WO2015144704A1 - Model-based pilot control for controlling the combustion rate - Google Patents
Model-based pilot control for controlling the combustion rate Download PDFInfo
- Publication number
- WO2015144704A1 WO2015144704A1 PCT/EP2015/056256 EP2015056256W WO2015144704A1 WO 2015144704 A1 WO2015144704 A1 WO 2015144704A1 EP 2015056256 W EP2015056256 W EP 2015056256W WO 2015144704 A1 WO2015144704 A1 WO 2015144704A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- injection
- combustion
- model
- pressure
- control
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/40—Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
- F02D41/402—Multiple injections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D35/00—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for
- F02D35/02—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions
- F02D35/023—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions by determining the cylinder pressure
- F02D35/024—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions by determining the cylinder pressure using an estimation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1401—Introducing closed-loop corrections characterised by the control or regulation method
- F02D41/1406—Introducing closed-loop corrections characterised by the control or regulation method with use of a optimisation method, e.g. iteration
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1401—Introducing closed-loop corrections characterised by the control or regulation method
- F02D2041/141—Introducing closed-loop corrections characterised by the control or regulation method using a feed-forward control element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1401—Introducing closed-loop corrections characterised by the control or regulation method
- F02D2041/1412—Introducing closed-loop corrections characterised by the control or regulation method using a predictive controller
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1401—Introducing closed-loop corrections characterised by the control or regulation method
- F02D2041/1433—Introducing closed-loop corrections characterised by the control or regulation method using a model or simulation of the system
-
- 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
- Y02T10/40—Engine management systems
Definitions
- the invention relates to a method for operating an internal combustion engine having a real-time capable pilot control of an injection profile and to a control device of an internal combustion engine having a real-time-based pilot control of an injection profile.
- the precontrol is implemented as a model-based pilot control algorithm for diesel engine combustion rate control by intermittent multiple injection (also sometimes referred to as digital multiple injection) in a control unit.
- intermittent multiple injection also sometimes referred to as digital multiple injection
- the diesel engine combustion can be optimized by implementing a predetermined cylinder pressure curve or a given combustion rate over the entire work cycle in the form of a combustion rate control with regard to pollutant emissions, fuel consumption and noise behavior.
- the combustion rate control has hitherto only been realized by a controller in the form of an iteratively learning feedback controller (ILR) on the basis of a previously completely recorded cylinder pressure curve.
- ILR iteratively learning feedback controller
- a predetermined combustion rate can be adjusted by means of digital multiple injection as a manipulated variable in a stationary engine operation.
- the controller does not work fast enough that this existing approach for real-time use can also be used, for example, in transient engine operation.
- the invention thus relates to a feedforward control or a method for pilot control of the injection profile for an internal combustion engine in order to be able to realize defined target combustion rates.
- a feedforward control is in addition to a regulation in order to accelerate the regulation in terms of their convergence behavior, which is the motivation for the development of a feedforward control is given.
- the regulation here the combustion rate control, is therefore not a mandatory part of the invention.
- a model-based method for the holistic prediction of a digital fuel injection profile under operating point-dependent predefinition of a nominal combustion curve over the entire operating cycle of an internal combustion engine is proposed. This results in preferably two basic fields of application: i. Use for real-time capable, model-based pilot control of the injection profile to optimize subsequent combustion rate control by digital multiple injection even in transient engine operation and ii. Design or offline calibration of a fuel injection strategy for map-based feedforward control of the injection profile to realize the
- the target combustion rate can be predetermined, for example on the basis of the specification required by the driver, for example due to gas and / or brake confirmation via a control unit, in particular via an engine control unit.
- the control unit may, for example, have the desired combustion rate stored or ascertain on the basis of the driver's requirement and then allocate the pilot control.
- an injection profile comprising the number, times, quantities and rail pressure of the injections is calculated as a function of the current engine operating point, thus enabling real-time use of the principle of combustion rate control even in transient engine operation.
- a possible example of an applicable combustion rate control in the context of the disclosure of this invention reference is made to the combustion rate control, as is apparent from the already mentioned DE 10 2007 012 604 A1. whose content is hereby made the disclosure content of the present application.
- the feedforward control offers the possibility of accelerating the control process of the preferably ILR or other controller, or of completely bypassing it or avoiding it in particular in transient engine operation.
- the acceleration of the adjustment process is achieved in that the precontrol calculates an injection profile in advance, which at least approximately results in the current combustion rate corresponding to a desired combustion rate.
- the combustion rate control using the ILR alone was not yet possible in transient engine operation. Due to the pilot control, the combustion rate control is now also possible in transient engine operation and thus for real vehicle use. In particular, the prediction of an entire injection profile is made possible starting from a predetermined target combustion rate.
- the method with the precontrol transfers the injection profile to the combustion rate control, wherein in the transient operating range, the combustion rate control operates on a real-time basis.
- the feedforward control operates in the transient operating range based on real time, wherein the injection profile determined by the latter is implemented directly by means of an injection device, possibly bypassing a control, in particular the combustion rate control.
- a further development provides that the pilot control iteratively calculates a pressure curve in a cylinder of the internal combustion engine, wherein the pressure curve is calculated by means of three sections comprising a polytropic compression, a pressure increase, preferably a constant pressure increase and a polytropic expansion.
- a pressure increase preferably a constant pressure increase and a polytropic expansion.
- operating point-dependent an optimum pressure increase is selected for the synthetic pressure curve.
- the predetermined pressure increase does not necessarily have to be constant.
- pressure increases For example, one or more variable pressure increases only in sections. For this purpose, further details are given below.
- a control unit of an internal combustion engine having a real-time based iterative pilot control of an injection profile is proposed by means of a model-based combustion process model, wherein the combustion process model is at least one fuel injector model and / or an ignition delay time model and / or a combustion heat release model.
- an ignition delay model, a fuel injector model, a combustion heat release model and / or a continuous combustion model can be designed as a black box, have one or more neural networks, include a phenomenological approach or be designed as a whitebox For example, as a physical and / or chemical model, and / or have a mixed approach or designed as a gray box.
- the control unit is coupled to other control units of the internal combustion engine, wherein a combustion rate control is deposited, upstream of the pilot control. It is preferred if the feedforward control is implemented in the control unit, while in another control unit of the internal combustion engine, a combustion rate control is implemented, wherein both control units are coupled to each other for the exchange of data from the pilot control for combustion rate control. Furthermore, it is preferred in this as well as in other proposed embodiments, when the feedforward control is implemented as a model-based pilot control algorithm for diesel engine combustion rate control by digital multiple injection in the control unit.
- an injection profile comprising the number, times, quantities and rail pressure of the injections is calculated as a function of the current engine operating point, thus enabling a real-time use of the principle of combustion rate control even in transient engine operation.
- the pre-control algorithm may be capable of generating a digital injection profile that results in a predetermined engine operating point-dependent combustion rate.
- the combustion process is modeled a priori.
- the knowledge about the injection profile is required.
- the injection profile is just the desired target size. Therefore, an iteration with respect to the calculation of the sought injection profile is used.
- the quality of the calculated injection profile with regard to the target combustion rate achieved depends largely on the accuracy of the engine model describing the fuel injection.
- This model is therefore preferably composed of at least one fuel injector model, an ignition delay time model and a combustion heat release model.
- an adjustment of the rail pressure can also be taken into account.
- the predetermined nominal combustion curve can generally only be approximated by the adaptation of the injection profile, the rail pressure already being preset.
- a sole optimization of the start, duration and number of individual injections may not lead to a sufficient approximation to the nominal combustion curve.
- an additional adaptation of the rail pressure may lead to a further approximation to the nominal combustion curve.
- a further iteration level can be inserted, which leads to an optimization of the operating point-dependent rail pressure.
- all the variabilities of the injection path i. E. the high pressure fuel injection by the high pressure fuel pump (rail pressure) and the fuel injection by the injectors are used by the pilot control algorithm.
- the pre-control quality depends to a great extent on the parameterization, ie. from finding suitable values of possible adjustment quantities of the precontrol; Possible parameters / settings are z.
- An adaptive parameterization should be considered.
- the parameterization indicated by the existing cylinder pressure, can initially be carried out for different engine configurations, for example an initialization of the initial individual injection quantities in steady state operation with the aid of the iterative learning feedback controller (ILR), but also adapt depending on the engine state, for example a detection of fuel variations and adaptation of parameters in the ignition delay model.
- ILR iterative learning feedback controller
- the feedforward control can also be used in offline mode for the pre-optimization of a map-based injection characteristic.
- the algorithm can also calculate ECU maps for the injection parameters, including injection times, quantities, number of injections, and rail pressure. This option is particularly useful if on-line operation of the pre-control algorithm is not possible due to ECU-side limitations of the computing capacity.
- the cylinder pressure indexing which is already available for this when using an ILR, for example, can be used to detect one or more disturbances of the work process.
- Disturbance variables of the working process may include, for example, fuel variances, component tolerances / wear or aging influences as well as environmental influences. The influence of these disturbance variables can be taken into account for the purpose of compensation by a corresponding adaptation of the parameterization of the pilot control algorithm. This will be clarified below with reference to two examples.
- Example 1 A detection of a changed ignition delay, for example due to a fuel variance, leads inversely to a change in the Cetane number, resulting in an adjustment of the parameter "cetane number" in the ignition delay model.
- Example 2 A detection of a changed energy input into the combustion chamber, for example by a fuel variance or by a deposit in the injection nozzles, has an effect on the flow coefficient of the injection nozzle and on the calorific value or the density of the fuel. From this follows an adaptation of the parameter "flow coefficient" in the injector model as well as an adjustment of the parameters "fuel density” and "lower calorific value” in the heat release model.
- the combustion process is ultimately a synthetic cylinder pressure curve as a target size in the pre-control algorithm.
- the desired course of the temperature can be synthesized accordingly, for example in order to avoid the formation of NO x formation, which occurs particularly in certain temperature ranges (in particular high temperatures); These temperature ranges should be avoided by a corresponding desired temperature profile is specified. As a result, compliance with predefinable NOx limit values can be monitored.
- an estimation of the combustion noise can also be carried out according to an embodiment of the invention. This can be done, for example, with the aid of a Föller analysis of the cylinder pressure curve, as described for example in the article "A method for analyzing and predicting the combustion noise of gasoline engines", MTZ October 2001, Vol .62, Issue 10, pp.774-782 and of the thesis at the RWTH Aachen with the title "combustion noise of the direct injection reciprocating engine", Stefan Heuer, downloadable under darwin.bth.rwth-aachen.de/opus/volltexte/2001/247/.../ your _Stef. df, which is referred to in the context of the disclosure.
- the estimation of the combustion noise can therefore be considered as an additional Lich criterion or be used as an additional boundary condition for the synthesis of the target pressure profile.
- FIG. 2 shows a setpoint calculation, shown schematically on the basis of diagrams and associated algorithms
- FIG. 23 shows a schematic representation of an overall iteration concept
- FIG. 23 shows a diagram of the parameters involved in the respective step for the execution of the possible precontrol algorithm
- FIG. 1 shows a schematic view of the synthetic composition of a desired pressure profile with a first time period relating to a polytropic compression, with an adjoining second time period relating to a preferably constant pressure increase and with a third time interval with regard to a polytropic expansion.
- this desired cylinder pressure curve for example based on an alpha process, a Miller or Atkinson and / or also Sariaer process or other processes, is thus composed.
- the alpha process will be For example, in the dissertation at the RWTH Aachen by Dipl.-Ing. Jan Hinkelbein with the title "Combustion characteristic control by means of injection curve modulation for direct injection diesel engines", in particular from p.
- the alpha process is characterized by the start of combustion, i. E. SOR (start of ramp) or ramp beginning, and a beginning of SOR constant ramp slope (therefore mathematically alpha) defined. Due to the independent variation of SOR and Alpha, the process allows thermodynamic degrees of freedom. The two extreme cases of equal pressure and equal space processes are with this consideration only special cases of the alpha process.
- the equalization process is known to be a typical ideal of an Otto engine combustion process. This refers to isochoric combustion, ie. the complete fuel conversion with the same cylinder volume.
- the alpha process was used only as an example as a target size due to its degrees of freedom. For further applications, however, beyond the alpha process, even more litigation, such. B. locally variable pressure increases, as setpoints definable.
- the setpoint characteristics of the pressure curve for example a ramp gradient Alpha or ⁇ and a ramp start SORT, are read from a memory or core field. With these characteristics, the pressure profile is then synthesized over the following three stages: i. Polytropic compression ii. Constant increase in pressure according to the predetermined ramp slope a, but also a variable, sectionwise ramp slope can be realized. iii. Polytropic expansion, for example corrected by, for example, an EGR rate and / or a rail pressure. In order to take into account the required indicated mean pressure of the high-pressure phase, expressed as load requirement pmi, the pressure profile must be calculated iteratively. In this case, in certain crankshaft step sizes (defined in degrees.
- the synthetic pressure curve can be represented more accurately than with a coarse increment (eg 1 degree crankshaft), whereby the set resolution results from the stress field between computing speed and accuracy) within the ramp Expansion phase initiated as a test.
- a fine resolution or step size eg 0.1 degree crankshaft
- the synthetic pressure curve can be represented more accurately than with a coarse increment (eg 1 degree crankshaft), whereby the set resolution results from the stress field between computing speed and accuracy) within the ramp Expansion phase initiated as a test.
- the entire pressure curve is given and it can be checked whether the given pmi is reached. If not, another step is added or "climbed" along the ramp and the test is repeated. This procedure is followed iteratively until a pressure curve corresponding to the load request results, as are the iterations 1 to 4 from FIG. 1 emerge.
- FIG. 2 shows that, taking into account the engine boundary conditions such as, for example, boost pressure, exhaust gas recirculation (EGR) rate and / or valve timing from the pressure curve, the desired total combustion profile can be determined based on an energy balance.
- the cumulative combustion process designates the cumulative heat energy converted in the work cycle.
- the saturation value of the cumulative combustion curve thus corresponds to the chemical energy quantity entered by the injectors (in the case of complete fuel conversion).
- the averaged temperature profile and the average oxygen concentration profile in the cylinder are also determined, as the individual superimposed diagrams in FIG. 2 show.
- These synthetically generated gradients are used for the pre-control as set values for the pressure curve or the combustion process as well as state variables for a temperature or an oxygen content. The following relationship is considered here:
- IVC-EVO calculation taking into account the cylinder gas state at IVC (EGR, temperature, pressure, degree of filling), with IVC as an abbreviation of Inlet Valve Close, EVO as an abbreviation of Exit Valve Open and pmi as an abbreviation for pressure mean indicated, ie. the indicated mean pressure the high-pressure or working phase, actually correct therefore even as pmi HD to call
- the ignition delay t zv , i is determined for the required hydraulic injection start SOI h ydr, i calculated by an ignition integral. This goes on the one hand from Fig. 5 as a sequence and on the other from FIG. 6 with respect to the diagram shown. 2.
- a temporal hydraulic injection curve is calculated by means of an injector model m F / i ((p), which is shown in FIG. 9 or FIG. 10.
- the resulting heat release Qb, Modei, i is calculated by means of a multi-part heat release model, wherein the heat release model can for example have a subdivision into different combustion phases such as premixed and diffusion-controlled combustion, see also FIG. 11 or FIG. 12.
- the resulting course of the heat release is compared with the target cumulative combustion curve taking into account an injection quantity iteration criterion. Will the injection quantity iteration criterion fulfilled, the first injection quantity has been found successfully. If the injection quantity iteration criterion can not yet be met, a new fuel quantity is generated on the basis of the resulting deviation. With this new amount of fuel again points 2 and 3 will go through again. This iteration repeats until the injection quantity iteration criterion is met. From this iteration also results in a fictitious combustion end MFB X / i for the pilot control algorithm, which point physically does not represent the end of combustion, but only the point to which combustion is monitored by the algorithm.
- any incineration share after this point will be calculated on the basis of the subsequent burns. This is shown in FIGS. 13 and 14. If it is determined by the comparison between the desired combustion profile and the modeled total heat release, for example from the superposition of the previous individual combustions, that further combustions are required, then the above-described fictitious combustion end of the current injection with the required start of combustion SOC X / i of the next injection equated. This is then the starting point for calculating the next injection, as shown in FIG. 15 and FIG. 16. In this way, besides the injection times and quantities, the number of required injections is automatically generated by the algorithm. Further explanations follow in the discussion of the injection quantity iteration criterion.
- the electrical signals such as relevant variables for processing in the engine control unit for starting SOQ + i and the duration ET e i e ctr, i are calculated for each individual injection event by an injector model, as for example, from Fig 17 and Fig. 18 can be seen.
- an injection profile which is generally composed of several injections, builds up successively. This results in a modeled overall heat release process, which results from the superimposition of the respective individual injections. resulting in heat release. This injection profile build-up takes place until the resulting overall heat release curve has approached the target cumulative combustion curve in accordance with the injection quantity iteration criterion with sufficient accuracy, which is shown in FIGS. 19 to 22 is shown.
- the individual injection quantity is preferably adjusted on the basis of the deviation between the nominal sum-combustion profile and the modeled total heat release profile in the effective range of the respective heat release associated with the current individual injection.
- this effective range is discretized into several partial effective ranges corresponding to the normalized fuel sales progress, referred to as mass fraction burned (MFB).
- a first partial active area can thus extend, for example, to the area MFBO - MFB30, ie.
- the crankshaft angle range (in degrees) between the point at which 0% of the single injection amount has been converted to the point where 30% of the single injection quantity has been converted (ie, the distance between two angular positions of the crankshaft position.)
- the corrected single injection quantity is used to recalculate the modeled total heat release history, and again the deviation is checked. until a single injection amount has been found, which causes the deviation within a permissible value range.
- the partial effective range is widened, e.g. MFBO - MFB40. Due to the described mechanism, the partial effective area has to be extended to MFBO - MFB100, i. E. the single injection refers to an effective range extending to the end of the working cycle, thus identifying the last single injection required for the current working cycle. The entire injection profile is then determined.
- FIG. 23 schematically illustrates the iterative procedure for determining the entire injection profile.
- a higher-order iteration circle is tracked as long as injections are added until the superposition of the previous injections leads to a sufficient approximation to the desired combustion profile.
- Each individual injection must also be determined iteratively. The result of each individual injection iteration is, in addition to the amount of fuel to be injected, the required start of combustion of the next injection.
- Fig. 24 to FIG. 28 show different simulation results, each of which shows that the pre-control gives the results sufficient accuracy that enables real-time-based combustion rate control, in particular in the transient range.
- Method with a pilot control characterized in that the pilot control passes the injection profile to a combustion rate control, wherein in the transient operating range, the combustion rate control operates real-time based.
- Method with a feedforward control characterized in that the feedforward control operates in the transient operating range real-time based, wherein the injection profile determined by this is implemented directly by means of an injection device with possible circumvention of a control.
- pilot control iteratively calculates a pressure curve in a cylinder of the internal combustion engine, wherein the pressure curve by means of three sections comprising a polytrope compression, a pressure increase, preferably a constant pressure increase and a polytropic expansion is calculated ,
- Method according to item 5 characterized in that on the part of the pilot control, a second iteration for determining an adjusted operating point-dependent rail pressure takes place, which is received in the determination of the injection profile.
- Method according to item 6 characterized in that an expansion phase, preferably the polytropic expansion, is introduced as a test during the iteration in order to check whether a predetermined indicated mean pressure p mi is reached.
- the combustion process model comprises at least one fuel injector model, an ignition delay time model and a combustion heat release model.
- Control unit characterized in that the control unit is coupled to other control units of the internal combustion engine, wherein a combustion rate control is deposited, upstream of the pilot control.
- Control unit characterized in that the control unit has the feedforward control implemented, while another control unit of the internal combustion engine has implemented a combustion rate control, both control units for data exchange from the feedforward control for combustion rate control are coupled together.
- Control unit characterized in that the pilot control is implemented as a model-based pilot control algorithm for diesel engine combustion rate control by digital multiple injection into the control unit.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112015001399.7T DE112015001399A5 (en) | 2014-03-25 | 2015-03-24 | Model-based pilot control for combustion rate control |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014004219.7 | 2014-03-25 | ||
DE102014004219 | 2014-03-25 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2015144704A1 true WO2015144704A1 (en) | 2015-10-01 |
Family
ID=52781052
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2015/056256 WO2015144704A1 (en) | 2014-03-25 | 2015-03-24 | Model-based pilot control for controlling the combustion rate |
Country Status (2)
Country | Link |
---|---|
DE (1) | DE112015001399A5 (en) |
WO (1) | WO2015144704A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016218583A1 (en) * | 2016-09-27 | 2017-05-11 | Continental Automotive Gmbh | Method for controlling an internal combustion engine and control unit for such an internal combustion engine |
EP3591184A1 (en) * | 2018-07-06 | 2020-01-08 | Mazda Motor Corporation | Fuel injection control device and fuel injection control method for diesel engine |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10258874A1 (en) * | 2002-12-17 | 2004-07-22 | Daimlerchrysler Ag | Model-based combustion engine control method in which, in an energy balance model, the total energy input corresponding to the fuel air mixture is matched to heat output and converted heat energy |
US20050251322A1 (en) * | 2004-04-20 | 2005-11-10 | Southwest Research Institute | Virtual cylinder pressure sensor with individual estimators for pressure-related values |
WO2008111904A1 (en) * | 2007-03-15 | 2008-09-18 | Scania Cv Ab (Publ) | Arrangement and method for controlling the burn in a combustion engine |
US20090182485A1 (en) * | 2008-01-15 | 2009-07-16 | Axel Loeffler | Method for regulating an internal combustion engine, computer program and control unit |
US20110172897A1 (en) * | 2010-01-14 | 2011-07-14 | Honda Motor Co., Ltd. | Plant control apparatus |
US20120221227A1 (en) * | 2011-02-28 | 2012-08-30 | GM Global Technology Operations LLC | Method for operating an internal combustion engine |
-
2015
- 2015-03-24 DE DE112015001399.7T patent/DE112015001399A5/en not_active Withdrawn
- 2015-03-24 WO PCT/EP2015/056256 patent/WO2015144704A1/en active Application Filing
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10258874A1 (en) * | 2002-12-17 | 2004-07-22 | Daimlerchrysler Ag | Model-based combustion engine control method in which, in an energy balance model, the total energy input corresponding to the fuel air mixture is matched to heat output and converted heat energy |
US20050251322A1 (en) * | 2004-04-20 | 2005-11-10 | Southwest Research Institute | Virtual cylinder pressure sensor with individual estimators for pressure-related values |
WO2008111904A1 (en) * | 2007-03-15 | 2008-09-18 | Scania Cv Ab (Publ) | Arrangement and method for controlling the burn in a combustion engine |
US20090182485A1 (en) * | 2008-01-15 | 2009-07-16 | Axel Loeffler | Method for regulating an internal combustion engine, computer program and control unit |
US20110172897A1 (en) * | 2010-01-14 | 2011-07-14 | Honda Motor Co., Ltd. | Plant control apparatus |
US20120221227A1 (en) * | 2011-02-28 | 2012-08-30 | GM Global Technology Operations LLC | Method for operating an internal combustion engine |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016218583A1 (en) * | 2016-09-27 | 2017-05-11 | Continental Automotive Gmbh | Method for controlling an internal combustion engine and control unit for such an internal combustion engine |
EP3591184A1 (en) * | 2018-07-06 | 2020-01-08 | Mazda Motor Corporation | Fuel injection control device and fuel injection control method for diesel engine |
Also Published As
Publication number | Publication date |
---|---|
DE112015001399A5 (en) | 2016-12-29 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2297444B1 (en) | Method and device for the pressure wave compensation of consecutive injections in an injection system of an internal combustion engine | |
DE102008004361A1 (en) | Method for controlling an internal combustion engine, computer program and control unit | |
EP3698032B1 (en) | Method for the model-based control and regulation of an internal combustion engine | |
DE102008004365A1 (en) | Method for operating an internal combustion engine, computer program and control unit | |
DE102004001118A1 (en) | Internal combustion engine managing method, involves extracting heat setting quantity from characteristic field, and adapting field and/or quantity according to characteristic obtained from real heat quantity | |
DE102011006787A1 (en) | Delay-compensated air-fuel control of an internal combustion engine of a vehicle | |
DE102012020489B4 (en) | Method for adjusting the injection behavior of injectors in an internal combustion engine, engine control unit and system for adjusting an injection behavior | |
DE102015225279A1 (en) | Method and device for the predictive control and / or regulation of an internal combustion engine and internal combustion engine with the device for carrying out the method | |
DE102007012604A1 (en) | A method of controlling an injection of a direct injection internal combustion engine injector and a direct injection internal combustion engine | |
DE102008043165A1 (en) | Method for calibrating amount of partial fuel injection into fuel injection system of internal combustion engine of motor vehicle, involves determining correction value for fuel injection by stimulating pattern and by changing vibration | |
DE102011013481A1 (en) | Method for determining temperature of gas in combustion chamber of e.g. diesel engine, for passenger car, involves determining temperature of gas based on total mass and pressure in chamber, rotation speed of engine and volume of chamber | |
DE102014118125B3 (en) | Device and method for controlling an internal combustion engine for motor vehicles, in particular a diesel engine | |
DE10159016A1 (en) | Method and device for controlling an internal combustion engine | |
DE102014208992A1 (en) | Method for calibrating post-injections in a fuel injection system of an internal combustion engine, in particular of a motor vehicle | |
DE102004001119A1 (en) | Method and device for controlling an internal combustion engine | |
WO2009143858A1 (en) | Method for controlling an injection process of an internal combustion engine, control device for an internal combustion engine and an internal combustion engine | |
WO2014064099A9 (en) | Method for calculating and predicting knocking and super-knocking phenomena, and control device for controlling combustion methods in internal combustion engines, in particular spark-ignition engines | |
WO2015144704A1 (en) | Model-based pilot control for controlling the combustion rate | |
DE4322270B4 (en) | Method and device for controlling an internal combustion engine | |
EP1672206B1 (en) | Method and device for engine control in a vehicle | |
EP3011159A1 (en) | Method and control device for correcting the start of injection of injectors of an internal combustion engine | |
DE102008005154A1 (en) | Method and device for monitoring a motor control unit | |
DE102008027151B4 (en) | Method for controlling an internal combustion engine with a temperature-dependent injection parameter | |
DE102008055931B4 (en) | Method for setting a pressure value in the pressure accumulator of a fuel supply system | |
DE102016219067A1 (en) | Method for operating an internal combustion engine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 15712599 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 112015001399 Country of ref document: DE |
|
REG | Reference to national code |
Ref country code: DE Ref legal event code: R225 Ref document number: 112015001399 Country of ref document: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 15712599 Country of ref document: EP Kind code of ref document: A1 |