WO2003064823A1 - Dispositif de commande de soupape de changement des gaz - Google Patents

Dispositif de commande de soupape de changement des gaz Download PDF

Info

Publication number
WO2003064823A1
WO2003064823A1 PCT/DE2002/004365 DE0204365W WO03064823A1 WO 2003064823 A1 WO2003064823 A1 WO 2003064823A1 DE 0204365 W DE0204365 W DE 0204365W WO 03064823 A1 WO03064823 A1 WO 03064823A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
pump
valves
outlet
Prior art date
Application number
PCT/DE2002/004365
Other languages
German (de)
English (en)
Inventor
Udo Diehl
Bernd Rosenau
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 EP02805683A priority Critical patent/EP1481148B1/fr
Priority to US10/473,528 priority patent/US20040144345A1/en
Priority to DE50204351T priority patent/DE50204351D1/de
Priority to JP2003564401A priority patent/JP2005516146A/ja
Priority to KR10-2004-7011583A priority patent/KR20040077808A/ko
Publication of WO2003064823A1 publication Critical patent/WO2003064823A1/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 relates to a device for controlling gas exchange valves according to the preamble of claim 1.
  • each electrohydraulic valve actuator has an actuating piston acting on a gas exchange valve and two hydraulic work spaces delimited by the actuating piston, of which the first work space acting on the gas exchange valve in the closing direction is constantly under high pressure Fluid is filled and the second working chamber acting on the gas exchange valve in the opening direction can be alternately filled and released with a high-pressure working medium or fluid via a first and second electrical control valve.
  • a pressure supply device supplies a high-pressure fluid which, on the one hand, to the first work space and, on the other hand, via the first electrical control valve second is fed.
  • the second work space is connected via the second electrical control valve to a return line leading back to the fluid reservoir.
  • the pressure supply device comprises a working pressure accumulator and a regulated variable pump which conveys fluid from a fluid reservoir into the working pressure accumulator via a check valve.
  • the second work chamber In the closed state of the gas exchange valve, the second work chamber is separated from the pressure supply device by the closed first control valve and is connected to the return line by the open second control valve, so that the actuating piston is transferred into its closed position by the fluid pressure prevailing in the first work chamber.
  • the control valves are switched, whereby the second work space is shut off from the return line and connected to the pressure supply device.
  • the actuating piston moves towards the first working chamber when the gas exchange valve is opened, since the piston area of the actuating piston in the second working chamber is larger than the effective area of the actuating piston in the first working chamber, the size of the opening stroke depending on the design of the electrical control signal applied to the first control valve and the opening speed depends on the fluid pressure entered by the pressure supply device.
  • the control valves switch again to close the gas exchange valve.
  • 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 guides the actuating piston in the latter Valve closed position back so that the gas exchange valve is closed by the actuating piston.
  • Gas exchange valves with the features of claim 1 has the advantage that by dividing the pressure storage unit into two high-pressure accumulators for separate fluid supply to the valve actuators 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 the inlet and outlet valves Depending on the requirements for the degrees of freedom in valve control made possible by the electro-hydraulic valve control, such as the time of valve actuation, stroke, stroke speed and
  • Valve opening duration different pressure levels can be realized. This makes it e.g. It is possible to design the fluid pressure in the high-pressure circuit for the inlet valves to be lower than the fluid pressure in the high-pressure reservoir for the outlet valves, which is predetermined by the force required by the combustion chamber pressure at the outlet valve. This reduction in pressure in the one high-pressure circuit enables the required energy to be reduced. As a result, the hydraulic valve actuators for the intake and exhaust valves can be standardized, since 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. Furthermore, by appropriately actuating the changeover element, the two high-pressure accumulators are supplied alternately
  • High-pressure circuits for the inlet valves and for the outlet valves also enable the use of a structurally simple constant pump instead of the previously more commonly used, technically complex variable displacement pump, which achieves a considerable saving effect in the manufacturing costs of the control device.
  • the known constant pump is characterized in that it delivers a delivery or volume flow that is dependent only on its drive speed, regardless of the delivery pressure.
  • the constant pump can either be connected upstream
  • Feed pump e.g. operated by the oil pump of the internal combustion engine, or designed as a self-priming pump.
  • the switching element for alternately connecting the two high-pressure accumulators to the constant 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, during the Valve inlet of the solenoid valve is connected to the pump outlet of the constant pump.
  • 1 is a circuit diagram of a device for controlling gas exchange valves for an internal combustion engine
  • Fig. 2 is a detailed circuit diagram of an electro-hydraulic valve actuator for
  • a device for controlling gas exchange valves shown in the circuit diagram in FIG. 1 controls a total of four intake valves 11 and a total of four exhaust valves 12 of an internal combustion engine via an electronic control unit 13. 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 combustion chamber formed in the combustion cylinder in a gas-tight manner.
  • Each gas exchange valve has a one in a known manner Opening cross section 15 in the cylinder head 14 enclosing valve seat 16 and a valve member 17 with a valve closing body 172 seated on an axially displaceably guided valve stem 171, which cooperates with the valve seat 16 for closing and releasing the opening cross section 15.
  • the valve closing body 172 lifts off the valve seat 16 or sits on the valve seat 16.
  • each gas exchange valve that is to say each inlet valve 11 and each outlet valve 12, is assigned an electrohydraulic valve actuator 18 for actuating it.
  • the electro-hydraulic valve actuator 18 known per se is shown in detail in FIG. 2. 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 operated by the electronic
  • the hydraulic working cylinder 19 has, in a known manner, a cylinder housing 22 and one axially displaceable therein. guided, connected to the valve stem 171 of a gas exchange valve on actuating piston 23, which the interior of the cylinder housing 25 into a first
  • the first working space 24 is directly connected and the second working space 25 is connected to a hydraulic input 181 of the valve actuator 18 via the first electrical control valve 20.
  • the second working space 25 is via the second electrical control valve 21 with a hydraulic outlet 182 the valve actuator 18 connected.
  • the mode of operation of the valve actuators 18 for opening and closing the associated gas exchange valve is known and is initially described in the section “prior art”.
  • the control device has a pressure supply device 26.
  • the pressure supply device 26 comprises a constant pump 27 for high pressure generation by a
  • Pre-feed pump 28 is fed from a fluid reservoir 29, a switching element 30 connected to the pump outlet of the constant pump 27 and two high-pressure accumulators 31, 32 which, depending on the switching position of the switching element 30, can be connected alternately via a check valve 33 or 34 to the pump outlet of the constant pump 27.
  • the first high-pressure accumulator 21 is connected to a first outlet 261 of the pressure supply device and the second high-pressure accumulator is connected to a second outlet 262 of the pressure supply device 26, and each high-pressure accumulator 31, 32 is connected to a pressure relief valve 35 or 36 via the outlet 261 or 262 of the pressure supply device 26 , whose valve outlet is connected to a return line 37 opening into the fluid reservoir 29.
  • the switching element 30 is a 4/3
  • Directional solenoid valve 41 formed with spring return, which is controlled by the electronic control unit 13.
  • a first valve outlet 412 is connected to the first high-pressure accumulator 31 with the check valve 33 interposed, and a second valve outlet 413 with the interposition of the Check valve 34 on the second high-pressure accumulator 32 and a third valve outlet 414 via a connecting line 42 on the return line 37 or directly on the fluid reservoir 29, while the valve inlet 411 is connected to the pump outlet of the constant pump 27.
  • All the electrohydraulic valve actuators 18 which operate an inlet valve 11 are connected with their hydraulic input 181 to the first output 261 of the pressure supply device 26 and thus to the first high-pressure accumulator
  • All hydraulic outputs 182 of this valve actuator 18 are connected to the return line 37 via a common connecting line 38.
  • All the electrohydraulic valve actuators 18 for actuating the outlet 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 to the return line 37 via a common connecting line 39.
  • Connecting lines 38, 39 can each have a check valve 43 or 44 arranged, which opens to the return line 37.
  • Gas exchange valves that is to say for all intake valves 11 and all exhaust valves 12, are of a uniform design.
  • These different forces are realized by different pressure levels in the high pressure accumulators 31, 32.
  • the different pressure levels are achieved by adjusting the pressure limiting valves 35, 36 accordingly.
  • the constant pump 27 can alternatively be designed as a self-priming pump. In this case, the prefeed pump 28 is omitted, and the constant pump 27 draws fluid directly from the fluid reservoir 29.
  • the invention is not restricted to the exemplary embodiment described above.
  • the number of intake valves 11 and exhaust valves 12 operated with the control device can thus be varied.
  • a so-called 3-valve operation is also possible in which two intake valves 11 and one exhaust valve 12 are associated with each combustion chamber of the internal combustion engine which is formed in a combustion cylinder.

Landscapes

  • 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).
PCT/DE2002/004365 2002-01-29 2002-11-28 Dispositif de commande de soupape de changement des gaz WO2003064823A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP02805683A EP1481148B1 (fr) 2002-01-29 2002-11-28 Dispositif de commande de soupape de changement des gaz
US10/473,528 US20040144345A1 (en) 2002-01-29 2002-11-28 Device for controlling charge exchange valves
DE50204351T DE50204351D1 (de) 2002-01-29 2002-11-28 Vorrichtung zur steuerung von gaswechselventilen
JP2003564401A JP2005516146A (ja) 2002-01-29 2002-11-28 ガス交換弁を制御する装置
KR10-2004-7011583A KR20040077808A (ko) 2002-01-29 2002-11-28 가스 교환 밸브 제어 장치

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10203275A DE10203275A1 (de) 2002-01-29 2002-01-29 Vorrichtung zur Steuerung von Gaswechselventilen
DE10203275.0 2002-01-29

Publications (1)

Publication Number Publication Date
WO2003064823A1 true WO2003064823A1 (fr) 2003-08-07

Family

ID=7713253

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2002/004365 WO2003064823A1 (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)

Cited By (1)

* 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

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0520633A2 (fr) * 1991-06-24 1992-12-30 Ford Motor Company Limited Dispositif de commande hydraulique de soupapes pour moteurs à combustion interne
US5645030A (en) * 1995-08-04 1997-07-08 Daimler-Bauz Ag Motorbrake for a diesel engine
DE19816817A1 (de) * 1997-11-25 1999-10-21 Bayerische Motoren Werke Ag Hydraulische Betätigungsvorrichtung für ein Gaswechselventil einer Brennkraftmaschine
WO1999058822A1 (fr) * 1998-05-14 1999-11-18 Sturman Industries, Inc. Module air-carburant adapte a un moteur a combustion interne
DE19826047A1 (de) * 1998-06-12 1999-12-16 Bosch Gmbh Robert Vorrichtung zur Steuerung eines Gaswechselventils für Brennkraftmaschinen

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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
DE69121904D1 (de) * 1991-10-11 1996-10-10 Caterpillar Inc Gedämpfte betätigungs- und ventilanordnung für eine elektronisch-gesteuerte einspritzeinheit
US6067946A (en) * 1996-12-16 2000-05-30 Cummins Engine Company, Inc. Dual-pressure hydraulic valve-actuation system
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

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0520633A2 (fr) * 1991-06-24 1992-12-30 Ford Motor Company Limited Dispositif de commande hydraulique de soupapes pour moteurs à combustion interne
US5645030A (en) * 1995-08-04 1997-07-08 Daimler-Bauz Ag Motorbrake for a diesel engine
DE19816817A1 (de) * 1997-11-25 1999-10-21 Bayerische Motoren Werke Ag Hydraulische Betätigungsvorrichtung für ein Gaswechselventil einer Brennkraftmaschine
WO1999058822A1 (fr) * 1998-05-14 1999-11-18 Sturman Industries, Inc. Module air-carburant adapte a un moteur a combustion interne
DE19826047A1 (de) * 1998-06-12 1999-12-16 Bosch Gmbh Robert Vorrichtung zur Steuerung eines Gaswechselventils für Brennkraftmaschinen

Cited By (1)

* 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

Also Published As

Publication number Publication date
US20040144345A1 (en) 2004-07-29
DE10203275A1 (de) 2003-08-07
KR20040077808A (ko) 2004-09-06
DE50204351D1 (de) 2005-10-27
JP2005516146A (ja) 2005-06-02
EP1481148B1 (fr) 2005-09-21
EP1481148A1 (fr) 2004-12-01

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