EP1519026B1 - Méthode et dispositif de commande d'une soupape et méthode et dispositif de commande d'une pompe-injecteur avec soupape - Google Patents

Méthode et dispositif de commande d'une soupape et méthode et dispositif de commande d'une pompe-injecteur avec soupape Download PDF

Info

Publication number
EP1519026B1
EP1519026B1 EP20040022133 EP04022133A EP1519026B1 EP 1519026 B1 EP1519026 B1 EP 1519026B1 EP 20040022133 EP20040022133 EP 20040022133 EP 04022133 A EP04022133 A EP 04022133A EP 1519026 B1 EP1519026 B1 EP 1519026B1
Authority
EP
European Patent Office
Prior art keywords
valve
time
valve seat
signal
seat
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.)
Expired - Lifetime
Application number
EP20040022133
Other languages
German (de)
English (en)
Other versions
EP1519026A3 (fr
EP1519026A2 (fr
Inventor
Jörg Dr. Beilharz
Maximilian Dr. Kronberger
Richard Pirkl
Christian Rissler
Hans-Jörg Wiehoff
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.)
Continental Automotive GmbH
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 EP1519026A2 publication Critical patent/EP1519026A2/fr
Publication of EP1519026A3 publication Critical patent/EP1519026A3/fr
Application granted granted Critical
Publication of EP1519026B1 publication Critical patent/EP1519026B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • F02D41/2096—Output circuits, e.g. for controlling currents in command coils for controlling piezoelectric injectors
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • 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
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • F02D2041/202—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit
    • F02D2041/2055—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit with means for determining actual opening or closing time
    • 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
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • F02D2041/202—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit
    • F02D2041/2065—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit the control being related to the coil temperature

Definitions

  • the invention relates to a method and a device for controlling a valve. It further relates to a method and apparatus for controlling a pump-nozzle device with a valve.
  • the valve has a valve drive, which is designed as a piezoelectric actuator, a valve member, a valve body and a valve seat.
  • a pump-nozzle device is used in particular for supplying fuel into a combustion chamber of a cylinder of an internal combustion engine, in particular a diesel internal combustion engine.
  • a pump, a control unit with the valve and a nozzle unit form a structural unit.
  • the drive of a piston of the pump is preferably via a camshaft of an internal combustion engine by means of a rocker arm.
  • the pump can be hydraulically coupled via the valve to a low-pressure fuel supply device. It is hydraulically coupled on the output side with the nozzle unit. Start of injection and injection quantity are determined by the valve and its valve drive. Due to the compact design of the pump-nozzle device results in a very low volume of high pressure and high hydraulic stiffness. This enables very high injection pressures of around 2,000 bar. This high injection pressure in conjunction with the good controllability of the start of injection and the injection quantity allow a significant reduction in emissions while low fuel consumption when using the internal combustion engines.
  • a pump-nozzle device is known with a pump and a valve with a valve member, the hydraulic coupling of a Ab horrraums with a Flow channel controls.
  • the drainage channel is hydraulically coupled to the pump and a nozzle unit.
  • An inlet channel is provided, which is hydraulically coupled to the Ab horrraum.
  • the valve member is associated with a piezoelectric valve drive, via which the valve member can be adjusted between two end positions. In a first end position of the valve member of the flow channel is hydraulically coupled to a Ab tenuraum and this in turn with the inlet channel. In a second end position of the valve member of the drainage channel is hydraulically decoupled from the Abberichtraum and the valve member is in a valve seat of the valve.
  • the end of injection is determined by controlling the valve member to its first end position by means of the actuator and thus allowing fluid to flow back into the discharge chamber and the inlet channel via the discharge channel, with the result that the pressure in the pump and thus also in the nozzle unit decreases, which in turn leads to a closing of the nozzle unit.
  • a precise metering of fuel through the pump-nozzle device requires a very precise controllability of the valve.
  • a valve is known with an actuator driven by a piezoelectric actuator.
  • the piezoelectric actuator is used simultaneously as a pressure sensor.
  • the voltage of the piezoelectric actuator is evaluated so that a voltage change occurs and this is detected as a detection signal.
  • Information about the time at which the valve member actually lifts off its valve seat and the pressure in a control chamber begins to decrease is derived from the detection signal.
  • the invention is characterized by a method for controlling a valve with a valve drive, which is designed as a piezoelectric actuator, a valve member, a valve body and a valve seat.
  • a valve drive which is designed as a piezoelectric actuator, a valve member, a valve body and a valve seat.
  • the valve member is controlled from a position away from the valve seat into the valve seat.
  • a signal characterizing the piezo voltage is detected.
  • At least the first derivative of the signal characterizing the piezoelectric voltage is then determined.
  • the time of impact of the valve member on the valve seat is detected when the at least first derivative of the signal exceeds a predetermined threshold.
  • a closing time is determined depending on the predefinable time and the time of impact.
  • the actuation of the valve drive then takes place depending on the closing time.
  • the valve of a pump-nozzle device is controlled accordingly.
  • the pump-nozzle apparatus has a pump having a piston and a working space, a control unit including a drain channel hydraulically coupled to the working space, and a valve having a valve actuator configured as a piezoactuator, a valve member, a valve body a valve seat and a spillway which is hydraulically decoupled from the drain passage when the valve member abuts the valve seat and which is otherwise coupled to the drain passage.
  • piezoelectric voltage such as the capacitance of the piezoelectric actuator or the current applied to the piezoactuator, or the charge of the piezoactuator or the electrical energy of the piezoactuator piezoelectric actuator.
  • the at least first derivative of the signal is monitored only within a predetermined time window to an expected time of impact on exceeding the predetermined threshold. This has the advantage of less computational effort and at the same time a lower probability a misjudgment of the time of impact due to noise.
  • the piezoelectric voltage characterizing signal is squared and then determined at least the first derivative of the squared signal. This is based on the knowledge that the signal characterizing the piezoelectric voltage has a substantially root-shaped profile and that, thus, the signal can be linearized by squaring and a higher signal-to-noise ratio can be easily achieved.
  • the second derivative of the squared signal is determined. This has the advantage that the characteristic kink of the original signal can then be recognized particularly well and easily.
  • the closing time period is determined several times and subjected to filtering. This has the advantage that such a very reliable value of the closing period can be determined.
  • a drive time of the valve drive depends on the closing time period and a set value of the closing time period corrected.
  • the predeterminable time at which the valve member is controlled from a position away from the valve seat into the valve seat is selected so that the piston of the pump in its Top dead center is and remains until the expected impact of the valve member on the valve seat.
  • the pump-nozzle device ( FIG. 1 ) comprises a pump unit, a control unit and a nozzle unit.
  • the pump-nozzle device is preferably used for supplying fuel into the combustion chamber of a cylinder of an internal combustion engine.
  • the internal combustion engine is preferably designed as a diesel engine.
  • the internal combustion engine has an intake tract for intake of air, which can be coupled by means of gas inlet valves with cylinders.
  • the internal combustion engine also has an exhaust tract, which discharges the gases to be discharged from the cylinders via the outlet valve.
  • the cylinders are each assigned pistons, which are each coupled via a connecting rod with a crankshaft.
  • the crankshaft is coupled to a camshaft.
  • the pump unit comprises a piston 11, a pump body 12, a working space 13 and a pump return means 14, which is preferably designed as a spring.
  • the piston 11 is coupled in the installed state in an internal combustion engine with a camshaft 16, preferably by means of a rocker arm, and is driven by this.
  • the piston 11 is guided in a recess of the pump body 12 and determined depending on its position, the volume of the working space 13.
  • the pump return means 14 is formed and arranged so that the limited volume of the piston 11 through the working space 13 has a maximum value when acting on the piston 11 no external forces, ie forces that are transmitted via the coupling with the camshaft 16.
  • the nozzle needle 53 abuts a needle seat 54 and thus closes a nozzle 56, which is provided for supplying the fuel into the combustion chamber of the cylinder of the internal combustion engine.
  • the nozzle unit is preferably, as shown, formed as an inwardly opening nozzle unit.
  • the nozzle needle 53 is slightly spaced from the needle seat 54 toward the nozzle return means 52, thus releasing the nozzle 56.
  • fuel is metered into the combustion chamber of the cylinder of the internal combustion engine.
  • the first or second state is assumed depending on a balance of forces from the force acting on the nozzle needle 53 by the nozzle return means 52 and the counteracting force which is caused by the hydraulic pressure in the region of the needle heel 57.
  • the control unit comprises an inlet channel 21 and an outlet channel 22.
  • the inlet channel 21 and the outlet channel 22 can be hydraulically coupled by means of a valve.
  • the inlet channel 21 is guided from a low-pressure side connection of the pump-nozzle device to the valve.
  • the drain passage 22 is hydraulically coupled to the working space 13 and is guided to the needle heel 57 and is hydraulically with the Nozzle 56 can be coupled depending on the condition occupied by the nozzle needle 53.
  • the valve comprises a valve member 231, which is preferably designed as a so-called.
  • a valve d. H. it opens outward against the flow direction of the fluid.
  • the valve further comprises a Abêtraum 232 which is hydraulically coupled to the inlet channel 21 and by means of the valve member 231 with a high-pressure chamber is hydraulically coupled.
  • the high-pressure chamber is hydraulically coupled to the drainage channel 22.
  • valve return means is provided, which is arranged and formed so that it the valve member 231 in an open position, d. H. spaced apart from the valve seat 234 when the forces acting on the valve member by an actuator 24 are less than the forces acting on the valve member 231 by the valve return means.
  • the actuator 24 is formed as a piezo stack.
  • a device 60 for controlling the pump-nozzle device is provided, which generates corresponding actuating signals for the valve.
  • valve member 231 In the open position of the valve member 231 is sucked in a movement of the piston 11, which is directed upward, ie in the direction away from the nozzle 56, fuel via the inlet channel 21 to the working space 13. As long as the valve member 231 during a subsequent downward movement of the piston 11, ie in a directed towards the nozzle 56 movement, is still in its open position, located in the working chamber 13 and the drain passage 22 fuel through the valve back into the Ab bruiseraum 232 and possibly pushed back into the inlet channel 21.
  • valve member 231 when the valve member 231 is controlled in its closed position during the downward movement of the piston 11, the fuel in the working chamber 13 and thus in the flow passage 22 and in the high-pressure chamber 233 is compressed, whereby the pressure with increasing downward movement of the piston 11 in the Working space 13, in the high-pressure chamber 233 and in the drain passage 22 increases.
  • the force caused by the hydraulic pressure increases, which acts on the needle shoulder 57 in the direction of an opening movement of the nozzle needle 53 to release the nozzle 56.
  • the nozzle needle 53 moves away from the needle seat 54, thus giving the nozzle 56 for the fuel supply to the cylinder of the internal combustion engine free.
  • the nozzle needle 53 then moves back into the needle seat 54 and thus closes the nozzle 56 when the hydraulic pressure in the drain passage 22 falls below the value at which the force caused by the hydraulic pressure at the needle heel 57 is smaller than that caused by the nozzle return means 52 Force.
  • the time at which this value is exceeded and at which thus the fuel metering is terminated, can be influenced by the control of the valve member 231 from its closed position to an open position.
  • the valve member By controlling the valve member from its closed position to its open position, the hydraulic coupling between the high-pressure chamber and the Abêtraum 232 and the inlet channel 21 produced. Due to the high pressure difference prevailing during opening between the fluid in the high-pressure space and the outlet channel 22 and the fluid in the discharge space 232 and the inlet channel 21, the fuel then flows from the high-pressure space into the discharge space 232 at very high speed, generally at the speed of sound and further into the inlet channel 21. As a result, the pressure in the high-pressure chamber and the outlet channel 22 is then rapidly reduced so much that the forces acting on the nozzle needle 53 by the nozzle return means 52 cause the nozzle needle 53 to move into the needle seat 54 and Thus then the nozzle 56 closes.
  • the valve member is controlled from a position away from the valve seat 234 into the valve seat 234.
  • the predetermined time is preferably chosen so that the piston is in its top dead center and remains until the expected impact of the valve member 231 on the valve seat 234. However, it can also be selected within a time range in which the piston is not in its upper Dead center is located.
  • the piezo voltage V_INJ which can assume values up to approximately 150 V, is transformed by means of a voltage divider into a predetermined voltage range and optionally subsequently filtered. Subsequently, an analog-to-digital conversion of the signal takes place by means of a so-called sample-and-hold analog-to-digital converter with a very short sampling time of a few ⁇ sec.
  • the digital voltage values thus obtained are preferably temporarily stored and processed further only after an expected impingement of the valve member 231 on its valve seat 234. Due to the known sampling rate of the analog-to-digital converter, a time assignment of the individual sampled values is then also possible.
  • the sampled piezo voltage V_INJ is still preferably interpolated, whereby a higher temporal resolution of the signal curve of the piezo voltage V_INJ can be achieved. This is preferably done by means of a finite impulse response (FIR) filter.
  • FIR finite impulse response
  • the piezo voltage V_INJ is squared. This corresponds to a linearization of the course of the piezoelectric voltage V_INJ, since this has a substantially root-shaped course. Alternatively, however, can be dispensed with the squaring, which is indicated by the dashed arrow.
  • a block B7 the first derivative of the signal curve of the piezo voltage V_INJ is then determined. There is thus a differentiation according to the time.
  • a second derivative of the signal curve of the piezo voltage V_INJ can be determined.
  • a block B11 only the values of the derived piezo voltage V_INJ are selected, which were detected within a predetermined time window by the expected time of impact of the valve member 231 on the valve seat 234.
  • the time window is preferably predetermined so that all known variations of the closing time period are taken into account.
  • a block B15 it is then made plausible whether the closing time period T_CL is less than a predetermined second threshold value or greater than a predetermined third threshold value SW3.
  • the second and third thresholds SW2, SW3 are selected so that falling below or exceeding is possible only in the case of a fault of the valve. Accordingly, a failure of the valve in block B15 is then diagnosed.
  • a first correction value T_CL_COR1 is determined as a function of a temperature TEMP which is characteristic for the temperature of the valve drive 24 and thus of the piezoactuator and an energy E supplied to the valve drive 24 and dependent on a setpoint value T_CL_SP of the closing time duration.
  • the first correction value T_CL_COR1 is an estimated value of the change of the closing time duration depending on the temperature TEMP and the supplied electric energy E.
  • the closing time period T_CL_SP is preferably given for predetermined operating conditions, ie for a predetermined temperature TEMP and supplied electric energy E. Er preferably determined for the prevailing during operation of the valve drive 24 in the average temperature TEMP and the electrical energy supplied to it on average.
  • the block B19 accordingly contains a corresponding model, by means of which the first correction value T_CL_COR1 is then determined.
  • a correction value T_SOI_OFS for the activation time T_SOI is then determined, preferably by forming the sum of the first and second correction values T_CL_COR1, T_CL_COR2.
  • a block B25 then becomes dependent on the correction value T_SOI_OFS for the drive time T_SOI and a requested time at which the valve member 231 on its valve seat 234, the triggering time T_SOI determined.
  • FIGS. 4a to 4d show gradients plotted over time t.
  • FIG. 4a shows the time course of the squared piezo voltage V_INJ.
  • FIG. 4b shows the stroke CTRL_VL of the valve member 231.
  • Figure 4c shows the course of the pressure P_H in the working space 13 of the pump.
  • FIG. 4d shows the time course of the metered with the pump-nozzle device amount of fuel MFF.
  • T_SOI the valve drive 24 is subjected to voltage, the piezo voltage V_INJ.
  • the valve member 231 impinges on the valve seat 234.
  • the slope of the substantially linear curve of the squared piezo voltage V_INJ then increases suddenly at the instant t1.
  • the pressure P_H in the working space 13 of the pump begins to increase from time t1.
  • time t2 the pressure required to open the nozzle needle 53 is reached and the injection process begins.
  • the determination of the closing period takes place during a period during which the piston 11 is in its upper dead center. This then has the consequence that the course of the pressure P_H in the working space 13 is substantially constant, namely at low pressure level with the result that the metered amount of fuel MFF according to Figure 4c is zero.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)

Claims (12)

  1. Procédé de commande d'une soupape, comprenant un entraînement de soupape (24), qui se présente sous la forme d'un actionneur piézoélectrique, un élément de soupape (231), un corps de soupape (237) et un siège de soupape (234), dans lequel,
    - à un moment prédéfinissable, l'élément de soupape (231) est commandé d'une position éloignée du siège de soupape (234) dans le siège de soupape (234),
    - tandis que l'élément de soupape (231) est commandé de la position éloignée du siège de soupape (234) dans le siège de soupape (234), un signal caractérisant la tension piézoélectrique (V_INJ) est enregistré,
    - le signal caractérisant la tension piézoélectrique (V_INJ) est élevé au carré et la au moins une première dérivée temporelle du signal au carré est ensuite déterminée,
    - le moment de positionnement de l'élément de soupape (231) sur le siège de soupape (234) est détecté si la au moins une première dérivée temporelle du signal au carré dépasse une première valeur de seuil prédéfinie (SW1),
    - une durée de fermeture (T_CL) est déterminée en fonction du moment prédéfinissable et du moment de positionnement, et
    - la commande de l'entraînement de soupape (24) s'effectue ensuite en fonction de la durée de fermeture (T_CL).
  2. Procédé selon la revendication 1,
    caractérisé en ce que
    la au moins une première dérivée temporelle du signal n'est contrôlée concernant le dépassement de la première valeur de seuil prédéfinie (SW1) qu'à l'intérieur d'une fenêtre temporelle prédéfinie, à un moment escompté du positionnement de l'élément de soupape (231) sur le siège de soupape (234).
  3. Procédé selon la revendication 1 ou 2,
    caractérisé en ce que
    la deuxième dérivée temporelle du signal au carré est déterminée.
  4. Procédé selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le moment du positionnement de l'élément de soupape (231) sur le siège de soupape (234) est détecté lors du premier dépassement de la première valeur de seuil (SW1).
  5. Procédé selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    la durée de fermeture (T_CL) est déterminée à plusieurs reprises et soumise à un filtrage.
  6. Procédé selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    une erreur est détectée dans la soupape lorsque la durée de fermeture est inférieure à une deuxième valeur de seuil (SW2) ou supérieure à une troisième valeur de seuil (SW3).
  7. Procédé selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    un moment de commande (T_SOI) est déterminé en fonction de la durée de fermeture (T_CL) et d'une valeur théorique (T_CL_SP) de la durée de fermeture.
  8. Procédé selon la revendication 7,
    caractérisé en ce que
    le moment de commande (T_SOI) est en outre déterminé en fonction d'une température (TEMP), qui est caractéristique de la température de la soupape, et d'une énergie électrique (E) appliquée à l'entraînement de soupape (24).
  9. Procédé de commande d'un dispositif à pompe et injecteur, comprenant :
    - une pompe qui a un piston (11) et un espace de travail (13),
    - une unité de commande, qui comprend un canal d'évacuation (22), qui est couplé par voie hydraulique à l'espace de travail (13), et une soupape, avec un entraînement de soupape (24) se présentant sous la forme d'un actionneur piézoélectrique, un élément de soupape (231), un corps de soupape (237), un siège de soupape (234) et un espace de déversement (232), qui est désaccouplé par voie hydraulique du canal d'évacuation (22), lorsque l'élément de soupape (231) est appliqué sur le siège de soupape (234), et qui est couplé autrement par voie hydraulique au canal d'évacuation (22),
    - dans lequel la soupape est commandée par un procédé selon l'une quelconque des revendications précédentes.
  10. Procédé selon la revendication 9,
    caractérisé en ce que
    le moment prédéfinissable est choisi de sorte que le piston (11) soit à son point mort haut et y reste jusqu'au positionnement escompté de l'élément de soupape (231) sur le siège de soupape (234).
  11. Dispositif de commande d'une soupape avec un entraînement de soupape (24), qui se présente sous la forme d'un actionneur piézoélectrique, un élément de soupape (231), un corps de soupape (237) et un siège de soupape (234), qui présente des moyens
    - qui commandent, à un moment prédéfinissable, l'élément de soupape (231) d'une position éloignée du siège de soupape (234) dans le siège de soupape (234),
    - qui, tandis que l'élément de soupape (231) est commandé de la position éloignée du siège de soupape (234) dans le siège de soupape (234), enregistrent un signal caractérisant la tension piézoélectrique (V_INJ),
    - qui élèvent au carré le signal caractérisant la tension piézoélectrique (V_INJ) et déterminent ensuite la au moins une première dérivée temporelle du signal au carré,
    - qui déterminent le moment du positionnement de l'élément de soupape (231) sur le siège de soupape (234), lorsque la au moins une première dérivée temporelle du signal au carré dépasse une première valeur de seuil prédéfinie (SW1),
    - qui déterminent une durée de fermeture (T_CL) en fonction du moment prédéfinissable et du moment de positionnement, et
    - qui commandent ensuite l'entraînement de soupape (24) en fonction de la durée de fermeture (T CL).
  12. Dispositif de commande d'un dispositif à pompe et injecteur, comprenant :
    - une pompe qui a un piston (11) et un espace de travail (13),
    - une unité de commande qui comprend un canal d'évacuation (22), qui est couplé par voie hydraulique à l'espace de travail (13), et une soupape avec un entraînement de soupape (24) se présentant sous la forme d'un actionneur piézoélectrique, un élément de soupape (231), un corps de soupape (237), un siège de soupape (234) et un espace de déversement (232), qui est désaccouplé par voie hydraulique du canal d'évacuation (22), lorsque l'élément de soupape (231) est appliqué sur le siège de soupape (234), et qui est couplé autrement par voie hydraulique au canal d'évacuation (22),
    - avec le dispositif de commande d'une soupape selon la revendication 11.
EP20040022133 2003-09-29 2004-09-17 Méthode et dispositif de commande d'une soupape et méthode et dispositif de commande d'une pompe-injecteur avec soupape Expired - Lifetime EP1519026B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10345226 2003-09-29
DE2003145226 DE10345226B4 (de) 2003-09-29 2003-09-29 Verfahren und Vorrichtung zum Steuern eines Ventils und Verfahren und Vorrichtung zum Steuern einer Pumpe-Düse-Vorrichtung mit einem Ventil

Publications (3)

Publication Number Publication Date
EP1519026A2 EP1519026A2 (fr) 2005-03-30
EP1519026A3 EP1519026A3 (fr) 2006-10-25
EP1519026B1 true EP1519026B1 (fr) 2010-12-29

Family

ID=34178011

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20040022133 Expired - Lifetime EP1519026B1 (fr) 2003-09-29 2004-09-17 Méthode et dispositif de commande d'une soupape et méthode et dispositif de commande d'une pompe-injecteur avec soupape

Country Status (2)

Country Link
EP (1) EP1519026B1 (fr)
DE (2) DE10345226B4 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005032087A1 (de) * 2005-07-08 2007-01-18 Siemens Ag Verfahren und Vorrichtung zum Steuern eines Einspritzventils
DE102006048979B8 (de) 2006-10-17 2017-02-23 Continental Automotive Gmbh Verfahren und Einspritzsystem zum Einspritzen eines Fluids
DE102006058742A1 (de) 2006-12-12 2008-06-19 Robert Bosch Gmbh Verfahren zum Betreiben eines Kraftstoffeinspritzventils
DE102008041527A1 (de) * 2008-08-25 2010-03-04 Robert Bosch Gmbh Verfahren zum Betreiben einer Kraftstoffeinspritzvorrichtung einer Brennkraftmaschine
DE102009003215A1 (de) * 2009-05-19 2010-11-25 Robert Bosch Gmbh Verfahren und Steuergerät zum Betreiben eines Einspritzventils
DE102009003212A1 (de) * 2009-05-19 2010-11-25 Robert Bosch Gmbh Verfahren und Steuergerät zum Betreiben eines Einspritzventils
DE102011075750B4 (de) * 2011-05-12 2021-02-11 Vitesco Technologies GmbH Verfahren zum Ermitteln einer Position eines Verschlusselements eines Einspritzventils für eine Brennkraftmaschine
DE102011082455B4 (de) 2011-09-09 2014-02-13 Continental Automotive Gmbh Verfahren zum Überwachen einer Einspritzmenge eines Fluids sowie Einspritzsystem zum Einspritzen einer Einspritzmenge eines Fluids
DE102012204278A1 (de) * 2012-03-19 2013-09-19 Continental Automotive Gmbh Verfahren zum Betreiben eines Kraftstoffeinspritzsystems und Kraftstoffeinspritzsystem mit Einspritzventil mit Regelung der Bewegung des Verschlusselementes
US9074552B2 (en) 2012-06-27 2015-07-07 GM Global Technology Operations LLC Fuel injector closing timing adjustment systems and methods
US9683510B2 (en) * 2014-04-01 2017-06-20 GM Global Technology Operations LLC System and method for improving fuel delivery accuracy by learning and compensating for fuel injector characteristics
DE102015219333B3 (de) * 2015-10-07 2016-12-15 Continental Automotive Gmbh Verfahren zur Detektion eines Nutzsignales
DE102019110711A1 (de) * 2019-04-25 2020-10-29 Schaeffler Technologies AG & Co. KG Ansteuerverfahren für ein Hydrauliksystem mit einer Pumpe und Ventilen zum Versorgen mehrerer Verbraucher sowie einer Kühl- und/oder Schmiereinrichtung; und Hydrauliksystem

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2805175A1 (de) * 1978-02-08 1979-08-09 Bosch Gmbh Robert Einrichtung zum erfassen des spritzbeginns eines einspritzventils
DE3118425A1 (de) * 1981-05-09 1982-12-09 Robert Bosch Gmbh, 7000 Stuttgart Einrichtung zum erfassen der den brennraeumen eines dieselmotors zugefuehrten kraftstoffmenge
BR9906558A (pt) * 1998-06-25 2000-08-15 Siemens Ag Processo e dispositivo para o comando de um atuador capacitivo
DE19835494C2 (de) * 1998-08-06 2000-06-21 Bosch Gmbh Robert Pumpe-Düse-Einheit
DE19930309C2 (de) * 1999-07-01 2001-12-06 Siemens Ag Verfahren und Vorrichtung zur Regelung der Einspritzmenge bei einem Kraftstoffeinspritzventil mit Piezoelement-Aktor
DE10024662B4 (de) * 2000-05-18 2005-12-15 Siemens Ag Verfahren zum Betreiben eines Einspritzventils
EP1172541B1 (fr) * 2000-07-01 2005-03-23 Robert Bosch GmbH Actionneur piézo-électrique pour système d'injection
DE10143501C1 (de) * 2001-09-05 2003-05-28 Siemens Ag Verfahren zum Ansteuern eines piezobetriebenen Kraftstoff-Einspritzventils
DE10146747A1 (de) * 2001-09-22 2003-04-10 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
EP1442206B1 (fr) * 2001-11-09 2005-04-13 Volkswagen Mechatronic GmbH & Co. Systeme d'injection pour moteur a combustion interne et procede de fonctionnement associe

Also Published As

Publication number Publication date
EP1519026A3 (fr) 2006-10-25
DE10345226B4 (de) 2006-04-06
DE10345226A1 (de) 2005-05-12
DE502004012047D1 (de) 2011-02-10
EP1519026A2 (fr) 2005-03-30

Similar Documents

Publication Publication Date Title
EP1519026B1 (fr) Méthode et dispositif de commande d'une soupape et méthode et dispositif de commande d'une pompe-injecteur avec soupape
DE102010021169B4 (de) Verfahren und Vorrichtung zur Ermittlung des tatsächlichen Einspritzbeginns eines Piezo-Kraftstoff-Einspritzventils
EP1488088B1 (fr) Procede et dispositif de detection du moment d'impact du pointeau d'une soupape de commande piezoelectrique
EP1836386B1 (fr) Procede et dispositif de commande d'un injecteur
DE102011075732A1 (de) Regelverfahren für ein Einspritzventil und Einspritzsystem
WO2012150298A1 (fr) Procédé et dispositif de commande d'une soupape
DE102005050338A1 (de) Verfahren zum Überprüfen eines Ventils
WO2006069750A1 (fr) Procede et dispositif de compensation des effets de rebond dans un systeme d'injection a commande piezo-electrique d'un moteur a combustion interne
EP1704316B1 (fr) Procede et dispositif pour reguler une soupape et procede et dispositif pour reguler un ensemble injecteur-pompe avec cette soupape
EP2022969A2 (fr) Procédé de fonctionnement d'une soupape d'injection à commande piézoélectrique
EP1159513B1 (fr) Commande a soupapes pour moteur a combustion interne
EP1430208B1 (fr) Dispositif d'injection de carburant destine a un moteur a combustion interne
DE102010038779A1 (de) Verfahren zum Betreiben einer Brennkraftmaschine mit mehreren Brennräumen und Brennkraftmaschine mit mehreren Brennräumen
EP1704315B1 (fr) Procede de commande d'une soupape et procede de commande d'un dispositif pompe-ajutage avec une soupape
DE102011075947B4 (de) Verfahren zum Bestimmen eines Kraftstoffdrucks in einem Hochdruckspeicher und Einspritzsystem
EP1751414B1 (fr) Procede et dispositif de commande d'une soupape
DE10225911B3 (de) Verfahren und Vorrichtung zum Messen und Regeln der Schließ- und Öffnungszeit eines Piezo-Steuerventils
EP1472454B1 (fr) Procede et dispositif de detection d'etats de fonctionnement d'un ensemble pompe-gicleur
DE10140550A1 (de) Verfahren zur Funktionsüberwachung schnellschaltender Einspritzventile
DE102004015045B4 (de) Verfahren zur Ermittlung der Position eines beweglichen Verschlusselementes eines Einspritzventils
WO2003091559A1 (fr) Dispositif et procede pour commander le piezo-actionneur d'une soupape de commande d'une unite pompe-gicleur
DE10310120B4 (de) Verfahren zur Bestimmung der auf einen Piezoaktor ausgeübten Last sowie Verfahren und Vorrichtung zur Ansteuerung eines Piezoaktors eines Steuerventils einer Pumpe-Düse-Einheit
DE102022202027A1 (de) Verfahren zur Ansteuerung eines elektromagnetisch ansteuerbaren Gasventils, Steuergerät
DE102012223786B3 (de) Verfahren zum Bestimmen einer Druckänderung im Brennraum einer Brennkraftmaschine und Brennkraftmaschine zum Durchführen des Verfahrens
DE102017213127A1 (de) Verfahren zum Ermitteln eines Kalibrierungsfaktors für einen Drucksensor eines Kraftstoffinjektors

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL HR LT LV MK

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL HR LT LV MK

17P Request for examination filed

Effective date: 20070420

17Q First examination report despatched

Effective date: 20070601

AKX Designation fees paid

Designated state(s): DE FR GB IT

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SIEMENS VDO MECHATRONIK GMBH & CO. KG

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: CONTINENTAL AUTOMOTIVE GMBH

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 502004012047

Country of ref document: DE

Date of ref document: 20110210

Kind code of ref document: P

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502004012047

Country of ref document: DE

Effective date: 20110210

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20110930

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502004012047

Country of ref document: DE

Effective date: 20110930

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20110917

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20101229

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110917

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20180924

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20180930

Year of fee payment: 15

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502004012047

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190930