WO2010012571A1 - Verfahren zur steuerung einer hochdruck-kraftstoffpumpe - Google Patents
Verfahren zur steuerung einer hochdruck-kraftstoffpumpe Download PDFInfo
- Publication number
- WO2010012571A1 WO2010012571A1 PCT/EP2009/058605 EP2009058605W WO2010012571A1 WO 2010012571 A1 WO2010012571 A1 WO 2010012571A1 EP 2009058605 W EP2009058605 W EP 2009058605W WO 2010012571 A1 WO2010012571 A1 WO 2010012571A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- inlet valve
- self
- controlling
- phase position
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
-
- 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
- F02D41/04—Introducing corrections for particular operating conditions
- F02D41/06—Introducing corrections for particular operating conditions for engine starting or warming up
- F02D41/062—Introducing corrections for particular operating conditions for engine starting or warming up for starting
-
- 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
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
Definitions
- the invention relates to a method for controlling a high-pressure fuel pump, as it can be used, for example, in connection with common rail injection systems.
- Common rail injection systems are already known. These are injection systems for internal combustion engines in which a high-pressure pump brings the fuel to a high pressure level. The pressurized fuel fills a piping system, which is constantly under pressure during engine operation.
- Such a common rail injection system is known from DE 102006 023 470 Al.
- the system described therein includes a high pressure fuel pump for delivering fuel, a high pressure fuel accumulator connected to the high pressure fuel pump for storing fuel at an injection pressure to the environment of the common rail injection system, at least one injector connected to the high pressure fuel accumulator of fuel in at least one combustion chamber, a return line for returning fuel from the injector to the high pressure fuel pump at a return pressure to the environment of the common rail injection system, and an adjusting means for adjusting the return pressure.
- Another common rail injection system is known from DE 10 2006 026 928 Al.
- the system described therein includes a fuel tank, a high pressure fuel pump, a rail conduit, an accumulator, an injector, and a digital controller.
- a volume flow control valve is arranged, which is controlled by the digital control via a Volumenstromregelventilan Kunststofftechnisch becomes.
- the high-pressure fuel pump has at least one displacement unit. During operation of the injection system, it supplies an injection pressure in the rail line at the injector.
- the state of the art also includes phase-ganged pumps equipped with electrically actuated inlet valves, in which the inlet valve is open when de-energized.
- phasenanroughriche pumps are known in which the inlet valve is closed in the de-energized state.
- the inlet valve is held closed by a spring.
- such pumps are self-controlling by the spring design and the pressure conditions in front of and behind the inlet valve.
- a high-pressure pump such a pump is not very suitable, since said self-control in the event of a drive failure, which may be caused for example by the drop of a plug, undesirably leads to a full demand of the pump.
- phase-gapped pumps equipped with electrically operated inlet valves in which the valve is normally closed and the spring force is greater than the force of the pressure difference (pressure in front of and behind the valve)
- the pump can not pump without an electric actuation of the inlet valve.
- a start of the internal combustion engine ie after the presence of a start signal
- first a detection of the phase position of the plunger of the pump must be made in order to make a synchronization of the electrical control of the intake valve with the rotation of the crankshaft.
- the object of the invention is to show a way in which the disadvantages described above can be eliminated.
- a high-pressure fuel pump having an electrically controllable electromechanical, closed in the de-energized state and held by the force of a spring in the closed state intake valve, an outlet valve and a displacer, the inlet valve after the presence of a Startbekerses first in a self-controlling operating mode, during which a determination of the phase position of the displacer takes place, and switched after the determination of the phase position of the displacer to a non-self-controlling mode of the intake valve.
- the inlet valve is a function of the pressure difference between the in a
- Pressure difference is generated in an advantageous manner by a movement of the displacer or by the pressure produced by a prefeed pump.
- the inlet valve In order to bring the inlet valve into the self-controlling operating mode after the presence of a start command, the inlet valve is controlled by means of a force acting on an actuator such that the spring force holding the inlet valve in the closed state is compensated. This has the consequence that even comparatively small pressure differences are sufficient to bring the inlet valve from the closed to the open state and vice versa.
- a determination of the at the time of entering the Startbetationes still unknown phase position of the Verdrangers takes place. This is preferably done by an evaluation of the pressure profile occurring during the Verdrangerhus in the pressure build-up chamber of the high-pressure fuel pump. In this case, transitions of the pressure characteristic from an increasing course to a flat course and from a flat course to a rising course are detected in an advantageous manner.
- the inlet valve is electrically controlled in dependence on the phase position of the displacer.
- the inlet valve is open when the decanter moves down. If the displacer is moving upwards, the inlet valve is preferably closed and the outlet valve is opened.
- the high-pressure fuel pump calls for fuel as soon as the crankshaft rotates due to an operation of the starter.
- a recognition of the crankshaft angle already taking place at this time, ie the pump phase, is not necessary.
- a full claim is favored and consequently the fastest possible pressure build-up possible.
- This also applies in the case of non-recognition of the pump phase, since in this case, when a definable pressure threshold is exceeded, the activation of the inlet valve can take place in such a way that a fuel demand is prevented.
- the inventive method is particularly advantageous if the high-pressure fuel pump is installed in a ratio not equal to 1: 1 to the crankshaft. In this case, there would be an even greater delay in the build-up of pressure, since in this case the rail pressure behavior had to be measured and analyzed to detect the pump phase position, but there would be a pressure build-up only if the intake valve could be meaningfully activated, ie with suitable pump phase position.
- the pumping phase can be detected by analyzing the rail pressure build-up at the first start at the end of the production line through the auto-intake mode.
- a saddle point of the pressure buildup characteristic, d. H. a transition between a rising course and a flat course of the pressure characteristic, the top dead center of the pump piston movement equated.
- the determined phase position is stored and called as an adaptation value at each subsequent start.
- FIG. 1 a first sketch to explain a device for carrying out the method according to the invention
- FIG. 2 shows a second sketch to explain a device for carrying out the method according to the invention
- FIG. 3 shows a third sketch to explain a device for carrying out the method according to the invention.
- Figure 4 diagrams for explaining the detection of the phase position of the plunger.
- FIG. 1 shows a first sketch for explaining a device for carrying out the method according to the invention.
- the illustrated device has a control unit 9. This provides at its output a control signal s available, which is provided for driving a switch 8. As an input signal, in dependence of which the control unit 9 determines the control signal s, the control unit 9 receives information about the crankshaft angle ⁇ of the pump crankshaft.
- the switch 8 is preferably realized in the form of a field effect transistor. One terminal of the switch 8 is connected to ground. The ground remote terminal of the switch 8 is connected to an actuator coil 7. The ground remote terminal of the switch 8 is further connected via a Zener diode 10 to ground.
- the illustrated device has a high-pressure fuel pump 1.
- This is provided with an inlet valve 2, a low-pressure channel 3, a cylinder 4, an outlet valve 5 and a displacer 6.
- the displacer 6 is preferably a plunger.
- the inlet valve 2 is an electromechanical valve, which includes a closure element 2a, a spring 2b and an actuator 2c.
- the actuator 2c cooperates with the actuator coil 7 and is pressed at a current flow through the actuator coil 7 in Figure 1 to the right, so that the inlet valve 2 is open. If no current flows through the actuator coil 7, then the inlet valve 2 is in the closed state.
- the characteristic of the spring 2b and / or the spring preload is selected such that the inlet valve is held in the closed state in the absence of current flow through the actuator coil 7, regardless of the pressure conditions in the low pressure passage 3 and the pressure buildup chamber 4a of the high-pressure fuel pump 1.
- Der Input 3a of the low-pressure channel 3 is connected to a fuel tank, not shown, from which the high-pressure fuel pump via a prefeed pump fuel is supplied.
- the output 3b of the low-pressure channel 3 is connected, for example, to a pressure-limiting valve.
- the cylinder 4 has the pressure buildup chamber 4a and a high pressure chamber 4b. Between the pressure buildup chamber 4a and the high pressure chamber 4b, the exhaust valve 5 is arranged so that when the exhaust valve 5 is open, fuel is supplied from the pressure buildup chamber 4a to the high pressure chamber 4b.
- Within the pressure buildup chamber 4a of the plunger 6 is movably mounted. By moving the plunger 6 downward, the pressure in the pressure buildup chamber 4a is lowered. Upon movement of the plunger 6 upwards, i. in the conveying direction, the pressure in the pressure build-up chamber 4a is increased.
- the plunger 6 cooperates in a known manner with the pump crankshaft.
- the instantaneous position of the plunger 6, i. whose phase angle is described by the crankshaft angle ⁇ . Information about the instantaneous crankshaft angle is supplied to the control unit 9 as an input signal.
- the outlet valve 5 is a mechanical valve which has a closure element 5a and a spring 5b. This valve is opened when the pressure in the Pressure build-up chamber 4a of the cylinder 4 is greater than the sum of the closing force caused by the spring 5b of the exhaust valve 5 and the force caused by the pressure prevailing in the high-pressure chamber 4b, and closed again when the pressure in the pressure build-up chamber 4a becomes smaller again as the said sum.
- the inlet valve 2 is shown in the open state, said open state was passed from the control unit 9 by issuing the control signal s in the way.
- this opened state as indicated by the arrow drawn in the pressure buildup chamber 4a, fuel is conveyed from the low pressure passage 3 into the pressure buildup chamber 4a.
- the plunger 6 moves - as indicated by the arrow below the plunger 6 - down, so that the pressure in the pressure build-up chamber 4a is lowered and fuel is sucked from the low pressure passage in the pressure buildup chamber 4a.
- FIG. 2 shows a second sketch to explain a device according to the invention.
- the illustrated device differs from the device shown in FIG. 1 in that the inlet valve 2 is in the closed state and the outlet valve 5 is in the opened state. Furthermore, the plunger 6 is in its upward movement, ie in the conveying direction. This is illustrated in FIG. 2 by the arrow below the plunger 6. By the plunger 6 moving upward, the pressure in the pressure buildup chamber 4a is increased.
- the device described with reference to FIGS. 1 and 2 has the advantage that the inlet valve is not opened and closed in the sense of a self-control by the pressure conditions in the low-pressure channel 3 and the pressure build-up chamber 4 a, but exclusively by an electrical control which is triggered by the control unit 9 emanates.
- the control unit 9 opens and closes the inlet valve 2 in dependence on the instantaneous position of the plunger 6, i. depending on the pump crank angle. Within the limits of the maximum possible flow rate and of said pump crank angle, it can regulate the delivered fuel quantity as a function of the respectively existing requirements. In particular, it can change the start of delivery and the end of delivery by a suitable control of the switch 8 as a function of any existing requirements and thereby regulate the fuel delivery rate and the pressure in the system.
- the end of the suction of fuel from the low pressure passage 3 into the pressure buildup chamber 4 is brought about by the closing of the intake valve 2. Then, the pressure prevailing in the pressure build-up chamber pressure is increased so that it is greater than the sum of the caused by the spring 5b Closing force and the force caused by the pressure prevailing in the high pressure chamber 4b, the exhaust valve 5 is opened to print fuel from the pressure buildup chamber 4a into the high pressure chamber 4b.
- the intake valve is initially operated in a self-controlling mode after the presence of a Startbetrayses until the crankshaft angle ⁇ , d. H. the phase angle of the plunger 6, is determined. Only then does a changeover to a non-self-controlling operating mode of the intake valve take place, in which the intake valve, as described above, is actuated exclusively electrically and in dependence on the crankshaft angle.
- the intake valve is electrically controlled in such a way that the force by means of which the actuator 2c of the intake valve 2 works against the force of the spring 2b which keeps the intake valve 2 closed balances the force of the spring ,
- Figure 3 in which the force of the actuator with Fl and the force of the spring with F2 is designated.
- the electrical control described above has the consequence that after the presence of a Startbeineses the opening and closing of the intake valve 2 in dependence on the prevailing between the pressure in the low pressure passage 3 and the pressure in the pressure buildup chamber 4a pressure difference .DELTA.p. Is the Pressure in the low-pressure passage 3 larger than the pressure in the pressure build-up chamber 4a, then the inlet valve 2 is opened by this pressure difference.
- This above-mentioned pressure difference .DELTA.p can be brought about by printing the fuel from the fuel tank, not shown, with a higher pressure in the low-pressure duct caused by a not-yet-called forecasting pump.
- the said pressure difference ⁇ p can also be brought about by the plunger 6 moving downwards in the pressure buildup chamber 4a, as illustrated by the arrow shown in FIG. 1 below the plunger 6.
- FIG. 4 shows diagrams for explaining the detection of the phase position of the plunger 6, as first performed after the input of a start command.
- the time t is plotted along the ordinate of the build-up in the pressure buildup chamber 4a and the time t and along the abscissa in the lower diagram, the movement of the plunger 6 as a function of the piston angle.
- the pressure characteristic curve measured by means of a pressure sensor not shown initially has a linearly increasing area B1, then a transition U1 from the linearly rising area B1 into a flat area B2 and then again a transition U2 from the flat area B2 into one again has a linearly increasing region B3.
- the phase position of the plunger 6 and thus the crankshaft angle ⁇ can be detected.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/000,731 US9217406B2 (en) | 2008-08-01 | 2009-07-07 | Method for controlling a high-pressure fuel pump |
CN2009801243686A CN102076953B (zh) | 2008-08-01 | 2009-07-07 | 用于控制高压燃料泵的方法 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008036120.8 | 2008-08-01 | ||
DE102008036120A DE102008036120B4 (de) | 2008-08-01 | 2008-08-01 | Verfahren zur Steuerung einer Hochdruck-Kraftstoffpumpe |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2010012571A1 true WO2010012571A1 (de) | 2010-02-04 |
Family
ID=41046522
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2009/058605 WO2010012571A1 (de) | 2008-08-01 | 2009-07-07 | Verfahren zur steuerung einer hochdruck-kraftstoffpumpe |
Country Status (5)
Country | Link |
---|---|
US (1) | US9217406B2 (de) |
KR (1) | KR101266367B1 (de) |
CN (1) | CN102076953B (de) |
DE (1) | DE102008036120B4 (de) |
WO (1) | WO2010012571A1 (de) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8965667B2 (en) * | 2012-06-27 | 2015-02-24 | GM Global Technology Operations LLC | Engine startup method |
DE102012218370B4 (de) * | 2012-10-09 | 2015-04-02 | Continental Automotive Gmbh | Verfahren und Vorrichtung zum Steuern eines Ventils |
DE102015218258B4 (de) * | 2015-09-23 | 2017-08-24 | Continental Automotive Gmbh | Verfahren zur Raildruckregelung eines Einspritzsystems |
FR3043141B1 (fr) * | 2015-10-29 | 2017-11-03 | Continental Automotive France | Procede de verification de la fonctionnalite d'un systeme d'alimentation en carburant haute pression d'un moteur a combustion interne |
DE102016204410A1 (de) * | 2016-03-17 | 2017-09-21 | Robert Bosch Gmbh | Verfahren zum Ermitteln eines Sollwertes für eine Stellgröße zur Ansteuerung einer Niederdruckpumpe |
Citations (6)
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EP1249599A2 (de) * | 2001-04-12 | 2002-10-16 | Toyota Jidosha Kabushiki Kaisha | Hochdruckkraftstoffversorgungssystem für Brennkraftmaschine |
US20040000289A1 (en) * | 2002-06-28 | 2004-01-01 | Hiromitsu Seo | High pressure fuel supplying apparatus for internal combustion engine and method for controlling the apparatus |
EP1541838A2 (de) * | 2003-12-12 | 2005-06-15 | Hitachi, Ltd. | Steuervorrichtung für die Hochdruckkraftstoffpumpe von einem Verbrennungsmotor |
DE10360332A1 (de) * | 2003-12-20 | 2005-07-21 | Robert Bosch Gmbh | Verfahren und Vorrichtung zum Bestimmen eines Förderintervalls einer Hochdruckpumpe |
US20050211224A1 (en) * | 2004-03-26 | 2005-09-29 | Denso Corporation | Fuel supply system of internal combustion engine |
FR2878291A1 (fr) * | 2004-11-24 | 2006-05-26 | Bosch Gmbh Robert | Procede de gestion d'une pompe a carburant ainsi que programme de mise en oeuvre, appareil de commande et de regulation pour la mise en oeuvre dans un moteur a combustion interne |
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DE4321127A1 (de) | 1993-06-25 | 1995-01-05 | Bosch Gmbh Robert | Vorrichtung zur Ansteuerung eines elektromagnetischen Verbrauchers |
DE69720603T2 (de) * | 1996-07-05 | 2004-03-04 | Nippon Soken, Inc., Nishio | Hochdruckpumpe |
DE19644915A1 (de) * | 1996-10-29 | 1998-04-30 | Bosch Gmbh Robert | Hochdruckpumpe |
US6694950B2 (en) * | 1999-02-17 | 2004-02-24 | Stanadyne Corporation | Hybrid control method for fuel pump using intermittent recirculation at low and high engine speeds |
JP2001041128A (ja) * | 1999-07-28 | 2001-02-13 | Toyota Motor Corp | 高圧燃料ポンプ |
JP2002115623A (ja) * | 2000-10-05 | 2002-04-19 | Mitsubishi Electric Corp | 可変吐出量燃料供給装置 |
JP4627603B2 (ja) * | 2001-03-15 | 2011-02-09 | 日立オートモティブシステムズ株式会社 | 燃料供給装置 |
AU2002335725A1 (en) * | 2001-09-10 | 2003-03-24 | Stanadyne Corporation | Hybrid demand control for hydraulic pump |
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DE10162989C1 (de) | 2001-12-20 | 2003-10-09 | Siemens Ag | Schaltungsanordnung zum Regeln einer regelbaren Kraftstoffpumpe, Verfahren zum Regeln einer Förderleistung und Verfahren zum Überprüfen der Funktionsfähigkeit einer regelbaren Kraftstoffpumpe |
ITBO20020498A1 (it) * | 2002-07-30 | 2004-01-30 | Magneti Marelli Powertrain Spa | Impianto di iniezione di carburante di tipo common rail con pompa a portata variabile |
JP4110065B2 (ja) * | 2003-09-01 | 2008-07-02 | 三菱電機株式会社 | 内燃機関の燃料供給制御装置 |
ITBO20040322A1 (it) * | 2004-05-20 | 2004-08-20 | Magneti Marelli Powertrain Spa | Metodo ed impianto per l'iniezione diretta di carburante in un motore a combustione interna |
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-
2008
- 2008-08-01 DE DE102008036120A patent/DE102008036120B4/de not_active Expired - Fee Related
-
2009
- 2009-07-07 CN CN2009801243686A patent/CN102076953B/zh not_active Expired - Fee Related
- 2009-07-07 US US13/000,731 patent/US9217406B2/en not_active Expired - Fee Related
- 2009-07-07 KR KR1020107029425A patent/KR101266367B1/ko active IP Right Grant
- 2009-07-07 WO PCT/EP2009/058605 patent/WO2010012571A1/de active Application Filing
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
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EP1249599A2 (de) * | 2001-04-12 | 2002-10-16 | Toyota Jidosha Kabushiki Kaisha | Hochdruckkraftstoffversorgungssystem für Brennkraftmaschine |
US20040000289A1 (en) * | 2002-06-28 | 2004-01-01 | Hiromitsu Seo | High pressure fuel supplying apparatus for internal combustion engine and method for controlling the apparatus |
EP1541838A2 (de) * | 2003-12-12 | 2005-06-15 | Hitachi, Ltd. | Steuervorrichtung für die Hochdruckkraftstoffpumpe von einem Verbrennungsmotor |
DE10360332A1 (de) * | 2003-12-20 | 2005-07-21 | Robert Bosch Gmbh | Verfahren und Vorrichtung zum Bestimmen eines Förderintervalls einer Hochdruckpumpe |
US20050211224A1 (en) * | 2004-03-26 | 2005-09-29 | Denso Corporation | Fuel supply system of internal combustion engine |
FR2878291A1 (fr) * | 2004-11-24 | 2006-05-26 | Bosch Gmbh Robert | Procede de gestion d'une pompe a carburant ainsi que programme de mise en oeuvre, appareil de commande et de regulation pour la mise en oeuvre dans un moteur a combustion interne |
Also Published As
Publication number | Publication date |
---|---|
US20110116938A1 (en) | 2011-05-19 |
KR20110010825A (ko) | 2011-02-07 |
CN102076953B (zh) | 2013-07-31 |
US9217406B2 (en) | 2015-12-22 |
KR101266367B1 (ko) | 2013-05-22 |
DE102008036120B4 (de) | 2010-04-08 |
CN102076953A (zh) | 2011-05-25 |
DE102008036120A1 (de) | 2010-02-18 |
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