EP0455937B1 - Dispositif de commande de soupape pour moteur à combustion interne - Google Patents

Dispositif de commande de soupape pour moteur à combustion interne Download PDF

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Publication number
EP0455937B1
EP0455937B1 EP91101372A EP91101372A EP0455937B1 EP 0455937 B1 EP0455937 B1 EP 0455937B1 EP 91101372 A EP91101372 A EP 91101372A EP 91101372 A EP91101372 A EP 91101372A EP 0455937 B1 EP0455937 B1 EP 0455937B1
Authority
EP
European Patent Office
Prior art keywords
intake
exhaust valve
hydraulic oil
valve
pressure
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
EP91101372A
Other languages
German (de)
English (en)
Other versions
EP0455937A1 (fr
Inventor
Yoshinori C/O Nagasaki Technical Institute Nagae
Yozo C/O Nagasaki Technical Institute Tosa
Etsuo C/O Nagasaki Technical Institute Kunimoto
Tadashi C/O Nagasaki Technical Inst. Fukuyoshi
Yasutaka C/O Yokohama Machinery Works Irie
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.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP0455937A1 publication Critical patent/EP0455937A1/fr
Application granted granted Critical
Publication of EP0455937B1 publication Critical patent/EP0455937B1/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
    • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means

Definitions

  • the present invention relates to a valve driving apparatus of an internal combustion engine of the type of opening and closing an intake and exhaust valve by means of an actuator.
  • FIG. 2 One example of an accumulator valve driving apparatus in the prior art is shown in Fig. 2.
  • reference numeral 01 designates a hydraulic pressure control valve main body having 5 ports.
  • Numeral 02 designates a control valve, which is driven in synchronism of a crank shaft of an engine via a cam 03 and a roller 04.
  • An intake and exhaust valve 07 is opened and closed on the inside of an actuator 06 mounted to a cylinder cover 05.
  • the actuator 06 includes an upper hydraulic oil chamber 06a and a lower hydraulic oil chamber 06b, which are respectively connected to a control valve 01 via pipings 08 and 09.
  • Reference numeral 010 designates a hydraulic pressure feeder composed of a filter and a pump, and numeral 010a designates a hydraulic oil tank.
  • Reference numeral 011 designates an accumulator, which is maintained at a necessary constant hydraulic pressure and is communicated with the control valve 01 via a piping.
  • FIG. 2 shows the state where the roller 04 is present on a basic circle of the cam 03 and the intake and exhaust valve is closed, and under this condition, hydraulic oil fed from the accumulator 011 flows from the control valve 01 through the piping 09, acts upon the lower hydraulic oil chamber 06b of the actuator 06, and pushes up the intake and exhaust valve 07. At this time, the hydraulic oil in the upper hydraulic oil chamber 06a is led back to the hydraulic oil tank 010a of the hydraulic pressure feeder or pressure source 010 through the piping 08 and the control valve 01.
  • the control valve 01 has 5 ports and is complicated in structure, also it is necessary to make the amount of hydraulic oil necessitated for opening and closing the intake and exhaust valve flow also through the control valve 01, and hence the hydraulic pressure source is large-sized.
  • control valve 01 is driven by the cam 03, and so, opening and closing timing of the intake and exhaust valve cannot be varied arbitrarily.
  • a more specific object of the present invention is to provide a valve driving apparatus of an internal combustion engine, in which a control valve is simple in structure, a large-sized hydraulic pressure source is not necessitated, pipings of high-pressure hydraulic oil for opening and closing a valve as well as a structure of an actuator are simplified, consumption of high-pressure hydraulic oil is reduced, and opening and closing timing of an intake and exhaust valve can be arbitrarily varied.
  • valve driving apparatus of an internal combustion engine comprising the features of claim 1.
  • the above-featured valve driving apparatus of an internal combustion engine wherein the means for closing the intake and exhaust valve with a resilient force, consists of an air cylinder, and an air piston adapted to slide within the air cylinder as driven by the intake and exhaust valve driving piston and to generate a pneumatic resilient force.
  • a structure such that the operating hydraulic oil at a high pressure is used only for opening an intake and exhaust valve and closure of the valve is effected with a resilient force of accumulated in a resilient means as a result of lift of the intake and exhaust valve, is employed.
  • control valves and two logic valves are provided, and provision is made such that the control valves may be electrically driven to only control the action of a hydraulic pressure applied from an accumulator to large-diameter portions of the logic valves, and hydraulic oil necessitated for opening the intake and exhaust valve may be made to act upon a piston of a hydraulic cylinder within a valve driving actuator from the accumulator via one logic valve and one high-pressure piping.
  • the small-diameter sides of the two logic valves are communicated with each other, and upon closing the intake and exhaust valve, the other logic valve is opened so as to release the hydraulic pressure within the hydraulic cylinder and within the high-pressure piping.
  • the operating hydraulic oil at a high pressure accumulated in the accumulator acts upon the piston within the valve driving actuator when an opening side logic valve is opened by an opening side control valve which can be electrically driven at an arbitrary timing, and after the piston has depressed the intake and exhaust valve, the closure side control valve returns to its original state and the opening side logic valve is closed.
  • a compression force of air caused by an air piston moving jointly with the intake and exhaust valve acts as a biassing force in the direction of opening the valve, and as a result of balance between the pneumatic compression force and a force generated by the hydraulic pressure, an appropriate lift can be maintained.
  • the closure side logic valve is opened by the closure side control valve, and since the hydraulic pressure is released, the intake and exhaust valve is closed by the pneumatic spring means.
  • opening and closing characteristics of an intake and exhaust valve which are optimum for an engine can be obtained, and so, an internal combustion engine of low fuel consumption and excellent performance can be provided.
  • a hydraulic pressure source can be designed small and it becomes less expensive.
  • power consumption is also little, and hence a further low fuel consumption expense is resulted.
  • a small amount of hydraulic oil can suffice in the control valve portion, hence a compact control valve is provided, and a valve driving apparatus having a high reliability and a good durability can be realized.
  • reference numeral 1 designates a cylinder cover
  • numeral 2 designates an intake and exhaust valve
  • numeral 3 designates an air reservoir
  • numeral 4 designates a check valve
  • Reference numeral 5 designates an air piston, which slides within an air cylinder 6 jointly with the intake and exhaust valve 2.
  • Reference numeral 7 designates a valve driving actuator main body
  • numeral 8 designates a hydraulic cylinder
  • numeral 9 designates an actuating piston
  • numeral 8a designates an upper hydraulic oil chamber
  • numeral 8b designates a lower hydraulic oil chamber.
  • Reference numeral 10 designates a high-pressure piping
  • numeral 11 designates an opening side logic valve
  • numeral 12 designates an opening side logic valve oil path, which is connected to an accumulator 16.
  • Reference numeral 13 designates an opening side spool control valve, which is driven by a controller not shown in synchronism with rotation of a crank of an engine.
  • Reference numeral 14 designates a closure side logic valve
  • numeral 15 designates a closure side spool control valve, which is driven by a controller not shown similarly to the opening side spool control valve 13, and which is a 3-port control valve.
  • Reference numeral 16 designates an accumulator
  • numeral 17 designates a hydraulic pressure source, which feeds high-pressure hydraulic oil and consists of a pump and a filter.
  • Reference numeral 18 designates a low-pressure hydraulic pressure source, which communicates with the valve driving actuator 7 through a piping 18a.
  • Reference numeral 19 designates an oil tank
  • numeral 20 designates a communication oil path connecting the opening side logic valve 11 with the closure side logic valve 14
  • numeral 21 designates an oil path connecting a large-diameter side of the opening side logic valve 11 with the opening side spool control valve 13
  • numeral 22 designates an oil path connecting an opening side spool control valve 13 with the accumulator 16
  • numeral 23 designates an oil path connecting a large-diameter side of the closure side logic valve 14 with the closure side spool control valve
  • numeral 24 designates an oil path connecting the closure side spool control valve 15 with the accumulator 16.
  • Reference numeral 25 designates an oil discharge piping extending from the closure side logic valve 14 to the oil tank 19
  • numeral 26 designates an oil discharge piping extending from the spool control valves 13 and 15.
  • These spool control valves are 3-port control valves having a P-port, a C-port and a T-port, and they are electromagnetically driven.
  • Fig. 1 shows the state where an air pressure in the air reservoir 3 acts upon the lower side of the air piston 5 and the intake and exhaust valve 2 is kept closed.
  • the opening side and closure side spool control valves 13 and 15 would make the hydraulic pressure fed from the accumulator 16 act upon the large-diameter sides of the opening and closure logic valves 11 and 14, and thereby the logic valves 11 and 14 are kept closed.
  • the opening side spool control valve 13 is driven at an appropriate time determined by a computer in response to a trigger signal issue in synchronism with an engine not shown and on the basis of the operating condition of the engine.
  • the oil path 22 is closed, the oil path 21 communicates with the oil discharge piping 26, and since the hydraulic pressure on the large-diameter side of the logic valve 11 is released, the logic valve 11 opens, and hence the hydraulic pressure in the accumulator 16 acts upon the upper hydraulic oil chamber 8a of the hydraulic cylinder 8 within the valve driving actuator 7 through the oil path 12 and the high-pressure piping 10.
  • the hydraulic piston 9 is depressed by this hydraulic pressure, and thereby the intake and exhaust valve 2 is opened.
  • the air within the air cylinder 6 is compressed and exerts an upward force upon the air piston 5, and the intake and exhaust valve 2 lifts up to the point where the upward force balances with a downward force generated by the hydraulic pressure.
  • the opening side control valve 13 is returned to its original position, hence the hydraulic pressure in the accumulator 16 acts upon the large-diameter portion of the opening side logic valve 11, and the opening side logic valve 11 is closed.
  • a valve driving apparatus of an internal combustion engine including a hydraulic pressure source and an accumulator for pressurizing operating hydraulic oil and accumulating the pressurized operating hydraulic oil and adapted to drive an intake and exhaust valve by controlling the operating hydraulic oil in the accumulator
  • two logic valves communicated with each other for opening and closing a high-pressure hydraulic oil path communicated with an upper side of an intake and exhaust valve driving piston
  • two electromagnetically driven control valves for controlling opening and closure of the two logic valves
  • the control hydraulic oil for opening and closing the logic valves and the operating hydraulic oil for driving the intake and exhaust valve to open being fed from the accumulator at a high pressure

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fluid-Driven Valves (AREA)

Claims (2)

  1. Dispositif de commande de soupape pour un moteur à combustion interne qui comprend une source (17) de pression hydraulique et un accumulateur (16), destiné à mettre sous pression une huile hydraulique d'actionnement et à accumuler l'huile hydraulique d'actionnement mise sous pression, et qui est apte à commander une soupape (2) d'admission et d'échappement par régulation de l'huile hydraulique d'actionnement dans l'accumulateur (16),
    caractérisé en ce que ledit appareil comprend:
    - deux soupapes logiques (11, 14) en communication l'une avec l'autre dans un trajet (10, 20) d'huile hydraulique haute-pression allant vers le côté supérieur d'un piston (9) d'entraînement de la soupape d'admission et d'échappement, l'une (11) desdites soupapes logiques (11, 14) se trouvant dans un trajet (10, 12) d'huile hydraulique haute-pression provenant de l'accumulateur (16) afin d'ouvrir et fermer une huile haute-pression vers un côté supérieur dudit piston (9) d'entraînement de la soupape d'admission et d'échappement, et l'autre soupape logique (14) se trouvant dans un trajet (10, 20, 25) d'huile hydraulique haute-pression provenant dudit côté supérieur dudit piston (9) d'entraînement de la soupape d'admission et d'échappement pour ouvrir et fermer vers un réservoir (19) d'huile basse-pression,
    - deux vannes de commande (13, 15) entraînées de façon électromagnétique, destinées à commander l'ouverture et la fermeture desdites deux soupapes logiques (11, 14), l'huile hydraulique de commande pour ouvrir et fermer lesdites soupapes logiques (11, 14) et l'huile hydraulique d'actionnement destinée à faire ouvrir ladite soupape (2) d'admission et d'échappement étant envoyée depuis ledit accumulateur (16) sous pression élevée, et
    - des moyens (3, 4, 5, 6) pour fermer ladite soupape (2) d'admission et d'échappement avec une force élastique produite en résultat du soulèvement dudit piston d'entraînement (9) de ladite soupape d'admission et d'échappement lors de l'ouverture de ladite soupape (2) d'admission et d'échappement.
  2. Dispositif de cominande de soupape pour un moteur à combustion interne selon la revendication 1, caractérisé en ce que ledit moyen pour fermer la soupape (2) d'admission et d'échappement avec une force élastique comprend un cylindre pneumatique (6) et un piston pneumatique (5) apte à coulisser dans ledit cylindre pneumatique (6) alors qu'il est entraîné par ledit piston d'entraînement (9) de la soupape d'admission et d'échappement et à produire une force pneumatique élastique.
EP91101372A 1990-05-11 1991-02-01 Dispositif de commande de soupape pour moteur à combustion interne Expired - Lifetime EP0455937B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP12007390 1990-05-11
JP120073/90 1990-05-11

Publications (2)

Publication Number Publication Date
EP0455937A1 EP0455937A1 (fr) 1991-11-13
EP0455937B1 true EP0455937B1 (fr) 1994-08-10

Family

ID=14777233

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91101372A Expired - Lifetime EP0455937B1 (fr) 1990-05-11 1991-02-01 Dispositif de commande de soupape pour moteur à combustion interne

Country Status (5)

Country Link
EP (1) EP0455937B1 (fr)
JP (2) JP2527268Y2 (fr)
KR (1) KR940010284B1 (fr)
DE (2) DE455937T1 (fr)
DK (1) DK0455937T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5526784A (en) 1994-08-04 1996-06-18 Caterpillar Inc. Simultaneous exhaust valve opening braking system
US5647318A (en) 1994-07-29 1997-07-15 Caterpillar Inc. Engine compression braking apparatus and method

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK170122B1 (da) * 1993-06-04 1995-05-29 Man B & W Diesel Gmbh Stor totakts forbrændingsmotor
US5410994A (en) * 1994-06-27 1995-05-02 Ford Motor Company Fast start hydraulic system for electrohydraulic valvetrain
US5540201A (en) * 1994-07-29 1996-07-30 Caterpillar Inc. Engine compression braking apparatus and method
AT403835B (de) * 1994-07-29 1998-05-25 Hoerbiger Ventilwerke Ag Vorrichtung und verfahren zur beeinflussung eines ventils
US5582141A (en) * 1994-10-12 1996-12-10 Eaton Corporation Engine valve hydraulic actuator locating mechanism
DE10135377A1 (de) * 2001-07-20 2003-02-13 Wolfgang Nestler Hydraulischer Antrieb und Steuerung der Ventile eines Verbrennungsmotors
DE10161438B4 (de) * 2001-12-14 2004-07-15 Man B&W Diesel A/S Hubkolbenmaschine
LU90889B1 (en) * 2002-02-04 2003-08-05 Delphi Tech Inc Hydraulicv control system for a gas exchange valve of an internal combustion engine
US7004122B2 (en) * 2002-05-14 2006-02-28 Caterpillar Inc Engine valve actuation system
US6907851B2 (en) 2002-05-14 2005-06-21 Caterpillar Inc Engine valve actuation system
JP2010164023A (ja) * 2009-01-19 2010-07-29 Mitsui Eng & Shipbuild Co Ltd 油圧シリンダブロックの油圧通路構造
EP2295786B1 (fr) * 2009-08-04 2016-04-13 Wärtsilä Schweiz AG Agencement de liaison
DE102009046943A1 (de) * 2009-11-20 2011-05-26 Robert Bosch Gmbh Elektrohydraulischer Aktor
JP5781345B2 (ja) * 2011-03-24 2015-09-24 三菱重工業株式会社 油圧アクチュエータシステム
CN103388502B (zh) * 2013-07-31 2016-01-27 哈尔滨工程大学 一种全可变电液气阀驱动装置
CN104632317A (zh) * 2015-01-30 2015-05-20 哈尔滨工程大学 一种大功率船用低速柴油机排气阀装置
CN104791043A (zh) * 2015-04-23 2015-07-22 哈尔滨工程大学 一种实现发动机米勒循环的气门电液驱动***及方法
DK178787B1 (en) * 2015-05-06 2017-02-06 Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland A large turbocharged two-stroke self-igniting internal combustion engine with an exhaust valve actuation system
CN107100689B (zh) * 2017-06-28 2023-04-07 吉林大学 一种电磁控制液压驱动式全可变气门机构
GB2572965A (en) * 2018-04-17 2019-10-23 Caterpillar Inc Exhaust valve actuation system
CN110500156A (zh) * 2019-08-29 2019-11-26 上海联芊电子科技有限公司 一种气门驱动装置、内燃机、发动机及交通工具
CN114087076B (zh) * 2022-01-24 2022-05-13 龙口中宇热管理***科技有限公司 一种发动机闭缸气门控制装置及方法

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Publication number Priority date Publication date Assignee Title
FR1361178A (fr) * 1963-06-27 1964-05-15 Mitsubishi Shipbuilding & Eng Dispositif de commande rapide des soupapes dans un moteur à combustion interne
DK225982A (da) * 1981-07-07 1983-01-08 Sulzer Ag Indstroemnings-eller udstoedningsventil til en forbraendingsmotors cylindertopstykke
FR2619457B1 (fr) * 1987-08-14 1989-11-17 Commissariat Energie Atomique Procede d'obtention d'un motif notamment en materiau ferromagnetique ayant des flancs de pente differente et tete magnetique comportant un tel motif
JP2664986B2 (ja) * 1989-04-03 1997-10-22 三菱重工業株式会社 内燃機関の動弁装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5647318A (en) 1994-07-29 1997-07-15 Caterpillar Inc. Engine compression braking apparatus and method
US5526784A (en) 1994-08-04 1996-06-18 Caterpillar Inc. Simultaneous exhaust valve opening braking system

Also Published As

Publication number Publication date
KR910020298A (ko) 1991-12-19
DE69103323T2 (de) 1994-12-01
EP0455937A1 (fr) 1991-11-13
DE455937T1 (de) 1992-02-27
JPH0444408U (fr) 1992-04-15
JP2527268Y2 (ja) 1997-02-26
DK0455937T3 (da) 1994-12-12
KR940010284B1 (ko) 1994-10-22
JPH04128508A (ja) 1992-04-30
DE69103323D1 (de) 1994-09-15
JP2809354B2 (ja) 1998-10-08

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