EP2705235A2 - Procédé et dispositif de commande d'une soupape - Google Patents

Procédé et dispositif de commande d'une soupape

Info

Publication number
EP2705235A2
EP2705235A2 EP12718664.1A EP12718664A EP2705235A2 EP 2705235 A2 EP2705235 A2 EP 2705235A2 EP 12718664 A EP12718664 A EP 12718664A EP 2705235 A2 EP2705235 A2 EP 2705235A2
Authority
EP
European Patent Office
Prior art keywords
valve
plunger
current
actuator
sealing element
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.)
Granted
Application number
EP12718664.1A
Other languages
German (de)
English (en)
Other versions
EP2705235B1 (fr
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
Original Assignee
Continental Automotive GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Continental Automotive GmbH filed Critical Continental Automotive GmbH
Publication of EP2705235A2 publication Critical patent/EP2705235A2/fr
Application granted granted Critical
Publication of EP2705235B1 publication Critical patent/EP2705235B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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.
  • the object of the invention is to provide a method and a
  • 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 to the plunger or is coupled, and a sealing seat, so that the valve is closed when the sealing element is applied to the sealing seat.
  • the current impressed with a predetermined course from an initial value of the current up to a predetermined final value of the current.
  • the initial value of the current is smaller than the final value.
  • the actuator thus has two functions. On the one hand, the actuator has the function of a valve actuator. Furthermore, the actuator allows damping of the impact 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 to a
  • 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 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 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 be ⁇ as the valve is closed.
  • a duration of the time interval is predetermined depending on a coupling of the plunger with the sealing element. This allows one through the
  • Actuator force caused braking action of the plunger and / or the sealing element during opening or closing Process of the valve to a valve type and / or a field of application.
  • the valve is arranged in an inlet region of a pump and the plunger is directly coupled to the sealing element.
  • the duration of the time interval is approximately equal to 15% to 20% of a period of a delivery phase of the pump.
  • the valve is arranged in the inlet region of the pump and the plunger can be coupled to the sealing element.
  • the 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 predetermine 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 chronologically 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 with a first embodiment of a valve in a longitudinal section
  • FIG. 2 shows the pump with a second embodiment of the valve in a longitudinal section, Figure 3A - 3C, a third embodiment of the valve in three operating states and
  • Figure 4 shows a current waveform and a time course of a position of a plunger.
  • 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 Ra ⁇ dialkolbenpumpe.
  • 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 it ⁇ facilitates the filling of the pressure chamber 16 and prevented during the filling of the backflow of fluid from the supply line 18.
  • the pressure chamber 16 further includes a drain line 22 in which is embodied as a discharge valve further valve 24 is attached ⁇ 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 comprises a valve housing 29 which has a recess 30.
  • a spring 32 biases this
  • the plunger 34 comprises a first cylindrical part 34a and a second zy- linderförmige part 34b, wherein the first part 34a has a larger diameter than the second part 34b.
  • a sealing seat 38 which is fixedly arranged relative to the valve housing 29 and has passage openings 40. 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 toward the sealing seat 38 by the spring force F_l of the spring 32. 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.
  • Figure 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_l 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 Endposi- onsbegrenzungselement 44, which is arranged and designed 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.
  • the pump piston 14 is moved away from the drive shaft 26 by the eccentric ring 28 by rotational movement of the drive shaft 26 in a direction of rotation D, thereby compressing the fluid in the pressure chamber 16.
  • the valve 20 is closed by applying a current to the actuator 42, whereby an opposite to the spring force F l acting 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 accumulator.
  • 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 current-applied 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 towards 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 towards the end position limiting element 44 (FIG ) 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.
  • 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.
  • Figure 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_l of the spring 32.
  • the initial value I_0 of the current may be zero, for example.

Landscapes

  • 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)
  • Details Of Reciprocating Pumps (AREA)
  • Regulating Braking Force (AREA)

Abstract

L'invention concerne une soupape (20) comprenant un ressort (32) doté d'une force (F_1), un actionneur (42) doté d'une force (F_2) agissant à l'encontre de la force (F_1) et un poussoir (34) pouvant être actionné au moyen de l'actionneur (42). La soupape (20) comprend en outre un élément d'étanchéité (36) pouvant être accouplé au poussoir (34) ou accouplé à ce dernier, et un siège d'étanchéité (38), de sorte que la soupape (20) soit fermée lorsque l'élément d'étanchéité (36) repose contre le siège d'étanchéité (38). Un courant doté d'une allure prédéfinie est appliqué à l'actionneur (42) après une phase de fermeture de la soupape (20) lorsqu'une soupape est ouverte sans courant, ou après une phase d'ouverture lorsqu'une soupape est fermée sans courant, pendant un intervalle de temps prédéfini, à partir d'une valeur de départ (I_0) du courant jusqu'à une valeur finale prédéfinie (I_END) du courant. La valeur de départ (I_0) du courant est inférieure à la valeur finale (I_END).
EP12718664.1A 2011-05-04 2012-05-03 Procédé et dispositif de commande d'une soupape Active EP2705235B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011075270A DE102011075270A1 (de) 2011-05-04 2011-05-04 Verfahren und Vorrichtung zum Steuern eines Ventils
PCT/EP2012/058151 WO2012150308A2 (fr) 2011-05-04 2012-05-03 Procédé et dispositif de commande d'une soupape

Publications (2)

Publication Number Publication Date
EP2705235A2 true EP2705235A2 (fr) 2014-03-12
EP2705235B1 EP2705235B1 (fr) 2016-10-19

Family

ID=46026819

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12718664.1A Active EP2705235B1 (fr) 2011-05-04 2012-05-03 Procédé et dispositif de commande d'une soupape

Country Status (6)

Country Link
US (1) US9382860B2 (fr)
EP (1) EP2705235B1 (fr)
KR (1) KR101871299B1 (fr)
CN (1) CN103620197B (fr)
DE (1) DE102011075270A1 (fr)
WO (1) WO2012150308A2 (fr)

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Publication number Priority date Publication date Assignee Title
DE102011075270A1 (de) 2011-05-04 2012-11-08 Continental Automotive Gmbh Verfahren und Vorrichtung zum Steuern eines Ventils
DE102014225642B4 (de) * 2014-12-12 2016-06-30 Continental Automotive Gmbh Ventilanordnung und Hochdruckpumpe für ein Kraftstoffeinspritzsystem einer Brennkraftmaschine
CN106032797B (zh) * 2015-03-17 2018-06-08 德尔福（上海）动力推进系统有限公司 一种GDi油泵线圈驱动控制降噪方法
JP6710045B2 (ja) 2015-12-25 2020-06-17 日立オートモティブシステムズ株式会社 高圧燃料供給ポンプの制御方法およびそれを用いた高圧燃料供給ポンプ
DE102016219956B3 (de) * 2016-10-13 2017-08-17 Continental Automotive Gmbh Verfahren zum Einstellen eines Dämpfungsstroms eines Einlassventils eines Kraftfahrzeug-Hochdruckeinspritzsystems, sowie Steuervorrichtung, Hochdruckeinspritzsystem und Kraftfahrzeug
CN106594356B (zh) * 2016-12-05 2020-08-04 广东美的制冷设备有限公司 一种电磁阀降噪音控制方法、系统及空调
CN106594355B (zh) * 2016-12-05 2020-03-27 广东美的制冷设备有限公司 一种电磁阀开关控制方法、系统及空调
CN108736870B (zh) * 2017-04-20 2023-05-23 佛山市顺德区美的电热电器制造有限公司 驱动控制方法、驱动控制装置和烹饪器具
DE102017207705A1 (de) * 2017-05-08 2018-11-08 Robert Bosch Gmbh Verfahren zum Ansteuern eines Ventils
US10683825B1 (en) * 2018-12-04 2020-06-16 Delphi Technologies Ip Limited Fuel pump and inlet valve assembly thereof

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JP2002115591A (ja) 2000-10-04 2002-04-19 Nissan Motor Co Ltd 内燃機関の燃料噴射装置
DE10148218B4 (de) 2001-09-28 2005-08-25 Robert Bosch Gmbh Verfahren zum Betreiben einer Brennkraftmaschine, Computerprogramm, Steuer- und/oder Regelgerät, sowie Kraftstoffsystem für eine Brennkraftmaschine
CN100354561C (zh) * 2001-12-11 2007-12-12 萱场工业株式会社 电磁比例流量控制阀
DE102007003211A1 (de) 2007-01-22 2008-07-24 Robert Bosch Gmbh Vorrichtung und Verfahren zur Steuerung eines elektromagnetischen Ventils
JP4691523B2 (ja) 2007-05-09 2011-06-01 日立オートモティブシステムズ株式会社 電磁式燃料噴射弁の制御回路
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Also Published As

Publication number Publication date
US20140196691A1 (en) 2014-07-17
DE102011075270A1 (de) 2012-11-08
CN103620197A (zh) 2014-03-05
WO2012150308A2 (fr) 2012-11-08
EP2705235B1 (fr) 2016-10-19
US9382860B2 (en) 2016-07-05
KR101871299B1 (ko) 2018-06-27
KR20140027385A (ko) 2014-03-06
CN103620197B (zh) 2018-05-22
WO2012150308A3 (fr) 2013-01-17

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