EP0393017A2 - Soupape actionnable hydrauliquement à levée réglable - Google Patents

Soupape actionnable hydrauliquement à levée réglable Download PDF

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Publication number
EP0393017A2
EP0393017A2 EP90890109A EP90890109A EP0393017A2 EP 0393017 A2 EP0393017 A2 EP 0393017A2 EP 90890109 A EP90890109 A EP 90890109A EP 90890109 A EP90890109 A EP 90890109A EP 0393017 A2 EP0393017 A2 EP 0393017A2
Authority
EP
European Patent Office
Prior art keywords
valve
stop
valve according
stop cam
cam
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.)
Granted
Application number
EP90890109A
Other languages
German (de)
English (en)
Other versions
EP0393017B1 (fr
EP0393017A3 (fr
Inventor
Christof D. Dipl.-Ing. Fischer
Diethard Dipl.-Ing. Plohberger
Karl Dipl.-Ing. Wojik
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.)
AVL List GmbH
Original Assignee
AVL List GmbH
AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH
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 AVL List GmbH, AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH filed Critical AVL List GmbH
Publication of EP0393017A2 publication Critical patent/EP0393017A2/fr
Publication of EP0393017A3 publication Critical patent/EP0393017A3/fr
Application granted granted Critical
Publication of EP0393017B1 publication Critical patent/EP0393017B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/04—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure using fluid, other than fuel, for injection-valve actuation
    • F02M47/043—Fluid pressure acting on injection-valve in the period of non-injection to keep it closed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/161—Means for adjusting injection-valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M67/00—Apparatus in which fuel-injection is effected by means of high-pressure gas, the gas carrying the fuel into working cylinders of the engine, e.g. air-injection type
    • F02M67/10—Injectors peculiar thereto, e.g. valve less type
    • F02M67/12—Injectors peculiar thereto, e.g. valve less type having valves

Definitions

  • the invention relates to a hydraulically actuated valve with a controllable stroke, in particular a mixture injection valve for internal combustion engines with a stop surface firmly connected to the valve stem.
  • a hydraulically actuated valve with a controllable stroke in particular a mixture injection valve for internal combustion engines with a stop surface firmly connected to the valve stem.
  • Such valves allow, for example, particularly high thermal efficiencies to be achieved in internal combustion engines.
  • a certain gas volume is taken from the respective cylinder and temporarily stored in a gas storage device.
  • the fuel is injected into this buffer. In this way, almost the entire duration of a working cycle of the internal combustion engine is available for the distribution of the fuel in the storage volume.
  • the valve opens during the next compression cycle.
  • Valves which have a piston with a stop surface. This stop surface interacts with a valve-fixed counter surface, which limits the maximum valve lift.
  • a valve-fixed counter surface which limits the maximum valve lift.
  • the object of the invention is to avoid these disadvantages and to provide a valve in which the maximum valve lift can be adapted to the respective operating conditions and set precisely. It is particularly important to note that different thermal expansions, wear, etc. cannot affect the accuracy of the setting.
  • a motor-driven stop cam which interacts with the stop surface, the maximum Ven being rotated by a predetermined angle by rotating the stop cam tilhub is adjustable and the stop cam can be brought into contact with the stop surface even in the closed position of the valve. Furthermore, a control device is provided which controls the drive of the stop cam depending on the operating states of the internal combustion engine.
  • the valve always has two end positions, which are defined on the one hand by the seating of the valve plate on the valve seat and on the other hand by the stop of the stop surface.
  • the stop cam is arranged so that it can be brought into contact with the stop surface even when the valve is closed. In this way it is possible for the stop cam to return to an initial position after each working stroke of the valve, in which the stop cam rests against the stop surface when the valve is closed. This results in a well-defined starting position for the dimensioning of the rotary movement of the stop cam, which is carried out to limit the next opening of the valve. In this way, different thermal expansions and wear can be compensated for.
  • the stop cam is preferably driven by an electric motor, preferably a stepper motor.
  • an electric motor preferably a stepper motor.
  • the adjustment mechanism responds quickly to the control pulses.
  • an ordinary servo motor or a stepper motor can be used.
  • slip clutch is arranged in a recess in the stop cam. This results in a particularly compact embodiment of the invention.
  • the drive shaft penetrates the valves, the assemblies consisting of slip clutch and stop cam being arranged within the valves.
  • the valve itself represents a housing for the more sensitive components, in particular the slip clutch. Only the drive takes place from the outside.
  • the slip clutch in the direction of rotation which brings the stop cam closer to the stop surface, transmits less torque than in the opposite direction.
  • the motor presses the cam against the stop surface of the closed valve.
  • the force applied corresponds to the torque that the slip clutch can transmit in the closing direction.
  • a higher torque may be required. This higher moment can be provided by a suitable slip clutch.
  • the slip clutch has at least one jaw, which rests on the inside of a cylindrical surface and is pressed against it by a spring, the self-amplification of the transmissible torque being achieved by the articulation of the drive shaft of the clutch at one end of the jaw in one direction of rotation becomes.
  • the slip clutch works like a shoe brake.
  • a control device for the engine which controls the maximum valve lift by rotating the stop cam on the basis of a predetermined characteristic diagram and data on the operating state of the internal combustion engine, and which in the closed valve reverses the on Knock cam causes, the motor makes a larger angle of rotation during this reverse rotation than corresponds to the return to the theoretical zero position. If the motor is designed as a stepper motor, this means that the control device, prior to opening the valve, executes a predetermined number of steps which correspond to a specific angle of rotation of the stop cam and thus to a specific maximum valve lift and which, after the valve is closed, the execution a larger number of steps than before opening in the opposite direction.
  • a hydraulic piston preferably pressurized with fuel, is provided to close the valve and acts against the force of a spring. This enables a particularly simple construction of the device according to the invention.
  • a further simplification can be achieved if a surface of the hydraulic piston simultaneously acts as a stop surface.
  • a gas accumulator for a gas volume extracted from the cylinder of an internal combustion engine and a fuel injection device for introducing the fuel into this gas accumulator are provided.
  • Such a mixture injection valve enables the highest thermal efficiencies to be achieved in internal combustion engines.
  • valve thermally against is isolated over the cylinder head of the internal combustion engine. In this way, the temperature of the valve is increased significantly, so that the formation of oil carbon is avoided and a self-cleaning effect is achieved.
  • the maximum valve lift can be limited to a value between 0 and 0.5 mm by the stop cam.
  • a mixture injection valve 1 is shown, which is arranged in the cylinder head 2 of an internal combustion engine, not shown.
  • the valve stem 3 is axially movable and has at its end a valve plate 4 which closes the opening between the combustion chamber 5 and the mixing chamber 6 arranged inside the valve 1.
  • a hydraulic piston 7 is fixedly connected to the valve stem 3, which seals a control chamber 8 in the valve 1.
  • a pressure spring 9 is also connected to the hydraulic piston 7 and presses the valve 1 into its open position.
  • the mixing chamber 6 and the control chamber 8 are separated from one another by a seal 10.
  • the stroke of the valve 1 is limited by a stop cam 11.
  • This stop cam 11 interacts with a stop surface 12 which is arranged on the hydraulic piston 7.
  • the stop cam 11 is connected via a shaft 13 to a slip clutch 14 which is driven by an electric stepper motor 16 via a further shaft 15.
  • the stop cam 11 is arranged such that contact with the stop surface 12 is possible even in the closed position of the valve 1.
  • a control unit 17 is provided to give a control command to the stepping motor 16 before opening the valve 1, which then executes a number of steps corresponding to the desired opening of the valve 1.
  • Fuel is removed from a reservoir 18 by means of a feed pump 19.
  • a pressure control valve 20 ensures a constant pressure in the line section 21.
  • the fuel for the injection is metered volumetrically.
  • the fuel is injected into the mixing chamber 6 via a slightly preloaded check valve 23 and a nozzle 24.
  • the check valve 23 is arranged as close as possible to the valve 1 in order to minimize the evaporation losses.
  • the injection takes place immediately after the valve 1 is closed. At this point in time, the pressure in the mixing chamber 6 is between 2 and 20 bar.
  • the corresponding cylinder of the internal combustion engine is currently executing the work cycle.
  • the valve 1 is opened during the compression stroke.
  • the injected fuel has now completely evaporated and is evenly distributed in the mixing chamber 6.
  • the stop cam 11 Before opening, the stop cam 11 is brought into its position limiting the valve lift as described above.
  • the opening is brought about by an electromagnetically controlled three-way valve 25 switching over and depressurizing the control chamber 8 filled with fuel.
  • the compression spring 9 presses the hydraulic piston 7 down until the stop surface 12 abuts the stop cam 11. At this time, the pressure in the combustion chamber 5 is lower than in the mixing chamber 6, so that the content of the mixing chamber 6 flows out into the combustion chamber 5.
  • the valve 1 then remains open until the working cycle, so that gases in turn flow back from the combustion chamber 5 into the mixing chamber 6.
  • the time of closing is chosen so that on the one hand in the mix mer 6 a sufficiently high pressure between 2 and 20 bar is guaranteed for the next injection, but on the other hand, penetration of the flame front into the mixing chamber 6 can be reliably excluded.
  • the closing of the valve 1 is brought about by switching the three-way valve 25 again by injecting fuel under pressure from the line section 21 into the control chamber 8.
  • the hydraulic piston 7 moves upwards and closes the valve 1 against the resistance of the compression spring 9.
  • an atomizing device 26 is provided for deflecting the gas jet, which has one or more bores 27.
  • the valve 1 is thermally insulated from the cylinder head 2. Oil coal mainly forms in a temperature range from 150 to 180 ° C. If the valve is operated above 180 ° C, self-cleaning takes place, which increases the service life considerably. This is caused by the formation of a gap 28 between valve 1 and cylinder head 2.
  • the sealing seat 29 between the valve 1 and the cylinder head can be made of a material with extremely poor thermal conductivity.
  • the slip clutch 14 shown in FIGS. 2 and 3 has a clutch shoe 30 which bears against the inside of a cylinder surface 31 which is incorporated into the shaft 13.
  • the coupling jaw 30 is connected by a pin 32 to a section 33 of the shaft 15.
  • a coil spring 34 which is supported in a recess 35 in the shaft 15, presses the clutch shoe 30 against the cylinder surface 31.
  • the pin 32 and the coil spring 34 engage at opposite ends of the clutch shoe 30. In this way it is achieved that different torques can be transmitted through the slip clutch 14 depending on the direction of rotation.
  • the clutch shoe 30 is pressed by the pin 32 and the spiral spring 34 against the cylinder surface 31 with a force which increases with the transmitted torque.
  • a common motor 16 is provided for driving a plurality of stop cams 114 of an internal combustion engine (not shown in more detail).
  • the drive shaft 115 penetrates the valves 101 in the region of the control chambers 108.
  • the drive shaft 115 is constructed from a plurality of segments which are connected to one another by flanges 90.
  • the outer contour of the slip clutch 114 also forms the stop cam 111. Inside this stop cam 111 there is a cylinder surface 31 against which the clutch shoe 30 bears.
  • the clutch shoe 30 is connected to the shaft 115 by a pin 32.
  • a spiral spring 34 which is supported on a seat ring 91, which is screwed onto the shaft 115, presses the coupling jaw 30 against the cylinder surface 31.
  • the axis 92 of the shaft 115 lies outside the plane defined by the axes 93 of the valves 101 to avoid penetration of the valve stem 103 and the drive shaft 115.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Valve Device For Special Equipments (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
EP90890109A 1989-04-12 1990-04-09 Soupape actionnable hydrauliquement à levée réglable Expired - Lifetime EP0393017B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT865/89 1989-04-12
AT0086589A AT407428B (de) 1989-04-12 1989-04-12 Hydraulisch betätigbares ventil mit steuerbarem hub

Publications (3)

Publication Number Publication Date
EP0393017A2 true EP0393017A2 (fr) 1990-10-17
EP0393017A3 EP0393017A3 (fr) 1991-03-27
EP0393017B1 EP0393017B1 (fr) 1992-12-02

Family

ID=3501596

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90890109A Expired - Lifetime EP0393017B1 (fr) 1989-04-12 1990-04-09 Soupape actionnable hydrauliquement à levée réglable

Country Status (5)

Country Link
US (1) US5048489A (fr)
EP (1) EP0393017B1 (fr)
JP (1) JP2571452B2 (fr)
AT (1) AT407428B (fr)
DE (1) DE59000524D1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT408137B (de) * 1995-02-27 2001-09-25 Avl Verbrennungskraft Messtech Einrichtung zum einbringen von kraftstoff in den brennraum einer brennkraftmaschine
CN103502620A (zh) * 2011-04-19 2014-01-08 蒂塔诺山有限公司 用于优化内燃机的方法

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4332124A1 (de) * 1993-09-22 1995-03-23 Bosch Gmbh Robert Kraftstoffeinspritzdüse für Brennkraftmaschinen
US5438968A (en) * 1993-10-06 1995-08-08 Bkm, Inc. Two-cycle utility internal combustion engine
US5398654A (en) * 1994-04-04 1995-03-21 Orbital Fluid Technologies, Inc. Fuel injection system for internal combustion engines
JPH0893601A (ja) * 1994-09-22 1996-04-09 Zexel Corp 燃料噴射ノズル
DE19504849A1 (de) * 1995-02-15 1996-08-22 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
AT408138B (de) * 1995-02-23 2001-09-25 Avl Verbrennungskraft Messtech Einrichtung zum einbringen von kraftstoff in den brennraum einer brennkraftmaschine
US6011195A (en) 1996-10-10 2000-01-04 Kimberly-Clark Worldwide, Inc. Wet resilient absorbent article
DE19623211A1 (de) * 1996-06-11 1997-12-18 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
US5685273A (en) * 1996-08-07 1997-11-11 Bkm, Inc. Method and apparatus for controlling fuel injection in an internal combustion engine
FI101739B1 (fi) * 1996-08-16 1998-08-14 Waertsila Nsd Oy Ab Ruiskutusventtiilijärjestely
US6095115A (en) * 1998-02-02 2000-08-01 Diesel Engine Retarders, Inc. Self-clipping slave piston device with lash adjustment for a compression release engine retarder
WO2000011336A1 (fr) 1998-08-19 2000-03-02 Diesel Engine Retarders, Inc. Piston a course limitee, a securite integree, a commande hydraulique
DE10048497A1 (de) * 1999-10-08 2001-05-17 Denso Corp Einstellverfahren für Brennstoffeinspritzsystem
US6691935B1 (en) * 2000-02-07 2004-02-17 Robert Bosch Gmbh Injection nozzle
US7341028B2 (en) * 2004-03-15 2008-03-11 Sturman Industries, Inc. Hydraulic valve actuation systems and methods to provide multiple lifts for one or more engine air valves
US7387095B2 (en) * 2004-04-08 2008-06-17 Sturman Industries, Inc. Hydraulic valve actuation systems and methods to provide variable lift for one or more engine air valves
US8794491B2 (en) * 2011-10-28 2014-08-05 Nordson Corporation Dispensing module and method of dispensing with a pneumatic actuator
CA2798870C (fr) 2012-12-17 2014-07-22 Westport Power Inc. Injection directe de carburant gazeux enrichi a l'air pour un moteur a combustion interne
WO2016034992A1 (fr) 2014-09-02 2016-03-10 Titano S.R.L. Boîte de magnétisation pour carburant, moteur à combustion interne comportant des moyens de magnétisation d'air et de carburant et procédé de magnétisation associé
WO2016034995A1 (fr) 2014-09-02 2016-03-10 Titano S.R.L. Moteur doté d'un système de magnétisation à activation pouvant être sélectionnée, de préférence apte à fonctionner à une vitesse de fonctionnement constante, et procédé d'optimisation du rendement dudit moteur
WO2016035001A1 (fr) 2014-09-02 2016-03-10 Titano S.R.L. Moteur à turbocompresseur alimenté par des fluides magnétisés et procédé associé
KR102395299B1 (ko) * 2017-10-24 2022-05-09 현대자동차주식회사 연료 인젝터 및 그의 제어방법

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4501245A (en) * 1983-03-25 1985-02-26 Diesel Kiki Co., Ltd. Fuel injection valve with variable lifting amount of the nozzle needle
WO1989001568A1 (fr) * 1987-08-12 1989-02-23 Avl Gesellschaft Für Verbrennungskraftmaschinen Un Procede et dispositif d'introduction de carburant dans la chambre de combustion d'un moteur a combustion interne

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JPS54155319A (en) * 1978-05-29 1979-12-07 Komatsu Ltd Fuel injection controller for internal combustion engine
US4300509A (en) * 1980-10-06 1981-11-17 Ford Motor Company Fuel injection and control systems
JPS633419Y2 (fr) * 1981-04-07 1988-01-27
JPS60201067A (ja) * 1984-03-26 1985-10-11 Diesel Kiki Co Ltd 分配型燃料噴射ポンプ
JPS60240868A (ja) * 1984-05-14 1985-11-29 Mitsubishi Motors Corp 燃料噴射ポンプの噴射時期調定方法
JPH064059Y2 (ja) * 1984-10-23 1994-02-02 スズキ株式会社 燃料噴射弁取付装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4501245A (en) * 1983-03-25 1985-02-26 Diesel Kiki Co., Ltd. Fuel injection valve with variable lifting amount of the nozzle needle
WO1989001568A1 (fr) * 1987-08-12 1989-02-23 Avl Gesellschaft Für Verbrennungskraftmaschinen Un Procede et dispositif d'introduction de carburant dans la chambre de combustion d'un moteur a combustion interne

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT408137B (de) * 1995-02-27 2001-09-25 Avl Verbrennungskraft Messtech Einrichtung zum einbringen von kraftstoff in den brennraum einer brennkraftmaschine
CN103502620A (zh) * 2011-04-19 2014-01-08 蒂塔诺山有限公司 用于优化内燃机的方法
CN103502620B (zh) * 2011-04-19 2017-02-08 蒂塔诺山有限公司 用于优化内燃机的方法

Also Published As

Publication number Publication date
JPH02294553A (ja) 1990-12-05
ATA86589A (de) 2000-07-15
EP0393017B1 (fr) 1992-12-02
US5048489A (en) 1991-09-17
AT407428B (de) 2001-03-26
DE59000524D1 (de) 1993-01-14
JP2571452B2 (ja) 1997-01-16
EP0393017A3 (fr) 1991-03-27

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