EP2705235B1 - Method and device for controlling a valve - Google Patents

Method and device for controlling a valve Download PDF

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Publication number
EP2705235B1
EP2705235B1 EP12718664.1A EP12718664A EP2705235B1 EP 2705235 B1 EP2705235 B1 EP 2705235B1 EP 12718664 A EP12718664 A EP 12718664A EP 2705235 B1 EP2705235 B1 EP 2705235B1
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EP
European Patent Office
Prior art keywords
valve
current
sealing element
actuator
predefined
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.)
Active
Application number
EP12718664.1A
Other languages
German (de)
French (fr)
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EP2705235A2 (en
Inventor
Christoph Klesse
Thomas Kraft
Hans Riepl
Tobias Ritsch
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
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Continental Automotive GmbH
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Publication date
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Publication of EP2705235A2 publication Critical patent/EP2705235A2/en
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Publication of EP2705235B1 publication Critical patent/EP2705235B1/en
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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
    • 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
    • F02D41/24—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means
    • 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
    • F02D41/24—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means
    • F02D41/2406—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means using essentially read only memories
    • F02D41/2425—Particular ways of programming the data
    • F02D41/2429—Methods of calibrating or learning
    • F02D41/2451—Methods of calibrating or learning characterised by what is learned or calibrated
    • F02D41/2464—Characteristics of 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
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/40—Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
    • F02D41/401—Controlling injection timing
    • 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
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • 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
    • F02D2041/2044—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit using pre-magnetisation or post-magnetisation of the coils

Definitions

  • the invention relates to a method and a device for controlling a valve.
  • such a valve is used in a high-pressure pump for conveying fluid for a storage injection system for internal combustion engines of motor vehicles.
  • Such valves are subject to heavy loads, especially when exposed to continuous loads, such as in high pressure pumps. Since high-pressure pumps are exposed to pressures of, for example, 2000 bar or more, high demands are placed on the valves in such pumps. Both when closing and when opening these valves, noise may occur.
  • DE 101 48 218 A1 discloses a method of operating an internal combustion engine, particularly with direct injection, in which a first fuel pump delivers fuel into a working space of a second fuel pump, which delivers fuel into a fuel rail.
  • the amount of fuel delivered by the second fuel pump into the fuel rail can be influenced by opening a valve element of an electric valve device, which is connected to the working space of the second fuel pump, at a certain time during a delivery cycle of the second fuel pump, thus opening the working space of the second fuel pump connecting the second fuel pump with a low-pressure region, wherein the valve element is braked shortly before reaching at least one of the two end positions.
  • a valve needle of an electromagnetic valve takes a non-energized first position and energizes a second position. In the transition from the second position to the first position of the valve needle takes place from a predetermined time for a certain period of time a Nachbestromung.
  • GB 2 331 554 A discloses a method for controlling a hydraulically actuated electronically controlled fuel injector.
  • the amount of fuel injected into the associated cylinder is controlled by regulating the pressure of the working fluid.
  • An electrical pulse is generated to actuate the injector.
  • the timing, duration and amplitude of the pulse are varied in response to changes in the pressure of the working fluid in idle, light load and normal load modes.
  • WO 2010/079027 A1 discloses a method of operating a fuel injection system in which fuel passes from an electromagnetically actuated injector into at least one combustion chamber of the internal combustion engine, and wherein at least a portion of the movement of a valve member of the injector is affected by an electromagnetic brake pulse. A closing delay time of the injection valve or a corresponding variable is determined and the determined closing delay time or the corresponding variable is used to determine at least one parameter of the braking pulse.
  • EP 1 990 526 A2 discloses an electromagnetic fuel injection valve device for an internal combustion engine.
  • the Device has a controller for controlling the supply of the magnetic coil.
  • the object of the invention is to provide a method and a device for controlling a valve, which enables a precise and cost-effective operation of the valve.
  • the invention is characterized by a method and a corresponding device for controlling a valve.
  • the valve comprises a spring with a spring force, an actuator with an actuator force acting against the spring force, and a plunger, which can be actuated by means of the actuator.
  • the valve comprises a sealing element, which can be coupled or coupled to the plunger, and a sealing seat, so that the valve is closed when the sealing element bears against the sealing seat.
  • the current is impressed on the actuator starting from an initial value of the current up to a predetermined final value of the current current.
  • the initial value of the current is smaller than the final value.
  • a duration of the time interval is predetermined depending on a coupling of the plunger with the sealing element.
  • the actuator thus has two functions. On the one hand, the actuator has the function of a valve actuator. Further, the actuator allows damping of the impingement of the plunger on the sealing seat and / or on the sealing element and / or the actuator allows the damping of the impingement of the sealing element to an end position limit, for example on a valve housing wall. Preferably, the actuator has an electromagnet.
  • the plunger can be at least partially pushed out of a magnetic field of the actuator so that the actuator force acting on the plunger decreases the farther the plunger is pushed out of the magnetic field becomes.
  • this effect can be compensated for by the rising profile of the current from the initial value to the final value, and the actuator force can be kept approximately constant.
  • a start of a valve opening of the normally open valve is detected and, as soon as the beginning of the valve opening is detected, a start of the time interval is specified depending on the detected start of the valve opening.
  • the beginning of the valve opening can be detected by detecting a movement of the plunger along a longitudinal axis of the plunger.
  • the time interval can be started as soon as it is detected that the plunger, starting from an initial position of the plunger, in which the plunger allows the valve to open or the valve is closed, moves in the direction of an end position of the plunger, in which the plunger Closing the valve is not allowed or the valve is open.
  • the start of the time interval can be predetermined as a function of a valve type and / or as a function of at least one operating parameter of the valve.
  • a beginning of a valve closing of the normally closed valve is detected and as soon as the beginning of the valve closing is detected, the start of the time interval is specified depending on the detected start of the valve closing.
  • the time interval can be started as soon as it is detected that the plunger, starting from the initial position of the plunger, in which the plunger allows the valve to close or the valve is opened, moves in the direction of an end position of the plunger, in which the plunger Opening the valve is not allowed or the valve is closed.
  • valve is arranged in an inlet region of a pump and the plunger is directly coupled to the sealing element.
  • duration of the time interval is approximately equal to 15% to 20% of a period of a delivery phase of the pump.
  • valve is arranged in the inlet region of the pump and the plunger is coupled with the sealing element.
  • duration of the time interval is approximately equal to 50% of the duration of the delivery phase of the pump.
  • the final value of the current is determined depending on the spring force of the spring.
  • this makes it possible to specify the final value of the flow in such a way that the valve can be opened or closed sufficiently quickly, and it can be ensured that the valve opens or closes.
  • the course of the current is predetermined stepwise.
  • the course of the current may have a plurality of temporally successive sections, each of the sections each having a value of the current having a substantially constant current profile, and the section following in time to a preceding section having a greater value of the current than the preceding section.
  • FIG. 1 shows a pump 10 with a pump housing 12.
  • the pump 10 is in particular designed as a high pressure pump, preferably as a radial piston pump.
  • a pump piston 14 is movably mounted in the pump housing 12 in order to fill the pressure chamber 16 with fluid, this has a supply line 18, in which preferably designed as an inlet valve valve 20 is arranged.
  • the valve 20 designed as an inlet valve is preferably designed as a digitally switched valve.
  • the valve 20 facilitates the filling of the pressure chamber 16 and prevents during filling the backflow of the fluid from the feed line 18.
  • the pressure chamber 16 further has a drain line 22, in which a valve designed as an outlet valve 24 is arranged. This fluid can be ejected from the pressure chamber 16.
  • the pump 10 further has a drive shaft 26, which is in operative connection with an eccentric ring 28 and is rotatable in a rotational direction D in the clockwise direction.
  • a drive shaft 26 is in operative connection with an eccentric ring 28 and is rotatable in a rotational direction D in the clockwise direction.
  • the eccentric ring 28 and a camshaft can be used.
  • the pump 10 may also be designed as a crank drive pump.
  • FIG. 1 shows a first embodiment of the valve 20.
  • the valve 20 includes a valve housing 29 having a recess 30.
  • a spring 32, a plunger 34 and a sealing element 36 are arranged in the recess 30, a spring 32, a plunger 34 and a sealing element 36 are arranged.
  • the spring 32 biases the sealing element 36 over the plunger 34 by being supported on a wall of the recess 30.
  • the sealing element 36 and the plunger 34 are mechanically coupled directly.
  • the plunger 34 comprises a first cylindrical part 34a and a second cylindrical part 34b, wherein the first part 34a has a larger diameter than the second part 34b.
  • the through holes 40 has. Fluid can flow via the passage recesses 40 when the sealing element 36 is not in contact with the sealing seat 38.
  • the valve 20 further comprises an actuator 42, which is designed in particular as a magnetic coil.
  • the first part 34 a of the plunger 34 is at least partially disposed within the actuator 42 and can be actuated by the actuator 42.
  • Both when opening and when closing the valve 20 may occur due to mechanical and hydraulic causes noise on the valve 20.
  • the plunger 34 is moved by the spring force F_1 of the spring 32 to the sealing seat 38. If the sealing seat 38 and the plunger 34, in particular the first part 34a of the plunger 34, meet, a noise may occur.
  • One Activation of the actuator 42 for example, just before the plunger 34 has reached its end position, in which the valve 20 is opened to the maximum and the first part 34a of the plunger 34 abuts the sealing seat 38, allows the plunger 34 can be braked and the impact of the Tappet 34 can be attenuated to the sealing seat 38.
  • FIG. 2 shows a second embodiment of the valve 20.
  • the plunger 34 and the sealing element 36 are not mechanically coupled directly.
  • the recess has an end position limiting element 44, which is arranged and designed to limit an axial movement of the plunger 34 and / or the sealing element 36 in the direction of the pressure chamber 16.
  • the end position limiting element 44 has further recesses 46, via which fluid can flow into the pressure chamber 16.
  • Both when opening and when closing the valve 20 may occur due to mechanical and hydraulic causes noise on the valve 20.
  • the sealing element 36 comes into abutment with the Endpositionsbegrenzungselement 44, whereby a first noise can occur.
  • the plunger 34 is then moved toward the sealing element 36 by the spring force F_1 of the spring 32. If the sealing element 36 and the plunger 34 meet, another noise can occur.
  • Activation of the actuator 42 for example just before the plunger 34 occurs on the sealing element 36, allows the plunger 34 can be braked and the impact of the plunger 34 can be damped on the sealing element 36.
  • FIG. 3A shows a third embodiment of the valve 20.
  • the valve 20 has a valve housing 29 which has a recess 30.
  • a spring 32, a plunger 34th and a sealing element 36 is arranged in the recess 30, a spring 32, a plunger 34th and a sealing element 36 is arranged.
  • the spring 32 biases the sealing element 36 over the plunger 34 by being supported on a wall of the recess 30.
  • the sealing element 36 and the plunger 34 are mechanically coupled directly.
  • the sealing element 36 and the plunger 34 are integrally formed.
  • the valve housing 29 includes a sealing seat 38.
  • the sealing seat 38 and the sealing element 36 are conical, so that when the sealing element 36 rests against the sealing seat 38 that valve 20 is closed.
  • valve 20 includes the Endpositionsbegrenzungselement 44, which is arranged and adapted to limit an axial movement of the plunger 34 and the sealing element 36 in the direction of the pressure chamber 16.
  • the end position limiting element 44 has further recesses 46, via which fluid can flow into the pressure chamber 16.
  • the sealing element 36 comes into abutment with the Endpositionsbegrenzungselement 44, whereby a noise can occur. If the plunger 34 and the sealing element 36 are integrally formed together, then the noise can be formed very clearly by the common mass of plunger 34 and sealing element 36.
  • FIGS. 3A to 3C the control of the valve for a normally open valve 20 will be explained in detail ( FIGS. 3A to 3C ). It is understood that this can be applied in a corresponding manner to a normally closed valve.
  • the pump 10 is moved by a rotational movement of the drive shaft 26 in a rotational direction D of the pump piston 14 through the eccentric ring 28 of the drive shaft 26 away and thereby compresses the fluid located in the pressure chamber 16.
  • the valve 20 is closed by applying a current to the actuator 42, thereby acting against the spring force F_1 Actuator force F_2 can act on the plunger 34.
  • the sealing element 36 can rest against the sealing seat 38 and a fluid flow from the supply line 18 into the pressure chamber 16 is prevented.
  • the compressed in the pressure chamber 16 fluid can now be completely discharged from the pump 10 via the formed as an outlet valve further valve 24.
  • the pump piston 14 has reached its top dead center.
  • the pump 10 is a high-pressure fuel pump of an injection system of an internal combustion engine
  • the fuel subjected to high pressure can reach a fluid reservoir, known as a common-rail, which is designed as a high-pressure fuel reservoir.
  • valve 20 begins due to the spring force F_1 of the spring 32 and the pressure difference before and behind the valve 20 to open.
  • the current is impressed on the actuator 42 for a predetermined time interval starting from an initial value I_0 of the current up to a predetermined final value I_END of the current, the initial value I_0 of the current is less than the final value I_End.
  • the time interval may start, for example, immediately after the end of the delivery phase or at a later time, in which the plunger 34 already moves and / or itself the sealing element 36 has already lifted at least partially from the sealing seat 38.
  • a start of a valve opening of the valve 20 can be detected and as soon as the beginning of the valve opening is detected, depending on the recognized start of the valve opening, a start of the time interval can be specified.
  • the start can take place immediately after the detection of the beginning of the valve opening or after a short period of time after the detection of the beginning.
  • the short period of time may be predetermined, for example, depending on an average valve opening time of the valve 20.
  • the actuator force F_2 generated by the energized actuator 42 counteracts the spring force F_1 and pressure difference, so that the plunger 34 and / or the sealing element 36 are braked in their movement.
  • the movement of the plunger 34 toward the sealing seat 38 ( FIG. 1 ) and / or the movement of the plunger 34 towards the sealing element 36 ( FIG. 2 ) or the movement of the plunger 34 and the sealing element 36 toward the end position limiting element 44 (FIG. FIG. 3B ) decelerated. Due to the reduced speed, an impact noise can be significantly reduced. Due to the slow movement of the plunger 34, the noise of the valve 20 can be kept very small and the valve 20 can still be opened reliably and quickly enough. In addition, the slow movement of the plunger 34, the wear of the valve 20 can be kept small.
  • the predetermined rising profile of the current starting from an initial value I_0 of the current up to a predetermined final value I_END of the current makes it possible to compensate for at least partial removal of the plunger from a magnetic field of the actuator 42 and thus approximates the actuator force F_2 keep constant.
  • the course of the current can be predetermined, for example stepwise.
  • FIG. 4 shows a schematic view of the current flow and a time course of the position POS of the plunger 34 with respect to an initial position of the plunger 34, in which the normally open valve 20 is closed.
  • a duration of the time interval can be predetermined, for example, depending on a coupling of the plunger 34 with the sealing element 36. For example, if the plunger 34 is directly coupled to the sealing member 36, the duration of the time interval may be approximately 15% to 20% of a duration of the delivery phase of the pump 10.
  • the duration of the time interval may be equal to approximately 50% of the duration of the delivery phase of the pump 10.
  • the final value I_END of the current can be predetermined, for example, depending on the spring force F_1 of the spring 32.
  • the initial value I_0 of the current may be zero, for example.

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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)
  • Magnetically Actuated Valves (AREA)
  • Regulating Braking Force (AREA)
  • Details Of Reciprocating Pumps (AREA)

Description

Die Erfindung betrifft ein Verfahren und eine Vorrichtung zum Steuern eines Ventils.The invention relates to a method and a device for controlling a valve.

Vorzugsweise wird ein derartiges Ventil in einer Hochdruckpumpe zur Förderung von Fluid für ein Speichereinspritzsystem für Brennkraftmaschinen von Kraftfahrzeugen verwendet.Preferably, such a valve is used in a high-pressure pump for conveying fluid for a storage injection system for internal combustion engines of motor vehicles.

Derartige Ventile unterliegen starken Beanspruchungen, insbesondere wenn sie Dauerbelastungen, wie zum Beispiel in Hochdruckpumpen, ausgesetzt sind. Da Hochdruckpumpen Drücken von beispielsweise 2000 bar oder mehr ausgesetzt sind, werden hohe Anforderungen an die Ventile in derartigen Pumpen gestellt. Sowohl beim Schließen als auch beim Öffnen dieser Ventile können Geräusche auftreten.Such valves are subject to heavy loads, especially when exposed to continuous loads, such as in high pressure pumps. Since high-pressure pumps are exposed to pressures of, for example, 2000 bar or more, high demands are placed on the valves in such pumps. Both when closing and when opening these valves, noise may occur.

DE 101 48 218 A1 offenbart ein Verfahren zum Betreiben einer Brennkraftmaschine, insbesondere mit Direkteinspritzung, bei dem eine erste Kraftstoffpumpe Kraftstoff in einen Arbeitsraum einer zweiten Kraftstoffpumpe fördert, welche Kraftstoff in eine Kraftstoff-Sammelleitung fördert. Die von der zweiten Kraftstoffpumpe in die Kraftstoff-Sammelleitung geförderte Kraftstoffmenge kann dadurch beeinflusst werden, dass ein Ventilelement einer elektrischen Ventileinrichtung, welche mit dem Arbeitsraum der zweiten Kraftstoffpumpe verbunden ist, zu einem bestimmten Zeitpunkt während eines Fördertaktes der zweiten Kraftstoffpumpe öffnet und so den Arbeitsraum der zweiten Kraftstoffpumpe mit einem Niederdruckbereich verbindet, wobei das Ventilelement kurz vor Erreichen mindestens einer der beiden_Endstellungen abgebremst wird. DE 101 48 218 A1 discloses a method of operating an internal combustion engine, particularly with direct injection, in which a first fuel pump delivers fuel into a working space of a second fuel pump, which delivers fuel into a fuel rail. The amount of fuel delivered by the second fuel pump into the fuel rail can be influenced by opening a valve element of an electric valve device, which is connected to the working space of the second fuel pump, at a certain time during a delivery cycle of the second fuel pump, thus opening the working space of the second fuel pump connecting the second fuel pump with a low-pressure region, wherein the valve element is braked shortly before reaching at least one of the two end positions.

DE 10 2007 003 211 A1 offenbart eine Vorrichtung und ein Verfahren zur Steuerung eines elektromagnetischen Ventils. Eine Ventilnadel eines elektromagnetischen Ventils nimmt unbestromt eine erste Position und bestromt eine zweite Position ein. Beim Übergang von der zweiten Position in die erste Position der Ventilnadel erfolgt ab einem vorgebbaren Zeitpunkt für eine bestimmte Zeitdauer eine Nachbestromung. DE 10 2007 003 211 A1 discloses an apparatus and method for controlling an electromagnetic valve. A valve needle of an electromagnetic valve takes a non-energized first position and energizes a second position. In the transition from the second position to the first position of the valve needle takes place from a predetermined time for a certain period of time a Nachbestromung.

GB 2 331 554 A offenbart ein Verfahren zum Steuern eines hydraulisch betätigten elektronisch gesteuerten Brennstoffinjektors. Die Menge an eingespritztem Brennstoff in den zugehörigen Zylinder wird gesteuert durch Regeln des Drucks des Arbeitsfluids. Ein elektrischer Puls wird erzeugt, um den Injektor zu betätigen. Um Geräusche und einen Verschleiß zu reduzieren, wird der Zeitpunkt, die Dauer und die Amplitude des Impulses variiert in Reaktion auf Änderungen des Drucks des Arbeitsfluids im Leerlaufbetrieb, bei leichter Last und bei Normallastbetrieb. GB 2 331 554 A discloses a method for controlling a hydraulically actuated electronically controlled fuel injector. The amount of fuel injected into the associated cylinder is controlled by regulating the pressure of the working fluid. An electrical pulse is generated to actuate the injector. To reduce noise and wear, the timing, duration and amplitude of the pulse are varied in response to changes in the pressure of the working fluid in idle, light load and normal load modes.

WO 2010/079027 A1 offenbart ein Verfahren zum Betreiben eines Kraftstoffeinspritzsystems, bei dem Kraftstoff von einem elektromagnetisch betätigten Einspritzventil in mindestens einen Brennraum der Brennkraftmaschine gelangt, und bei dem mindestens zweitweise die Bewegung eines Ventilelements des Einspritzventils durch einen elektromagnetischen Bremsimpuls beeinflusst wird. Eine Schließverzugszeit des Einspritzventils oder eine entsprechende Größe wird ermittelt und die ermittelte Schließverzugszeit oder die entsprechende Größe wird zur Bestimmung mindestens eines Parameters des Bremsimpulses verwendet. WO 2010/079027 A1 discloses a method of operating a fuel injection system in which fuel passes from an electromagnetically actuated injector into at least one combustion chamber of the internal combustion engine, and wherein at least a portion of the movement of a valve member of the injector is affected by an electromagnetic brake pulse. A closing delay time of the injection valve or a corresponding variable is determined and the determined closing delay time or the corresponding variable is used to determine at least one parameter of the braking pulse.

EP 1 990 526 A2 offenbart eine elektromagnetische Kraftstoffeinspritzventilvorrichtung für eine Brennkraftmaschine. Die Vorrichtung weist eine Steuerung auf zur Steuerung der Speisung der Magnetspule. EP 1 990 526 A2 discloses an electromagnetic fuel injection valve device for an internal combustion engine. The Device has a controller for controlling the supply of the magnetic coil.

Die Aufgabe der Erfindung ist es, ein Verfahren und eine Vorrichtung zum Steuern eines Ventils zu schaffen, das beziehungsweise die einen präzisen und kostengünstigen Betrieb des Ventils ermöglicht.The object of the invention is to provide a method and a device for controlling a valve, which enables a precise and cost-effective operation of the valve.

Die Aufgabe wird gelöst durch die Merkmale der unabhängigen Ansprüche. Vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprüchen gekennzeichnet.The object is solved by the features of the independent claims. Advantageous embodiments of the invention are characterized in the subclaims.

Die Erfindung zeichnet sich aus durch ein Verfahren und eine korrespondierende Vorrichtung zum Steuern eines Ventils. Das Ventil umfasst eine Feder mit einer Federkraft, einen Aktuator mit einer entgegen der Federkraft wirkenden Aktuatorkraft, und einen Stößel, der mittels des Aktuators betätigbar ist. Ferner umfasst das Ventil ein Dichtelement, das mit dem Stößel koppelbar oder gekoppelt ist, und einen Dichtsitz, sodass das Ventil geschlossen ist, wenn das Dichtelement an dem Dichtsitz anliegt. Bei einem stromlos offenen Ventil wird nach einer Schließphase des Ventils oder bei einem stromlos geschlossenen Ventil nach einer Öffnungsphase während eines vorgegebenen Zeitintervalls zum Abbremsen des Stößels dem Aktuator ein Strom mit einem vorgegebenen ansteigenden Verlauf aufgeprägt ausgehend von einem Anfangswert des Stromes bis zu einem vorgegebenen Endwert des Stromes. Hierbei ist der Anfangswert des Stromes kleiner als der Endwert. Hierbei wird eine Dauer des Zeitintervalls vorgegeben abhängig von einer Kopplung des Stößels mit dem Dichtelement.The invention is characterized by a method and a corresponding device for controlling a valve. The valve comprises a spring with a spring force, an actuator with an actuator force acting against the spring force, and a plunger, which can be actuated by means of the actuator. Furthermore, the valve comprises a sealing element, which can be coupled or coupled to the plunger, and a sealing seat, so that the valve is closed when the sealing element bears against the sealing seat. In the case of a normally open valve, after a closing phase of the valve or in the case of a normally closed valve after an opening phase during a predetermined time interval for braking the plunger, the current is impressed on the actuator starting from an initial value of the current up to a predetermined final value of the current current. Here, the initial value of the current is smaller than the final value. Here, a duration of the time interval is predetermined depending on a coupling of the plunger with the sealing element.

Dies hat den Vorteil, dass das Ventil derart langsam geöffnet beziehungsweise geschlossen werden kann, dass eine Geräuschentwicklung des Ventils klein gehalten und dennoch ein zuverlässiges und ausreichend rasches Öffnen beziehungsweise Schließen des Ventils erreicht werden kann. Des Weiteren kann ein Verschleiß des Ventils klein gehalten werden. Darüber hinaus ist eine kostengünstige Ausführung des Ventils möglich. Der Aktuator weist somit zwei Funktionen auf. Zum einen weist der Aktuator die Funktion eines Ventilstellgliedes auf. Ferner ermöglicht der Aktuator ein Dämpfen des Auftreffens des Stößels auf den Dichtsitz und/oder auf das Dichtelement und/oder der Aktuator ermöglicht das Dämpfen des Auftreffens des Dichtelements auf eine Endpositionsbegrenzung, beispielsweise auf eine Ventilgehäusewand. Vorzugsweise weist der Aktuator einen Elektromagneten auf. Während des Zeitintervalls, bei dem der Aktuator zum Abbremsen des Stößels aktiviert wird, kann der Stößel aus einem Magnetfeld des Aktuators zumindest teilweise herausgeschoben werden, so dass sich die Aktuatorkraft, die auf den Stößel wirkt, verringert, je weiter der Stößel aus dem Magnetfeld herausgeschoben wird. Vorteilhafterweise kann durch den ansteigenden Verlauf des Stromes von dem Anfangswert zu dem Endwert dieser Effekt kompensiert werden und die Aktuatorkraft kann näherungsweise konstant gehalten werden. Die Vorgabe der Dauer des Zeitintervalls abhängig von einer Kopplung des Stößels mit dem Dichtelement ermöglicht, eine durch die Aktuatorkraft bewirkte Bremswirkung des Stößels und/oder des Dichtelements beim Öffnungsvorgang beziehungsweise Schließvorgang des Ventils einem Ventiltyp und/oder einem Anwendungsbereich anzupassen.
In einer vorteilhaften Ausgestaltung wird ein Beginn einer Ventilöffnung des stromlos offenen Ventils detektiert und, sobald der Beginn der Ventilöffnung erkannt wird, wird abhängig von dem erkannten Beginn der Ventilöffnung ein Start des Zeitintervalls vorgegeben. Der Beginn der Ventilöffnung kann mittels einer Erfassung einer Bewegung des Stößels entlang einer Längsachse des Stößels detektiert werden. Beispielsweise kann das Zeitintervall gestartet werden, sobald erkannt wird, dass sich der Stößel ausgehend von einer Anfangsposition des Stößels, in der der Stößel ein Öffnen des Ventils erlaubt oder das Ventil geschlossen ist, in Richtung einer Endposition des Stößels bewegt, in der der Stößel das Schließen des Ventils nicht erlaubt beziehungsweise das Ventil offen ist. Ferner kann der Start des Zeitintervalls abhängig von einem Ventiltyp und/oder abhängig von zumindest einem Betriebsparameter des Ventils vorgegeben werden.This has the advantage that the valve can be opened or closed so slowly that a noise the valve kept small and yet a reliable and sufficiently rapid opening or closing of the valve can be achieved. Furthermore, wear of the valve can be kept small. In addition, a cost-effective design of the valve is possible. The actuator thus has two functions. On the one hand, the actuator has the function of a valve actuator. Further, the actuator allows damping of the impingement of the plunger on the sealing seat and / or on the sealing element and / or the actuator allows the damping of the impingement of the sealing element to an end position limit, for example on a valve housing wall. Preferably, the actuator has an electromagnet. During the time interval in which the actuator is activated to decelerate the plunger, the plunger can be at least partially pushed out of a magnetic field of the actuator so that the actuator force acting on the plunger decreases the farther the plunger is pushed out of the magnetic field becomes. Advantageously, this effect can be compensated for by the rising profile of the current from the initial value to the final value, and the actuator force can be kept approximately constant. The specification of the duration of the time interval as a function of a coupling of the tappet with the sealing element makes it possible to adapt a braking action of the tappet and / or the sealing element caused by the actuator force to a valve type and / or a field of application during the opening or closing operation of the valve.
In an advantageous embodiment, a start of a valve opening of the normally open valve is detected and, as soon as the beginning of the valve opening is detected, a start of the time interval is specified depending on the detected start of the valve opening. The beginning of the valve opening can be detected by detecting a movement of the plunger along a longitudinal axis of the plunger. For example, the time interval can be started as soon as it is detected that the plunger, starting from an initial position of the plunger, in which the plunger allows the valve to open or the valve is closed, moves in the direction of an end position of the plunger, in which the plunger Closing the valve is not allowed or the valve is open. Furthermore, the start of the time interval can be predetermined as a function of a valve type and / or as a function of at least one operating parameter of the valve.

In einer weiteren vorteilhaften Ausgestaltung wird ein Beginn einer Ventilschließung des stromlos geschlossenen Ventils detektiert und sobald der Beginn der Ventilschließung erkannt wird, wird abhängig von dem erkannten Beginn der Ventilschließung der Start des Zeitintervalls vorgegeben. Beispielsweise kann das Zeitintervall gestartet werden, sobald erkannt wird, dass sich der Stößel ausgehend von der Anfangsposition des Stößels, in der der Stößel ein Schließen des Ventils erlaubt oder das Ventil geöffnet ist, in Richtung einer Endposition des Stößels bewegt, in der der Stößel das Öffnen des Ventils nicht erlaubt beziehungsweise das Ventil geschlossen ist.In a further advantageous embodiment, a beginning of a valve closing of the normally closed valve is detected and as soon as the beginning of the valve closing is detected, the start of the time interval is specified depending on the detected start of the valve closing. For example, the time interval can be started as soon as it is detected that the plunger, starting from the initial position of the plunger, in which the plunger allows the valve to close or the valve is opened, moves in the direction of an end position of the plunger, in which the plunger Opening the valve is not allowed or the valve is closed.

In einer weiteren vorteilhaften Ausgestaltung ist das Ventil in einem Einlassbereich einer Pumpe angeordnet und der Stößel ist direkt gekoppelt mit dem Dichtelement. Hierbei ist die Dauer des Zeitintervalls näherungsweise gleich 15% bis 20% einer Zeitdauer einer Förderphase der Pumpe.In a further advantageous embodiment, the valve is arranged in an inlet region of a pump and the plunger is directly coupled to the sealing element. Here, the duration of the time interval is approximately equal to 15% to 20% of a period of a delivery phase of the pump.

In einer weiteren vorteilhaften Ausgestaltung ist das Ventil in dem Einlassbereich der Pumpe angeordnet und der Stößel ist koppelbar mit dem Dichtelement. Hierbei ist die Dauer des Zeitintervalls näherungsweise gleich 50% der Zeitdauer der Förderphase der Pumpe.In a further advantageous embodiment, the valve is arranged in the inlet region of the pump and the plunger is coupled with the sealing element. Here, the duration of the time interval is approximately equal to 50% of the duration of the delivery phase of the pump.

In einer weiteren vorteilhaften Ausgestaltung wird der Endwert des Stromes abhängig von der Federkraft der Feder vorgegeben. Vorteilhafterweise ermöglicht dies, den Endwert des Stromes so vorzugeben, dass das Ventil ausreichend schnell geöffnet beziehungsweise geschlossen werden kann und es kann sichergestellt werden, dass sich das Ventil öffnet beziehungsweise schließt.In a further advantageous embodiment of the final value of the current is determined depending on the spring force of the spring. Advantageously, this makes it possible to specify the final value of the flow in such a way that the valve can be opened or closed sufficiently quickly, and it can be ensured that the valve opens or closes.

In einer weiteren vorteilhaften Ausgestaltung ist der Verlauf des Stroms stufenförmig vorgegeben. Der Verlauf des Stromes kann mehrere zeitlich aufeinander folgende Abschnitte aufweisen, wobei jeder der Abschnitte jeweils einen Wert des Stroms mit einem im Wesentlichen konstanten Stromverlauf aufweist und der zeitlich auf einen vorhergehenden Abschnitt folgende Abschnitt einen größeren Wert des Stromes aufweist als der vorhergehende Abschnitt. Dies hat den Vorteil, dass der Verlauf des Stroms eine einfache und leicht herstellbare Form aufweist.In a further advantageous embodiment, the course of the current is predetermined stepwise. The course of the current may have a plurality of temporally successive sections, each of the sections each having a value of the current having a substantially constant current profile, and the section following in time to a preceding section having a greater value of the current than the preceding section. This has the advantage that the course of the current has a simple and easily producible form.

Ausführungsbeispiele der Erfindung sind im Folgenden anhand von schematischen Zeichnungen näher erläutert. Es zeigen:

Figur 1
eine Pumpe mit einem ersten Ausführungsbeispiel eines Ventils in einem Längsschnitt,
Figur 2
die Pumpe mit einem zweiten Ausführungsbeispiel des Ventils in einem Längsschnitt,
Figur 3A - 3C
ein drittes Ausführungsbeispiel des Ventils in drei Betriebszuständen und
Figur 4
einen Stromverlauf und einen zeitlichen Verlauf einer Position eines Stößels.
Embodiments of the invention are explained in more detail below with reference to schematic drawings. Show it:
FIG. 1
a pump with a first embodiment of a valve in a longitudinal section,
FIG. 2
the pump with a second embodiment of the valve in a longitudinal section,
FIGS. 3A-3C
a third embodiment of the valve in three operating states and
FIG. 4
a current waveform and a time course of a position of a plunger.

Elemente gleicher Konstruktion oder Funktion sind figurenübergreifend mit den gleichen Bezugszeichen gekennzeichnet.Elements of the same construction or function are identified across the figures with the same reference numerals.

Figur 1 zeigt eine Pumpe 10 mit einem Pumpengehäuse 12. Die Pumpe 10 ist insbesondere als Hochdruckpumpe, vorzugsweise als Radialkolbenpumpe ausgebildet. In dem Pumpengehäuse 12 ist ein Pumpenkolben 14 bewegbar gelagert. In dem Pumpengehäuse 12 befindet sich an einem Ende des Pumpenkolbens 14 ein Druckraum 16. Um den Druckraum 16 mit Fluid befüllen zu können, weist dieser eine Zulaufleitung 18 auf, in der vorzugsweise ein als Einlassventil ausgebildetes Ventil 20 angeordnet ist. Das als Einlassventil ausgebildete Ventil 20 ist vorzugsweise als digital geschaltetes Ventil ausgebildet. Das Ventil 20 erleichtert die Befüllung des Druckraums 16 und verhindert beim Befüllen das Zurückströmen des Fluids aus der Zulaufleitung 18. Der Druckraum 16 weist weiter eine Ablaufleitung 22 auf, in der ein als Auslassventil ausgebildetes weiteres Ventil 24 angeordnet ist. Damit kann Fluid aus dem Druckraum 16 ausgestoßen werden. FIG. 1 shows a pump 10 with a pump housing 12. The pump 10 is in particular designed as a high pressure pump, preferably as a radial piston pump. In the pump housing 12, a pump piston 14 is movably mounted. In the pump housing 12 is located at one end of the pump piston 14, a pressure chamber 16. In order to fill the pressure chamber 16 with fluid, this has a supply line 18, in which preferably designed as an inlet valve valve 20 is arranged. The valve 20 designed as an inlet valve is preferably designed as a digitally switched valve. The valve 20 facilitates the filling of the pressure chamber 16 and prevents during filling the backflow of the fluid from the feed line 18. The pressure chamber 16 further has a drain line 22, in which a valve designed as an outlet valve 24 is arranged. This fluid can be ejected from the pressure chamber 16.

Die Pumpe 10 weist weiter eine Antriebswelle 26 auf, die mit einem Exzenterring 28 in Wirkverbindung steht und in einer Drehrichtung D im Uhrzeigersinn drehbar ist. Anstelle des Exzenterrings 28 kann auch eine Nockenwelle eingesetzt werden. Alternativ kann die Pumpe 10 auch als Kurbeltriebpumpe ausgeführt sein.The pump 10 further has a drive shaft 26, which is in operative connection with an eccentric ring 28 and is rotatable in a rotational direction D in the clockwise direction. Instead of the eccentric ring 28 and a camshaft can be used. Alternatively, the pump 10 may also be designed as a crank drive pump.

Figur 1 zeigt ein erstes Ausführungsbeispiel des Ventils 20. Das Ventil 20 umfasst ein Ventilgehäuse 29, das eine Ausnehmung 30 aufweist. In der Ausnehmung 30 sind eine Feder 32, ein Stößel 34 und ein Dichtelement 36 angeordnet. Die Feder 32 spannt das Dichtelement 36 über den Stößel 34 vor, indem sie sich an einer Wand der Ausnehmung 30 abstützt. Das Dichtelement 36 und der Stößel 34 sind direkt mechanisch gekoppelt. Der Stößel 34 umfasst einen ersten zylinderförmigen Teil 34a und einen zweiten zylinderförmigen Teil 34b, wobei der erste Teil 34a einen größeren Durchmesser aufweist als der zweite Teil 34b. FIG. 1 shows a first embodiment of the valve 20. The valve 20 includes a valve housing 29 having a recess 30. In the recess 30, a spring 32, a plunger 34 and a sealing element 36 are arranged. The spring 32 biases the sealing element 36 over the plunger 34 by being supported on a wall of the recess 30. The sealing element 36 and the plunger 34 are mechanically coupled directly. The plunger 34 comprises a first cylindrical part 34a and a second cylindrical part 34b, wherein the first part 34a has a larger diameter than the second part 34b.

In der Ausnehmung 30 befindet sich weiter ein gegenüber dem Ventilgehäuse 29 fest angeordneter Dichtsitz 38, der Durchgangsausnehmungen 40 aufweist. Über die Durchgangsausnehmungen 40 kann Fluid strömen, wenn das Dichtelement 36 nicht an dem Dichtsitz 38 anliegt.In the recess 30 is further located opposite the valve housing 29 fixedly arranged sealing seat 38, the through holes 40 has. Fluid can flow via the passage recesses 40 when the sealing element 36 is not in contact with the sealing seat 38.

Das Ventil 20 weist weiter einen Aktuator 42 auf, der insbesondere als Magnetspule ausgebildet ist. Der erste Teil 34a des Stößels 34 ist zumindest teilweise innerhalb des Aktuators 42 angeordnet und kann von dem Aktuator 42 betätigt werden.The valve 20 further comprises an actuator 42, which is designed in particular as a magnetic coil. The first part 34 a of the plunger 34 is at least partially disposed within the actuator 42 and can be actuated by the actuator 42.

Sowohl beim Öffnen als auch beim Schließen des Ventils 20 können aufgrund mechanischer und hydraulischer Ursachen Geräusche an dem Ventil 20 auftreten. Der Stößel 34 wird durch die Federkraft F_1 der Feder 32 auf den Dichtsitz 38 zu bewegt. Treffen der Dichtsitz 38 und der Stößel 34, insbesondere der erste Teil 34a des Stößels 34, aufeinander, so kann ein Geräusch auftreten. Ein Aktivieren des Aktuators 42 beispielsweise kurz bevor der Stößel 34 seine Endposition erreicht hat, bei der das Ventil 20 maximal geöffnet ist und der erste Teil 34a des Stößels 34 an dem Dichtsitz 38 anliegt, ermöglicht, dass der Stößel 34 abgebremst werden kann und das Auftreffen des Stößels 34 auf den Dichtsitz 38 gedämpft werden kann.Both when opening and when closing the valve 20 may occur due to mechanical and hydraulic causes noise on the valve 20. The plunger 34 is moved by the spring force F_1 of the spring 32 to the sealing seat 38. If the sealing seat 38 and the plunger 34, in particular the first part 34a of the plunger 34, meet, a noise may occur. One Activation of the actuator 42, for example, just before the plunger 34 has reached its end position, in which the valve 20 is opened to the maximum and the first part 34a of the plunger 34 abuts the sealing seat 38, allows the plunger 34 can be braked and the impact of the Tappet 34 can be attenuated to the sealing seat 38.

Figur 2 zeigt ein zweites Ausführungsbeispiel des Ventils 20. Im Vergleich zu dem ersten Ausführungsbeispiel sind der Stößel 34 und das Dichtelement 36 nicht direkt mechanisch gekoppelt. Ferner weist die Ausnehmung ein Endpositionsbegrenzungselement 44 auf, das angeordnet und ausgebildet ist, eine axiale Bewegung des Stößels 34 und/oder des Dichtelements 36 in Richtung Druckraum 16 zu begrenzen. Das Endpositionsbegrenzungselement 44 weist weitere Ausnehmungen 46 auf, über die Fluid in den Druckraum 16 strömen kann. FIG. 2 shows a second embodiment of the valve 20. Compared to the first embodiment, the plunger 34 and the sealing element 36 are not mechanically coupled directly. Furthermore, the recess has an end position limiting element 44, which is arranged and designed to limit an axial movement of the plunger 34 and / or the sealing element 36 in the direction of the pressure chamber 16. The end position limiting element 44 has further recesses 46, via which fluid can flow into the pressure chamber 16.

Sowohl beim Öffnen als auch beim Schließen des Ventils 20 können aufgrund mechanischer und hydraulischer Ursachen Geräusche an dem Ventil 20 auftreten. Beim Öffnen des Ventils 20 gelangt in einem ersten Schritt das Dichtelement 36 in Anschlag mit dem Endpositionsbegrenzungselement 44, wodurch ein erstes Geräusch auftreten kann. Der Stößel 34 wird anschließend durch die Federkraft F_1 der Feder 32 auf das Dichtelement 36 zu bewegt. Treffen das Dichtelement 36 und der Stößel 34 aufeinander, so kann ein weiteres Geräusch auftreten. Ein Aktivieren des Aktuators 42 beispielsweise kurz bevor der Stößel 34 auf das Dichtelement 36 auftritt, ermöglicht, dass der Stößel 34 abgebremst werden kann und das Auftreffen des Stößels 34 auf das Dichtelement 36 gedämpft werden kann.Both when opening and when closing the valve 20 may occur due to mechanical and hydraulic causes noise on the valve 20. When opening the valve 20, in a first step, the sealing element 36 comes into abutment with the Endpositionsbegrenzungselement 44, whereby a first noise can occur. The plunger 34 is then moved toward the sealing element 36 by the spring force F_1 of the spring 32. If the sealing element 36 and the plunger 34 meet, another noise can occur. Activation of the actuator 42, for example just before the plunger 34 occurs on the sealing element 36, allows the plunger 34 can be braked and the impact of the plunger 34 can be damped on the sealing element 36.

Figur 3A zeigt ein drittes Ausführungsbeispiels des Ventils 20. Das Ventil 20 hat ein Ventilgehäuse 29, das eine Ausnehmung 30 aufweist. In der Ausnehmung 30 sind eine Feder 32, ein Stößel 34 und ein Dichtelement 36 angeordnet. Die Feder 32 spannt das Dichtelement 36 über den Stößel 34 vor, indem sie sich an einer Wand der Ausnehmung 30 abstützt. Das Dichtelement 36 und der Stößel 34 sind direkt mechanisch gekoppelt. Vorzugsweise sind das Dichtelement 36 und der Stößel 34 einstückig ausgebildet. Das Ventilgehäuse 29 umfasst einen Dichtsitz 38. Der Dichtsitz 38 und das Dichtelement 36 sind konisch ausgebildet, sodass wenn das Dichtelement 36 an dem Dichtsitz 38 anliegt, dass Ventil 20 geschlossen ist. Ferner umfasst das Ventil 20 das Endpositionsbegrenzungselement 44, das angeordnet und ausgebildet ist, eine axiale Bewegung des Stößels 34 und des Dichtelements 36 in Richtung Druckraum 16 zu begrenzen. Das Endpositionsbegrenzungselement 44 weist weitere Ausnehmungen 46 auf, über die Fluid in den Druckraum 16 strömen kann. FIG. 3A shows a third embodiment of the valve 20. The valve 20 has a valve housing 29 which has a recess 30. In the recess 30, a spring 32, a plunger 34th and a sealing element 36 is arranged. The spring 32 biases the sealing element 36 over the plunger 34 by being supported on a wall of the recess 30. The sealing element 36 and the plunger 34 are mechanically coupled directly. Preferably, the sealing element 36 and the plunger 34 are integrally formed. The valve housing 29 includes a sealing seat 38. The sealing seat 38 and the sealing element 36 are conical, so that when the sealing element 36 rests against the sealing seat 38 that valve 20 is closed. Further, the valve 20 includes the Endpositionsbegrenzungselement 44, which is arranged and adapted to limit an axial movement of the plunger 34 and the sealing element 36 in the direction of the pressure chamber 16. The end position limiting element 44 has further recesses 46, via which fluid can flow into the pressure chamber 16.

Beim Öffnen des Ventils 20 gelangt das Dichtelement 36 in Anschlag mit dem Endpositionsbegrenzungselement 44, wodurch ein Geräusch entstehen kann. Sind der Stößel 34 und das Dichtelement 36 zusammen einstückig ausgebildet, so kann durch die gemeinsame Masse von Stößel 34 und Dichtelement 36 das Geräusch sehr deutlich ausgebildet sein.When opening the valve 20, the sealing element 36 comes into abutment with the Endpositionsbegrenzungselement 44, whereby a noise can occur. If the plunger 34 and the sealing element 36 are integrally formed together, then the noise can be formed very clearly by the common mass of plunger 34 and sealing element 36.

Im Folgenden wird das Steuern des Ventils für ein stromlos offenes Ventil 20 im Detail erläutert (Figur 3A bis 3C) . Es versteht sich, dass dies in entsprechender Weise auf ein stromlos geschlossenes Ventil angewendet werden kann.Hereinafter, the control of the valve for a normally open valve 20 will be explained in detail ( FIGS. 3A to 3C ). It is understood that this can be applied in a corresponding manner to a normally closed valve.

Während der Förderphase (Figur 3A) der Pumpe 10 wird durch eine Drehbewegung der Antriebswelle 26 in einer Drehrichtung D der Pumpenkolben 14 durch den Exzenterring 28 von der Antriebswelle 26 weg bewegt und verdichtet dabei das in dem Druckraum 16 befindliche Fluid. Zu einem vorgegebenen Zeitpunkt wird das Ventil 20 durch Anlegen eines Stroms an den Aktuator 42 geschlossen, wodurch eine entgegen der Federkraft F_1 wirkende Aktuatorkraft F_2 auf den Stößel 34 wirken kann. Durch die Bewegung des Stößels 34 in Richtung der Aktuatorkraft F_2 und der herrschenden Druckverhältnisse vor und hinter dem Ventil 20 kann sich das Dichtelement 36 an den Dichtsitz 38 anlegen und eine Fluidströmung von der Zulaufleitung 18 in die Druckraum 16 ist unterbunden. Das in den Druckraum 16 verdichtete Fluid kann nun vollständig über das als Auslassventil ausgebildete weitere Ventil 24 aus der Pumpe 10 ausgestoßen werden. Am Ende der Förderphase hat der Pumpenkolben 14 seinen oberen Totpunkt erreicht.During the funding phase ( FIG. 3A ) of the pump 10 is moved by a rotational movement of the drive shaft 26 in a rotational direction D of the pump piston 14 through the eccentric ring 28 of the drive shaft 26 away and thereby compresses the fluid located in the pressure chamber 16. At a given time, the valve 20 is closed by applying a current to the actuator 42, thereby acting against the spring force F_1 Actuator force F_2 can act on the plunger 34. By the movement of the plunger 34 in the direction of the actuator force F_2 and the prevailing pressure conditions in front of and behind the valve 20, the sealing element 36 can rest against the sealing seat 38 and a fluid flow from the supply line 18 into the pressure chamber 16 is prevented. The compressed in the pressure chamber 16 fluid can now be completely discharged from the pump 10 via the formed as an outlet valve further valve 24. At the end of the delivery phase, the pump piston 14 has reached its top dead center.

Handelt es sich bei der Pumpe 10 um eine Kraftstoffhochdruckpumpe einer Einspritzanlage einer Brennkraftmaschine, so kann der mit hohem Druck beaufschlagte Kraftstoff zu einem als Hochdruckkraftstoffspeicher ausgebildeten Fluidspeicher, dem so genannten Common Rail, gelangen.If the pump 10 is a high-pressure fuel pump of an injection system of an internal combustion engine, the fuel subjected to high pressure can reach a fluid reservoir, known as a common-rail, which is designed as a high-pressure fuel reservoir.

Zu Beginn einer Saugphase der Pumpe 10 (Figur 3B) wird durch die weitere Drehbewegung der Antriebswelle 26 in der Drehrichtung D der Pumpenkolben 14 mittels des Exzenterrings 28 zu der Antriebswelle 26 hin bewegt. Dabei beginnt sich das Ventil 20 aufgrund der Federkraft F_1 der Feder 32 und der Druckdifferenz vor und hinter dem Ventil 20 zu öffnen.At the beginning of a suction phase of the pump 10 (FIG. FIG. 3B ) is moved by the further rotational movement of the drive shaft 26 in the direction of rotation D of the pump piston 14 by means of the eccentric ring 28 to the drive shaft 26 through. In this case, the valve 20 begins due to the spring force F_1 of the spring 32 and the pressure difference before and behind the valve 20 to open.

Nach der Schließphase des Ventils 20 beziehungsweise nach der Förderphase der Pumpe 10 wird während eines vorgegebenen Zeitintervalls dem Aktuator 42 ein Strom mit einem vorgegebenen Verlauf aufgeprägt ausgehend von einem Anfangswert I_0 des Stromes bis zu einem vorgegebenen Endwert I_END des Stromes, wobei der Anfangswert I_0 des Stromes kleiner ist als der Endwert I_End. Das Zeitintervall kann beispielsweise unmittelbar nach dem Ende der Förderphase starten oder zu einem späteren Zeitpunkt, bei dem sich der Stößel 34 bereits bewegt und/oder sich das Dichtelement 36 bereits zumindest teilweise von dem Dichtsitz 38 abgehoben hat.After the closing phase of the valve 20 or after the delivery phase of the pump 10, the current is impressed on the actuator 42 for a predetermined time interval starting from an initial value I_0 of the current up to a predetermined final value I_END of the current, the initial value I_0 of the current is less than the final value I_End. The time interval may start, for example, immediately after the end of the delivery phase or at a later time, in which the plunger 34 already moves and / or itself the sealing element 36 has already lifted at least partially from the sealing seat 38.

Beispielsweise kann ein Beginn einer Ventilöffnung des Ventils 20 detektiert werden und sobald der Beginn der Ventilöffnung erkannt wird, abhängig von dem erkannten Beginn der Ventilöffnung ein Start des Zeitintervalls vorgegeben werden. Der Start kann zeitlich unmittelbar nach dem Erkennen des Beginns der Ventilöffnung erfolgen oder nach einer kurzen Zeitdauer nach dem Erkennen des Beginns. Die kurze Zeitdauer kann beispielsweise vorgegeben werden abhängig von einer durchschnittlichen Ventilöffnungszeit des Ventils 20.For example, a start of a valve opening of the valve 20 can be detected and as soon as the beginning of the valve opening is detected, depending on the recognized start of the valve opening, a start of the time interval can be specified. The start can take place immediately after the detection of the beginning of the valve opening or after a short period of time after the detection of the beginning. The short period of time may be predetermined, for example, depending on an average valve opening time of the valve 20.

Die von dem mit Strom beaufschlagten Aktuator 42 erzeugte Aktuatorkraft F_2 wirkt der Federkraft F_1 und Druckdifferenz entgegen, sodass der Stößel 34 und/oder das Dichtelement 36 in ihrer Bewegung abgebremst werden. So wird die Bewegung des Stößels 34 auf den Dichtsitz 38 hin (Figur 1) und/oder die Bewegung des Stößels 34 auf das Dichtelement 36 hin (Figur 2) oder die Bewegung des Stößels 34 und des Dichtelements 36 hin zum Endpositionsbegrenzungselement 44(Figur 3B) abgebremst. Durch die verringerte Geschwindigkeit kann ein Auftreffgeräusch wesentlich reduziert werden. Durch die langsame Bewegung des Stößels 34 kann die Geräuschentwicklung des Ventils 20 sehr klein gehalten werden und das Ventil 20 dennoch zuverlässig und ausreichend rasch geöffnet werden. Durch die langsame Bewegung des Stößels 34 kann darüber hinaus der Verschleiß des Ventils 20 klein gehalten werden.The actuator force F_2 generated by the energized actuator 42 counteracts the spring force F_1 and pressure difference, so that the plunger 34 and / or the sealing element 36 are braked in their movement. Thus, the movement of the plunger 34 toward the sealing seat 38 ( FIG. 1 ) and / or the movement of the plunger 34 towards the sealing element 36 ( FIG. 2 ) or the movement of the plunger 34 and the sealing element 36 toward the end position limiting element 44 (FIG. FIG. 3B ) decelerated. Due to the reduced speed, an impact noise can be significantly reduced. Due to the slow movement of the plunger 34, the noise of the valve 20 can be kept very small and the valve 20 can still be opened reliably and quickly enough. In addition, the slow movement of the plunger 34, the wear of the valve 20 can be kept small.

Der vorgegebene ansteigende Verlauf des Stromes ausgehend von einem Anfangswert I_0 des Stromes bis zu einem vorgegebenen Endwert I_END des Stromes ermöglicht, ein zumindest teilweises Herausbewegen des Stößels aus einem Magnetfeld des Aktuators 42 zu kompensieren und so die Aktuatorkraft F_2 näherungsweise konstant zuhalten. Der Verlauf des Stroms kann beispielsweise stufenförmig vorgegeben sein. Figur 4 zeigt eine schematische Ansicht des Stromverlaufs und einen zeitlichen Verlauf der Position POS des Stößels 34 bezogen auf eine Anfangsposition des Stößels 34, in der das stromlos offene Ventil 20 geschlossen ist.The predetermined rising profile of the current starting from an initial value I_0 of the current up to a predetermined final value I_END of the current makes it possible to compensate for at least partial removal of the plunger from a magnetic field of the actuator 42 and thus approximates the actuator force F_2 keep constant. The course of the current can be predetermined, for example stepwise. FIG. 4 shows a schematic view of the current flow and a time course of the position POS of the plunger 34 with respect to an initial position of the plunger 34, in which the normally open valve 20 is closed.

Eine Dauer des Zeitintervalls kann beispielsweise abhängig von einer Kopplung des Stößels 34 mit dem Dichtelement 36 vorgeben werden. Ist zum Beispiel der Stößel 34 direkt gekoppelt ist mit dem Dichtelement 36 kann die Dauer des Zeitintervalls gleich näherungsweise 15% bis 20% einer Zeitdauer der Förderphase der Pumpe 10 sein.A duration of the time interval can be predetermined, for example, depending on a coupling of the plunger 34 with the sealing element 36. For example, if the plunger 34 is directly coupled to the sealing member 36, the duration of the time interval may be approximately 15% to 20% of a duration of the delivery phase of the pump 10.

Sind der Stößel 34 und das Dichtelement 36 nicht direkt mechanisch gekoppelt, sondern koppelbar angeordnet, kann die Dauer des Zeitintervalls gleich näherungsweise 50% der Zeitdauer der Förderphase der Pumpe 10 sein.If the plunger 34 and the sealing element 36 are not directly mechanically coupled, but arranged to be coupled, the duration of the time interval may be equal to approximately 50% of the duration of the delivery phase of the pump 10.

Der Endwert I_END des Stromes kann beispielsweise abhängig von der Federkraft F_1 der Feder 32 vorgegeben werden. Der Anfangswert I_0 des Stromes kann beispielsweise Null sein.The final value I_END of the current can be predetermined, for example, depending on the spring force F_1 of the spring 32. The initial value I_0 of the current may be zero, for example.

Während einer Fortsetzung der Saugphase (Figur 3C) der Pumpe 10 wird durch eine Fortsetzung der weitern Drehbewegung der Antriebswelle 26 in der Drehrichtung D der Pumpenkolben 14 mittels des Exzenterrings 28 weiter zu der Antriebswelle 26 hin bewegt. Das Ventil 20 ist geöffnet. Der Druckraum 16 wird nun mit Fluid befüllt.During a continuation of the suction phase ( FIG. 3C ) of the pump 10 is further moved by a continuation of the further rotation of the drive shaft 26 in the direction of rotation D of the pump piston 14 by means of the eccentric ring 28 to the drive shaft 26. The valve 20 is open. The pressure chamber 16 is now filled with fluid.

Claims (8)

  1. Method for controlling a valve (20) that comprises a spring (32) having a spring force (F_1), an actuator (42) having an actuator force (F_2) acting against the spring force (F_1), and a tappet (34) which can be actuated by means of the actuator (42), a sealing element (36), which is or can be coupled to the tappet (34), and a sealing seat (38), so that the valve (20) is closed when the sealing element (36) bears on the sealing seat (38), in which
    - following a closing phase of the valve (20) in the case of a normally open valve, or following an opening phase in the case of a normally closed valve, a current having a predefined rising course is impressed on the actuator (42) during a predefined time interval in order to brake the tappet (34), starting from an initial value (I_0) of the current to a predefined final value (I_END) of the current, wherein the initial value (I_0) of the current is lower than the final value (I_END) and a duration of the time interval is predefined on the basis of a coupling between the tappet (34) and the sealing element (36).
  2. Method according to Claim 1, in which a beginning of a valve opening of the normally open valve is detected and, as soon as the beginning of the valve opening is detected, a start of the time interval is predefined on the basis of the detected beginning of the valve opening.
  3. Method according to Claim 1, in which a beginning of a valve closure of a normally closed valve is detected and, as soon as the beginning of the valve closure is detected, the start of the time interval is predefined on the basis of the detected beginning of the valve closure.
  4. Method according to one of the preceding claims, in which the valve (20) is arranged in an inlet area of a pump (10) and the tappet (34) is coupled directly to the sealing element (36), and the duration is equal to approximately 15% to 20% of a time period of a delivery phase of the pump (10).
  5. Method according to one of the preceding Claims 1 to 3, in which the valve (20) is arranged in the inlet area of the pump (10) and the tappet (34) can be coupled to the sealing element (36) and the duration is equal to approximately 50% of the time period of the delivery phase of the pump (10).
  6. Method according to one of the preceding claims, in which the final value (I_END) of the current is predefined on the basis of the spring force (F_1) of the spring (32)
  7. Method according to one of the preceding claims, in which the course of the current is predefined in the form of steps.
  8. Device for controlling a valve (20) that comprises a spring (32) having a spring force (F_1), an actuator (42) having an actuator force (F_2) that acts against the spring force (F_1), and a tappet (34) which can be actuated by means of the actuator (42), a sealing element (36), which is or can be coupled to the tappet (34), and a sealing seat (38), so that the valve (20) is closed when the sealing element (36) bears on the sealing seat (38), wherein the device is designed
    - following a closing phase of the valve (20) in the case of a normally open valve, or following an opening phase in the case of a normally closed valve, to impress a current having a predefined rising course on the actuator (42) during a predefined time interval in order to brake the tappet (34), starting from an initial value (I_0) of the current to a predefined final value (I_END) of the current, wherein the initial value (I_0) of the current is lower than the final value (I_END) and a duration of the time interval is predefined on the basis of a coupling between the tappet (34) and the sealing element (36).
EP12718664.1A 2011-05-04 2012-05-03 Method and device for controlling a valve Active EP2705235B1 (en)

Applications Claiming Priority (2)

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DE102011075270A DE102011075270A1 (en) 2011-05-04 2011-05-04 Method and device for controlling a valve
PCT/EP2012/058151 WO2012150308A2 (en) 2011-05-04 2012-05-03 Method and device for controlling a valve

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EP2705235A2 EP2705235A2 (en) 2014-03-12
EP2705235B1 true EP2705235B1 (en) 2016-10-19

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EP12718664.1A Active EP2705235B1 (en) 2011-05-04 2012-05-03 Method and device for controlling a valve

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US (1) US9382860B2 (en)
EP (1) EP2705235B1 (en)
KR (1) KR101871299B1 (en)
CN (1) CN103620197B (en)
DE (1) DE102011075270A1 (en)
WO (1) WO2012150308A2 (en)

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DE102011075270A1 (en) 2011-05-04 2012-11-08 Continental Automotive Gmbh Method and device for controlling a valve

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KR101871299B1 (en) 2018-06-27
CN103620197A (en) 2014-03-05
EP2705235A2 (en) 2014-03-12
US9382860B2 (en) 2016-07-05
DE102011075270A1 (en) 2012-11-08
WO2012150308A3 (en) 2013-01-17
WO2012150308A2 (en) 2012-11-08
US20140196691A1 (en) 2014-07-17
CN103620197B (en) 2018-05-22
KR20140027385A (en) 2014-03-06

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