EP0539320B1 - Dispositif de commande hydraulique d'une soupape d'échappement d'un moteur à combustion interne à piston - Google Patents

Dispositif de commande hydraulique d'une soupape d'échappement d'un moteur à combustion interne à piston Download PDF

Info

Publication number
EP0539320B1
EP0539320B1 EP92810735A EP92810735A EP0539320B1 EP 0539320 B1 EP0539320 B1 EP 0539320B1 EP 92810735 A EP92810735 A EP 92810735A EP 92810735 A EP92810735 A EP 92810735A EP 0539320 B1 EP0539320 B1 EP 0539320B1
Authority
EP
European Patent Office
Prior art keywords
servo
line
cylinder
pressure medium
piston
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
EP92810735A
Other languages
German (de)
English (en)
Other versions
EP0539320A1 (fr
Inventor
Alfred Franz Wunder
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.)
Winterthur Gas and Diesel AG
Original Assignee
Winterthur Gas and Diesel AG
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 Winterthur Gas and Diesel AG filed Critical Winterthur Gas and Diesel AG
Publication of EP0539320A1 publication Critical patent/EP0539320A1/fr
Application granted granted Critical
Publication of EP0539320B1 publication Critical patent/EP0539320B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/16—Silencing impact; Reducing wear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • 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

Definitions

  • the invention relates to a device for hydraulically actuating an exhaust valve with the features of the preamble of claim 1.
  • Such a device is known from DE-PS 38 09 954. It is intended to compensate for changes in length of the exhaust valve stem due to temperature changes, because otherwise the position of the servo piston shifts relative to the servo cylinder, which would result in a change in the closing point of the exhaust valve.
  • the known device is used in connection with a so-called “hydraulic bumper", which consists of the hydraulic fluid located in the pressure medium line between the servo cylinder and a cam-controlled lifting piston.
  • the pressure medium line and the relief line are therefore connected to the same location on the servo cylinder, ie pressure medium escapes into the pressure medium line when the outlet valve is closed.
  • a check valve opening against the pressure chamber is provided in the servo piston and an axial groove is provided in the section of the servo piston surrounded by the guide bushing, which together with the front edge of the guide bushing forms a throttling point that becomes smaller during the closing movement of the exhaust valve.
  • the throttle point is also closed.
  • a braking force is to be exerted on the valve movement with the throttle point during the closing movement of the outlet valve.
  • the guide bush is moved relative to the servo piston, whereby the pressure-filled space is refilled from the ventilation line (shortening of the shaft).
  • the PS does not explain how a displacement of the guide bush in the closed state of the outlet valve is to be carried out in the case of a shaft extension. It obviously does not take place automatically during the operation of the reciprocating piston internal combustion engine.
  • the invention is based on the object of modifying and improving the device of the type mentioned at the outset such that it can be used in conjunction with an electro-hydraulic control device according to EP-OS 441 100 and that changes in the stem length of the exhaust valve can be compensated for completely automatically.
  • this object is achieved by the features of the characterizing part of claim 1.
  • This ensures that the guide bush always automatically shifts in the same direction and to the same extent as the servo piston when the length of the valve stem changes, since even when the guide bush is shifted towards the pressure-filled space, pressure medium is displaced from this space into the pressure space, so that the relative assignment between servo pistons and guide bushing is retained. Changes in the length of the outlet valve stem are therefore automatically compensated in both directions, so that the opening and closing geometry of the servo device of the outlet valve remains the same regardless of thermal expansion.
  • the advantage of the new device is that damping of this movement occurs in the last phase of the closing movement of the exhaust valve because after the passage through the servo piston communicating with the relief line, the relief line remains connected to the pressure chamber.
  • a working cylinder 1 is formed in the machine housing of a 2-stroke diesel internal combustion engine, and then an exhaust duct 4 is formed in a separate housing 10 at its upper end.
  • an exhaust valve 2 is arranged at the entrance of the exhaust duct 4, which separates the combustion chamber 3 in the working cylinder 1 from the exhaust duct 4 in the closed position shown.
  • a working piston 5 is guided up and down.
  • the air to be compressed in the working cylinder is admitted into the cylinder chamber via slots (not shown) arranged in the lower region of the working cylinder 1 and is compressed in the combustion chamber 3 during the subsequent upward stroke of the working piston 5.
  • the fuel is supplied with the aid of at least one injection nozzle (not shown) which projects into the combustion chamber 3.
  • a piston 6 is arranged, which is guided in a cylinder 7 of the housing 10.
  • a compressed air line 9 is connected below the piston 6 of the cylinder space 7 'via a check valve 8.
  • the air enclosed in the cylinder space 7 'in this way forms an air spring which acts on the exhaust valve 2 in a closing sense.
  • the control device 12 has a pilot valve 15 designed as a 2/2-way valve and actuated by an electromagnet 14 and a 4/2-way valve 16.
  • the hydraulic pressure medium for example oil, is supplied to the control device 12 via a line 17 from a pressure medium source 18 designed as an accumulator.
  • the accumulator 18 receives the pressure medium from a reservoir 20 by means of a pump 19 which is driven by the crankshaft (not shown) of the internal combustion engine or electrically.
  • the pressure medium is under a pressure of, for example, 200 bar.
  • the line 17 leading from the accumulator 18 to the control device 12 forks upstream of the 4/2-way valve 16 into two line branches 17 'and 17''.
  • the line branch 17 ′′ contains a throttle point 22 and leads on the one hand to the pilot valve 15 and on the other hand to an end face of the 4/2-way valve 16.
  • a relief line 24 which leads to the 4/2-way valve 16 leads and continues as drain line 24 ', which opens into the reservoir 20 via a check valve 25.
  • Drain line 24 ' is also connected to a vent line 26 which branches off from the servo cylinder 13 above the piston 11 and has a throttle point 57.
  • the servo piston 11 has at its end facing away from the rod 11 'a blind bore 40 which is connected to an annular space 58 at its lower end in FIG. 1 in the region of the connection point 21 via transverse bores 56. In the area of the connection point 23 there is an annular space 59 between the servo piston 11 and the servo cylinder 13.
  • a guide bush 60 is arranged between the servo cylinder 13 and the servo piston 11, each of which has a breakthrough in the area of the connection points 21 and 23 in the form of an outer annular groove 61 or 62 and several of these extending from the circumference the guide bush has distributed radial bores 61 'or 62'.
  • the guide sleeve 60 is axially movably guided in the servo cylinder 13 and has at its upper end in FIG. 2 a transverse wall 60 'in the form of a cover detachably connected to the guide sleeve.
  • the servo piston 11 is slidably mounted in the guide bush 60 and, in the position shown in FIG.
  • the upper end wall 13 'of the servo cylinder 13 in FIG. 2 has a connection point 67 for the ventilation line 26.
  • a pressure medium-filled space 68 which communicates with the pressure chamber 65 on the one hand via a check valve 69 closing against this space and on the other hand communicates with the relief line 26 via a check valve 70 closing against the connection point 67.
  • the device according to Fig.2 works as follows. If the stem of the exhaust valve is lengthened due to an increase in temperature, the servo piston 11 is moved upward in FIG. 2 via the rod 11 '. Since the upper end face of the servo piston 11 bears against the shoulder 63, the guide bush 60 is also displaced upward when the servo piston is moved. As a result of this displacement, pressure medium is displaced from the space 68 into the pressure space 65 via the opening check valve 69. The pressure medium volume thus displaced escapes via the channels 71, 66, the annular groove 62 and the connection point 23 into the relief line 24.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (3)

  1. Dispositif d'actionnement hydraulique d'une soupape d'échappement (2) d'un moteur à combustion interne à piston alternatif, comportant un servopiston (11), guidé dans un servocylindre (13), qui est en liaison active avec l'extrémité de la soupape d'échappement, tournée vers la partie fermeture, qui est alimenté, à la cadence de travail du moteur, avec un fluide hydraulique sous pression dans le sens d'ouverture de la soupape, lequel fluide est envoyé à partir d'une source de fluide sous pression (18), par une conduite de fluide sous pression (27), à une chambre de pression (65) dans le servocylindre (13), à laquelle sont raccordées une conduite de décharge (24) ainsi qu'une conduite de purge d'air (26), une douille de guidage (60) axialement mobile, entourant le servopiston, étant placée entre le servocylindre (13) et le servopiston (11), laquelle douille est hermétiquement fermée à son extrémité, tournée à l'opposé de la partie de fermeture, par une cloison transversale (60'), et un compartiment (68), qui communique avec la conduite de purge d'air, par un clapet de non-retour (70), fermant vers la conduite de purge d'air (26), étant prévu entre la cloison transversale (60') et la paroi frontale (13') du servocylindre, caractérisé en ce que la conduite de fluide sous pression (27) et la conduite de décharge (24) sont raccordées au servocylindre (13), séparées l'une de l'autre, de manière que la douille de guidage (60) présente au moins un ajour (61' ou 62') communiquant avec le raccord (21) de la conduite de fluide sous pression (27) et le raccord (23) de la conduite de décharge (24) sur le servocylindre, en ce que le compartiment (68) rempli de fluide sous pression communique, par un clapet de non-retour (69), fermant vers ce compartiment (68), avec la chambre de pression (65) et en ce que la chambre de pression (65) est toujours reliée au raccord (23) pour la conduite de décharge (24) sur le servocylindre.
  2. Dispositif selon la revendication 1, caractérisé en ce que la cloison transversale (60') est conçue à la manière d'un couvercle pouvant être détaché de la douille de guidage (60).
  3. Dispositif selon les revendications 1 ou 2, caractérisé en ce que dans le servopiston (11) est prévu un canal (72) qui relie, vers la fin du déplacement d'ouverture de la soupape d'échappement (2), la chambre de pression (65) avec l'ajour (61') pratiqué sur la douille de guidage (60), communiquant avec le raccord (21) de la conduite de fluide sous pression (27).
EP92810735A 1991-10-23 1992-09-30 Dispositif de commande hydraulique d'une soupape d'échappement d'un moteur à combustion interne à piston Expired - Lifetime EP0539320B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH309891 1991-10-23
CH3098/91 1991-10-23

Publications (2)

Publication Number Publication Date
EP0539320A1 EP0539320A1 (fr) 1993-04-28
EP0539320B1 true EP0539320B1 (fr) 1995-01-11

Family

ID=4248578

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92810735A Expired - Lifetime EP0539320B1 (fr) 1991-10-23 1992-09-30 Dispositif de commande hydraulique d'une soupape d'échappement d'un moteur à combustion interne à piston

Country Status (6)

Country Link
EP (1) EP0539320B1 (fr)
JP (1) JP3564149B2 (fr)
KR (1) KR100222139B1 (fr)
CN (1) CN1032381C (fr)
DE (1) DE59201193D1 (fr)
DK (1) DK0539320T3 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5531192A (en) * 1994-08-04 1996-07-02 Caterpillar Inc. Hydraulically actuated valve system
DK1114918T3 (da) 2000-01-06 2004-09-06 Waertsilae Nsd Schweiz Ag Gasskiftesystem til en forbrændingsmotor og fremgangsmåde til drift af et sådant
GB0017425D0 (en) * 2000-07-14 2000-08-30 Lotus Car A valve system for controlling flow of gas into or out of a variable volume chamber of an internal combustion engine or a compressor
DE10311493B4 (de) * 2003-03-15 2005-01-05 Man B & W Diesel A/S Zweitakt-Dieselmotor
ITBO20030389A1 (it) * 2003-06-23 2004-12-24 Magneti Marelli Powertrain Spa Gruppo elettroidraulico di azionamento delle valvole
DE10361221B4 (de) * 2003-12-24 2006-03-09 Man B&W Diesel A/S Vorrichtung zur Steuerung der zeitlich versetzten Verbindung von zwei mit einem Druckmittel beaufschlagbaren Aggregaten mit einer Druckmittelquelle
US7290509B2 (en) * 2005-08-01 2007-11-06 Zheng Lou Variable valve actuator
US7587863B2 (en) * 2006-08-17 2009-09-15 Fike Corporation Seal for sanitary overpressure vent structure
CN102787878B (zh) * 2012-07-27 2014-07-30 长城汽车股份有限公司 一种液压驱动的发动机配气机构
CN105756739B (zh) * 2016-05-04 2018-05-18 哈尔滨工程大学 电磁液压驱动式配气系统
CN109372607A (zh) * 2018-10-23 2019-02-22 中船动力研究院有限公司 多级泄油排气阀及其工作方法

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3809954C1 (en) * 1988-03-24 1989-08-24 Bayerische Motoren Werke Ag, 8000 Muenchen, De Device for the hydraulic opening of a lifting valve
DE59001316D1 (de) * 1990-02-08 1993-06-03 Sulzer Ag Einrichtung zum steuern des auslassventils einer hubkolbenbrennkraftmaschine.

Also Published As

Publication number Publication date
DK0539320T3 (da) 1995-03-20
JP3564149B2 (ja) 2004-09-08
KR930008317A (ko) 1993-05-21
EP0539320A1 (fr) 1993-04-28
KR100222139B1 (ko) 1999-10-01
JPH05195731A (ja) 1993-08-03
DE59201193D1 (de) 1995-02-23
CN1032381C (zh) 1996-07-24
CN1071733A (zh) 1993-05-05

Similar Documents

Publication Publication Date Title
EP0432404A2 (fr) Commande de soupape pour soupapes de distribution de moteurs à combustion interne
DE60318363T2 (de) Hydraulisches Ventilbetätigungssystem
DE3714762C2 (fr)
EP0133470B1 (fr) Injecteur de carburant pour moteurs à combustion interne
DE3833459A1 (de) Hydraulischer ventiltrieb fuer eine brennkraftmaschine
DE2732063C2 (de) Arbeitskolben zur Veränderung der Kompression
DE3808542A1 (de) Ventiltrieb fuer ein gaswechselventil einer brennkraftmaschine
EP0562286A1 (fr) Dispositif de commande d'une soupape d'échappement en phase de frein moteur
DE10155669A1 (de) Vorrichtung zur Steuerung mindestens eines Gaswechselventils
EP0539320A1 (fr) Dispositif de commande hydraulique d'une soupape d'échappement d'un moteur à combustion interne à piston
WO1988005863A1 (fr) Pompe a injection de carburant pour moteur a combustion interne
DE3939002A1 (de) Hydraulische ventilsteuervorrichtung fuer eine mehrzylinder-brennkraftmaschine
DE2721412B2 (de) Druckmittelgetriebene Fettschmierpresse
DE4118555A1 (de) Foerderbeginnverstelleinrichtung einer kraftstoffeinspritzpumpe
DE3044255C2 (fr)
EP0193142B1 (fr) Dispositif de frein moteur pour moteur à combustion interne
DE3150675A1 (de) Zuendvorrichtung fuer verbrennungsmotoren mit innerer verbrennung und selbstzuendung
CH681825A5 (fr)
EP0441100B1 (fr) Dispositif pour commander la soupape d'échappement d'un moteur à combustion interne à piston
DE4202542A1 (de) Variabler ventiltrieb fuer ein hubventil
EP0240686A1 (fr) Pompe d'injection de combustible pour moteurs à combustion interne à recirculation des gaz d'échappement
DE2223292B2 (de) Hydraulisch betaetigbares schlaggeraet
DE102016203559A1 (de) Hydraulisch betätigtes Schaltventil
DE3625664C2 (fr)
DE1809160A1 (de) Einlassventil fuer Kolben mit veraenderbarem Kompressionsverhaeltnis

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): CH DE DK FR IT LI

17P Request for examination filed

Effective date: 19930622

17Q First examination report despatched

Effective date: 19931122

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE DK FR IT LI

RIN1 Information on inventor provided before grant (corrected)

Inventor name: WUNDER, ALFRED FRANZ

REF Corresponds to:

Ref document number: 59201193

Country of ref document: DE

Date of ref document: 19950223

ITF It: translation for a ep patent filed
REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

ET Fr: translation filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19950930

Ref country code: CH

Effective date: 19950930

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

26N No opposition filed
REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DK

Payment date: 20090910

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20090922

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20090926

Year of fee payment: 18

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100930

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20110531

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59201193

Country of ref document: DE

Effective date: 20110401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110401

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100930

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20091001

Year of fee payment: 18

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100930