WO2008090033A1 - Procédé de régulation d'un dispositif d'alimentation en carburant d'un moteur à combustion interne - Google Patents

Procédé de régulation d'un dispositif d'alimentation en carburant d'un moteur à combustion interne Download PDF

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Publication number
WO2008090033A1
WO2008090033A1 PCT/EP2008/050270 EP2008050270W WO2008090033A1 WO 2008090033 A1 WO2008090033 A1 WO 2008090033A1 EP 2008050270 W EP2008050270 W EP 2008050270W WO 2008090033 A1 WO2008090033 A1 WO 2008090033A1
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WO
WIPO (PCT)
Prior art keywords
pressure
mode
control valve
accumulator
control mode
Prior art date
Application number
PCT/EP2008/050270
Other languages
German (de)
English (en)
Inventor
Erwin Achleitner
Martin Cwielong
Gerhard Eser
Original Assignee
Continental Automotive 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 Continental Automotive Gmbh filed Critical Continental Automotive Gmbh
Publication of WO2008090033A1 publication Critical patent/WO2008090033A1/fr

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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
    • F02D41/3809—Common rail control systems
    • F02D41/3836—Controlling the fuel pressure
    • F02D41/3845—Controlling the fuel pressure by controlling the flow into the common rail, e.g. the amount of fuel pumped
    • 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
    • F02D41/3836—Controlling the fuel pressure
    • F02D41/3863—Controlling the fuel pressure by controlling the flow out of the common rail, e.g. using pressure relief valves
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2250/00—Engine control related to specific problems or objectives
    • F02D2250/31—Control of the fuel pressure

Definitions

  • the invention relates to a method for controlling a fuel supply device for an internal combustion engine, and to an internal combustion engine having a control device which is designed such that it can execute the method.
  • German Offenlegungsschrift DE 10 2004 016 943 A1 discloses a method for controlling a fuel supply device for an internal combustion engine.
  • the fuel supply device comprises a low-pressure circuit and a high-pressure circuit with a high-pressure pump, which is coupled on the input side to the low-pressure circuit and requires fuel in a fuel reservoir.
  • a high-pressure pump associated with the volume flow control valve of the high pressure pump in the accumulator required fuel flow is adjustable.
  • the pressure in the fuel reservoir can be adjusted by means of a pressure regulator assigned to the fuel reservoir, which is coupled to the low-pressure circuit.
  • the fuel supply device furthermore has a regulator device which generates a control signal for the volume flow control valve in a first operating mode and a control signal for the pressure regulator in a second operating mode. At a predetermined deviation of the detected pressure in the pressure accumulator from a predetermined pressure setpoint is switched between the operating modes.
  • the pressure control and the switching between the modes are performed based on characteristics for the flow control valve and the pressure regulator.
  • the characteristic curves are usually created on the basis of fewer test copies of the components. Due to aging and manufacturing tolerances, however, the components have a certain dispersion, so that the characteristic curves are faulty. There- This can lead to control deviations from the pressure setpoint and undesired jerk switching operations, especially immediately after a switching process between the operating modes. Even if, according to DE 10 2004 016 943 A1, the respective operating mode is forcibly maintained immediately after a switching operation for a specific blocking period, an undesirably heavy loading of the I component of the regulator device may occur due to the inaccurate characteristic curves.
  • a method according to claim 1 relates to a fuel supply device for an internal combustion engine, wherein the fuel supply means a pressure accumulator for the fuel, a volume flow control valve, by means of a fuel flow in the pressure accumulator is adjustable, and a pressure control valve, by means of which the pressure in the pressure accumulator adjustable is, has.
  • the fuel supply device is associated with a regulator device, which is coupled to the volume flow control valve and the pressure control valve to adjust the pressure in the pressure accumulator to a predetermined pressure setpoint.
  • the regulator means is adapted to operate selectively in a volumetric flow control mode in which the pressure in the accumulator is regulated by means of the volumetric flow control valve, or in a pressure control mode in which the pressure in the pressure accumulator is regulated by the pressure control valve.
  • the method is characterized in that, after switching from one of the modes to the other mode, the regulator means remains in that mode for a predetermined period of time. A during this period of time tende deviation of the pressure in the pressure accumulator from the pressure setpoint is detected and taken into account in a next switch to the same mode.
  • the regulation of the pressure in the pressure accumulator takes place both in the volume flow control mode and in the pressure control mode based on stored in the control device characteristics for the flow control valve and the pressure control valve.
  • Both the pressure control valve and the volumetric flow control valve characteristics are normally calibrated to a few specimens of each component.
  • the characteristics of the components are subject to certain fluctuations, which are due to aging or component tolerances and can lead to undesirable regulator behavior. According to the invention this is
  • the switching operation between the volume flow control mode and the pressure control mode is precontrolled under the specification of at least one pre-control value.
  • the pre-control value is determined based on the pressure deviation, which was detected in a previous switch to the same mode.
  • the switching operation from the volume flow control mode in the pressure control mode under precedence of a first pilot value for the pressure control valve is performed pilot-controlled.
  • the first precontrol value is determined based on the pressure deviation, which was detected in a previous switch to the pressure control mode.
  • the switching operation of the pressure control mode in the volume flow control mode is performed under control of a second pilot value for the flow control valve pilot-operated.
  • the second pilot control value is determined based on the pressure deviation which was detected in a previous switch to the volumetric flow control mode.
  • the switching operation between the volume flow control mode and the pressure control mode is carried out pilot-controlled.
  • This can be realized, for example, in the case of a changeover from the volumetric flow control mode into the pressure control mode, by switching from the characteristic for the volume flow control valve to the characteristic curve for the pressure control valve while specifying a corresponding precontrol value.
  • a change-over from the pressure control mode to the volume flow control mode occurs analogously. Since the respective precontrol value is determined taking into account the pressure deviation which occurs in the case of a previous switchover in the respective same modes, the control behavior can be stabilized.
  • This embodiment of the method avoids excessive fuel pressure in the fuel reservoir.
  • Safety components such as a pressure accumulator henes overpressure valve, which secures the fuel supply device from damage, thereby protected.
  • undesired changes in the pressure in the fuel storage which arise due to tolerances or defects of other components of the fuel supply device, are compensated. As a result, the reliability of the fuel supply device can be significantly increased.
  • the fuel is required by means of a high-pressure pump in the pressure accumulator and operated the regulator device in the pressure control mode, if the demanded by the high-pressure pump fuel volume flow is smaller than a predetermined threshold.
  • An internal combustion engine has a fuel supply device with a pressure accumulator for the fuel, a volume flow control valve, by means of a fuel flow in the pressure accumulator is adjustable, a pressure control valve, by means of which the pressure in the pressure accumulator is adjustable, and a control device, which with the flow control valve and the pressure control valve is coupled to the pressure in the pressure accumulator to a set the preset pressure setpoint to.
  • the regulator means is adapted to operate selectively in a volumetric flow control mode in which the pressure in the pressure accumulator is regulated by means of the volumetric flow control valve, or in a pressure control mode in which the pressure in the pressure accumulator is regulated by the pressure control valve.
  • the regulator device is designed such that, after switching from one of the modes to the other mode, the regulator device remains in this mode for a predetermined period of time and a deviation of the pressure in the pressure accumulator occurring during this time period is detected by the pressure setpoint. The detected pressure deviation is taken into account in the next control in the same mode in the feedforward control.
  • Figure 1 is a schematic representation of an internal combustion engine
  • Figure 2 is a schematic representation of a functioning as a flow control valve and pressure control valve combination valve
  • Figure 3 is a schematic representation of characteristics for the flow control valve and the pressure control valve
  • FIG. 4 is a flowchart of a control method.
  • the internal combustion engine 1 shows an internal combustion engine 1 is shown schematically. For the sake of clarity, the representation is made much simpler.
  • the internal combustion engine 1 comprises at least one cylinder 2 and a piston 3 movable up and down in the cylinder 2.
  • the internal combustion engine 1 further comprises an intake manifold 27 in which an air mass sensor 5, a throttle valve 6 and a suction pipe 7 are arranged downstream of an intake opening 4.
  • the intake tract opens into a combustion chamber 28 delimited by the cylinder 2 and the piston 3.
  • the fresh air required for combustion is introduced into the combustion chamber via the intake tract 27, the fresh air supply being controlled by opening and closing an inlet valve 8.
  • the internal combustion engine 1 shown here is an internal combustion engine 1 with direct fuel injection, in which the fuel is injected directly into the combustion chamber 28 via an injection valve 9.
  • Combustion serves a projecting in the combustion chamber spark plug 10.
  • the combustion exhaust gases are discharged via an exhaust valve 11 in an exhaust tract 29 of the internal combustion engine 1 and cleaned by means of a arranged in the exhaust tract 29 exhaust catalyst 12.
  • the internal combustion engine 1 further has a Kuhlstofftemperatursensor 14, a speed sensor 15 for detecting the rotational speed of the crankshaft 13 and a lambda sensor 16 for detecting the exhaust gas composition ,
  • the internal combustion engine 1 is assigned a fuel supply device which has a fuel tank 17 and a fuel pump 18 arranged therein.
  • the fuel is supplied by means of the fuel pump 18 via a supply line 19 to a pressure accumulator 20.
  • This is a common pressure accumulator 20, from which the injection valves 9 for a plurality of cylinders 2 are supplied with pressurized fuel.
  • a fuel filter 21, a high-pressure pump 22 and a flow control valve 35 are further arranged.
  • the high pressure pump 22 is used by the fuel pump 18th with relatively low pressure (about 3 to 6 bar) required fuel to the accumulator 20 to supply high pressure (typically up to 200 bar).
  • the high-pressure pump 22 is thereby driven by means of its own drive (not shown), for example an electric motor, or by corresponding coupling with the crankshaft 13.
  • the volume flow control valve 35 By means of the volume flow control valve 35, the fuel volume supplied to the pressure accumulator 20 and thus the pressure in the pressure accumulator 20 can be adjusted.
  • a pressure control valve 23 is arranged, via which the fuel located in the pressure accumulator 20 can flow back into the fuel tank 17 via a return flow line 24.
  • a pressure sensor 25 is further provided for monitoring the pressure in the accumulator 20.
  • the internal combustion engine 1 is associated with a control device 26 which is connected via signal and data lines with all actuators and sensors.
  • a control device 26 which is connected via signal and data lines with all actuators and sensors.
  • characteristic-based engine control functions KF1 to KF5
  • a regulator device 39 for regulating the pressure in the pressure reservoir 20 are implemented in software.
  • the regulator device 39 is preferably designed as a PI controller.
  • control signals are generated and transmitted to the actuators of the internal combustion engine 1.
  • control device 26 via the data and signal lines with the fuel pump 18, the flow control valve 35, the pressure control valve 23, the pressure sensor 25, the air mass sensor 5, the throttle valve 6, the spark plug 10, the injection valve 9, the Kuhlstoff- temperature sensor 14, the speed sensor 15 and the Lambda sensor 16 coupled.
  • the pressure control valve 23 and the volume flow control valve 35 may be formed as separate components or as an integrated combination valve.
  • the combination valve comprises a common 31, which is operatively connected to the high pressure pump 22, has a port 32 operatively connected to the fuel pump 18, an inlet 33 operatively connected to the accumulator 20, a common valve actuator 34, a common actuator 36 for the valve actuator 34 , one
  • Valve closure 37 for interrupting the connection between the port 32 and the inlet 33, and a compression spring 38 which is disposed between the valve actuator 34 and the valve closure 37 and this apart depending on the axial position of the valve actuator 34 with a certain force apart.
  • the port 32, the outlet 31, the common valve actuator 34 and the common actuator 36 act as the volume flow control valve 35.
  • the inlet 33, the port 32, the common valve plate 34, the compression spring 38, the valve closure 37 and the common actuator 36 as the pressure control valve 23 function as a pressure control valve 23.
  • the actuator 36 moves the valve actuator 34 as a function of an actuating signal of the control device 39 in the axial direction.
  • the valve actuator 34 is urged by the force of the compression spring 38 in a rest position.
  • a groove is formed at the valve actuator 34.
  • the port 32 and the outlet 31 are selectively hydraulically connected or disconnected via the groove, so that the fuel flow between the port 32 and the outlet 31 is selectively enabled or interrupted.
  • the fuel flow between the port 32 and the outlet 31 is substantially interrupted. In this state, which is shown in FIG. 2, only a leakage volume flow flows from the connection 32 to the outlet 31.
  • the valve actuator 34 moves counter to the spring force in the direction of the valve closure, whereby the port 32 is hydraulically coupled to the outlet 31 via the groove.
  • the pressure accumulator 20 zugechtte fuel flow and thus the pressure in the accumulator 20 can be varied continuously depending on the strength of the control signal.
  • a first control loop consisting of the volume flow control valve 35, the regulator device 39 and the pressure sensor, therefore, a regulation of the pressure in the pressure accumulator 20 on the basis of the pressure accumulator 20 zugebert fuel flow is possible.
  • This operation mode of the controller 39 will be hereinafter referred to as the volume flow control mode.
  • the port 32 and the outlet 31 are hydraulically isolated and only the leakage volume flow of fuel from the port 32 to the outlet 31 flows. If the force caused by the fuel pressure in the pressure accumulator 20 at the inlet 33 of the combination valve is greater than that the bias of the spring and applied to the valve closure 37 force, the inlet 33 is hydraulically coupled to the port 32 so that fuel from the pressure accumulator 20 via the inlet 33 toward the outlet 31 into the fuel tank 17 can flow.
  • the force exerted on the valve closure 37 is variable in dependence on the strength of the control signal. The smaller the control signal, the lower the force on the valve closure 37 and the greater the fuel flow from the pressure accumulator 20 back into the fuel tank 17.
  • the regulator device 39 controls based on the signal of the pressure sensor, the fuel pressure in the accumulator 20 to a predetermined pressure setpoint.
  • the regulator means 39 will be selectively operated in the pressure control mode or in the volume flow control mode. If predetermined switching conditions are met, the system switches between the two modes.
  • FIG. 3 shows characteristic curves of the combination valve 30.
  • a pressure curve 80 shows the relationship between the control signal in amperes and the fuel pressure in the pressure accumulator 20 in bar. Increases at a given control signal, the pressure in the pressure accumulator 20 above the desired pressure value, the regulator means 39 reduces the strength of the control signal, whereby the pressure in the pressure accumulator 20 is regulated by discharging fuel from the accumulator 20 back to the desired pressure value. If the pressure in the pressure accumulator 20 falls below the desired pressure value given a control signal, the control device 39 increases the strength of the control signal, as a result of which less fuel can flow out of the pressure accumulator 20 and the pressure in the pressure accumulator 20 returns to the desired pressure value.
  • a predetermined threshold which has a value of about 0.5 amps in this embodiment, opens the volume flow control valve 35 and allows a specified in liters per minute fuel flow from the fuel tank 17 via the high-pressure pump 22 in the pressure accumulator 20.
  • the diagram of Figure 3 shows an upper flow curve 81, which represents an upper tolerance limit for the combination valve, a lower flow curve 82, which is a lower tolerance limit for the Combination valve, and a mean flow curve 83, which represents the average between upper and lower flow curve 81, 82.
  • the controller 39 reduces the strength of the control signal, whereby the pressure in the pressure accumulator 20 drops by reducing the supplied fuel flow and constant injection quantity into the combustion chamber of the internal combustion engine and the Pressure setpoint is adjusted. If the pressure in the pressure accumulator 20 falls below the desired pressure value given a control signal, the control device 39 increases the strength of the control signal, whereby a larger fuel volume flow is supplied to the pressure accumulator 20 and the pressure in the pressure accumulator 20 returns to the desired pressure value.
  • the flow curves 81, 82 and 83 show that in this exemplary embodiment, below the threshold value, that is, when the volume flow control valve 35 is substantially closed, the leakage volume flow can still flow.
  • the regulator device 39 is no longer meaningful to operate in the flow control mode, so that at the latest when falling below this threshold, i. the corresponding fuel consumption of the internal combustion engine, a switchover to the pressure control mode takes place. This switching ensures that a pressure control even with very small injection quantities, i. smaller than the leakage volume flow, is still reliablyteurvigbar.
  • the pressure in the accumulator 20 is less than the predetermined pressure setpoint by a second amount, it is switched from the pressure control mode to the volumetric flow control mode. This ensures that the pressure in the pressure accumulator 20 is always maintained at a certain value in order to ensure a sufficient metering of fuel into the combustion chamber of the internal combustion engine and to prevent misfiring.
  • the characteristic curves for the pressure control valve 23 and the volume flow control valve 35 illustrated in FIG. 3 are generally created based on corresponding measurement series on a limited number of test specimens. Due to manufacturing tolerances and also due to changes over the life of the combination valves show deviant behavior.
  • the switching between the flow control mode and the pressure control mode are usually carried out pilot-operated. For example, if one of the above conditions is for
  • the control device 39 changes from the characteristic of the volumetric flow control valve 35 to the characteristic curve of the pressure control valve 23, given a first precontrol value for the control signal of the valve actuator 34.
  • the characteristic of the pressure control valve 23 changes for the reasons stated above not exactly true for all combination valves, it can change immediately after the change to a sudden Pressure drop in the accumulator 20 come. This pressure drop can be so great that the condition for the return switch to the flow control mode is met and an undesirable jerk change takes place.
  • the changeover from the pressure control mode into the volume control mode is also carried out with the specification of a second precontrol value for the actuating signal of the valve actuator 34.
  • a second precontrol value for the actuating signal of the valve actuator 34 is also carried out immediately after switching due to the deviating characteristic of the volume flow control valve 35.
  • an increase in pressure in the pressure accumulator 20 may occur immediately after switching due to the deviating characteristic of the volume flow control valve 35.
  • an increase in pressure in the pressure accumulator 20 may occur.
  • the above-described condition for switching back to the pressure control mode can be fulfilled and an undesired jerk changeover can take place.
  • the regulator device 39 When starting the method in step 400, the regulator device 39 is operated, for example, in the volume flow control mode. In this case, the regulation of the pressure in the pressure accumulator 20 is carried out based on the characteristic of the volume flow control valve 35.
  • step 401 it is checked whether any of the above-mentioned conditions for switching from the volume flow control mode to the pressure control mode is satisfied. If none of the conditions is met, the regulator device 39 remains in the flow control mode. If one of the conditions is fulfilled, for example because the detected pressure in the pressure accumulator 20 is greater than the desired pressure value by a first amount, then, in step 402, a first precontrol value for the valve positioner 34 is switched to the pressure control mode. In this case, the characteristic of the volume flow control valve 35 is jumped to the characteristic for the pressure control valve 23 and the regulation of the pressure in the pressure accumulator 20 is continued based on this characteristic, given the first precontrol value.
  • a payer Z is started, wherein the regulator device 39 remains in the pressure control mode at least until the value of the payer Z has exceeded a predefined limit value Z thr it in step 403. This prevents fast and unwanted switching back to the volume control mode.
  • step 404 it is checked whether there has been a deviation of the pressure from the pressure setpoint due to the switching to the pressure control mode, which results from the above-described discrepancies between the characteristic and the actual characteristic of the combination valve. If no deviation is detected, then the method continues to step 407.
  • the value of the actuating signal for the valve actuator 34 is changed by means of the regulator device 39 in step 405 such that the pressure in the pressure accumulator 20 reaches the pressure setpoint and is adjusted to this.
  • the first pilot control value is corrected taking into account the correction of the control signal by the control device 39. This can be done, for example, by assuming an output value of the control device 39 for the control signal in the adjusted state, ie when the pressure in the pressure accumulator 20 has been adjusted to the desired pressure value, for the first pilot control value.
  • This corrected first pilot value for the control signal for switching from the volume flow control mode to the pressure control mode is stored in a memory device of the control device (not shown).
  • the next changeover from the pressure control mode to the volume flow control mode is then carried out using the corrected first pilot value, whereby the pressure fluctuation resulting from the change of the characteristic curves can be significantly reduced.
  • step 407 it is checked whether any of the above-mentioned conditions for switching from the pressure control mode to the volume flow control mode is satisfied. If none of the condition is satisfied, the regulator means 39 remains in the pressure control mode.
  • step 408 a second precontrol value for the valve actuator 34 is switched to the flow control mode.
  • the characteristic curve of the volume flow control valve 35 is jumped from the characteristic of the pressure control valve 23 under specification of the second pilot value and the regulation of the pressure in the pressure accumulator 20 based on this characteristic continued.
  • the payer Z is restarted, whereby the regulator device 39 remains in the volume flow control mode at least until the value of the payer Z has again exceeded the predetermined limit value Z thr it in step 409. This prevents fast and unwanted switching back to the print control mode.
  • step 410 it is checked whether there has been a deviation of the pressure from the pressure setpoint due to the switching to the flow control mode, which results from the above-described inconsistencies between the characteristics and the actual characteristic of the combination valve. If no pressure deviation is detected, the method is either ended in step 413 or restarted. Upon detection of a pressure deviation, the value of the control signal for the valve actuator 34 is corrected by means of the regulator device 39 in step 411 such that the pressure in the pressure accumulator 20 again reaches the pressure setpoint and is adjusted to this.
  • the second precontrol value is corrected in step 410 taking into account the correction of the actuating signal by the control device 39. This can also be done here, for example, by taking over the output value of the control device 39 for the actuating signal in the adjusted state for the second precontrol value.
  • This corrected second pilot value for the control signal for switching from the pressure control mode to the volume flow control mode is stored in a memory device of the control device
  • the process is optionally terminated or restarted in step 413.

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  • 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)
  • Fuel-Injection Apparatus (AREA)

Abstract

Procédé de commande d'un dispositif d'alimentation en carburant d'un moteur à combustion interne (1), comportant un accumulateur de pression (20) pour le carburant, une soupape de commande de flux volumique (35) permettant de régler le flux volumique de carburant dans l'accumulateur de pression (20), et une soupape de commande de pression (23) permettant de régler la pression dans l'accumulateur de pression (20) à une valeur de consigne prédéfinie, le dispositif de régulation (39) pouvant fonctionner sélectivement dans un mode de commande de flux volumique dans lequel la pression dans l'accumulateur de pression (20) est régulée au moyen de la soupape de commande de flux volumique (35), ou dans un mode de commande de pression dans lequel la pression dans l'accumulateur de pression (20) est régulée au moyen de la soupape de commande de pression (23). Après passage d'un mode à l'autre, le dispositif de régulation (39) reste dans ce mode sur un intervalle de temps défini, un écart de la pression dans l'accumulateur de pression (20) par rapport à la valeur de pression de consigne, apparaissant au cours de cet intervalle, est détecté, et l'écart de pression détecté est pris en compte lors du prochain passage vers le même mode.
PCT/EP2008/050270 2007-01-24 2008-01-11 Procédé de régulation d'un dispositif d'alimentation en carburant d'un moteur à combustion interne WO2008090033A1 (fr)

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Application Number Priority Date Filing Date Title
DE102007003494 2007-01-24
DE102007003494.8 2007-01-24

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011000480A1 (fr) * 2009-07-02 2011-01-06 Mtu Friedrichshafen Gmbh Procédé de régulation de la pression de rampe dans un système d'injection à rampe commune de moteur à combustion interne
EP2273091A1 (fr) * 2009-06-22 2011-01-12 Honda Motor Co., Ltd. Système de contrôle d'injection de carburant pour un moteur à combustion interne et procédé de contrôle correspondant
WO2011082938A1 (fr) * 2010-01-08 2011-07-14 Continental Automotive Gmbh Dispositif destiné à empêcher le moteur de caler dans un véhicule équipé d'un système d'injection diesel

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DE19916100A1 (de) * 1999-04-09 2000-10-12 Bosch Gmbh Robert Verfahren und Vorrichtung zur Steuerung einer Brennkraftmaschine
WO2004104397A1 (fr) * 2003-05-26 2004-12-02 Siemens Aktiengesellschaft Procede pour faire fonctionner un moteur a combustion, systeme d'alimentation en carburant et soupape de regulation de debit volumetrique
EP1526268A2 (fr) * 2003-10-24 2005-04-27 Robert Bosch Gmbh Méthode de régulation de la pression d'un accumulateur de carburant dans un moteur à combustion interne
DE102004016724A1 (de) * 2004-04-05 2005-10-27 Siemens Ag Verfahren zum Überwachen einer Kraftstoffzuführeinrichtung einer Brennkraftmaschine
DE102004016943A1 (de) * 2004-04-06 2005-11-03 Siemens Ag Verfahren zum Steuern einer Kraftstoffzuführeinrichtung einer Brennkraftmaschine
DE102004039311A1 (de) * 2004-08-13 2006-02-23 Robert Bosch Gmbh Verfahren und Steuergerät zur Steuerung eines Enspritzdruckaufbaus bei einem Start eines Verbrennungsmotors

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Publication number Priority date Publication date Assignee Title
DE19916101A1 (de) * 1999-04-09 2000-10-12 Bosch Gmbh Robert Verfahren und Vorrichtung zur Steuerung einer Brennkraftmaschine
DE19916100A1 (de) * 1999-04-09 2000-10-12 Bosch Gmbh Robert Verfahren und Vorrichtung zur Steuerung einer Brennkraftmaschine
WO2004104397A1 (fr) * 2003-05-26 2004-12-02 Siemens Aktiengesellschaft Procede pour faire fonctionner un moteur a combustion, systeme d'alimentation en carburant et soupape de regulation de debit volumetrique
EP1526268A2 (fr) * 2003-10-24 2005-04-27 Robert Bosch Gmbh Méthode de régulation de la pression d'un accumulateur de carburant dans un moteur à combustion interne
DE102004016724A1 (de) * 2004-04-05 2005-10-27 Siemens Ag Verfahren zum Überwachen einer Kraftstoffzuführeinrichtung einer Brennkraftmaschine
DE102004016943A1 (de) * 2004-04-06 2005-11-03 Siemens Ag Verfahren zum Steuern einer Kraftstoffzuführeinrichtung einer Brennkraftmaschine
DE102004039311A1 (de) * 2004-08-13 2006-02-23 Robert Bosch Gmbh Verfahren und Steuergerät zur Steuerung eines Enspritzdruckaufbaus bei einem Start eines Verbrennungsmotors

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Publication number Priority date Publication date Assignee Title
EP2273091A1 (fr) * 2009-06-22 2011-01-12 Honda Motor Co., Ltd. Système de contrôle d'injection de carburant pour un moteur à combustion interne et procédé de contrôle correspondant
WO2011000480A1 (fr) * 2009-07-02 2011-01-06 Mtu Friedrichshafen Gmbh Procédé de régulation de la pression de rampe dans un système d'injection à rampe commune de moteur à combustion interne
US9624867B2 (en) 2009-07-02 2017-04-18 Mtu Friedrichshafen Gmbh Method for the closed-loop control of the rail pressure in a common-rail injection system of an internal combustion engine
WO2011082938A1 (fr) * 2010-01-08 2011-07-14 Continental Automotive Gmbh Dispositif destiné à empêcher le moteur de caler dans un véhicule équipé d'un système d'injection diesel

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