CN112632867B - Design method and control method for minimum compression ratio of diesel engine - Google Patents
Design method and control method for minimum compression ratio of diesel engine Download PDFInfo
- Publication number
- CN112632867B CN112632867B CN202011517913.2A CN202011517913A CN112632867B CN 112632867 B CN112632867 B CN 112632867B CN 202011517913 A CN202011517913 A CN 202011517913A CN 112632867 B CN112632867 B CN 112632867B
- Authority
- CN
- China
- Prior art keywords
- diesel engine
- air
- temperature
- res
- compression ratio
- 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
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
- G06F30/28—Design optimisation, verification or simulation using fluid dynamics, e.g. using Navier-Stokes equations or computational fluid dynamics [CFD]
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D15/00—Varying compression ratio
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2113/00—Details relating to the application field
- G06F2113/08—Fluids
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/08—Thermal analysis or thermal optimisation
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Theoretical Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Computer Hardware Design (AREA)
- Geometry (AREA)
- Mathematical Optimization (AREA)
- Mathematical Physics (AREA)
- Pure & Applied Mathematics (AREA)
- Fluid Mechanics (AREA)
- Evolutionary Computation (AREA)
- Mathematical Analysis (AREA)
- Computing Systems (AREA)
- Algebra (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
The invention discloses a design method and a control method for the minimum compression ratio of a diesel engine, wherein the air leakage of the diesel engine is larger in the cold starting process due to the reasons of low rotating speed, large cold-state clearance of parts and the like; in addition, the temperature of the diesel engine body and the cooling liquid is lower in a low-temperature environment, and the heat dissipation capacity of the air in the cylinder is larger in the cold starting process. Therefore, T1-min is calculated according to an adiabatic compression theoretical formula, and the result error is large; the invention researches the difference between the actual value and the theoretical value on the diesel engine, obtains the relational expression between the actual compression final state in the cylinder along with the start-injection rotating speed, the compression ratio and the engine air inlet state in the cold starting process of the diesel engine through data fitting, and can obtain the minimum compression ratio of the diesel engine required under different environmental temperatures when starting without preheating and idling stably without preheating due to the consideration of the energy loss coefficient after air leakage and heat dissipation, so that the diesel engine using the design method has low-temperature adaptability and the cold starting performance of the diesel engine is improved.
Description
Technical Field
The invention belongs to the technical field of diesel engine design and control, and particularly relates to a design method and a control method for a minimum compression ratio of a diesel engine.
Background
Due to the characteristics of high thermal efficiency, good reliability and the like, the diesel engine is widely applied in the fields of agriculture, industry, transportation, national defense equipment and the like. The design of the compression ratio of the diesel engine has great influence on the economy, the dynamic property, the starting property, the reliability and the emission property, so the selection of the compression ratio of the diesel engine is a key problem which must be solved firstly in the design and the manufacture of the diesel engine.
There are minimum and maximum compression ratios for any diesel engine. Generally, the maximum pressure in the cylinder of the diesel engine increases sharply after increasing the compression ratio, and the mechanical load on the diesel engine increases. Therefore, the maximum value of the compression ratio is determined by the mechanical load limit and reliability of the diesel engine. The minimum value of the compression ratio needs to ensure that the final compression temperature in the cylinder of the diesel engine is higher than the critical ignition temperature of the diesel spray so as to ensure that the diesel spray can be normally spontaneously combusted to release heat and push the piston to do work. The rotation speed is low, the air leakage is large, the heat dissipation is high in the starting process of the diesel engine, and the final compression temperature in the cylinder is lower than that in the normal working process at the high rotation speed in the starting process. Therefore, the minimum value of the compression ratio is determined by the startability limit of the diesel engine. The basic characteristics of climate and terrain in China are that China has broad breadth, large temperature difference between south and north and large difference between east and west altitudes. The lowest temperature of the north juncture river in China can reach-52.3 ℃ in winter. When the existing diesel engine is used, in a high-altitude and extremely-low-temperature area, the temperature in the cylinder at the moment when the compression stroke is ended cannot be guaranteed to be higher than the critical temperature of ignition of diesel spray, so that the diesel spray is ignited, and the diesel spray cannot be started normally.
In summary, the starting performance of the existing diesel engine under the low-temperature environment is poor, and even the diesel engine cannot be started normally. In order to improve the cold start performance of the diesel engine in a low temperature environment, a minimum compression ratio of the diesel engine needs to be designed or controlled.
Disclosure of Invention
In view of this, the present invention provides a design method and a control method for a minimum compression ratio of a diesel engine, which can improve the cold starting performance of the diesel engine in a low temperature environment and improve the environmental adaptability of the diesel engine.
A design method for minimum compression ratio of diesel engine includes such steps as designing the minimum compression ratio of diesel engine, and designing the minimum compression ratio of diesel engine according to the lowest temp T of diesel engine at start-up speed without preheating and air admission 1-min Relation to compression ratio ε:
determining the minimum compression ratio of the diesel engine at the start-injection rotation speed; wherein κ is the adiabatic index; f 1-3.68 n -0.5 N is the diesel engine speed; p in Is at atmospheric pressure;
then according to the lowest temperature T after the inlet air is preheated during the period that the rotating speed of the diesel engine rises in-min Relation with the rotation speed and the compression ratio epsilon:
determining the minimum compression ratio of the diesel engine under the condition of increasing the rotating speed; in the formula, LHV represents the lower heating value LHV, c of the fuel v The specific heat is constant volume and specific heat of air;
and selecting the larger value of the minimum compression ratio under the start-injection rotation speed and the minimum compression ratio under the rotation speed rise as the final compression ratio of the diesel engine.
A minimum compression ratio control method for a diesel engine comprises the steps of controlling the diesel engine according to the minimum temperature T after no preheating air inlet at the start-up rotation speed of the diesel engine 1-min Relation to compression ratio ε:
determining the minimum compression ratio of the diesel engine at the start-injection rotation speed; wherein κ is the adiabatic index; f 1-3.68 n -0.5 N is the diesel engine speed; p in Is atmospheric pressure;
then according to the lowest temperature T after preheating the inlet air during the period of increasing the rotating speed of the diesel engine in-min Relation with rotation speed and compression ratio epsilon:
determining the minimum compression ratio of the diesel engine under the condition of increasing the rotating speed; in the formula, LHV represents fuel lower heating value LHV, c v The specific heat is constant volume and specific heat of air;
and selecting the larger value of the minimum compression ratio under the condition of starting injection rotation speed and the minimum compression ratio under the condition of rising rotation speed as the final compression ratio of the diesel engine.
The invention has the following beneficial effects:
due to the reasons of low rotating speed, large cold-state clearance of parts and the like, the air leakage of the diesel engine is large in the cold starting process, and the proportion of the air leakage in the total air input of the engine can reach 17%. In addition, the temperature of the diesel engine body and the cooling liquid is lower in a low-temperature environment, and the heat dissipation capacity of the air in the cylinder is larger in the cold starting process. Therefore, the result error is larger when T1-min is calculated according to the adiabatic compression theoretical formula; according to the method, the difference between an actual value and a theoretical value is researched on the diesel engine, a relational expression between an actual compression final state (P2; T2, rho 2) in a cylinder along with a start-injection rotating speed n, a compression ratio and an engine air inlet state (T1, P1) in the cold starting process of the diesel engine is obtained through data fitting, and due to the fact that energy loss coefficients after air leakage and heat dissipation are considered, the minimum compression ratio of the diesel engine required under different environment temperatures during non-preheating starting and non-preheating stable idling can be obtained, so that the diesel engine using the design method has low-temperature adaptability, and the cold starting performance of the diesel engine is improved.
Drawings
FIG. 1 is a schematic diagram of a non-preheating air intake process of a diesel engine;
FIG. 2 is a non-preheat minimum inlet air temperature design flow;
FIG. 3 images of diesel spray fires at different temperatures;
FIG. 4 is a fitting relationship between critical ignition temperature and critical ignition density;
FIG. 5(a) is a graph showing T at 200rpm for different epsilon in-min-start (ii) a change;
FIG. 5(b) is the variation of the lowest intake air temperature of the engine with the rotation speed under different epsilon of the jet rotation speed of 200rpm-800 rpm.
Detailed Description
The invention is described in detail below by way of example with reference to the accompanying drawings.
In view of the above, the invention provides a design method and a control method for a minimum compression ratio of a diesel engine, which can improve the cold starting performance of the diesel engine in a low-temperature environment, improve the defects of the existing design method, and are beneficial to improving the environmental adaptability of the diesel engine.
The design flow chart is shown in fig. 2, and the specific design steps are as follows:
the method comprises the following steps: determining the critical ignition temperature (T) of a diesel spray c ) And critical ignition density (p) c ) The relationship between (A) and (B) is as follows:
step two: determining the actual compression stroke calculation formula in the starting process of the diesel engine according to the temperature T of the air inlet state of the diesel engine 1 And pressure P 1 Compression ratio epsilon, gas constant R g Calculating the temperature T of the actual compression end state from the adiabatic index kappa and the diesel engine speed n 2 And density ρ 2 ；
f＝1-3.68*n -0.5
Step three: taking the critical ignition condition as the critical state T of the compression end in the cylinder of the diesel engine 2 ＝T c ,ρ 2 ＝ρ c Calculating the lowest compression initial point temperature T of the diesel engine by combining the formulas in the step one and the step two 1-min ；
Step four: without considering residual waste gas, the lowest temperature T after no preheating air inlet under the starting speed of the diesel engine in-min-start Equal to the lowest compression onset temperature T 1-min ；
T in-min-start ＝T 1-min
Step five: calculating a minimum post-intake warm-up temperature T during an increase in engine speed, taking into account residual exhaust gases in-min-ramp ；
Assuming that the Ramp diesel in-cylinder circulation is an Otto cycle in the rising period of the engine speed, and assuming that the compression starting point state after the residual exhaust gas and the fresh air are mixed is T mixed And ρ mixed . Extending the expansion line of the Otto cycle until the expansion line intersects with the intake pressure line, which is equivalent to the expansion of the gas in the cylinder to the atmospheric pressure P in 1bar, LHV and air according to the low heat value of fuelSpecific heat of constant volume c v Calculating the thermal state T of the residual waste gas res And ρ res ：
The constant volume pressure ratio of the OTO circulation is as follows:
the equivalent expansion ratio of the octupole cycle is:
the thermal state of the residual exhaust gas is calculated as:
calculating Single Cylinder Displacement (V) h ) Fresh air mass (m) air-cycle ) And combustion chamber volume (V) c ) Mass (m) of residual exhaust gas res ) And the total mass (m) after mixing air-cycle +m res )；
m res ＝V c ·ρ res
m air-cycle ＝V h ·ρ in
m air-cycle +m res ＝(V h +V c )·ρ mixed
Assuming a volume of V h (Single-cylinder displacement) and temperature of T in Of fresh air and volume V c (volume of combustion chamber) temperature T res The residual waste gas constant pressure adiabatic mixing, the total internal energy before and after mixing is unchanged, then:
m res ·c V-res ·T res +m air-cycle ·c V-air ·T in
＝(m air-cycle +m res )·c V-mixed ·T mixed
assuming constant specific heat capacity (c) of residual exhaust gas V-res ) Fresh air constant-volume specific heat (c) V-air ) And the specific heat (c) of the mixed gas with constant volume V-mixed ) The compression initial point temperature T of the mixed residual waste gas and fresh air can be obtained after the same mixed Comprises the following steps:
when T is mixed Is equal to T obtained in step three 1-min Temperature (T) of fresh air in ) Is the lowest pre-heated intake air temperature (T) during the diesel engine Ramp in-min-ramp ) And then:
therefore, the lowest intake air temperature T of the diesel engine in-min Is a piecewise function of engine speed: no residual waste gas action at the start-spraying rotating speed, T in-min ＝T in-min-start ＝T 1-min (ii) a In the process of diesel engine Ramp, T in-min ＝T in-min-ramp 。
At this point, basic parameters of the diesel engine are input, and T under different epsilon during starting can be obtained in-min-start Curve of variation with rotational speed, and T at different epsilon in-min A variation curve with rotational speed; in practical application, the relationship between the temperature and the compression ratio obtained by the invention can be applied to the design and control of a diesel engine; during design, according to the temperature of the use environment, based on the relation, the required minimum compression ratio of the diesel engine under the environment can be obtained; when the diesel engine is used, the diesel engine can be obtained according to the environmental temperature and based on the relationAnd finally controlling the diesel engine to the minimum compression ratio of the operation of the oil engine.
Example 1:
firstly, based on the diesel spray test, the critical ignition temperature of the diesel spray is obtained under the premise of constant density. As shown in FIG. 3, the critical ignition temperature was 720K at this density.
Then, the density conditions were changed to obtain critical ignition temperatures at different densities, and a fitting relation in the form of a cubic polynomial of the critical ignition temperature with respect to the critical ignition density was obtained, as shown in fig. 4.
Finally, according to the calculation formulas in the third step and the fifth step, when the starting injection speed of the engine is 200rpm (one speed is taken as an example in the embodiment), the Ramp speed is 200rpm to 800rpm, the compression ratio is 13.8, the displacement is 2L, the charging efficiency is 0.8, and the calorific value of fuel is 43kJ/kg, the T under different epsilon is respectively calculated in-min-start And T at different εs in-min The curve with the rotation speed is shown in fig. 5. As can be seen from FIG. 5(a), T increases with ε in-min-start And gradually decreases. When T is air ≥T in-min-start In time, the diesel engine can be successfully started without intake air auxiliary preheating measures. When T is air ≤T in-min-start In the meantime, the diesel engine needs an intake air auxiliary preheating measure to be successfully started at the start-injection speed of 200 rpm. E.g. 13.8,. epsilon.T air When the pressure is less than or equal to 271.05K, the diesel engine needs air inlet auxiliary preheating to be successfully started at the start-up rotation speed of 200 rpm. As can be seen from fig. 5(b), the lowest intake air temperature of the diesel engine during Ramp is lowered due to the heating effect of the residual exhaust gas. Epsilon is 13.8, and the air inlet temperature 238K can be stably idled at the idling speed of 800 rpm.
From the above examples, it can be seen that the design method and the control method for the minimum compression ratio of the diesel engine with low-temperature adaptability provided by the invention can obtain the minimum compression ratio of the diesel engine required under different environmental temperatures during non-preheating starting and non-preheating stable idling, so that the diesel engine applying the design method has low-temperature adaptability, and the cold starting performance of the diesel engine is improved.
In summary, the above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (4)
1. A design method for minimum compression ratio of a diesel engine is characterized in that: when the minimum compression ratio of the diesel engine is designed, the minimum temperature T after no preheating air inlet is carried out at the starting rotation speed of the diesel engine 1-min Relation to compression ratio ε:
determining the minimum compression ratio of the diesel engine at the start-injection rotation speed; wherein κ is the adiabatic index; f 1-3.68 n -0.5 N is the diesel engine speed; p in Is at atmospheric pressure;
without considering residual waste gas, the lowest temperature T after no preheating air inlet under the starting speed of the diesel engine in-min-start Equal to the lowest compression onset temperature T 1-min ；
T in-min-start ＝T 1-mmin
Calculating a minimum post-intake warm-up temperature T during an increase in engine speed, taking into account residual exhaust gases in-min-ramp ；
Assuming that the Ramp diesel in-cylinder circulation is an Otto cycle in the rising period of the engine speed, and assuming that the compression starting point state after the residual exhaust gas and the fresh air are mixed is T mixed And ρ mixed (ii) a Extending the expansion line of the Otto cycle until the expansion line intersects with the intake pressure line, which is equivalent to the expansion of the gas in the cylinder to the atmospheric pressure P in According to the LHV of the low calorific value of the fuel and the specific heat c of the air with constant volume v Calculating the thermal state T of the residual waste gas res And ρ res ：
The constant volume pressure ratio of the OTO circulation is as follows:
the equivalent expansion ratio of the octupole cycle is:
the thermal state of the residual exhaust gas is calculated as:
calculating single-cylinder displacement V h Fresh air mass m air-cycle And combustion chamber volume V c Mass m of residual exhaust gas res And the total mass m after mixing air-cycle +m res ；
m res ＝V c ·ρ res
m air-cycle ＝V h ·ρ in
m air-cycle +m res ＝(V h +V c )·ρ mixed
Assuming a volume V h Single cylinder displacement and temperature of T in Fresh air and volume of V c Temperature of T res The residual waste gas constant pressure adiabatic mixing, the total internal energy before and after mixing is unchanged, then:
m res ·c V-res ·T res +m air-cycle ·c V-air ·T in
＝(m air-cycle +m res )·c V-mixed ·T mixed
assuming constant volume specific heat c of residual waste gas V-res Fresh air constant volume specific heat c V-air And the constant specific heat c of the mixed gas V-mixed Equal to obtain residual waste gas andcompression start temperature T after mixing of fresh air mixed Comprises the following steps:
when T is mixed Is equal to T 1-min Time, temperature T of fresh air in Is the lowest warmed-up intake air temperature T during the diesel engine Ramp in-min-ramp And then:
therefore, the lowest intake air temperature T of the diesel engine in-min Is a piecewise function of engine speed: no residual waste gas action at the start-spraying rotating speed, T in-min ＝T in-min-start ＝T 1-min (ii) a In the process of diesel engine Ramp, T in-min ＝T in-min-ramp ；
According to the lowest temperature T after the intake air is preheated during the period of the rise of the rotating speed of the diesel engine in-min Determining the minimum compression ratio of the diesel engine under the condition of increasing the rotating speed by a relational expression of the rotating speed and the compression ratio epsilon; in the formula, LHV represents fuel lower heating value LHV, c v The specific heat is constant volume and specific heat of air;
and selecting the larger value of the minimum compression ratio under the start-injection rotation speed and the minimum compression ratio under the rotation speed rise as the final compression ratio of the diesel engine.
2. A method for controlling the minimum compression ratio of a diesel engine is characterized in that: when the diesel engine is controlled, according to the minimum temperature T after no preheating air inlet at the starting speed of the diesel engine 1-min Relation to compression ratio ε:
determining the minimum compression ratio of the diesel engine at the start-injection rotation speed; wherein κ is thermal insulationAn index; f 1-3.68 n -0.5 N is the diesel engine speed; p is in Is at atmospheric pressure;
the lowest temperature T after non-preheating air inlet under the starting speed of the diesel engine without considering the residual waste gas in-min-start Equal to the lowest compression onset temperature T 1-min ；
T in-min-start ＝T 1-min
Calculating a minimum post-intake warm-up temperature T during an increase in engine speed, taking into account residual exhaust gases in-min-ramp ；
Assuming that the Ramp diesel in-cylinder circulation is an Otto cycle in the rising period of the engine speed, and assuming that the compression starting point state after the residual exhaust gas and the fresh air are mixed is T mixed And ρ mixed (ii) a The expansion line of the Otto cycle is prolonged until the expansion line intersects with the intake pressure line, which is equivalent to the expansion of the gas in the cylinder to the atmospheric pressure P in According to the lower heating value LHV of the fuel and the constant volume specific heat c of the air v Calculating the thermal state T of the residual waste gas res And ρ res ：
The constant volume pressure ratio of the OTO circulation is as follows:
the equivalent expansion ratio of the octupole cycle is:
the thermal state of the residual exhaust gas is calculated as:
calculation sheetCylinder displacement V h Fresh air mass m air-cycle And combustion chamber volume V c Mass m of residual exhaust gas res And the total mass m after mixing air-cycle +m res ；
m res ＝V c ·ρ res
m air-cycle ＝V h ·ρ in
m air-cycle +m res ＝(V h +V c )·ρ mixed
Assuming a volume of V h Single cylinder displacement and temperature of T in Fresh air and volume of V c Temperature of T res The residual waste gas constant pressure adiabatic mixing, the total internal energy before and after mixing is unchanged, then:
m res ·c V-res ·T res +m air-cycle ·c V-air ·T in
＝(m air-cycle +m res )·c V-mixed ·T mixed
assuming constant volume specific heat c of residual waste gas V-res Fresh air constant volume specific heat c V-air And the constant specific heat c of the mixed gas V-mixed The same, the compression initial point temperature T after the residual waste gas and the fresh air are mixed can be obtained mixed Comprises the following steps:
when T is mixed Is equal to T 1-min Time, temperature T of fresh air in Is the lowest warmed-up intake air temperature T during the diesel engine Ramp in-min-ramp Then:
therefore, the lowest intake air temperature T of the diesel engine in-min Is a piecewise function of engine speed: no residual waste gas effect exists under the starting jet rotating speed,T in-min ＝T in-min-start ＝T 1-min (ii) a In the process of diesel engine Ramp, T in-min ＝T in-min-ramp ；
According to the lowest temperature T after the intake air is preheated during the period of the rise of the rotating speed of the diesel engine in-min Determining the minimum compression ratio of the diesel engine under the condition of increasing the rotating speed by a relational expression of the rotating speed and the compression ratio epsilon; in the formula, LHV represents the lower heating value LHV, c of the fuel v The specific heat is constant volume and specific heat of air;
and selecting the larger value of the minimum compression ratio under the condition of starting injection rotation speed and the minimum compression ratio under the condition of rising rotation speed as the final compression ratio of the diesel engine.
3. A method for controlling a minimum compression ratio of a diesel engine as set forth in claim 2, wherein: critical ignition temperature T of diesel spray c And critical ignition density ρ c The relationship between (A) and (B) is as follows:
4. a method for controlling a minimum compression ratio of a diesel engine as set forth in claim 3, wherein: temperature T according to air inlet state of diesel engine 1 And pressure P 1 Compression ratio epsilon, gas constant R g Calculating the temperature T of the actual compression end state from the adiabatic index kappa and the diesel engine speed n 2 And density ρ 2 ；
f＝1-3.68*n -0.5 。
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011517913.2A CN112632867B (en) | 2020-12-21 | 2020-12-21 | Design method and control method for minimum compression ratio of diesel engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011517913.2A CN112632867B (en) | 2020-12-21 | 2020-12-21 | Design method and control method for minimum compression ratio of diesel engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112632867A CN112632867A (en) | 2021-04-09 |
| CN112632867B true CN112632867B (en) | 2022-08-23 |
Family
ID=75320277
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011517913.2A Active CN112632867B (en) | 2020-12-21 | 2020-12-21 | Design method and control method for minimum compression ratio of diesel engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112632867B (en) |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BR112015000026A2 (en) * | 2012-07-02 | 2017-06-27 | Pinnacle Engines Inc | variable compression ratio diesel engine |
| CN106285917B (en) * | 2016-08-05 | 2018-10-26 | 同济大学 | A kind of diesel engine starting auxiliary system and method suitable for high altitude localities |
-
2020
- 2020-12-21 CN CN202011517913.2A patent/CN112632867B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN112632867A (en) | 2021-04-09 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US10378436B2 (en) | Internally cooled high compression lean-burning internal combustion engine | |
| US6923167B2 (en) | Controlling and operating homogeneous charge compression ignition (HCCI) engines | |
| JP2004519583A (en) | Operation method of supercritical water injection type internal combustion engine | |
| US10961943B1 (en) | Method and system for controlling combustion of natural gas engine | |
| CN112377319B (en) | Oil injection pressure control method for improving cold starting performance of diesel engine | |
| US4123997A (en) | Motor adapted for fuel comprising a product different from mineral oil product | |
| CN112594076B (en) | Diesel engine minimum intake preheating power design method with low-temperature adaptability | |
| Siegla et al. | Exploratory study of the low-heat-rejection diesel for passenger-car application | |
| CN112632867B (en) | Design method and control method for minimum compression ratio of diesel engine | |
| Ling et al. | One-dimensional simulation using port water injection for a spark ignition engine | |
| CN112594075B (en) | Method for designing minimum intake preheating power of diesel engine with plateau adaptability | |
| Rehman et al. | Influence of coolant temperature on the performance of a four stroke spark ignition engine employing a dual circuit cooling system | |
| Leman et al. | Engine modelling of a single cylinder diesel engine fuelled by diesel-methanol blend | |
| CN113898487B (en) | Cold start method of high-power Miller cycle diesel engine | |
| CN108026871B (en) | Control device for engine system | |
| WO2024139139A1 (en) | Engine, engine control method, and vehicle | |
| CN218991739U (en) | Engine and vehicle | |
| US11591953B2 (en) | Method for controlling hydrogen combustion in a hydrogen internal combusting engine | |
| WO2024109963A2 (en) | Temperature-controllable glow plug assisted compression-ignition-type methanol engine and control method therefor | |
| CN112576393B (en) | Diesel engine starting oil quantity slope control method based on instantaneous rotating speed and storage medium | |
| Dare et al. | Development of four-zone segmented transitional model for reciprocating internal combustion engine analysis using gasoline | |
| Allen et al. | Heat balanced IC engine transition studies | |
| Lighty et al. | Engine performance with gasoline and alcohol | |
| Saito et al. | Intercooling effects of methanol on turbocharged diesel engine performance and exhaust emissions | |
| Nitnaware et al. | Design development and analysis of exhaust gas recirculation system for cng fuelled si 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 | ||
| CB03 | Change of inventor or designer information |
Inventor after: Shi Zhongjie Inventor after: Li Yijie Inventor after: Peng Jing Inventor before: Peng Jing Inventor before: Li Yijie Inventor before: Shi Zhongjie |
|
| CB03 | Change of inventor or designer information | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |