EP1266134A1 - Procede pour faire fonctionner un moteur a combustion interne - Google Patents

Procede pour faire fonctionner un moteur a combustion interne

Info

Publication number
EP1266134A1
EP1266134A1 EP01911396A EP01911396A EP1266134A1 EP 1266134 A1 EP1266134 A1 EP 1266134A1 EP 01911396 A EP01911396 A EP 01911396A EP 01911396 A EP01911396 A EP 01911396A EP 1266134 A1 EP1266134 A1 EP 1266134A1
Authority
EP
European Patent Office
Prior art keywords
pressure
accumulator
injection
internal combustion
combustion engine
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.)
Withdrawn
Application number
EP01911396A
Other languages
German (de)
English (en)
Inventor
Hansjoerg Bochum
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1266134A1 publication Critical patent/EP1266134A1/fr
Withdrawn legal-status Critical Current

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
    • 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
    • F02D41/3809—Common rail control systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/06—Fuel or fuel supply system parameters
    • F02D2200/0602—Fuel pressure
    • F02D2200/0604—Estimation of fuel pressure

Definitions

  • the present invention relates to a method for operating an internal combustion engine, in particular a direct-injection internal combustion engine, in which fuel is pumped into a pressure accumulator by at least one pump and the fuel is injected from the pressure accumulator into a combustion chamber via an injection valve, the opening duration of the injection valve depending is calculated from the accumulator pressure prevailing in the pressure accumulator.
  • the invention also relates to an internal combustion engine, in particular a direct-injection internal combustion engine, with - a pressure accumulator, at least one pump for delivering fuel to the pressure accumulator, a combustion chamber, an injection valve for injecting fuel from the pressure accumulator into the combustion chamber, and a control unit for calculating the opening duration of the injection valve as a function of the accumulator pressure prevailing in the pressure accumulator.
  • an internal combustion engine in particular a direct-injection internal combustion engine, with - a pressure accumulator, at least one pump for delivering fuel to the pressure accumulator, a combustion chamber, an injection valve for injecting fuel from the pressure accumulator into the combustion chamber, and a control unit for calculating the opening duration of the injection valve as a function of the accumulator pressure prevailing in the pressure accumulator.
  • the present invention also relates to a control apparatus for such a machine Brennkraf.
  • a V out and a machine at the outset Brennkraf mentioned type are known from DE 195 48 278.
  • a method for regulating the accumulator pressure in a pressure accumulator of a Co mon-rail injection system (CR system) is described.
  • the opening duration of the injection valves is calculated as a function of the quantity of fuel to be injected and of the accumulator pressure prevailing in the pressure accumulator.
  • the accumulator pressure prevailing in the pressure accumulator must be included in the calculation of the opening duration, since the flow through the injection valves is dependent on the accumulator pressure.
  • the accumulator pressure is recorded synchronously with the speed.
  • the pressure control takes place in a fixed time grid. For pressure control, the accumulator pressure recorded in synchronism with the speed is sampled in a synchronous manner.
  • the opening duration of the injection valves does not depend on a storage pressure prevailing in the pressure accumulator at the time of the injection, but rather in
  • the present invention has for its object to reduce errors in the fuel mass injected into the combustion chambers in an internal combustion engine, thereby improving the emission behavior, noise and fuel consumption of the internal combustion engine.
  • the invention proposes, starting from the method for operating an internal combustion engine of the type mentioned at the outset, that an estimated pressure value is calculated from at least two measured pressure values and is used as the storage pressure prevailing in the pressure accumulator for calculating the opening duration of the injection valve, if the Amount of the gradient of the
  • Memory pressure history exceeds a predetermined threshold.
  • the calculation of the opening times of the injection valves does not use a relatively old pressure value measured before the injection, but rather a current, estimated pressure value for the period of time during the injection.
  • the estimated pressure value is calculated on the basis of at least two measured pressure values.
  • dynamic pressure changes in the storage pressure can also be taken into account.
  • Corresponding opening times of the injection valves can be calculated and the fuel mass to be injected into the combustion chambers can be measured particularly precisely even in the event of dynamic pressure changes.
  • the method according to the invention leads to an improvement in the emission behavior, the noise level and the fuel consumption of the internal combustion engine.
  • the estimated pressure value is only used to calculate the opening times of the injection valves if the gradient of the accumulator pressure curve exceeds a predetermined threshold value, i. H. if the accumulator pressure curve exceeds a certain dynamic.
  • the gradient shows the direction of the greatest pressure change in the storage pressure curve.
  • the amount of the gradient reflects the amount of the maximum pressure change.
  • the estimated pressure value characterizes an average storage pressure between the beginning and the end of the injection.
  • the mean accumulator pressure can be a value between the accumulator pressure at the beginning and the accumulator pressure at the end of the injection. It is preferably the accumulator pressure that lies exactly in the middle between the accumulator pressure at the beginning and the accumulator pressure at the end of the injection.
  • the mean accumulator pressure is the accumulator pressure that prevails in the pressure accumulator at a point in time exactly between the start of injection and the end of injection.
  • a compensation function be placed by measured pressure values and the estimated one
  • Pressure value is calculated using the compensation function.
  • a first-order compensation polynomial is advantageously placed through the measured pressure values. If the expected injection start or a point in time between the start of injection and the end of injection is inserted into the compensation function or into the compensation polynomial, a relatively precise estimated pressure value is obtained for the point in time of the start of injection or for a point in time between the start of injection and the end of injection.
  • An equalization polynomial of the first order can be put through two measured pressure values without a great amount of computing time and with a small storage space requirement and provides an estimated pressure value with sufficient accuracy.
  • the measured pressure values be recorded over several injection cycles. In this way, short-term pressure fluctuations in the pressure accumulator can be dealt with, which results in a particularly smooth running of the internal combustion engine is made possible.
  • the opening times of the injection valves calculated using the method according to the invention are smaller than the opening times calculated on the basis of pressure values measured before the injection.
  • the opening times calculated using the method according to the invention are greater than the opening times calculated on the basis of pressure values measured before the injection.
  • the difference between the opening times calculated using the method according to the invention and the difference calculated on the basis of pressure values measured before the injection is the difference between the opening times calculated using the method according to the invention and the difference calculated on the basis of pressure values measured before the injection
  • the estimated pressure value be multiplied by a reduction factor which is ⁇ 1 before it is considered to be that in the
  • the accumulator pressure prevailing in the pressure accumulator is used to calculate the opening duration of the injection valve.
  • control element which is provided for a control unit of an internal combustion engine, in particular a direct injection internal combustion engine.
  • a program is stored on the control element, which is executable on a computing device, in particular on a microprocessor, of the control device and is suitable for executing the method according to the invention.
  • the invention is implemented by a program stored on the control element, so that this control element provided with the program does the same in the same way
  • an electrical storage medium can be used as the control element, for example a read-only memory (ROM) or a flash memory.
  • control unit calculates an estimated pressure value from at least two measured pressure values and uses the estimated pressure value as the storage pressure prevailing in the pressure accumulator if the amount of the gradient of the accumulator pressure curve exceeds a predeterminable threshold value.
  • the pressure accumulator is designed as a high-pressure accumulator of a Co mon-Rail (CR) fuel injection system and the injection valve as a high-pressure injection valve.
  • CR Co mon-Rail
  • the control unit calculates an estimated pressure value from at least two measured pressure values and attracts the estimated pressure value than the pressure prevailing in the accumulator reservoir pressure, if the amount exceeds the gradient of the S peicherdruckverlaufs a predeterminable threshold value.
  • Figure 1 shows a fuel supply system of an internal combustion engine according to the invention
  • FIG. 2 is a procedural diagram of an inventive
  • Figure 3 shows a dynamic pressure curve of the
  • a fuel supply system of an internal combustion engine according to the invention with high-pressure injection is designated in its entirety with reference number 1.
  • the fuel supply system 1 is usually referred to as a common rail (CR) fuel injection system.
  • CR common rail
  • the reference numeral 2 designates a fuel reservoir which is connected to a prefeed pump 3. From the pre-feed pump 3, the fuel passes through a line 4 to a metering valve 5. The line 4 is via a low pressure relief valve 6 with the Fuel tank 2 in connection.
  • the metering valve 5 is connected to a high-pressure accumulator 8 via a high-pressure pump 7.
  • the high-pressure accumulator 8 is designed as a high-pressure accumulator line (rail).
  • the high-pressure accumulator 8 is connected to high-pressure injection valves 10 (so-called injectors) via fuel lines 9.
  • the high-pressure accumulator 8 is connected to the fuel tank 2 via a pressure relief valve 11.
  • the metering valve 5 can be controlled by means of a coil 12.
  • the area of the fuel injection system 1 between the outlet of the high pressure pump 7 and the inlet of the pressure relief valve 11 is referred to as the high pressure area.
  • the pressure in the high pressure area is detected by means of a sensor 13.
  • Fuel reservoir 2 and the high pressure pump 7 is referred to as the low pressure area.
  • control unit 14 a control unit of the internal combustion engine is designated, which also controls the fuel supply system 1.
  • the control unit 14 acts on the high-pressure injection valves 10 with control signals A and controls the coil 12 of the intake valve 5.
  • the output signal P_r of the pressure sensor 13 and various output signals n from further sensors 15, such as a speed sensor, are evaluated.
  • the controller 14 comprises a filter 16, which the
  • Output signal P_r of the pressure sensor 13 is fed.
  • the filter 16 applies a filtered pressure value P r of the pressure sensor 13 to a quantity calculation device 17 and a summation point 18.
  • the output signal P_soll of a setpoint specification device 19 is present at a second input of the summation point 18. This processes the Output signals n of the further sensors 15 and the output signal Q_n of the quantity calculation device 17.
  • the quantity calculation device 17 applies control signals A to the high-pressure injection valves 10 and the setpoint specification device 19 to the signal Q_n, which corresponds to the quantity of fuel to be injected into the combustion chambers of the internal combustion engine.
  • the output signal of the summation point 18 is applied to a pressure regulator 20, which in turn controls the coil 12 of the metering valve 5.
  • the Kraf material supply device 1 works as follows: First, fuel is delivered from the fuel tank 2 by the pre-feed pump 3. As soon as the pressure in the low-pressure area rises to impermissibly high values, the low-pressure relief valve 6 opens and releases the connection between the outlet of the prefeed pump 3 and the fuel tank 2.
  • the high-pressure feed pump 7 delivers the fuel from the low-pressure area to the high-pressure area.
  • the high pressure pump 7 builds up a high pressure in the high pressure accumulator 8.
  • pressure values of approximately 30 to 200 bar are achieved in a fuel supply system for a spark-ignition internal combustion engine and pressure values of approximately 1000 to 2000 bar in a high-pressure accumulator 8 in a self-igniting internal combustion engine.
  • the fuel can be metered under high pressure to the individual combustion chambers in the cylinders of the internal combustion engine.
  • the pressure in the high pressure area can be regulated by the metering valve 5.
  • the metering valve 5 supplies different delivery rates of the high-pressure pump 7 Available.
  • Additional actuators can also be used to regulate the accumulator pressure p_r in the high pressure range.
  • these are one in the high pressure range.
  • Flow adjustable electric pre-feed pump or a pressure relief valve which can also be controlled by means of a coil.
  • the control signals A for the high-pressure injection valves 10 are dependent on the accumulator pressure p_r and on the fuel quantity Q_n to be injected.
  • the fuel mass to be injected is set via the opening period t_i of the high-pressure injection valves 10. Since the flow through the open injectors 10 from the
  • Storage pressure p_r depends in the high pressure accumulator 8, this must be included in the calculation of the opening period t_i.
  • the control signals A are calculated depending on the speed with a variable time interval. The time interval between the individual calculations depends on the speed n of the internal combustion engine.
  • the control signal for the metering valve 5 in the pressure regulator 20 is calculated in a fixed time cycle. This time cycle is selected so that the pressure regulator 20 can immediately react to changing setpoints p_soll and the new setpoint p_soll is set as quickly as possible.
  • the opening period of the high-pressure injection valves ie the control signal A, is calculated directly from measured pressure values p_r. Since the injection can theoretically take place at relatively early points in time (for example at 340 ° before top dead center (TDC ) of the ignition phase), the opening duration of the high-pressure injection valves 10 calculated for an injection must already be before this early
  • High-pressure injection valves 10 as a function of relatively old, previously measured pressure values p_r have hardly any effects in the stationary operation of the internal combustion engine.
  • the pressure in the high-pressure accumulator 8 can fluctuate greatly.
  • the pressure fluctuations are caused by the injection on the one hand and by the pressure build-up in the high pressure area on the other hand.
  • the measured pressure value used for calculating the opening duration t_i deviates in part greatly from the accumulator pressure actually prevailing in the high-pressure accumulator 8 at the time of the injection.
  • FIG. 2 A flow chart of the method according to the invention is shown in FIG. 2. The method begins in a function block 30. In a subsequent function block 31, the current accumulator pressure p_r_act prevailing in the high-pressure accumulator 8 is measured and stored in a accumulator 32. In a function block 33, a previously measured old pressure value p_r_ist_alt is taken from the memory 32.
  • the gradient of the accumulator pressure curve dp_r_syn is then formed in a function block 34, in which the old accumulator pressure value p_r_is the current one Storage pressure value p_r_ist_alt is subtracted.
  • a query block 35 then checks whether the magnitude of the gradient dp_r_syn exceeds a predetermined threshold value.
  • the magnitude of the gradient of the accumulator pressure curve exceeds the predetermined threshold if the accumulator pressure p_r in the high-pressure accumulator 8 changes relatively quickly.
  • an estimated pressure value p_r_est is calculated in a function block 36.
  • the opening duration t_i of the high-pressure injection valves 10 is then calculated in a function block 37 as a function of the estimated pressure value p_r_est.
  • a first-order compensation polynomial is set by means of two measured pressure values p_r and the estimated pressure value p_r_est is calculated on the basis of the compensation line.
  • the estimated pressure value p_r_est can characterize a storage pressure p_r at the beginning of the injection, as is described in detail in DE 198 57 971, to which reference is expressly made here.
  • the estimated pressure value p_r_est is calculated using the following equation (see FIG. 3):
  • w_esb_x p_r_est ⁇ _r_ist + dp_r_syn, w_syn
  • w_esb_x is the angle at the start of injection.
  • the estimated pressure value p_r_est characterizes a storage pressure p_r in the Middle of the injection, ie between the beginning and the
  • the estimated pressure value p_r_est is calculated using the following equations:
  • w_esm_x p_r_est p_r_ist + dp_r_syn, w_syn
  • w_esm_x w_esb_x + angle ⁇ 0, 5 • t_i ⁇
  • the opening time t_i of the high-pressure injection valves 10 is calculated directly from the measured pressure values p_r_ist in a function block 38 in a manner known per se from DE 195 48 278. Finally, the calculated opening time t_i of the high-pressure injection valves 10 is output in a function block 39. The method according to the invention is ended in a function block 40.

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)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne un procédé pour faire fonctionner un moteur à combustion interne, en particulier un moteur à combustion à injection directe, selon lequel le carburant est amené, par au moins une pompe (3, 7), dans un accumulateur de pression (8) à partir duquel il est injecté par l'intermédiaire d'une soupape d'injection (10), dans une chambre de combustion. La durée d'ouverture (t_i) de la soupape d'injection (10) est calculée en fonction de la pression accumulée (p_r) régnant dans l'accumulateur de pression (8). Pour que, en particulier lors de fortes fluctuations de la pression accumulée (p_r), la masse de carburant à injecter puisse être déterminée le plus précisément possible, il est proposé qu'une valeur de pression estimée (p_r_est) soit calculée à partir d'au moins deux valeurs de pression et prise en compte, en tant que pression accumulée (p_r) régnant dans l'accumulateur de pression (8), pour le calcul de la durée d'ouverture (t_i) de la soupape d'injection (10), au cas où la somme des gradients (dp_r_syn) de la courbe de pression accumulée dépasse une valeur de seuil prédéterminée.
EP01911396A 2000-03-11 2001-01-30 Procede pour faire fonctionner un moteur a combustion interne Withdrawn EP1266134A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10012024A DE10012024A1 (de) 2000-03-11 2000-03-11 Verfahren zum Betreiben einer Brennkraftmaschine
DE10012024 2000-03-11
PCT/DE2001/000347 WO2001069067A1 (fr) 2000-03-11 2001-01-30 Procede pour faire fonctionner un moteur a combustion interne

Publications (1)

Publication Number Publication Date
EP1266134A1 true EP1266134A1 (fr) 2002-12-18

Family

ID=7634441

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01911396A Withdrawn EP1266134A1 (fr) 2000-03-11 2001-01-30 Procede pour faire fonctionner un moteur a combustion interne

Country Status (5)

Country Link
EP (1) EP1266134A1 (fr)
JP (1) JP2003528243A (fr)
KR (1) KR20020081425A (fr)
DE (1) DE10012024A1 (fr)
WO (1) WO2001069067A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10053091A1 (de) * 2000-10-26 2002-05-08 Bosch Gmbh Robert Verfahren zum Starten einer Brennkraftmaschine
DE10147815A1 (de) * 2001-09-27 2003-04-24 Bosch Gmbh Robert Verfahren, Computerprogramm und Steuer- und/oder Regelgerät zum Betreiben einer Brennkraftmaschine, sowie Brennkraftmaschine
DE10357158B4 (de) * 2003-12-06 2013-02-07 Bayerische Motoren Werke Aktiengesellschaft Verfahren zum Korrigieren der Einspritzdauer eines Injektors für eine Brennkraftmaschine
DE102004033008B4 (de) * 2004-07-08 2014-03-20 Audi Ag Verfahren zum Einspritzen von Kraftstoff beim Start
DE102005056704B4 (de) * 2005-11-28 2013-05-29 Continental Automotive Gmbh Verfahren zur Erzielung einer vorgesehenen Einspritzmenge von Kraftstoff in einen Verbrennungsmotor
DE102006045923A1 (de) 2006-08-18 2008-02-21 Robert Bosch Gmbh Verfahren zur Bestimmung eines Raildruck-Sollwertes
DE102007019640A1 (de) * 2007-04-26 2008-10-30 Robert Bosch Gmbh Verfahren und Steuergerät zur Steuerung der Einspritzung bei einer Brennkraftmaschine
DE102010022818B4 (de) 2010-06-05 2021-08-19 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Verfahren zum Betrieb einer Verbrennungskraftmaschine mit Kraftstoffeinspritzung
DE102014200591A1 (de) * 2014-01-15 2015-07-16 Volkswagen Aktiengesellschaft Verfahren zum Ermitteln eines Einspritzdruckes und Kraftfahrzeug
CH715207B1 (de) 2018-07-25 2022-04-14 Liebherr Components Deggendorf Gmbh Verfahren zum Betrieb eines Verbrennungsmotors.

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JPH05106495A (ja) * 1991-10-15 1993-04-27 Nippondenso Co Ltd 内燃機関の蓄圧式燃料噴射装置
JP2991574B2 (ja) * 1992-09-14 1999-12-20 株式会社デンソー 内燃機関の蓄圧式燃料噴射制御装置
DE19548278B4 (de) * 1995-12-22 2007-09-13 Robert Bosch Gmbh Verfahren und Vorrichtung zur Steuerung einer Brennkraftmaschine
JP3878258B2 (ja) * 1996-11-01 2007-02-07 株式会社日立製作所 エンジン制御装置
DE19712143C2 (de) * 1997-03-22 2002-03-28 Bosch Gmbh Robert Verfahren und Vorrichtung zur Steuerung einer Brennkraftmaschine
JPH1162676A (ja) * 1997-08-25 1999-03-05 Unisia Jecs Corp 内燃機関の燃料噴射制御装置
DE19740608C2 (de) * 1997-09-16 2003-02-13 Daimler Chrysler Ag Verfahren zur Bestimmung einer kraftstoffeinspritzbezogenen Kenngröße für einen Verbrennungsmotor mit Hochdruckspeicher-Einspritzanlage
JP3975559B2 (ja) * 1998-06-12 2007-09-12 株式会社デンソー 内燃機関の蓄圧式燃料噴射制御装置
DE19857971A1 (de) * 1998-12-16 2000-06-21 Bosch Gmbh Robert Verfahren und Vorrichtung zur Steuerung einer Brennkraftmaschine

Non-Patent Citations (1)

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Title
See references of WO0169067A1 *

Also Published As

Publication number Publication date
JP2003528243A (ja) 2003-09-24
WO2001069067A1 (fr) 2001-09-20
KR20020081425A (ko) 2002-10-26
DE10012024A1 (de) 2001-09-27

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