXBe
A large amount of generations are had in the case of high-temperature oxygen-enriched, therefore is unfavorable for improving reliability and reducing discharging.
The content of the invention
In view of prior art is not enough above, it is an object of the invention to propose a kind of internal combustion engine of gas-liquid two-phase natural gas
Combustion system, using the discharge of the internal combustion engine of the system is low, reliability is high.
The purpose of the present invention is realized by following technological means.
It is a kind of that to use gas-liquid two-phase natural gas be the automotive fuel carrying method of fuel, by liquid compressed natural gas source and
Gaseous compressed gas source is delivered to an adiabatic common rail by thermal insulation, through an electric-controlled fuel injector after completing mixing in adiabatic common rail
It is delivered to cylinder；Its specific course of conveying and condition of work are：
1) fuel into adiabatic common rail 5 has fluid path and gas circuit two-way：Fluid path is by liquid compressed natural gas bottle (1) by exhausted
Heat low pipe 2 and adiabatic pressure pump 10 are delivered to adiabatic common rail 5；Gas circuit passes through corresponding pipe valve by gaseous compressed natural gas cylinder 7
Into adiabatic common rail 5；
2) exported by adiabatic common rail 5 through the mixed fuel of adiabatic common rail 5 and be delivered to cylinder after electric-controlled fuel injector 8；
3) fluid path and gas circuit set corresponding pipe valve and are attached, and corresponding pressure sensor is set in gas circuit；It is interior
Combustion engine electronic control unit 9
Adiabatic low-voltage tube 2 is connected with the import of adiabatic pressure pump 10；Adiabatic pressure pump 10 passes through adiabatic high-voltage tube through magnetic valve 4
It is connected with adiabatic common rail 5 afterwards；Adiabatic common rail 5 passes through adiabatic high-voltage tube and is connected with the electric-controlled fuel injector 8 on cylinder；Gaseous compressed day
Right gas bottle 7 passes through adiabatic high-voltage tube and is connected with adiabatic common rail 5；Adiabatic pressure pump 10, magnetic valve 4, adiabatic common rail 5, pressure are passed
Sensor 6 and electric-controlled fuel injector 8 are electrically connected with internal combustion engine electronic-control unit 9 and control adiabatic pressure pump 10, magnetic valve 4, absolutely
Hot common rail 5, pressure sensor 6 and electric-controlled fuel injector 8 are controlled with meeting the optimal combustion condition of internal combustion engine.
Using technical scheme as above, its running is：
The liquified natural gas being stored in gas cylinder is delivered in adiabatic pressure pump by heat-insulated pipe, and compression pump is by liquified natural gas
It is forced into during 20MPa or so delivers to adiabatic common rail by adiabatic high-voltage tube and magnetic valve, is stored in pressure for 20MPa gas cylinders
In gaseous compressed natural gas adiabatic common rail delivered to by heat-insulated pipe, by controlling the opening/closing time of magnetic valve and then to common rail
In natural gas carry out gas-liquid two-phase real-time design after deliver to electric-controlled fuel injector.Gas-liquid two-phase natural gas sprays in compression process,
And lighted by spark.
When two phase flow natural gas sprays to low-voltage high-temperature environment, the degree of superheat of gas increases, and gas is expanded, and forms bubble
Foam is simultaneously grown up, and is drastically disengaged in nozzle exit gas, is overcome the viscous force and surface tension of liquid and gas explosion is occurred and is atomized, and
Produce violent flash distillation boiling phenomenon；Further, since the thermograde that two-phase natural gas enters in cylinder is big, heat absorption evaporation is fast；Most
Two phase flow natural gas is set to be readily generated homogeneous mixture with air eventually.
At normal temperatures, when pressure change is 0~50MPa, the compressed coefficient β of diesel oil (C10~C21 hydrocarbons) is
(4~6.5) × 10-4(MPa)-1, and because of the compressed coefficient of the compressed coefficient more than weight values oil of light oil, if liquefied natural gas
(CH4) the compressed coefficient be 5 × 10-3(MPa)-1, to 1m3Liquefied natural gas constant entropy be pressurized to 20MPa after, compression volume ratio
For:
Δ V/V=β p (1)
The absorption work(of compressed natural gas is：
W=PV (2)
Because in the case of constant entropy, the absorption work(is completely converted into heat Q, wherein not considering specific heat after liquefied natural gas vaporization
The change of appearance,
W=Q=cm Δs t (3)
Data are brought into above-mentioned formula to obtain：After liquefied natural gas constant entropy is pressurized to 20MPa, temperature rises 7.577K.According to
The saturation temperature of liquefied natural gas, natural gas now is still liquid.
In the structure of the combustion system, because austenitic stainless steel has an excellent cryogenic property, therefore heat-insulated pipe, high-pressure oil pump
Middle contact LNG portion, adiabatic rail use the austenitic stainless steel of 304L/316 materials.Heat-insulated pipe, the cold insulation of adiabatic rail are using bag
Type thermal insulation is covered, its heat-insulating material is using the deep cooling of the successful application improvement polyurethane foam plastics in production practices
(PUH, PUB), but the cold insulation of contact LNG portion is solved using surface spraying ceramics in high-pressure oil pump.
The real-time design control of fuel has numerous studies at present, and the real-time design control of gas-liquid two-phase natural gas can also be joined
Shine into row.
Following table compares for natural gas with the physico-chemical property of gasoline, diesel oil：
The natural gas of table 1 and gasoline, the physico-chemical property of diesel oil
| Physico-chemical property | Natural gas | Gasoline | Diesel oil |
| Molecular formula | C5~C12 hydrocarbons | C10~C21 hydrocarbons | |
| Boiling point/DEG C | -162 | 125.7 | 180~360 |
| Octane number (RON) | 130 | 70~97 | 20~30 |
| Cetane number | It is low | -15 | 40~55 |
| Autoignition temperature/DEG C | 650 | 420 | ≈250 |
| Stoichiometric air-fuel ratio | 16.4 | 14.8~15.1 | 14.3 |
| 50.00 | 43.97 | 42.50~44.40 | |
| 297 | 250 | ||
| 34~37 | 35~47 | ||
| 430 | 679 | 860 | |
| 0.28~0.59 (20 DEG C) | 3~8 |
As can be seen that the H/C ratios of natural gas are big, therefore calorific value is high.It is low temperature two-phase-flow and natural gas octane number into cylinder
Height, so compression ratio can bring up to preferable 15 or so, makes increase compression ratio to the Beneficial Effect and increased machine of the thermal efficiency
Tool loss obtains compromise；The raising of compression ratio equally can also improve cold-start performance.
Liquified natural gas vaporization needs to absorb substantial amounts of heat, and the natural gas after vaporization is five atomic gas, with very high
Specific heat capacity, in 1000K, the specific heat at constant pressure of gaseous natural gas is 2.2 times of air, is CO21.3 times, therefore in order to
Intensification is accomplished by absorbing more heats.Finally so that burning finishing temperature is relatively low, heat transfer loss is few, equally improves thermal effect
Rate.
Because a large amount of H burnings become harmless H2O, liquified natural gas is impure few in addition, contained CH4Purity up to 99% with
On, so CO, CO for being discharged after burning2, the harmful substance such as unburned hydrocarbons and soot, particulate reduces.In NOXDischarge
Aspect, because burning finishing temperature is relatively low, natural gas can completely substitute CO before combustion2EGR effect so that NOXDischarge compared with
It is low.But gaseous mixture flame propagation velocity is slow, after-burning is serious, so as to cause NOXThe pyroreaction time it is long, the raising meeting of compression ratio
Increase maximum combustion temperature, which adds NOXDischarge.But there is relatively low NO than current natural gas engineXRow
Put.
Compared to gasoline and diesel oil, the Cetane number of natural gas is very low, and autoignition temperature is high, therefore it is slower to burn.Identical
During quality, natural gas, because H will consume many many oxygen, so the stoichiometric air-fuel ratio of natural gas is big.Liquified natural gas
Though density is smaller than petrol and diesel oil, volume energy density is more for the twice of compressed natural gas.
The main consideration of adiabatic low-voltage tube is insulation, liquified natural gas is unlikely to vaporization in flow process.It is adiabatic high
Pressure pipe will still consider insulation, separately because having biphase gas and liquid flow in adiabatic high-voltage tube it is also contemplated that the influence of cavitation pitting.If because suppressing
Reeb is passed at bubble or bubble is transported to high pressure position, then bubble can instantaneously reduce, collapse and produce high hydraulic punch
Power is hit, causes noise and vibration, when pressure surge is iteratively operating on adiabatic high-voltage tube wall, can also make its reliability decrease.
Because needing charge oil pressure not change with the change of the operating point of engine, ram type pump is used for this.But plunger idol
Part itself have to also be required adiabatic, it is desirable to which adiabatic Another reason is in low temperature using surface treatment in addition to considering sealing
Under the conditions of, plunger matching parts has black brittleness.Letting out between plunger and plunger bushing is not fee from during compressed liquid natural gas
Leakage, the biphase gas and liquid flow of leakage can all become gas in adiabatic high-pressure pump, gaseous naturally to be reclaimed by canister.Because of list
The pressure fluctuation of cylinder pump is big, and to ensure that heated biphase gas and liquid flow does not flow back, therefore adiabatic high-pressure pump uses multi-cylinder axial columns
Plug fuel pump.The increase of pressure is sprayed, spray can be thicker, jet velocity increases the quantity for power is atomized particle swarm and also increases,
The reduction of Sauter average values.But in view of there is flash distillation boiling phenomenon, liquified natural gas vapourizing temperature gradient is big, and liquified natural gas exists
Temperature is raised and is unlikely to too many during compression, and the pressure of compressed natural gas cylinder is not higher than 20MPa, therefore gas-liquid two-phase flowing pressure
It is set to 20MPa or so.
Adiabatic common rail has to the influence for being incubated and being also contemplated that air pocket.To be installed outside pressure sensor on adiabatic rail.
To know the vaporization situation in adiabatic common rail, for the determination of the two phase flow of real-time design control provides basic data.
Using basic scheme of the invention, can be also optimized from different perspectives in actual implementation process, such as：
Engine is significantly improved using its dynamic property, economy and discharge performance after exhaust gas turbocharge.Consider
Technology maturation, therefore use single-stage exhaust gas bypass turbocharger.
Use VVT to reduce pumping loss, making up average mixing direct-injection system can not reduce the deficiency of pumping loss.
The direct injection gasoline engine of commercialization mostly produces tumble flow using straight air flue, but depends on oil supply system, control
The integrated application of the technology such as system processed and combustion system, has designed and developed larger difficulty.And this combustion system employs spiral gas
Road is coordinating the combustion recess shape of top land.The vortex of generation can make to be sprayed at compression process latter half and still keep very fast
Atomization mixing.This mixed Daqu mode combines the feature of spray-guided and air-flow guiding, and one is that spraying is relativelyed close to
Spark plug and it is not directly protruding at spark plug, so avoids two-phase natural gas adhesional wetting spark plug and cause spark plug to lose
Fire and carbon distribution, two is to make full use of vortex turning effort to accelerate spray evaporation.
In compression process injection, homogeneous mixture is quickly formed.Wish the reason for being sprayed the time as late as possible
It is to reduce because the HC that gap effect is caused is discharged.If the time of mixed Daqu can be tried one's best postponement, in compression process
It is generally pure air near crack between piston and cylinder sleeve.Natural gas should be free of in being pressed into crack in compression process, from
And reduce HC discharges, improve the thermal efficiency.
Ensureing NOXIgnition advance angle is increased in the case of less as far as possible.Engine is set to be operated in detonation edge, so that
To good dynamic property and economy.
Compared with prior art, the beneficial effects of the invention are as follows：
, using gas-liquid two-phase natural gas is used, it is compared with current natural gas machine, diesel engine and gasoline engine for this combustion system
Have the advantage that：
(1) because using the schemes such as in-cylinder direct-jet, high compression ratio, therefore with dynamic property high and economy；
(2) it is gas-liquid two-phase natural gas because what is burnt, therefore CO, CO2, PM discharge it is low, without NMHC；Sprayed using compression process
Penetrate, HC discharges are low；Cylinder temperature is low, NOXDischarge is low；Therefore with extremely low emission performance；
(3) ignition temperature is low, and thermic load is light, therefore part reliability is high in cylinder.
Brief description of the drawings
Fig. 1 is the I. C engine combustion system essential structure schematic diagram of gas-liquid two-phase natural gas.
Fig. 2 is nozzle and spark plug arrangement schematic diagram.
Fig. 3 is combustion chamber schematic diagram.
Specific embodiment
The technology of the present invention content is described in further detail below in conjunction with the accompanying drawings.
As shown in figure 1, the gas-liquid two-phase natural gas I. C engine combustion system of the embodiment of the present invention, its composition is：Into exhausted
The fuel of hot common rail 5 has fluid path and gas circuit two-way：Fluid path passes through adiabatic low-voltage tube 2 and adiabatic pressure by liquid compressed natural gas bottle 1
Power pump 10 is delivered to adiabatic common rail 5；Gas circuit enters adiabatic common rail 5 by gaseous compressed natural gas cylinder 7 by corresponding pipe valve；
2) exported by adiabatic common rail 5 through the mixed fuel of adiabatic common rail 5 and be delivered to cylinder after electric-controlled fuel injector 8；
3) fluid path and gas circuit set corresponding pipe valve and are attached, and corresponding pressure sensor is set in gas circuit；It is interior
Combustion engine electronic control unit 9
Low-voltage tube 2 is connected with the import of adiabatic pressure pump 10；Adiabatic pressure pump 10 pass through adiabatic high-voltage tube after magnetic valve 4 with
Adiabatic common rail 5 is connected；Adiabatic common rail 5 passes through adiabatic high-voltage tube 3 and is connected with the electric-controlled fuel injector 8 on cylinder；Gaseous compressed is natural
Gas bottle 7 passes through adiabatic high-voltage tube and is connected with adiabatic common rail 5；Adiabatic pressure pump 10, magnetic valve 4, adiabatic common rail 5, pressure sensing
Device 6 and electric-controlled fuel injector 8 are electrically connected with internal combustion engine electronic-control unit 9 and control adiabatic pressure pump 10, magnetic valve 4, adiabatic
Common rail 5, pressure sensor 6 and electric-controlled fuel injector 8 are controlled with meeting the optimal combustion condition of internal combustion engine.Internal combustion engine Electronic Control list
The liquified natural gas and gaseous natural gas that 9 pairs, unit enters adiabatic common rail 5 carry out gas-liquid two-phase real-time traffic control.
Spark plug arrangement schematic diagram is shown in Fig. 2.For the requirement of identical ignition voltage, surface gap spark is than the air gap fire
Flower can skip more large electrode gap, so, can form bigger flame kernel in subsequent catching fire, and make fire behaviour
It is obviously improved.Because the combustion system is low-temperature burning, the spark-discharge gap for protruding relatively deep into combustion chamber is beneficial to gaseous mixture
Catch fire.Therefore use the less surface gap type spark plug of calorific value.
This combustion system uses ω combustion chambers with the level as shown in Figure 3.Make intake swirl near
It is maintained in top land pit, while being also to coordinate jet rose.The purpose for having step is to be flowed and inverse crowded using crowded
Stream promotes two-phase natural gas and air mixing and burning, to improving burning and discharging highly beneficial.
Claims (2)
1. it is the automotive fuel carrying method of fuel to use gas-liquid two-phase natural gas, it is characterised in that liquid compression is natural
Source of the gas and gaseous state compressed natural gas source are delivered to an adiabatic common rail by thermal insulation, automatically controlled through one after completing mixing in adiabatic common rail
Fuel injector is delivered to cylinder；Its specific course of conveying and condition of work are：
1) fuel into adiabatic common rail (5) has fluid path and gas circuit two-way：Fluid path is by liquid compressed natural gas bottle (1) by thermal insulation
Low-voltage tube (2) and adiabatic pressure pump (10) are delivered to adiabatic common rail (5)；Gas circuit is by gaseous compressed natural gas cylinder (7) by phase
Pipe valve is answered to enter adiabatic common rail (5)；
2) it is delivered to cylinder after electric-controlled fuel injector (8) by the outlet of adiabatic common rail through the mixed fuel of adiabatic common rail；
3) fluid path and gas circuit set corresponding pipe valve and are attached, and corresponding pressure sensor is set in gas circuit；Internal combustion engine
Electronic control unit (9)；
Adiabatic low-voltage tube (2) is connected with adiabatic pressure pump (10) import；Adiabatic pressure pump (10) is by adiabatic high-voltage tube through electromagnetism
Valve (4) is connected with adiabatic common rail afterwards；Adiabatic common rail passes through adiabatic high-voltage tube and is connected with the electric-controlled fuel injector on cylinder；Gaseous compressed
Natural gas cylinder (7) is connected by adiabatic high-voltage tube with adiabatic common rail；Adiabatic pressure pump (10), magnetic valve (4), adiabatic common rail
(5), pressure sensor (6) and electric-controlled fuel injector (8) are electrically connected with internal combustion engine electronic-control unit (9) and control adiabatic pressure
Pump (10), magnetic valve (4), adiabatic common rail (5), pressure sensor (6) and electric-controlled fuel injector (8) are meeting the optimal combustion of internal combustion engine
Burning condition is controlled.
2. automotive fuel carrying method according to claim 1, it is characterised in that internal combustion engine electronic-control unit (9) is right
Liquified natural gas and gaseous natural gas into adiabatic common rail (5) carry out gas-liquid two-phase real-time traffic control.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510153562.4A CN104806382B (en) | 2015-04-02 | 2015-04-02 | It is the automotive fuel carrying method of fuel to use gas-liquid two-phase natural gas |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510153562.4A CN104806382B (en) | 2015-04-02 | 2015-04-02 | It is the automotive fuel carrying method of fuel to use gas-liquid two-phase natural gas |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104806382A CN104806382A (en) | 2015-07-29 |
| CN104806382B true CN104806382B (en) | 2017-06-13 |
Family
ID=53691517
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510153562.4A Expired - Fee Related CN104806382B (en) | 2015-04-02 | 2015-04-02 | It is the automotive fuel carrying method of fuel to use gas-liquid two-phase natural gas |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104806382B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114810447B (en) * | 2022-04-11 | 2023-06-13 | 哈尔滨工程大学 | Device and method for testing gas-liquid two-phase ratio in transient injection process of ammonia fuel with phase change |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004150333A (en) * | 2002-10-30 | 2004-05-27 | Aisan Ind Co Ltd | Fuel supply device of liquefied gas internal combustion engine |
| CN103069137A (en) * | 2010-06-07 | 2013-04-24 | 阿尔塞特知识产权公司 | Bi-fuel engine with variable air fuel ratio |
| CN103422999A (en) * | 2012-05-17 | 2013-12-04 | 卡特彼勒公司 | Direct injection gas engine and method |
| CN103573452A (en) * | 2012-08-08 | 2014-02-12 | 卡特彼勒公司 | Dual fuel engine and evaporated natural gas system |
| CN103958860A (en) * | 2011-11-30 | 2014-07-30 | 爱三工业株式会社 | Fuel supply control apparatus for bi-fuel internal combustion engine, and method of switching fuel in bi-fuel internal combustion engine |
-
2015
- 2015-04-02 CN CN201510153562.4A patent/CN104806382B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004150333A (en) * | 2002-10-30 | 2004-05-27 | Aisan Ind Co Ltd | Fuel supply device of liquefied gas internal combustion engine |
| CN103069137A (en) * | 2010-06-07 | 2013-04-24 | 阿尔塞特知识产权公司 | Bi-fuel engine with variable air fuel ratio |
| CN103958860A (en) * | 2011-11-30 | 2014-07-30 | 爱三工业株式会社 | Fuel supply control apparatus for bi-fuel internal combustion engine, and method of switching fuel in bi-fuel internal combustion engine |
| CN103422999A (en) * | 2012-05-17 | 2013-12-04 | 卡特彼勒公司 | Direct injection gas engine and method |
| CN103573452A (en) * | 2012-08-08 | 2014-02-12 | 卡特彼勒公司 | Dual fuel engine and evaporated natural gas system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104806382A (en) | 2015-07-29 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP6907157B2 (en) | Internal combustion engine that is internally cooled and its method | |
| CN101571069B (en) | Dual-fuel combustion system for internal combustion engines | |
| US20130104850A1 (en) | Multi-fuel pre-mixed combustion system of internal combustion engine | |
| KR20150100659A (en) | Internally cooled exhaust gas recirculation system for internal combustion engine and method thereof | |
| CN109098835A (en) | A kind of natural gas engine burning tissues method with high pressure direct injection in precombustion chamber low pressure gas supply and cylinder | |
| EP0914550A1 (en) | Internal combustion engine | |
| US20140299105A1 (en) | Methods for Low Temperature Combustion and Engines Using the Same | |
| US20190170077A1 (en) | Combustion control method and combustion control system with variable excess air coefficient for gasoline engine | |
| CN105673281B (en) | In a kind of gas/liquid double fuel cylinder/cylinder outer pair of injection apparatus and control method | |
| CN107939517B (en) | Jet ignition-based engine ultrahigh compression ratio combustion control device and method | |
| CN111219269A (en) | Partial premixing combustion system based on liquid hydrogen fuel piston engine and engine | |
| CN204677293U (en) | A kind of direct-injection LNG-diesel dual-fuel system | |
| CN104806382B (en) | It is the automotive fuel carrying method of fuel to use gas-liquid two-phase natural gas | |
| CN110821638B (en) | Ignition chamber type engine with high-energy ignition fuel and control method thereof | |
| CN1272539C (en) | Dimethyl ether engine efficient, ultra-low emission combustion system | |
| CN116044583A (en) | Diesel and ammonia dual-fuel engine combustion system and combustion method based on composite EGR loop | |
| CN110821664A (en) | Dual-fuel ignition chamber type four-stroke engine and combustion control method | |
| CN110821658A (en) | Single-fuel ignition chamber type four-stroke engine based on reformed gas and combustion control method | |
| CN103075264A (en) | Direct-injection compression-ignition engine | |
| CN110821641A (en) | Ignition chamber type engine with high-energy ignition fuel and control method thereof | |
| CN110821643B (en) | Ignition chamber type engine with high-energy ignition fuel | |
| CN110821652A (en) | Dual-fuel ignition chamber type two-stroke engine based on reformed gas and combustion control method | |
| CN110821639B (en) | Multi-mode engine with high-energy ignition fuel and control method thereof | |
| CN110821654B (en) | Dual-fuel spark plug type four-stroke engine based on reformed gas and combustion control method | |
| CN201354689Y (en) | Small-sized energy-saving petrol motor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| EXSB | Decision made by sipo to initiate substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20170613 Termination date: 20200402 |