EP1430201B1 - Procede de commande d'un systeme de controle de soupape electrohydraulique de moteur a combustion interne, programme d'ordinateur et ensamble de controle et de regulation pour commander un moteur a combustion interne - Google Patents

Procede de commande d'un systeme de controle de soupape electrohydraulique de moteur a combustion interne, programme d'ordinateur et ensamble de controle et de regulation pour commander un moteur a combustion interne Download PDF

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Publication number
EP1430201B1
EP1430201B1 EP02747175A EP02747175A EP1430201B1 EP 1430201 B1 EP1430201 B1 EP 1430201B1 EP 02747175 A EP02747175 A EP 02747175A EP 02747175 A EP02747175 A EP 02747175A EP 1430201 B1 EP1430201 B1 EP 1430201B1
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EP
European Patent Office
Prior art keywords
pressure
low
actuator
pressure hydraulic
working space
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02747175A
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German (de)
English (en)
Other versions
EP1430201A1 (fr
Inventor
Hans Schlembach
Hermann Gaessler
Udo Diehl
Karsten Mischker
Rainer Walter
Ulf Pischke
Andreas Baumann
Hurbert Schweiggart
Gerhard Filp
Bernd Rosenau
Jürgen Ulm
Uwe Hammer
Thomas Mocken
Sevan Tatiyosyan
Jürgen Schiemann
Christian Grosse
Volker Beuche
Stefan Reimer
Simon Kieser
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1430201A1 publication Critical patent/EP1430201A1/fr
Application granted granted Critical
Publication of EP1430201B1 publication Critical patent/EP1430201B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2800/00—Methods of operation using a variable valve timing mechanism

Definitions

  • the invention relates firstly to a method for operating an electrohydraulic valve control of an internal combustion engine, having at least one actuator operating on a gas exchange valve having at least one working space, which is connected to actuate the actuator from a first position to a second position with a high-pressure hydraulic accumulator and a low pressure -Rücklauf separated and which is connected to an actuation of the actuator from the second position to the first position back to the low-pressure return and separated from the high-pressure hydraulic accumulator.
  • Electrohydraulic valve controls of internal combustion engines allow the control of the gas exchange valves regardless of the position of the crankshaft or the camshaft. As a result, including gasoline savings and improvements in the emission characteristics of an internal combustion engine are possible.
  • the shaft of the gas exchange valve is connected to a hydraulic actuator.
  • This has two working spaces on both sides of the piston end faces, which are different in size.
  • the small face is constantly subjected to high pressure from a high-pressure hydraulic accumulator, which in turn is fed by a hydraulic pump.
  • the large end face of the piston is optionally also connected to the high-pressure hydraulic accumulator or to a low-pressure return line. Depending on results in a force resultant, which opens or closes the gas exchange valve.
  • the amount of hydraulic fluid flowing from the high-pressure hydraulic accumulator via the actuator to the low-pressure return and used to actuate the actuator can vary widely.
  • the amount of fluid delivered by the hydraulic pump into the high-pressure hydraulic accumulator can also vary, for example when the hydraulic pump is driven directly by the internal combustion engine and then there is a speed-dependent delivery rate of the hydraulic pump.
  • an overpressure or pressure regulating valve which, if a certain pressure is exceeded, discharges hydraulic fluid from the high-pressure hydraulic accumulator. Also, a regulation of the flow rate through the hydraulic pump is known. Furthermore, dynamic pressure peaks in the high-pressure hydraulic accumulator can be passively smoothed, for example, by a large volume of the high-pressure hydraulic accumulator.
  • the present invention therefore has the object, a method of the type mentioned in such a way that the pressure in the high pressure hydraulic accumulator can be kept constant in a simple manner.
  • This object is achieved in a method of the type mentioned in that a pressure maintenance or a pressure reduction in the high-pressure hydraulic accumulator is effected in that the working space is connected simultaneously with the high-pressure hydraulic accumulator and the low-pressure return.
  • the measure according to the invention allows a direct connection from the high-pressure hydraulic accumulator to the low-pressure return without additional components such. B. a pressure control valve, are necessary. To make this possible, an operating state is expressly permitted in which the working space is simultaneously connected to the high-pressure hydraulic accumulator and the low-pressure return of the electro-hydraulic valve control. If, for example, determined by a sensor, the need arises to remove hydraulic fluid from the high-pressure hydraulic accumulator to the pressure in this To keep constant, this can be done according to the invention in a simple manner via the working space for low-pressure return.
  • the working chamber of an actuator is connected simultaneously to the high-pressure hydraulic accumulator and the low-pressure return, whose associated gas exchange valve is currently closed.
  • This development of the method according to the invention is particularly useful when the actuation of the actuator and an opening of the gas exchange valve by applying the full pressure. In the closed state of rest of the gas exchange valve is thus in the working space of the actuator usually at a pressure which is less than the full high pressure of the high-pressure hydraulic accumulator.
  • the working pressure of an actuator is simultaneously connected to the high-pressure hydraulic accumulator and the low-pressure return to maintain pressure or pressure reduction in the high-pressure hydraulic accumulator whose associated gas exchange valve just can not open due to a high internal cylinder pressure.
  • an unintentional opening of the gas exchange valve is effectively prevented in response to pressure fluctuations in the working space "sensitive" actuator.
  • the working space of an actuator which is to be moved from the first position to the second position, is connected to the high-pressure hydraulic accumulator immediately before the separation from the low-pressure return, and / or the working space of an actuator, the of the second position is to be moved to the first position, is connected immediately before the separation of the high pressure hydraulic accumulator with the low pressure return.
  • the pressure maintenance or pressure reduction is combined by a simultaneous connection of the working space of an actuator with the low-pressure return and the high-pressure hydraulic accumulator with a control or regulation of the flow through a hydraulic pump. While very rapid and highly dynamic influence on the pressure in the high-pressure hydraulic accumulator can be taken by the said connection of the working space, the control or regulation of the flow through the hydraulic pump allows a long-term and quantitatively significant adjustment of the pressure in the high-pressure hydraulic accumulator.
  • the inventive method is particularly preferred when the actuator has two working spaces, which are separated by differently sized and oppositely acting pressure surfaces on a piston, and the one working space is constantly subjected to high pressure and the other working space with the high-pressure hydraulic accumulator and the low-pressure return can be connected. With such actuators very short switching times can be realized, which facilitates the implementation of the method according to the invention.
  • the hydraulic fluid from the working space can also flow into a low-pressure hydraulic accumulator.
  • the pressure difference is reduced in the outflow of the hydraulic fluid, which counteracts the occurrence of cavitation.
  • the invention also relates to a computer program programmed for use in a method according to any one of the preceding claims
  • the invention further relates to a control apparatus for operating an internal combustion engine, which is suitable for use in the above method.
  • an electrohydraulic valve control as a whole carries the reference numeral 10. It initially comprises a reservoir for hydraulic fluid, which in the present case bears the reference numeral 12 and which may be the oil sump of the internal combustion engine. From the hydraulic reservoir 12, the hydraulic fluid is conveyed from a controllable high-pressure hydraulic pump 14 into a high-pressure hydraulic accumulator 16. A hydraulic line 18 leads from the high-pressure hydraulic accumulator 16 via a pressure regulating valve 20 to a solenoid valve 22.
  • the hydraulic line 18 leads from the solenoid valve 22 on to an actuator 24.
  • This is a hydraulic cylinder with a double-acting piston 26.
  • the piston 26 is guided in a housing 28.
  • a first working space 30 is formed between this and the housing 28. This is connected to the solenoid valve 22.
  • a second working space 32 is formed between this and the housing 28. This is connected via a branch line 33 with that portion of the hydraulic line 18, which is located between the high-pressure hydraulic accumulator 16 and the solenoid valve 22.
  • the upper end surface 34 of the piston 26 in FIG. 1 is overall larger than the lower end surface 36 of the piston 26 which delimits the second working space 32.
  • the piston 26 is therefore a so-called "differential piston".
  • the piston 26 is connected to a gas exchange valve 38. This comprises a valve rod 40 and a valve element 42. Through the valve element 42, an opening (without reference numeral) of a combustion chamber 44 can be closed or opened.
  • the combustion chamber 44 is present in an engine block 46 of an internal combustion engine (without reference number).
  • a hydraulic line 48 via a second solenoid valve 50 leads to a low-pressure hydraulic accumulator 52.
  • This is in turn connected via a pressure control valve 54 with a low-pressure return 56, which eventually returns to the hydraulic reservoir 12.
  • a hydraulic line 58 leads via a pressure regulating valve 60 back to the high-pressure hydraulic accumulator 16.
  • the two solenoid valves 22 and 50 are actuated by magnetic actuators 62 and 64 and are each pressed by a compression spring 66 and 68 in their rest position.
  • the first solenoid valve 22 is in its rest position 70, in which the magnetic actuator 62 is not energized, closed, whereas it is open in the actuated switching position 72.
  • the second solenoid valve 50 is open in its closed position 74 and closed in the actuated switching position in which the magnetic plate 64 is energized. This switch position bears the reference numeral 76.
  • the electro-hydraulic valve control 10 also includes a control and regulating device 78. This is the output side connected to the magnetic actuators 62 and 64. Furthermore, it can also control the hydraulic pump 14. On the input side, the control and regulating device 78 is connected to a pressure sensor 80, which detects the pressure in the high-pressure hydraulic accumulator 16. Further, the control and regulating device 78 is connected to a speed sensor for the crankshaft of the internal combustion engine. This speed sensor bears the reference number 82.
  • the electrohydraulic valve control 10 is operated as follows (the method described hereafter is stored as a computer program on a ferrite RAM (not shown) in the control and regulation unit 78). To open the gas exchange valve 38, the piston 26 in Fig. 1 after move down. This is achieved in that from the rest position 74, the second solenoid valve 50 is energized and thus closed. The connection between the first working space 30 and the low-pressure hydraulic accumulator 52 is thus interrupted.
  • the magnetic controller 62 of the first solenoid valve 22 is energized by the control and regulation unit 78, then that this solenoid valve 22 moves from its closed rest position 70 into the open switching position 72.
  • the first working space 30 is connected to the high-pressure hydraulic accumulator 16. In the first working space 30 thus essentially the prevailing in the high-pressure hydraulic accumulator 16 hydraulic pressure.
  • the first solenoid valve 22 is de-energized by the control and regulating device 78 so that it is pressed by the open switch position 72 by the compression spring 66 in the closed switching position 70.
  • the connection between the high pressure hydraulic accumulator 16 and the first working space 30 is thus interrupted again.
  • the second solenoid valve 50 is de-energized by the control and regulating device 78, so that this moves due to the compression spring 68 from the closed switching position 76 in the open rest position 74.
  • the first working space 30 is again connected to the low-pressure hydraulic accumulator 52.
  • the pressure in the first working chamber 30 decreases until a force resulting results, which moves the piston 26 upwards again.
  • the gas exchange valve 38 closes.
  • the first solenoid valve 22 is controlled by the control and regulating device 78 into its open switching position 72, whereas the second solenoid valve 50 remains in its open rest position 74. It is assumed that the internal combustion engine is in an operating state in which the gas exchange valve 38, which is connected to the actuator 24, should remain closed.
  • the first solenoid valve 22 is now a direct connection from the high pressure hydraulic accumulator 16 via the first solenoid valve 22, the first working space 30 and the second solenoid valve 50 to the low pressure hydraulic accumulator 52 before.
  • hydraulic lines 18 and 48 By an appropriate design of the hydraulic lines 18 and 48 can be achieved that in this state, the pressure in the first working chamber 30 is never so high that an undesirable movement of the piston 26 is induced. Due to the direct connection from the high-pressure hydraulic accumulator 16 to the low-pressure hydraulic accumulator 52, hydraulic fluid can flow from the high-pressure hydraulic accumulator 16 directly to the low-pressure hydraulic accumulator 52, without this leading to an actuation of the actuator 24. Thus, the pressure in the high-pressure hydraulic accumulator 16 can be selectively reduced or kept constant.
  • the direct connection between high-pressure hydraulic accumulator 16 and low-pressure hydraulic accumulator 52 is preferably established when, due to a high pressure prevailing in the combustion chamber 44, the valve element 42 is pressed into its closed position becomes.
  • the electrohydraulic valve control 10 can still be operated in another way to keep the pressure in the high-pressure hydraulic accumulator 16 constant or lower:
  • connection of the high-pressure hydraulic accumulator 16 with the low-pressure hydraulic accumulator 52 can be coupled to an actuation of the actuator 24.
  • the actuator 24 Upon actuation of the actuator 24 to the effect that the gas exchange valve 38 opens, for example.
  • the solenoid valve 22 of its closed Resting position 70 are controlled in the actuated and open switching position 72.
  • the pressure in the high-pressure hydraulic accumulator 16 can be kept constant, as shown in FIG.
  • the amount of fluid to be discharged is controlled by the duration of the direct connection.
  • the pressure without a corresponding actuation of the solenoid valves 22 and 50 is shown in dashed lines, the pressure curve, which can be made by a corresponding actuation of the solenoid valves 22 and 50, shown in solid line.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

L'invention concerne une commande électrohydraulique des soupapes (10) d'un moteur à combustion interne. Cette commande comprend au moins un actionneur (24) qui agit sur une soupape d'échange des gaz (38). Cet actionneur dispose, à son tour, d'au moins un compartiment (30) qui est relié à un accumulateur hydraulique haute pression (16), pour commander l'actionneur (24) et faire quitter une première position et prendre une deuxième position et qui est coupé d'une conduite de retour de basse pression (56). Afin de commander l'actionneur (24) pour lui faire quitter la deuxième position et reprendre la première position, le compartiment (30) est raccordé à la conduite de retour de basse pression (56) et est coupé de l'accumulateur hydraulique haute pression (16). Pour facilement obtenir une conservation de la constante de pression ou une chute de pression dans l'accumulateur hydraulique haute pression (16), le compartiment (30) est simultanément relié à l'accumulateur hydraulique haute pression (16) et à la conduite de retour de basse pression (56).

Claims (10)

  1. Procédé pour faire fonctionner une commande de soupape (10) électrohydraulique d'un moteur à combustion interne comportant au moins un actionneur (24) qui agit sur une soupape d'échange de gaz (38) et muni d'au moins une chambre de travail (30), laquelle pour faire passer l'actionneur (24) d'une première position à une deuxième position est reliée à un accumulateur hydraulique à haute pression (16) et est séparée d'un retour à basse pression (56), alors que pour faire passer l'actionneur (24) de la deuxième position à la première position est de nouveau reliée au retour à basse pression (56) et elle est séparée de l'accumulateur hydraulique à haute pression (16),
    caractérisé en ce que
    la pression est maintenue constante ou est abaissée dans l'accumulateur hydraulique à haute pression (16) en reliant la chambre de travail (30) en même temps à l'accumulateur hydraulique à haute pression (16) et au retour à basse pression (56).
  2. Procédé selon la revendication 1,
    caractérisé en ce que
    pour maintenir la pression constante ou pour abaisser la pression dans l'accumulateur hydraulique à haute pression (16), la chambre de travail (30) d'un actionneur (24) est en même temps reliée à l'accumulateur hydraulique à haute pression (16) et au retour à basse pression (56) dont la soupape d'échange de gaz (38) correspondante est alors fermée.
  3. Procédé selon la revendication 2,
    caractérisé en ce que
    pour maintenir la pression constante ou pour abaisser la pression dans l'accumulateur hydraulique à haute pression (16), la chambre de travail (30) d'un actionneur (24) est en même temps reliée à l'accumulateur hydraulique à haute pression (16) et au retour à basse pression (56) dont la soupape d'échange de gaz (38) correspondante ne peut alors s'ouvrir à ce moment parce que la pression est importante dans la chambre de combustion (44).
  4. Procédé selon l'une des revendications précédentes,
    caractérisé en ce que
    la chambre de travail (30) d'un actionneur (24) qui doit passer de la première position à la deuxième position est reliée à l'accumulateur hydraulique à haute pression (16) immédiatement avant d'être séparée du retour à basse pression (56), et/ou la chambre de travail (30) d'un actionneur (24) qui doit passer de la deuxième position à la première position est reliée au retour à basse pression (56) immédiatement avant d'être séparée de l'accumulateur hydraulique à haute pression (16).
  5. Procédé selon l'une des revendications précédentes,
    caractérisé en ce que
    lorsque le moteur à combustion interne a une faible vitesse de rotation, la chambre de travail (30) d'un actionneur (24) est ensuite reliée temporairement en même temps à l'accumulateur hydraulique à haute pression (16) et au retour à basse pression (56).
  6. Procédé selon l'une des revendications précédentes,
    caractérisé en ce que
    la quantité refoulée est en outre commandée ou réglée par une pompe hydraulique (14).
  7. Procédé selon l'une des revendications précédentes,
    caractérisé en ce que
    l'actionneur (24) présente deux chambres de travail (30, 32) séparées l'une de l'autre par des surfaces de pression (34, 36), situées sur un piston (26), dont les dimensions sont différentes et qui agissent en sens opposé, et
    l'une des chambres de travail (32) est constamment alimentée en haute pression et l'autre chambre de travail (30) peut être reliée à l'accumulateur hydraulique à haute pression (16) et au retour à basse pression (56).
  8. Procédé selon l'une des revendications précédentes,
    caractérisé en ce que
    le fluide hydraulique s'écoule depuis la chambre de travail (30) dans un accumulateur hydraulique à basse pression (52).
  9. Programme informatique
    caractérisé en ce que
    il est programmé pour être utilisé dans un procédé selon l'une des revendications précédentes.
  10. Appareil de commande et de réglage (78) pour faire fonctionner un moteur à combustion interne,
    caractérisé en ce que
    il est programmé pour être utilisé dans un procédé selon l'une des revendications 1 à 8.
EP02747175A 2001-08-08 2002-05-28 Procede de commande d'un systeme de controle de soupape electrohydraulique de moteur a combustion interne, programme d'ordinateur et ensamble de controle et de regulation pour commander un moteur a combustion interne Expired - Lifetime EP1430201B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10138881A DE10138881A1 (de) 2001-08-08 2001-08-08 Verfahren zum Betreiben einer elektrohydraulischen Ventilsteuerung einer Brennkraftmaschine, Computerprogramm sowie Steuer- und Regelgerät zum Betreiben einer Brennkraftmaschine
DE10138881 2001-08-08
PCT/DE2002/001957 WO2003016682A1 (fr) 2001-08-08 2002-05-28 Procede permettant de faire fonctionner une commande electrohydraulique des soupapes d'un moteur a combustion interne, programme d'ordinateur et appareil de commande et de reglage destine au fonctionement du moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1430201A1 EP1430201A1 (fr) 2004-06-23
EP1430201B1 true EP1430201B1 (fr) 2005-09-21

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EP02747175A Expired - Lifetime EP1430201B1 (fr) 2001-08-08 2002-05-28 Procede de commande d'un systeme de controle de soupape electrohydraulique de moteur a combustion interne, programme d'ordinateur et ensamble de controle et de regulation pour commander un moteur a combustion interne

Country Status (6)

Country Link
US (1) US20040069255A1 (fr)
EP (1) EP1430201B1 (fr)
JP (1) JP4047807B2 (fr)
KR (1) KR100852805B1 (fr)
DE (2) DE10138881A1 (fr)
WO (1) WO2003016682A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10261022A1 (de) * 2002-12-24 2004-07-08 Robert Bosch Gmbh Verfahren und Steuereinrichtung zum Ansteuern von Gaswechselventilen zugeordneten Magnetventilen
CN1287069C (zh) * 2003-11-27 2006-11-29 宁波华液机器制造有限公司 一种压差式变气门控制***
DE102004030306A1 (de) * 2004-06-23 2006-01-12 Robert Bosch Gmbh Verfahren zur Erfassung mindestens einer Ventilhubposition bei einer Brennkraftmaschine mit variabler Ventilsteuerung
DE102009046943A1 (de) * 2009-11-20 2011-05-26 Robert Bosch Gmbh Elektrohydraulischer Aktor
JP5589634B2 (ja) * 2010-07-20 2014-09-17 いすゞ自動車株式会社 カムレスエンジン弁開閉制御装置
JP5891475B2 (ja) * 2011-03-24 2016-03-23 三菱重工業株式会社 油圧アクチュエータシステム
DE102013207863A1 (de) * 2013-04-30 2014-10-30 Mahle International Gmbh Vorrichtung zur Steuerung eines Gaswechselventils einer Brennkraftmaschine
FR3071869B1 (fr) * 2017-10-02 2019-10-11 Vianney Rabhi Actionneur hydraulique de soupape a regeneration

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5123397A (en) * 1988-07-29 1992-06-23 North American Philips Corporation Vehicle management computer
DE4407585C2 (de) * 1994-03-08 1996-09-19 Mtu Friedrichshafen Gmbh Variable Ventilsteuerung
US5572961A (en) * 1995-04-05 1996-11-12 Ford Motor Company Balancing valve motion in an electrohydraulic camless valvetrain
US5806300A (en) * 1995-12-22 1998-09-15 United Technologies Corporation Electronic control for a variable delivery, positive displacement fuel pump
US6067946A (en) * 1996-12-16 2000-05-30 Cummins Engine Company, Inc. Dual-pressure hydraulic valve-actuation system
DE19826047A1 (de) * 1998-06-12 1999-12-16 Bosch Gmbh Robert Vorrichtung zur Steuerung eines Gaswechselventils für Brennkraftmaschinen
DE19826045A1 (de) * 1998-06-12 2000-01-13 Bosch Gmbh Robert Verfahren zur Steuerung eines Gaswechselventils für Brennkraftmaschinen

Also Published As

Publication number Publication date
EP1430201A1 (fr) 2004-06-23
KR100852805B1 (ko) 2008-08-18
DE10138881A1 (de) 2003-02-27
DE50204345D1 (de) 2005-10-27
US20040069255A1 (en) 2004-04-15
JP4047807B2 (ja) 2008-02-13
KR20040019008A (ko) 2004-03-04
WO2003016682A1 (fr) 2003-02-27
JP2004538416A (ja) 2004-12-24

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