WO2003016682A1 - 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 - Google Patents

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 Download PDF

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Publication number
WO2003016682A1
WO2003016682A1 PCT/DE2002/001957 DE0201957W WO03016682A1 WO 2003016682 A1 WO2003016682 A1 WO 2003016682A1 DE 0201957 W DE0201957 W DE 0201957W WO 03016682 A1 WO03016682 A1 WO 03016682A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
hydraulic accumulator
actuator
low
pressure hydraulic
Prior art date
Application number
PCT/DE2002/001957
Other languages
German (de)
English (en)
Inventor
Hans Schlembach
Hermann Gaessler
Udo Diehl
Karsten Mischker
Rainer Walter
Ulf Pischke
Andreas Baumann
Hubert Schweiggart
Gerhard Filp
Bernd Rosenau
Jürgen Ulm
Uwe Hammer
Thomas Mocken
Sevan Tatiyosyan
Jürgen Schiemann
Christian Grosse
Volker Beuche
Stefan Reimer
Simon Kieser
Original Assignee
Robert Bosch 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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to US10/398,577 priority Critical patent/US20040069255A1/en
Priority to EP02747175A priority patent/EP1430201B1/fr
Priority to JP2003520955A priority patent/JP4047807B2/ja
Priority to DE50204345T priority patent/DE50204345D1/de
Priority to KR1020037004929A priority patent/KR100852805B1/ko
Publication of WO2003016682A1 publication Critical patent/WO2003016682A1/fr

Links

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 first relates to a method for operating an electrohydraulic valve control of an internal combustion engine, with at least one actuator working on a gas exchange valve with 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 from a low pressure -Return separated and connected to actuate the actuator from the second position to the first position back to the low pressure return and separated from the high pressure hydraulic accumulator.
  • Electro-hydraulic valve controls of internal combustion engines enable the control of the gas exchange valves regardless of the position of the crankshaft or the camshaft. This enables, among other things, gasoline savings and improvements in the emission characteristics of an internal combustion engine.
  • 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 of different sizes. The small end 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 also optionally connected to the high-pressure hydraulic accumulator or to a low-pressure return. Depending on the result, a force result that opens or closes the gas exchange valve.
  • the amount of hydraulic fluid that flows from the high-pressure hydraulic accumulator via the actuator to the low-pressure return and is used to actuate the actuator can vary widely.
  • the amount of fluid conveyed 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 control valve has been provided so far, for example, which discharges hydraulic fluid from the high-pressure hydraulic accumulator when a certain pressure is exceeded. Regulation of the delivery rate by the hydraulic pump is also known. Dynamic pressure peaks in the high-pressure hydraulic accumulator can also be passively smoothed, for example, by a large volume of the high-pressure hydraulic accumulator. However, the measures with which the pressure in the high-pressure hydraulic accumulator can be kept constant are relatively complex and sometimes react only sluggishly to pressure changes in the high-pressure hydraulic accumulator. A large-scale high-pressure hydraulic accumulator for smoothing pressure peaks is also disadvantageous, since usually little space is usually available in the engine compartment, for example of motor vehicles. The same disadvantage also results from a pressure control valve.
  • the present invention therefore has the task of developing a method of the type mentioned in the introduction / 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 that a
  • Maintaining constant pressure or lowering the pressure in the high-pressure hydraulic accumulator is achieved by connecting the work space to the high-pressure hydraulic accumulator and the low-pressure return at the same time.
  • the measure according to the invention enables a direct connection from the high-pressure hydraulic accumulator to the low-pressure return, without additional components, such as, for. B. a pressure control valve are necessary.
  • an operating state is expressly permitted in which the work area is connected to the high-pressure hydraulic accumulator and the low-pressure return of the electrohydraulic valve control at the same time. Results, for example.
  • the switching valves usually used have a short response time and highly dynamic switching behavior, short-term fluctuations in the pressure in the high-pressure hydraulic accumulator can also be smoothed out.
  • a pressure control valve can therefore be dispensed with on the one hand by the method according to the invention.
  • the high-pressure hydraulic accumulator can be made smaller. This saves costs in the manufacture of the electro-hydraulic valve control and the electro-hydraulic valve control requires less installation space.
  • the working space of an actuator is simultaneously connected to the high-pressure hydraulic accumulator and the low-pressure return to keep the pressure constant or reduce the pressure in the high-pressure hydraulic accumulator, the associated gas exchange valve of which cannot open precisely due to a high internal cylinder pressure. This effectively prevents an undesired opening of the gas exchange valve in the case of an actuator which is “sensitive” to pressure fluctuations in the work space.
  • 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, which is moved from the second position to be moved to the first position, is connected to the low-pressure return immediately before the separation from the high-pressure hydraulic accumulator.
  • an actuation of the actuator that is intended in any case is used to discharge hydraulic fluid from the high-pressure hydraulic accumulator.
  • This is made possible by a shift in the time at which the connection of the work space with the low-pressure return or the high-pressure hydraulic accumulator takes place.
  • This makes it possible to integrate pressure maintenance or pressure reduction in the high-pressure hydraulic accumulator into the normal operation of an actuator.
  • the constant pressure or pressure reduction be 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 delivery rate by a hydraulic pump. While the above-mentioned connection of the work space can influence the pressure in the high-pressure hydraulic accumulator very quickly and highly dynamically, the control or regulation of the delivery rate by the hydraulic pump enables a long-term and quantitatively significant adjustment of the pressure in the high-pressure hydraulic accumulator.
  • the method according to the invention is particularly preferred when the actuator has two working spaces, which are separated by different sizes and acting in opposite directions' pressure surfaces on a piston, and one working space is constantly subjected to high pressure and the other work chamber with the high pressure hydraulic accumulator and the low pressure return can be connected. Actuators of this type can be used to achieve very short switching times, which facilitates the implementation of the method according to the invention.
  • the hydraulic fluid can also flow from the working space into a low-pressure hydraulic accumulator in the method according to the invention.
  • the pressure difference when the hydraulic fluid flows out is thus reduced, which counteracts the formation of cavitation.
  • the invention also relates to a computer program which is suitable for carrying out the method according to one of the preceding claims when it is executed on a computer. It is particularly preferred if the computer program is stored on a memory, in particular on a flash memory or a ferrite RAM.
  • the invention further relates to a control and regulating device for operating an internal combustion engine, which is connected at least to a first control valve and a second control valve of an electrohydraulic valve control, with which a working space of an actuator of a gas exchange device is connected to a high-pressure hydraulic accumulator or a low-pressure return can be.
  • Figure 1 is a schematic representation of an electro-hydraulic valve control of an internal combustion engine
  • FIG. 2 shows a diagram in which the pressure curve in a high-pressure hydraulic accumulator from FIG. 1 is shown over time
  • Figure 3 is a diagram showing the pressure in the high pressure hydraulic accumulator of Fig. 1 over a speed of the internal combustion engine.
  • an electrohydraulic valve control system bears the reference number 10 overall. It first comprises a reservoir for hydraulic fluid, which in the present case bears reference number 12 and which can be the oil sump of the internal combustion engine.
  • the hydraulic fluid is conveyed from the hydraulic reservoir 12 into a high-pressure hydraulic accumulator 16 by a controllable high-pressure hydraulic pump 14.
  • a hydraulic line 18 leads from the high-pressure hydraulic accumulator 16 via a pressure control valve 20 to a solenoid valve 22.
  • the hydraulic line 18 leads from the solenoid valve 22 to an actuator 24.
  • This is a hydraulic cylinder with a double-acting piston 26.
  • the piston 26 is guided in a housing 28. In Fig. 1 above the piston 26, a first working space 30 is formed between the latter and the housing 28.
  • a second working space 32 is formed between the piston 26 and the housing 28. This is connected via a branch line 33 to that section of the hydraulic line 18 which lies between the high-pressure hydraulic accumulator 16 and the solenoid valve 22.
  • the upper end face 34 of the piston 26 in FIG. 1 is overall larger than the lower end face 36 of the piston 26 in FIG. 1, 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.
  • An opening (without reference number) of a combustion chamber 44 can be closed or opened by the valve element 42.
  • the combustion chamber 44 is present in an engine block 46 of an internal combustion engine (without reference numerals).
  • a hydraulic line 48 leads via a second solenoid valve 50 to a low-pressure hydraulic accumulator 52. This is in turn connected via a pressure control valve 54 to a low-pressure return 56, which finally leads back to the hydraulic reservoir 12.
  • a hydraulic line 58 also leads from the first working space 30 of the actuator 24 back to the high-pressure hydraulic accumulator 16 via a pressure control valve 60.
  • the two solenoid valves 22 and 50 are actuated by solenoid actuators 62 and 64 and are each pressed into their rest position by a compression spring 66 and 68, respectively.
  • the first solenoid valve 22 is closed in its idle switching position 70, in which the magnetic actuator 62 is not energized, whereas it is open in the actuated switching position 72.
  • the second solenoid valve 50 is open in its idle switching position 74 and closed in the actuated switching position in which the magnetic actuator 64 is energized. This switch position bears the reference number 76.
  • the electro-hydraulic valve control 10 also includes a control and regulating device 78. This is connected on the output side to the magnetic actuators 62 and 64. 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. Furthermore, 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 electro-hydraulic valve control 10 is operated as follows (the method described below is stored as a computer program on a ferrite RAM (not shown) in the control and regulating device 78): In order to open the gas exchange valve 38, the piston 26 in FIG move down. This is achieved by energizing the second solenoid valve 50 from the rest position 74 and thus closing it. The connection between the first working space 30 and the low-pressure hydraulic accumulator 52 is thus interrupted.
  • the control unit 78 then energizes the magnetic actuator 62 of the first solenoid valve 22, see above that this solenoid valve 22 moves from its closed rest position 70 into the open switch position 72.
  • the first working space 30 is thus connected to the high-pressure hydraulic accumulator 16. Essentially, the hydraulic pressure also prevailing in the high-pressure hydraulic accumulator 16 is set in the first working space 30.
  • the first solenoid valve 22 is first de-energized by the control and regulating device 78, so that it is pressed from the open switch position 72 by the compression spring 66 into the closed switch 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 it moves due to the compression spring 68 from the closed switching position 76 into the open rest position 74.
  • the first working space 30 is now connected to the low-pressure hydraulic accumulator 52 again.
  • the pressure in the first working space 30 drops until a resultant force occurs, which moves the piston 26 up again.
  • the gas exchange valve 38 closes. If control device 78 is now informed via pressure sensor 80 that the pressure in high-pressure hydraulic accumulator 16 is higher than a target pressure, control device 78 controls first solenoid valve 22 into its open switch position 72, whereas the second solenoid valve 50 remains in its open rest position 74.
  • the direct connection between the high-pressure hydraulic accumulator 16 and the low-pressure hydraulic accumulator 52 is preferably established when the valve element 42 is pressed into its closed position due to a high pressure prevailing in the combustion chamber 44 becomes.
  • the outflow of hydraulic fluid from the high-pressure hydraulic accumulator 16 to the low-pressure hydraulic accumulator 52 is terminated simply by the first solenoid valve 22 being de-energized by the control and regulating device 78, so that it returns to its closed rest position 70.
  • the pressure prevailing in the low-pressure hydraulic accumulator 52 is then set again in the first working space 30.
  • the electro-hydraulic valve control 10 can, however, be operated in another way in order to keep the pressure in the high-pressure hydraulic accumulator 16 constant or to lower it:
  • connection of the high-pressure hydraulic accumulator 16 to the low-pressure hydraulic accumulator 52 can thus be coupled to an actuation of the actuator 24.
  • the solenoid valve 22 can, for example, immediately before the energization of the magnetic actuator 64 of the second solenoid valve 50, as a result of which it moves from its open rest position 74 to the closed switching position 76 Rest position 70 can be controlled in the actuated and open switch position 72.
  • Such short-term actuation of the valves and such a short-term direct connection between the high-pressure hydraulic accumulator 16 to the low-pressure return line 56 can keep the pressure in the high-pressure hydraulic accumulator 16 constant, as can be seen from FIG. 2.
  • the amount of fluid to be discharged is controlled by the duration of the direct connection.
  • the pressure is dashed without a corresponding actuation of the solenoid valves 22 and 50, that pressure curve which can be produced by a corresponding actuation of the solenoid valves 22 and 50 is shown in a solid line.
  • the control and regulating device 78 can then control the solenoid valves 22 and 50 so that the pressure in the high-pressure hydraulic accumulator 16 is reduced. Typically, the operating pressure is reduced from the usual 200 bar to approximately 50 bar. If the speed rises again, a direct fluid connection between the high-pressure hydraulic accumulator 16 and the low-pressure return is avoided, so that the pressure in the high-pressure hydraulic accumulator 16 again due to the continuous delivery by the high-pressure hydraulic pump 14 increases.
  • the relationship between the engine speed n and the pressure P in the high-pressure hydraulic accumulator 16 is shown in FIG. 3.
  • the pressure setting in the high-pressure hydraulic accumulator 16 can, if necessary, be supported by a corresponding control of the high-pressure hydraulic pump 14.

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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).
PCT/DE2002/001957 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 WO2003016682A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US10/398,577 US20040069255A1 (en) 2001-08-08 2002-05-28 Method for operating an electrohydraulic valve control system of an internal combustion engine, computer program, and control, and regulating unit for operating an internal combustion engine
EP02747175A 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
JP2003520955A JP4047807B2 (ja) 2001-08-08 2002-05-28 内燃機関の電動液圧式バルブ制御システムの駆動方法、コンピュータプログラム、内燃機関を駆動する開制御および閉ループ制御装置
DE50204345T DE50204345D1 (de) 2001-08-08 2002-05-28 Verfahren zum betreiben einer elektrohydraulischen ventilsteuerung einer brennkraftmaschine, computerprogramm sowie steuer- und regelgerät zum betreiben einer brennkraftmaschine
KR1020037004929A KR100852805B1 (ko) 2001-08-08 2002-05-28 엔진의 전기 유압식 밸브 제어 장치의 작동 방법, 엔진작동을 위한 컴퓨터 프로그램 및 제어 및 조절 장치

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10138881.0 2001-08-08
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

Publications (1)

Publication Number Publication Date
WO2003016682A1 true WO2003016682A1 (fr) 2003-02-27

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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

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)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007512457A (ja) * 2003-11-27 2007-05-17 ▲にん▼波▲ほあ▼液机器制造有限公司 差圧式可変動弁制御システム
JP2008503686A (ja) * 2004-06-23 2008-02-07 ロベルト・ボッシュ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング 可変弁制御を有する内燃機関における少なくとも１つの弁リフト位置の検出方法
WO2011060855A3 (fr) * 2009-11-20 2011-07-14 Robert Bosch Gmbh Actionneur électrohydraulique
WO2014177422A1 (fr) * 2013-04-30 2014-11-06 Mahle International Gmbh Dispositif de commande d'une soupape d'échanges des gaz d'un moteur à combustion interne

Families Citing this family (4)

* 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
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
FR3071869B1 (fr) * 2017-10-02 2019-10-11 Vianney Rabhi Actionneur hydraulique de soupape a regeneration

Citations (4)

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DE4407585A1 (de) * 1994-03-08 1995-09-21 Mtu Friedrichshafen Gmbh Variable Ventilsteuerung
EP0736671A2 (fr) * 1995-04-05 1996-10-09 Ford Motor Company Limited Equilibrage du mouvement de soupape dans une distribution électro-hydraulique sans came
DE19826047A1 (de) * 1998-06-12 1999-12-16 Bosch Gmbh Robert Vorrichtung zur Steuerung eines Gaswechselventils für Brennkraftmaschinen
US6067946A (en) * 1996-12-16 2000-05-30 Cummins Engine Company, Inc. Dual-pressure hydraulic valve-actuation system

Family Cites Families (3)

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US5123397A (en) * 1988-07-29 1992-06-23 North American Philips Corporation Vehicle management computer
US5806300A (en) * 1995-12-22 1998-09-15 United Technologies Corporation Electronic control for a variable delivery, positive displacement fuel pump
DE19826045A1 (de) * 1998-06-12 2000-01-13 Bosch Gmbh Robert Verfahren zur Steuerung eines Gaswechselventils für Brennkraftmaschinen

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4407585A1 (de) * 1994-03-08 1995-09-21 Mtu Friedrichshafen Gmbh Variable Ventilsteuerung
EP0736671A2 (fr) * 1995-04-05 1996-10-09 Ford Motor Company Limited Equilibrage du mouvement de soupape dans une distribution électro-hydraulique sans came
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

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007512457A (ja) * 2003-11-27 2007-05-17 ▲にん▼波▲ほあ▼液机器制造有限公司 差圧式可変動弁制御システム
JP2008503686A (ja) * 2004-06-23 2008-02-07 ロベルト・ボッシュ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング 可変弁制御を有する内燃機関における少なくとも１つの弁リフト位置の検出方法
WO2011060855A3 (fr) * 2009-11-20 2011-07-14 Robert Bosch Gmbh Actionneur électrohydraulique
CN102713173A (zh) * 2009-11-20 2012-10-03 罗伯特·博世有限公司 电液式致动器
WO2014177422A1 (fr) * 2013-04-30 2014-11-06 Mahle International Gmbh Dispositif de commande d'une soupape d'échanges des gaz d'un moteur à combustion interne

Also Published As

Publication number Publication date
KR100852805B1 (ko) 2008-08-18
DE10138881A1 (de) 2003-02-27
US20040069255A1 (en) 2004-04-15
KR20040019008A (ko) 2004-03-04
DE50204345D1 (de) 2005-10-27
EP1430201A1 (fr) 2004-06-23
EP1430201B1 (fr) 2005-09-21
JP4047807B2 (ja) 2008-02-13
JP2004538416A (ja) 2004-12-24

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