EP1481148B1 - Dispositif de commande de soupape de changement des gaz - Google Patents

Dispositif de commande de soupape de changement des gaz Download PDF

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Publication number
EP1481148B1
EP1481148B1 EP02805683A EP02805683A EP1481148B1 EP 1481148 B1 EP1481148 B1 EP 1481148B1 EP 02805683 A EP02805683 A EP 02805683A EP 02805683 A EP02805683 A EP 02805683A EP 1481148 B1 EP1481148 B1 EP 1481148B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
pump
valves
inlet
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
EP02805683A
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German (de)
English (en)
Other versions
EP1481148A1 (fr
Inventor
Udo Diehl
Bernd Rosenau
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
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
Publication of EP1481148A1 publication Critical patent/EP1481148A1/fr
Application granted granted Critical
Publication of EP1481148B1 publication Critical patent/EP1481148B1/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 to a device for controlling gas exchange valves according to the preamble of claim 1.
  • each electrohydraulic valve actuator has a force acting on a gas exchange valve actuator piston and two limited by the actuator piston, hydraulic work spaces, of which the gas exchange valve in the closing direction acting first working space constantly with a high pressure Fluid is filled and the gas exchange valve in the opening direction acting second working space via a first and second electric control valve alternately filled with a high pressure working fluid or fluid and can be relieved.
  • a pressure supply device supplies a fluid under high pressure, on the one hand the first working space and on the other hand via the first electric control valve the second working space is supplied.
  • the second working space is connected via the second electrical control valve with a return line leading back to the fluid reservoir.
  • the pressure supply device comprises a working pressure accumulator and a regulated variable displacement pump, which promotes fluid from a fluid reservoir via a check valve in the working pressure accumulator.
  • the second working space is separated by the closed first control valve from the pressure supply device and connected by the open second control valve to the return line, so that the actuating piston is transferred by the prevailing in the first working space fluid pressure in its closed position.
  • the control valves are switched, whereby the second working space is shut off from the return line and connected to the pressure supply device.
  • the actuating piston shifts towards the first working chamber when the gas exchange valve is opened, since the piston area of the actuating piston in the second working space is greater than the effective area of the actuating piston in the first working space, the size of the opening stroke being dependent on the design of the electrical control signal applied to the first control valve and the opening speed depends on the fluid pressure supplied by the pressure supply means.
  • the control valves switch again.
  • the second working space which is shut off from the pressure supply device lies on the return line, and the fluid pressure prevailing in the first working space leads the adjusting piston into its Valve closing position back, so that the gas exchange valve is closed by the actuating piston.
  • the inventive device for controlling gas exchange valves with the features of claim 1 has the advantage that by dividing the pressure storage unit on two high-pressure accumulator for separate fluid supply the valve actuator for the at least one inlet valve on the one hand and for the at least one outlet valve on the other hand, the fluid pressure in the two high-pressure circuits for intake and exhaust valve depending on the requirements of the degrees of freedom enabled by the electrohydraulic valve control in the valve control, such as time of valve actuation, stroke, stroke speed and valve duration, different pressure levels can be realized.
  • the fluid pressure in the high-pressure circuit for the intake valves lower than the fluid pressure in the high-pressure accumulator for the exhaust valves, which is predetermined by the force required by the combustion chamber pressure at the exhaust valve.
  • a reduction of the required energy can be achieved.
  • the hydraulic valve actuators for the intake and exhaust valves can be unified because the higher forces required to actuate the exhaust valves against the combustion chamber pressure are realized via the higher fluid pressure in the associated high pressure circuit.
  • a torque balance in the energy consumption is possible by appropriate control of the switching element for alternately supplying the two high-pressure accumulator. This will be achieves a more homogenous torque tap with reduced impact on ride comfort.
  • the division of the pressure supply device according to the invention on two separate high-pressure circuits for the intake valves and the exhaust valves also allows the use of a structurally simple constant pump instead of the previously commonly used, technically complex variable; whereby a significant savings effect on the manufacturing cost of the control device is achieved.
  • the known constant-flow pump is characterized in that it delivers regardless of the delivery pressure dependent only on their drive speed flow or volume flow.
  • the constant displacement pump can either be connected to an upstream feed pump, e.g. from the oil pump of the internal combustion engine, operated or run as a self-priming pump.
  • the switching element for alternately connecting the two high-pressure accumulator to the fixed displacement pump is designed as a 4/3-way solenoid valve with spring return. Of the three valve outlets of the solenoid valve one is connected to one and one to the other high-pressure accumulator and the third to the return line, while the Valve inlet of the solenoid valve is connected to the pump outlet of the constant pump.
  • a total of four intake valves 11 and a total of four exhaust valves 12 of an internal combustion engine are controlled via an electronic control unit 13 in the selected embodiment.
  • the number of intake and exhaust valves 11, 12 may vary.
  • Each of the intake or exhaust valves 11, 12 is arranged in a cylinder head 14 of a combustion cylinder shown in detail in Fig. 2 and closes a gas cylinder formed in the combustion chamber from gas-tight.
  • Each gas exchange valve has a in a known manner Opening cross section 15 in the cylinder head 14 enclosing the valve seat 16 and a valve member 17 with a seated on an axially displaceable valve stem 171 valve closing body 172 which cooperates with the valve seat 16 for closing and releasing the opening cross section 15.
  • the valve closing body 172 lifts off from the valve seat 16 or sits on the valve seat 16.
  • each gas exchange valve so each inlet valve 11 and each outlet valve 12, an electro-hydraulic valve actuator 18 associated with its operation.
  • the known per se electro-hydraulic valve actuator 18 is shown in Fig. 2 in detail. It comprises a double-acting, hydraulic working cylinder 19 and two electrical control valves 20, 21, which are preferably designed as 2/2-way solenoid valves with spring return.
  • the electrical control valves 20, 21 are controlled by the electronic control unit 13.
  • the hydraulic working cylinder 19 has, in a known manner, a cylinder housing 22 and an axially displaceably guided therein, connected to the valve stem 171 of a gas exchange valve actuating piston 23, which divides the interior of the cylinder housing 25 into a first working space 24 and a second working space 25.
  • the first working space 24 is connected directly and the second working space 25 is connected via the first electrical control valve 20 to a hydraulic input 181 of the valve actuator 18.
  • the second working space 25 is via the second electrical control valve 21 with a hydraulic outlet 182 the valve actuator 18 is connected.
  • the operation of the valve actuator 18 for opening and closing the associated gas exchange valve is known and described in the introduction section in the "prior art".
  • the control device has a pressure supply device 26.
  • the pressure supply device 26 comprises a fixed displacement pump 27 for high pressure generation, which is fed by a feed pump 28 from a fluid reservoir 29, a connected to the pump outlet of the fixed displacement pump 27 switching element 30 and two high-pressure accumulator 31, 32, depending on the switching position of the switching element 30 alternately via a check valve 33 and 34 are connected to the pump outlet of the fixed displacement pump 27.
  • the first high-pressure accumulator 21 is located at a first output 261 of the pressure supply device and the second high-pressure accumulator at a second output 262 of the pressure supply device 26, and each high-pressure accumulator 31, 32 is connected via the output 261 and 262 of the pressure supply device 26 with a pressure relief valve 35 and 36 respectively whose valve outlet is connected to a recirculation line 37 opening in the fluid reservoir 29.
  • the switching member 30 is formed as a 4/3-way solenoid valve 41 with spring return, which is controlled by the electronic control unit 13.
  • valve outlets of the solenoid valve 41 Of the total of three valve outlets of the solenoid valve 41 is a first valve outlet 412 with the interposition of the check valve 33 to the first high pressure accumulator 31, a second valve outlet 413 with the interposition of Check valve 34 to the second high pressure accumulator 32 and a third valve outlet 414 via a connecting line 42 to the return line 37 or directly to the fluid reservoir 29, while the valve inlet 411 is connected to the pump outlet of the fixed displacement pump 27.
  • All electrohydraulic valve actuators 18, which actuate an inlet valve 11, are connected with their hydraulic inlet 181 to the first outlet 261 of the pressure supply device 26 and thus connected to the first high-pressure accumulator 31.
  • All hydraulic outputs 182 of these valve actuators 18 are connected to the return line 37 via a common connection line 38.
  • All electro-hydraulic valve actuators 18 for actuating the exhaust valves 12 are connected with their hydraulic inputs 181 to the second input 262 of the pressure supply device 26 and thus connected to the second high-pressure accumulator 32.
  • the hydraulic outputs 182 of these valve actuators 18 are in turn connected via a common connecting line 39 to the return line 37.
  • both connecting lines 38, 39 may each have a check valve 43 or 44 may be arranged, which opens to the return line 37 back.
  • the electro-hydraulic valve actuator 18 for all gas exchange valves, ie for all intake valves 11 and all exhaust valves 12, are made uniform.
  • These different forces are realized by different pressure levels in the high pressure accumulators 31, 32.
  • the different pressure levels are achieved by appropriate adjustment of the pressure relief valves 35, 36.
  • the high-pressure accumulator 32 or the high-pressure accumulator 32 is tensioned by the constant pump 37 to the pressure level predetermined by the respective pressure relief valve 35 or 36.
  • the high-pressure accumulator 31 is tensioned to a lower pressure level, the energy required for pressure generation is reduced. If no fluid is withdrawn via the valve actuators 18 in the two high-pressure circuits, the 4/3-way solenoid valve 41 is controlled to its middle position shown in FIG. 1, in which the fluid circulates without pressure via the fluid reservoir 29.
  • the constant displacement pump 27 can alternatively be designed as a self-priming pump. In this case, the pre-feed pump 28 is omitted, and the constant-displacement pump 27 sucks fluid directly from the fluid reservoir 29.
  • the invention is not limited to the embodiment described above.
  • the number of intake valves 11 and exhaust valves 12 operated by the control device can be varied. Also so that a so-called. 3-valve operation is possible in which each formed in a combustion cylinder combustion chamber of the internal combustion engine, two intake valves 11 and an exhaust valve 12 are associated.

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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 un dispositif de commande de soupapes de changement des gaz, au moins une de ces soupapes servant de soupape d'admission (11) et au moins une de ces soupapes servant de soupape de sortie (12) d'une chambre de combustion d'un moteur à combustion interne. Ce dispositif comprend des actionneurs de soupape (18) électrohydrauliques respectivement associés à une soupape de changement des gaz afin de l'actionner, ainsi qu'une unité d'alimentation sous pression (26) qui est conçue pour alimenter les actionneurs de soupape (18) avec un fluide soumis à une pression élevée et comporte une pompe haute pression ainsi qu'une unité d'accumulation de pression. Pour réduire l'énergie absorbée par le dispositif de commande, l'unité d'accumulation de pression comprend deux accumulateurs haute pression (31, 32) dont un est relié avec un actionneur de soupape (18) pour la/les soupape(s) d'admission (11) et dont l'autre est relié avec un actionneur de soupape (18) pour la/les soupapes de sortie (12). Un élément de commutation (30) permet de raccorder la pompe haute pression (27) à l'un des deux accumulateurs haute pression (31, 32), et à une conduite de retour (37) menant à un réservoir de fluide (29).

Claims (10)

  1. Dispositif pour commander des soupapes d'échange gazeux dont au moins une sous forme de soupape d'admission (11) et au moins une sous forme de soupape de décharge (12) est associée à une chambre de combustion du moteur à combustion interne, comportant des actionneurs de soupape (18) électrohydrauliques chacun associé à une soupape d'échange gazeux (11, 12) afin de l'actionner, et comportant une installation d'alimentation en pression (26) qui alimente en fluide sous haute pression les actionneurs de soupape (18) et qui comporte une pompe haute pression et une unité accumulatrice de pression,
    caractérisé en ce que
    l'unité accumulatrice de pression comporte deux accumulateurs haute pression (31, 32) distincts dont l'un est relié à l'actionneur de soupape (18) pour l'au moins une soupape d'admission (11) et l'autre à l'actionneur de soupape (18) pour l'au moins une soupape de décharge (12), et
    un organe de commutation (30) permet de brancher la pompe haute pression à l'un ou à l'autre des accumulateurs haute pression (31, 32) ainsi qu'à une conduite de retour (37) qui mène à un réservoir de fluide (29).
  2. Dispositif selon la revendication 1,
    caractérisé en ce que
    la pompe haute pression est une pompe à cylindrée constante (27) dont la décharge de pompe se trouve à l'entrée de l'organe de commutation (30).
  3. Dispositif selon la revendication 1 ou 2,
    caractérisé en ce que
    l'organe de commutation (30) est une électrovanne linéaire, à 4/3 voies (41) et à rappel de ressort, équipée d'une admission de soupape (411) et de trois décharges de soupape (412, 413, 414), son admission de soupape (411) étant reliée à la décharge de pompe et parmi ses trois décharges de soupape (412, 413, 414) l'une est reliée à l'un des accumulateurs haute pression (31, 32), la deuxième à l'autre accumulateur haute pression et la troisième à la conduite de retour (37).
  4. Dispositif selon la revendication 3,
    caractérisé en ce que
    l'électrovanne à 4/3 voies est commandée par un appareil de commande (13) électronique.
  5. Dispositif selon l'une des revendications 1 à 4,
    caractérisé en ce que
    les deux accumulateurs haute pression (31, 32) ont des niveaux de pression différents.
  6. Dispositif selon la revendication 5,
    caractérisé en ce que
    chacun des accumulateurs haute pression (31, 32) est raccordé à la conduite de retour (37) par l'intermédiaire d'une soupape de limitation de pression (35, 36).
  7. Dispositif selon l'une des revendications 1 à 6,
    caractérisé en ce que
    lorsqu'il y a un grand nombre de soupapes d'échange gazeux (11, 12), les actionneurs de soupape (18) de toutes les soupapes d'admission (11) sont raccordés à l'un des accumulateurs haute pression (31, 32) et les actionneurs de soupape (18) de toutes les soupapes de décharge (12) à l'autre accumulateur haute pression.
  8. Dispositif selon l'une des revendications 2 à 7,
    caractérisé en ce que
    une pompe de prérefoulement (28) qui refoule à partir du réservoir de fluide (29) est montée en amont de la pompe à cylindrée constante (27).
  9. Dispositif selon l'une des revendications 2 à 7,
    caractérisé en ce que
    la pompe à cylindrée constante (27) est une pompe auto-aspirante dont l'admission est directement en liaison avec le réservoir de fluide (29).
  10. Dispositif selon l'une des revendications 1 à 9,
    caractérisé en ce que
    chaque actionneur de soupape (18) électrohydraulique comporte un vérin hydraulique (19) à double action pour actionner la soupape et comporte des soupapes de commande (20, 21) électriques qui commandent la pression de travail dans le vérin hydraulique (19).
EP02805683A 2002-01-29 2002-11-28 Dispositif de commande de soupape de changement des gaz Expired - Lifetime EP1481148B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10203275 2002-01-29
DE10203275A DE10203275A1 (de) 2002-01-29 2002-01-29 Vorrichtung zur Steuerung von Gaswechselventilen
PCT/DE2002/004365 WO2003064823A1 (fr) 2002-01-29 2002-11-28 Dispositif de commande de soupape de changement des gaz

Publications (2)

Publication Number Publication Date
EP1481148A1 EP1481148A1 (fr) 2004-12-01
EP1481148B1 true EP1481148B1 (fr) 2005-09-21

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP02805683A Expired - Lifetime EP1481148B1 (fr) 2002-01-29 2002-11-28 Dispositif de commande de soupape de changement des gaz

Country Status (6)

Country Link
US (1) US20040144345A1 (fr)
EP (1) EP1481148B1 (fr)
JP (1) JP2005516146A (fr)
KR (1) KR20040077808A (fr)
DE (2) DE10203275A1 (fr)
WO (1) WO2003064823A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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系统
KR20040013033A (ko) * 2004-01-09 2004-02-11 (주)하이드로 메틱스 다수의 실린더와 유압축적기를 구비한 중앙집중식 가스밸브구동용 유압장치
US8602002B2 (en) 2010-08-05 2013-12-10 GM Global Technology Operations LLC System and method for controlling engine knock using electro-hydraulic valve actuation
DE102016213976B4 (de) * 2016-07-29 2018-07-05 Schaeffler Technologies AG & Co. KG Elektrohydraulischer Ventiltrieb eines Verbrennungsmotors
DE102016224772A1 (de) * 2016-12-13 2018-06-14 Bayerische Motoren Werke Aktiengesellschaft Hubkolbenbrennkraftmaschine
EP3406866A1 (fr) * 2017-05-22 2018-11-28 EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement

Family Cites Families (10)

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Publication number Priority date Publication date Assignee Title
DE2928737A1 (de) * 1979-07-17 1981-01-29 Sack Gmbh Hydraulische steuerung mit rohrbruchsicherung fuer einen doppelt beaufschlagbaren antriebszylinder zum positionieren, insbesondere einer angetriebenen fuehrungsrolle in der strangfuehrung einer stranggiessanlage
US4833971A (en) * 1988-03-09 1989-05-30 Kubik Philip A Self-regulated hydraulic control system
DE69212730T2 (de) * 1991-06-24 1996-12-05 Ford Werke Ag Hydraulisches Ventilsteuerung für Brennkraftmaschinen
BR9107316A (pt) * 1991-10-11 1994-04-19 Caterpillar Inc Conjunto de atuador e valvula para um injetor controlado eletronicamente
US6148778A (en) * 1995-05-17 2000-11-21 Sturman Industries, Inc. Air-fuel module adapted for an internal combustion engine
DE19528792C1 (de) * 1995-08-04 1996-08-14 Daimler Benz Ag Motorbremse für eine Dieselbrennkraftmaschine
US6067946A (en) * 1996-12-16 2000-05-30 Cummins Engine Company, Inc. Dual-pressure hydraulic valve-actuation system
DE19816817A1 (de) * 1997-11-25 1999-10-21 Bayerische Motoren Werke Ag Hydraulische Betätigungsvorrichtung für ein Gaswechselventil einer Brennkraftmaschine
DE19826047A1 (de) * 1998-06-12 1999-12-16 Bosch Gmbh Robert Vorrichtung zur Steuerung eines Gaswechselventils für Brennkraftmaschinen
JP4802394B2 (ja) * 2000-08-03 2011-10-26 アイシン精機株式会社 弁開閉時期制御装置

Also Published As

Publication number Publication date
DE50204351D1 (de) 2005-10-27
US20040144345A1 (en) 2004-07-29
KR20040077808A (ko) 2004-09-06
WO2003064823A1 (fr) 2003-08-07
JP2005516146A (ja) 2005-06-02
EP1481148A1 (fr) 2004-12-01
DE10203275A1 (de) 2003-08-07

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