EP1704316B1 - Procede et dispositif pour reguler une soupape et procede et dispositif pour reguler un ensemble injecteur-pompe avec cette soupape - Google Patents

Procede et dispositif pour reguler une soupape et procede et dispositif pour reguler un ensemble injecteur-pompe avec cette soupape Download PDF

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Publication number
EP1704316B1
EP1704316B1 EP04803891A EP04803891A EP1704316B1 EP 1704316 B1 EP1704316 B1 EP 1704316B1 EP 04803891 A EP04803891 A EP 04803891A EP 04803891 A EP04803891 A EP 04803891A EP 1704316 B1 EP1704316 B1 EP 1704316B1
Authority
EP
European Patent Office
Prior art keywords
valve
value
piezoelectric actuator
valve seat
determined
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.)
Not-in-force
Application number
EP04803891A
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German (de)
English (en)
Other versions
EP1704316A1 (fr
Inventor
Jörg BEILHARZ
Maximilian Kronberger
Richard Pirkl
Christian Rissler
Harald Schmidt
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.)
Volkswagen AG En Continental Automotive GmbH
Original Assignee
Siemens AG
Volkswagen AG
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Publication date
Application filed by Siemens AG, Volkswagen AG filed Critical Siemens AG
Publication of EP1704316A1 publication Critical patent/EP1704316A1/fr
Application granted granted Critical
Publication of EP1704316B1 publication Critical patent/EP1704316B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02D41/20—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
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/02—Circuit arrangements for generating control signals
    • F02D41/14—Introducing closed-loop corrections
    • F02D41/1401—Introducing closed-loop corrections characterised by the control or regulation method
    • F02D2041/1409—Introducing closed-loop corrections characterised by the control or regulation method using at least a proportional, integral or derivative controller
    • 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
    • F02D2200/0606—Fuel 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 engine.
  • a pump-nozzle device comprising a pump and a valve having a valve member which controls the hydraulic coupling of a spill space to a drain passage.
  • the drainage channel is hydraulically coupled to the pump and a nozzle unit.
  • An inlet channel is provided, which is hydraulically coupled to the Abberichtraum.
  • 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, the flow 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.
  • WO 03/081007 A1 a method and a device for detecting the impact time of a valve needle of a piezo control valve is known.
  • the piezo control valve is used in a pump-nozzle unit for injecting fuel into an internal combustion engine.
  • the point of impact of the valve needle of the piezo control valve of the pump-nozzle unit is determined by evaluating the piezo voltage and / or the piezoelectric current.
  • WO 03/104633 A1 a method and a device for measuring and controlling the closing and opening time of a piezo control valve, in which the time duration is measured, which requires a valve needle of a control valve of a piezo pump nozzle unit to move from a first end position to a second end position, wherein the response time of the control valve is taken into account.
  • the time duration is determined as a function of the voltage applied to the control valve and / or the applied current.
  • an actuating signal is generated, which is used for moving the control valve from the first to the second end position, wherein the actuating signal is generated at a time at which it is ensured that the pressure in the control valve and in the injection nozzle during the measurement largely the pressure corresponds to the fuel low pressure range.
  • the object of the invention is to provide a method and a device for controlling a valve, which ensures that the valve switches precisely over a long period of operation. It is another object of the invention to provide a method and apparatus for controlling a pump-nozzle device with the valve that ensures that the valve shifts precisely over a long period of operation.
  • the invention is characterized by a method and a corresponding device for controlling a valve with a valve drive, which is designed as a piezoelectric actuator, with a valve member, a valve body and a valve seat, wherein at a first predetermined time, the valve member from a position away from the valve seat is controlled in the valve seat by means of a charging operation of the piezoelectric actuator, in which a first value is determined, which is characteristic of the piezoelectric actuator supplied electrical energy upon impact of the valve member on the valve seat, in which a second value is determined, which is characteristic of the piezoelectric actuator supplied electrical energy at the completion of the charging of the piezoelectric actuator.
  • a difference actual value is determined from the difference of the second and first value.
  • a difference of a differential setpoint which can be predetermined, and the difference actual value is fed to a controller and a control signal for charging the piezoelectric actuator is determined depending on the manipulated variable of the controller.
  • the invention is characterized by a method and a corresponding device for controlling a pump-nozzle device with a pump having a piston and a working space, a control unit having a drainage channel which is hydraulically coupled to the working space, and the valve comprises and comprises a Abêtraum which is hydraulically decoupled from the drainage channel when the valve member abuts the valve seat, and which is otherwise hydraulically coupled to the drainage channel.
  • the valve is controlled by the method or apparatus for controlling the valve.
  • the invention is characterized in that the valve seat force, with which the valve member is pressed by the valve drive in the valve seat, when it is in contact with the valve seat, is very accurate and very reproducible adjustable.
  • the valve seat force is critical to the tightness of the valve when the valve member is in contact with the valve seat.
  • the mechanical stress of the valve member and the valve seat can be selectively reduced over a long period of operation of the valve and at the same time ensure that over this long period of operation, the valve seat force is constant. It can also be easily minimized tolerances during closing and opening of the valve. In connection with the pump-nozzle device can thus be adjusted very precisely over a long period of operation, the start of delivery and in particular the delivery end of the fuel.
  • the invention is based on the recognition that the first value depends significantly on a force which is caused by the pressure of the fluid acting on the valve member and a force of a regularly existing return means and that the second value significantly depends on a valve seat force and in addition to the force that is caused by the pressure of the fluid acting on the valve member, and the force of the return means. Furthermore, the invention is based on the recognition that the difference actual value significantly depends on the valve seat force, ie the force exerted by the valve member on the valve seat of the valve body. The method or devices according to the invention can thus be used to precisely determine a value which is characteristic of the valve seat force and which is the difference actual value.
  • the sealing force can be permanently adjusted very precisely.
  • the piezoelectric actuator is thus simply used simultaneously as a sensor.
  • the actuating signal for charging the piezoelectric actuator is determined depending on a pre-control value.
  • the valve can be controlled even more precisely and faster, since the controller only needs to compensate for deviations from the pilot control value.
  • the pilot control value is determined as a function of a fuel temperature and / or a rotational speed and / or the predefinable first time.
  • the controller has a proportional and an integral component. This has the advantage that the sealing force is stationary adjustable extremely precise.
  • the differential actual value is low-pass filtered before forming the difference with the difference setpoint.
  • the first value is an actual value of the supplied electrical energy when the valve member hits the valve seat
  • the second value is an actual value of the supplied electrical energy at the conclusion of the charging process
  • the difference actual value is an actual value electrical differential energy which is supplied to the piezoelectric actuator and the Differential setpoint a setpoint of the electrical differential energy.
  • the first value is an actual value of the piezoelectric voltage when the valve member hits the valve seat
  • the second value is an actual value of the piezoelectric voltage at the conclusion of the charging process
  • the differential actual value is an actual value of the differential voltage and the difference Setpoint a setpoint of the differential voltage.
  • the method for controlling the pump-nozzle device of the first predetermined time is selected so that the piston is in its top dead center and remains until the expected impact of the valve member on the valve seat, and that the determined manipulated variable for determining the control signal is used when in a second predetermined time, the valve member is controlled from a position away from the valve seat in the valve seat by means of a charging of the piezoelectric actuator, wherein the second predetermined time can also be selected so that the piston has left its top dead center until the expected impingement 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 associated with pistons, the 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 volume of the working chamber 13 limited by the piston 11 has a maximum value acting on the piston 11 no external forces, d. H. Forces transmitted via the coupling with the camshaft 16.
  • the nozzle unit comprises a nozzle body 51, in which a nozzle return means 52, which is designed as a spring and possibly additionally as a damping unit, and a nozzle needle 53 are arranged.
  • the nozzle needle 53 is arranged in a recess of the nozzle body 51 and is guided in the region of a needle guide 55.
  • 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 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 drainage channel 22 is hydraulically coupled to the working space 13 and is guided to the needle hub 57 and is hydraulically coupled to the nozzle 56 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 pushes the valve member 231 in an open position, ie spaced from the valve seat 234, when acting by an actuator 24 to the valve member forces are lower than the forces by the Pressure of the fluid, here the fuel, are caused and act through the valve return means on the valve member 231.
  • the actuator 24 is formed as a piezo stack.
  • the actuator 24 is preferably coupled to the valve member 231 by means of a transformer which preferably amplifies the stroke of the actuator 24.
  • a transformer which preferably amplifies the stroke of the actuator 24.
  • On the actuator 24 is preferably also a plug for receiving electrical contacts for driving the actuator 24 is provided.
  • a device 60 for controlling the pump-nozzle device is provided, which generates a control signal SG for the valve.
  • valve member 231 In the open position of the valve member 231 is at a movement of the piston 11, the upward d. H. is directed away from the nozzle 56, sucked fuel through the inlet channel 21 toward the working space 13. As long as the valve member 231 during a subsequent downward movement of the piston 11, d. H. 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 is pushed back through the valve back into the Abêtraum 232 and possibly 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 also in the discharge passage 22 and in the high-pressure chamber is compressed, whereby the pressure with increasing downward movement of the piston 11 in the working space 13, in the high pressure chamber 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 and gives so the nozzle 56 for the fuel supply to the cylinder of the 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 hydraulic coupling between the high pressure chamber and the Abêtraum 232 and the inlet channel 21 is made. 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 231 is controlled from its position away from the valve seat 234 into the valve seat.
  • the predetermined first time t1 is preferably chosen so that the piston 11 in his Top dead center is and remains until the expected impingement of the valve member 231 on the valve seat 234.
  • the impact time can be detected very precisely.
  • the predefinable first time t1 can also be selected such that the piston 11 has left its top dead center until the expected impact of the valve member 231 on the valve seat 234.
  • a pre-control value EGY_PRE of the electrical energy to be supplied is determined as a function of a fuel temperature T_FU and / or a rotational speed N and the specifiable time t1.
  • the precontrol value EGY_PRE of the electrical energy to be supplied is determined, for example, by means of a characteristic map whose characteristic map values were determined in advance by tests.
  • a desired value EGY_D_SP of an electrical differential energy is determined in block B1.
  • the differential electric energy reference EGY_D_SP is characteristic of the valve seat force exerted by the valve member 231 on the valve seat 234 of the valve body 237 when the valve member 231 is in contact with the valve seat 234.
  • the desired value EGY_D_SP of the electrical differential energy is determined in the block B1 depending on the fuel temperature T_FU, the rotational speed N and / or the predefinable first time t1. This can also be done for example by means of a corresponding map.
  • a block B2 depending on actual values EGY_AV, the electrical energy supplied to the piezoactuator during the charging process is supplied. Further, in the block B2, the timing t2 of the impact of the valve member 231 is detected. This can be done, for example, by evaluating actual values V_AV the piezoelectric voltage or the corresponding characterizing variables, such as the actual current through the piezoelectric actuator or the piezoelectric actuator supplied charge or electrical energy done. Upon impact of the valve member 231 results in a characteristic course of these variables, based on which the time t2 of the impingement of the valve member 231 can be detected.
  • an actual value EGY_DET of the supplied electrical energy is determined in the block B2 on the basis of the determined time t2 of the impingement of the valve member 231 in the valve seat 234 and the actual value EGY_AV of the energy supplied thereto when the valve member 231 impinges on the valve seat 234.
  • the actual values EGY_AV of the supplied electrical energy are also read in and the actual value EGY_AV is assigned to an actual value EGY_CHA of the supplied electrical energy at the end of the charging process at the end of the charging process of the piezoactuator.
  • the conclusion of the charging process can be recognized, for example, by the fact that the actual values EGY_AV of the supplied electrical energy reach a maximum or also by a corresponding information of a further control function for the pump-nozzle device.
  • a block B4 the difference of the actual value EGY_CHA of the supplied electrical energy at the conclusion of the charging process and the actual value EGY_DET of the supplied electrical energy is determined when the valve member 231 hits the valve seat 234 and fed to a block B5 which comprises a low-pass filter and provides an actual value EGY_D_AV of the electrical differential energy at its output.
  • the difference between the setpoint value EGY_D_SP and the actual value EGY_D_AV of the electrical differential energy is formed.
  • the actual value EGY_D_AV of the electrical differential energy can also be determined directly without the low-pass filter of the block B5.
  • the output of the block B6 is connected on the input side to a block B7, which comprises a regulator, which is preferably designed as a PI controller.
  • the manipulated variable of the regulator which in this exemplary embodiment is a control value EGY_FBC of the electrical energy to be supplied, is then fed to a block B7 in which a desired electrical energy EGY_THRUST to be supplied to the piezoactuator is determined by summation from the control value EGY_FBC and the precontrol value EGY_PRE of the electrical energy to be supplied becomes.
  • the value EGY_THRUST of the desired electrical energy to be supplied is supplied to a block B8, in which a corresponding actuating signal SG for driving the valve drive 24 designed as a piezoactuator is generated.
  • the control signal SG is preferably a pulse width modulated signal and the desired electrical energy EGY THRUST to be supplied is preferably divided into a predetermined number of partial energy quantities, which are supplied to the piezoelectric actuator in each case in one period of the pulse width modulated signal.
  • the block B8 further preferably comprises a further subordinate controller, in which the actual supply of electrical energy to the piezoelectric actuator is controlled, wherein the manipulated variable is the respective pulse width of the actuating signal SG.
  • the respective current charge or the actual values V_AV of the piezoelectric voltage or the actual values EGY_AV of the supplied electrical energy serve.
  • control signal SG is to be determined for a charging operation following a second predefinable time, which may also be selected such that the piston 11 has left its top dead center until the expected impact of the valve member 231 on the valve seat 234, the control value is preferred EGY_FBC of the supplied electrical energy taken over by a charging operation, which took place in advance after the first predeterminable time t1. Only the pre-control value EGY_PRE of the electrical energy to be supplied is then recalculated.
  • FIG. 3 shows an alternative embodiment of the block diagram according to FIG. 1 , Only the differences are explained below.
  • a piezoelectric voltage V_DET is determined when the valve member 231 impinges on the valve seat 234 by correspondingly assigning an actual value V_D_AV of the piezoelectric voltage.
  • a piezo voltage V_CHA is determined at the conclusion of the charging process, specifically depending on actual values V_AV of the piezo voltage.
  • a block B4 ' the difference between the piezo voltage V_CHA at the conclusion of the charging process and the piezo voltage V_DET when the valve member 231 hits the valve seat 234 is then formed and fed to the block B5' which, like the block B5, comprises a low-pass filter and the provides an actual value V_DAV of the differential voltage at its output.
  • the difference of the setpoint value V_D_SP and the actual value V_D_AV of the differential voltage is formed and fed to a controller which is formed in the block B7' and corresponds to that of the block B7.
  • the regulator may be supplied with other quantities which are characteristic of the electrical energy to be supplied to the piezoactuator, such as e.g. the electric charge to be supplied to the piezoactuator.
  • 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.
  • t1 is the predefinable first time, However, it can also be the second predefinable time.
  • t2 is the timing of the impact of the valve member 231 on the valve seat 234 and t3 is the time of the end of the charging process.
  • the determination of the control value EGY_FBC of the electrical energy to be supplied takes place during a period of time during which the piston 11 is in its top dead center. In this case, then remains the course of the pressure P_H in the working space of the pump over the entire period shown at the level of time t1, also in this case no amount of fuel is promoted.

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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)
  • Fluid-Driven Valves (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Electrically Driven Valve-Operating Means (AREA)

Claims (12)

  1. Procédé de commande d'une soupape comprenant un entraînement de soupape (24) réalisé sous forme d'actionneur piézo-électrique, un obturateur (231), un corps de soupape (237) et un siège de soupape (234), suivant lequel:
    - à un premier instant prescriptible (t1), l'obturateur (231) est déplacé d'une position éloignée du siège de soupape (234) dans le siège de soupape (234) au moyen d'un processus de chargement de l'actionneur piézo-électrique,
    - on détermine une première valeur qui est caractéristique de l'énergie électrique apportée à l'actionneur piézo-électrique lorsque l'obturateur (231) rencontre le siège de soupape (234),
    - on détermine une deuxième valeur qui est caractéristique de l'énergie électrique apportée à l'actionneur piézo-électrique lors de l'achèvement du processus de chargement de l'actionneur piézo-électrique,
    - on détermine une valeur différentielle réelle d'après la différence entre la deuxième et la première valeur,
    - on apporte à un régulateur la différence entre une valeur différentielle de consigne, qui peut être prescrite, et la valeur différentielle réelle, et
    - on détermine un signal de réglage (SG) pour le chargement de l'actionneur piézo-électrique en fonction de la grandeur réglante du régulateur.
  2. Procédé suivant la revendication 1, suivant lequel le signal de réglage (SG) pour le chargement de l'actionneur piézo-électrique est déterminé par une valeur de pilotage.
  3. Procédé suivant l'une des revendications précédentes, suivant lequel la valeur différentielle de consigne est déterminée en fonction d'une température de carburant (T_FU) et/ou d'une vitesse de rotation (N) et/ou du premier instant prescriptible (t1).
  4. Procédé suivant la revendication 2 ou 3, suivant lequel la valeur de pilotage est déterminée en fonction d'une température de carburant et/ou d'une vitesse de rotation et/ou du premier instant prescriptible (t1).
  5. Procédé suivant l'une des revendications précédentes, suivant lequel le régulateur est un régulateur avec une part proportionnelle et une part intégrale.
  6. Procédé suivant l'une des revendications précédentes, suivant lequel la valeur différentielle réelle est filtrée avec un filtre passe-bas avant de former la différence avec la valeur différentielle de consigne.
  7. Procédé suivant l'une des revendications précédentes, suivant lequel la première valeur est une valeur réelle (EGY_AV) de l'énergie électrique apportée lorsque l'obturateur (231) rencontre le siège de soupape (234), la deuxième valeur est une valeur réelle (EGY_CHA) de l'énergie électrique apportée lors de l'achèvement du processus de chargement, la valeur différentielle réelle est une valeur réelle (EGY_D_AV) de l'énergie électrique différentielle qui est apportée à l'actionneur piézo-électrique, et la valeur différentielle de consigne est une valeur de consigne (EGY_D_SP) de l'énergie électrique différentielle.
  8. Procédé suivant l'une des revendications 1 à 6, suivant lequel la première valeur est une valeur réelle (V_DET) de la tension piézo-électrique lorsque l'obturateur (231) rencontre le siège de soupape (234), la deuxième valeur est une valeur réelle (V_CHA) de la tension piézo-électrique lors de l'achèvement du processus de chargement, la valeur différentielle réelle est une valeur réelle (V_D_AV) de la tension différentielle, et la valeur différentielle de consigne est une valeur de consigne (V_D_SP) de la tension différentielle.
  9. Procédé de commande d'un ensemble injecteur-pompe comprenant
    - une pompe, qui a un piston (11) et une chambre de travail (13),
    - une unité de commande, qui comprend un canal de sortie (22) qui est hydrauliquement couplé à la chambre de travail (13) et qui comprend une soupape, dotée d'un entraînement de soupape (24) réalisé sous forme d'actionneur piézo-électrique, d'un obturateur (231), d'un corps de soupape (237), d'un siège de soupape (234) et d'une chambre de décharge (232), qui est hydrauliquement découplée du canal de sortie (22) lorsque l'obturateur (231) s'applique contre le siège de soupape (234) et qui est autrement hydrauliquement couplée au canal de sortie (22),
    suivant lequel la soupape est commandée par un procédé suivant l'une des revendications précédentes.
  10. Procédé suivant la revendication 9, suivant lequel le premier instant prescriptible (t1) est choisi de telle sorte que le piston (11) se trouve à son point mort haut et y demeure jusqu'à la rencontre attendue de l'obturateur (231) avec le siège de soupape (234), et que la grandeur réglante ainsi déterminée est utilisée pour déterminer le signal de réglage lorsque, à un deuxième instant prescriptible, l'obturateur (231) est déplacé d'une position éloignée du siège de soupape (234) dans le siège de soupape (234) au moyen d'un processus de chargement de l'actionneur piézo-électrique, sachant que le deuxième instant prescriptible peut aussi être choisi de telle sorte que le piston (11) a quitté son point mort haut jusqu'à la rencontre attendue de l'obturateur (231) avec le siège de soupape (234).
  11. Dispositif de commande d'une soupape dotée d'un entraînement de soupape (24) réalisé sous forme d'actionneur piézo-électrique, d'un obturateur (231), d'un corps de soupape (237) et d'un siège de soupape (234), qui comprend des moyens
    - qui, à un premier instant prescriptible (t1), déplacent l'obturateur (231) d'une position éloignée du siège de soupape (234) dans le siège de soupape (234) au moyen d'un processus de chargement de l'actionneur piézo-électrique,
    - qui déterminent une première valeur qui est caractéristique de l'énergie électrique apportée à l'actionneur piézo-électrique lorsque l'obturateur (231) rencontre le siège de soupape (234),
    - qui déterminent une deuxième valeur qui est caractéristique de l'énergie électrique apportée à l'actionneur piézo-électrique lors de l'achèvement du processus de chargement de l'actionneur piézo-électrique,
    - qui déterminent une valeur différentielle réelle d'après la différence entre la deuxième et la première valeur,
    - qui apportent à un régulateur la différence entre une valeur différentielle de consigne, qui peut être prescrite, et la valeur différentielle réelle, eut
    - qui déterminent un signal de réglage (SG) pour le chargement de l'actionneur piézo-électrique en fonction de la grandeur réglante du régulateur.
  12. Dispositif de commande d'un ensemble injecteur-pompe comprenant
    - une pompe, qui possède un piston (11) et une chambre de travail (13),
    - une unité de commande, qui comprend un canal de sortie (22) qui est hydrauliquement couplé à la chambre de travail (13) et qui comprend une soupape, dotée d'un entraînement de soupape (24) réalisé sous forme d'actionneur piézo-électrique, d'un obturateur (231), d'un corps de soupape (237), d'un siège de soupape (234) et d'une chambre de décharge (232), qui est hydrauliquement découplée du canal de sortie (22) lorsque l'obturateur (231) s'applique contre le siège de soupape (234) et qui est autrement hydrauliquement couplée au canal de sortie (22),
    au moyen du dispositif de commande d'une soupape suivant la revendication 11.
EP04803891A 2003-12-18 2004-12-15 Procede et dispositif pour reguler une soupape et procede et dispositif pour reguler un ensemble injecteur-pompe avec cette soupape Not-in-force EP1704316B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10359675A DE10359675B3 (de) 2003-12-18 2003-12-18 Verfahren und Vorrichtung zum Steuern eines Ventils und Verfahren und Vorrichtung zum Steuern einer Pumpe-Düse-Vorrichtung mit dem Ventil
PCT/EP2004/014271 WO2005059337A1 (fr) 2003-12-18 2004-12-15 Procede et dispositif pour reguler une soupape et procede et dispositif pour reguler un ensemble injecteur-pompe avec cette soupape

Publications (2)

Publication Number Publication Date
EP1704316A1 EP1704316A1 (fr) 2006-09-27
EP1704316B1 true EP1704316B1 (fr) 2008-04-23

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EP04803891A Not-in-force EP1704316B1 (fr) 2003-12-18 2004-12-15 Procede et dispositif pour reguler une soupape et procede et dispositif pour reguler un ensemble injecteur-pompe avec cette soupape

Country Status (6)

Country Link
US (1) US7275522B2 (fr)
EP (1) EP1704316B1 (fr)
CN (1) CN100529369C (fr)
AT (1) ATE393308T1 (fr)
DE (2) DE10359675B3 (fr)
WO (1) WO2005059337A1 (fr)

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DE102004058971B4 (de) * 2004-12-08 2006-12-28 Volkswagen Mechatronic Gmbh & Co. Kg Verfahren zum Steuern eines piezoelektrischen Aktors und Steuereinheit zum Steuern eines piezoelektrischen Aktors
DE102004062073B4 (de) * 2004-12-23 2015-08-13 Continental Automotive Gmbh Verfahren und Vorrichtung zur Kompensation von Prelleffekten in einem piezogesteuerten Einspritzsystem einer Verbrennungskraftmaschine
US8202267B2 (en) 2006-10-10 2012-06-19 Medsolve Technologies, Inc. Method and apparatus for infusing liquid to a body
TW200903975A (en) * 2007-07-09 2009-01-16 Micro Base Technology Corp Piezoelectric miniature pump and its driving circuit
US8708961B2 (en) 2008-01-28 2014-04-29 Medsolve Technologies, Inc. Apparatus for infusing liquid to a body
US7980224B2 (en) * 2008-02-05 2011-07-19 Caterpillar Inc. Two wire intensified common rail fuel system
DE102009001077A1 (de) * 2009-02-23 2010-08-26 Robert Bosch Gmbh Verfahren zum Betreiben einer Endstufe für mindestens einen Piezoaktor
GB2475224B (en) * 2009-09-28 2016-03-16 Gm Global Tech Operations Inc Method for controlling a piezoelectric injector
DE102010040283B3 (de) * 2010-09-06 2011-12-22 Continental Automotive Gmbh Verfahren zur Regelung der Einspritzmenge eines Piezoinjektors eines Kraftstoffeinspritzsystems
WO2014107487A1 (fr) 2013-01-02 2014-07-10 Regents Of The University Of Minnesota Injecteurs de carburant direct à débit d'injection variable
CN105190133B (zh) 2013-05-07 2019-06-04 皇家飞利浦有限公司 线性数字比例压电阀
CN110032060B (zh) * 2018-01-11 2022-05-17 西门子能源有限公司 过程控制方法、过程控制装置和存储介质

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JP3529577B2 (ja) * 1997-02-14 2004-05-24 本田技研工業株式会社 燃料噴射弁制御装置
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Also Published As

Publication number Publication date
WO2005059337A1 (fr) 2005-06-30
DE502004006965D1 (de) 2008-06-05
CN1938509A (zh) 2007-03-28
US7275522B2 (en) 2007-10-02
CN100529369C (zh) 2009-08-19
DE10359675B3 (de) 2005-07-07
US20060289670A1 (en) 2006-12-28
ATE393308T1 (de) 2008-05-15
EP1704316A1 (fr) 2006-09-27

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