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EP0497194B1 - Procédé pour actionner un poussoir de soupape d'échappement d'un moteur en mode frein moteur - Google Patents

Procédé pour actionner un poussoir de soupape d'échappement d'un moteur en mode frein moteur Download PDF

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Publication number
EP0497194B1
EP0497194B1 EP92100960A EP92100960A EP0497194B1 EP 0497194 B1 EP0497194 B1 EP 0497194B1 EP 92100960 A EP92100960 A EP 92100960A EP 92100960 A EP92100960 A EP 92100960A EP 0497194 B1 EP0497194 B1 EP 0497194B1
Authority
EP
European Patent Office
Prior art keywords
pressure
inner part
tappet
piston
pressure chamber
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
EP92100960A
Other languages
German (de)
English (en)
Other versions
EP0497194A1 (fr
Inventor
Heribert Dipl.-Ing. Kubis
Dieter Wittmann
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.)
MAN Truck and Bus SE
Original Assignee
MAN Nutzfahrzeuge 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 MAN Nutzfahrzeuge AG filed Critical MAN Nutzfahrzeuge AG
Publication of EP0497194A1 publication Critical patent/EP0497194A1/fr
Application granted granted Critical
Publication of EP0497194B1 publication Critical patent/EP0497194B1/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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • 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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/245—Hydraulic tappets

Definitions

  • the invention relates to a method according to the preamble of claim 1.
  • GB-A 20 06 373 which is considered to be the subsequent state of the art, discloses a valve tappet which allows a valve clearance to be compensated for hydraulically.
  • the valve lifter has an inner part which is guided in an outer part so as to be axially movable. The movement of the inner part is limited by a stop.
  • the inner part interacts with a push rod of a valve.
  • a spring-loaded piston is provided in the inner part, which holds a check valve arranged at the base of the inner part in the open position via a mandrel connected to the piston. If pressure from an external pressure source is now applied to the pressure chamber under the piston, the inner part is first raised relative to the outer part until any valve play that may exist is equalized.
  • the inner part experiences a counterforce, so that the pressure under the piston rises and the piston and the mandrel are raised against the force of the spring and the check valve closes.
  • a reaction of the hydraulic pressure under the inner part on pressure-carrying parts of the periphery of the valve tappet is avoided.
  • the invention has for its object to further develop this method so that the stroke of the exhaust valve tappet during a compression stroke in engine braking mode takes place solely by application of an external pressure source and the amount of the stroke is limited to a predetermined value.
  • the valve stroke of the exhaust valve can be precisely regulated by the constant oil quantity supplied by the external pressure source. Damage caused by the reaction of excessive hydraulic pressure on the supply lines or the pressure source is reliably avoided.
  • the exhaust valve 4 In engine braking mode, the exhaust valve 4 should also be slightly raised during the compression stroke to blow off the compressed air, so that additional braking work is performed.
  • the outlet valve tappet 1 has an inner part 8 which is axially movable in a tappet outer part 7 and which is installed with a stroke 9.
  • pressure fluid is supplied from an external pressure source 11, which raises the inner part 8 together with the push rod 3 until the inner part 8 has performed a designated stroke 9 and between the inner part 8 and a stop 8a a game 9a remains ( Figure 2).
  • the outlet valve 4 thereby opens and the pre-compressed air is blown off.
  • the inner part 8 is subjected to a special design in order to prevent the reaction to excessive hydraulic pressure on the pressure-carrying parts.
  • the inner part 8 has an axially movable piston 12, which is held in the starting position by a compression spring 13 and keeps the valve seat 25 open.
  • the piston 12 has a stroke limiter 14 on the one hand and a mandrel 15 on the other hand.
  • the inner part has a ball socket 16 at its upper end, while the lower end is closed by a valve 17.
  • the push rod 3 shown in FIG. 1 is mounted in the ball socket 16.
  • a first pressure chamber 19 under the piston 12 can be connected to the external pressure source 11 (FIG. 1) via through bores 18.
  • the first pressure chamber 19 in turn communicates in the illustrated rest position of the piston 12 via first and second bores 20, 21 in the valve 17 with a second pressure chamber 22 below the inner part 8.
  • valve 17 there is a spring 23 with a ball 24 which is held in the starting position by means of the compression spring 13 via the mandrel 15.
  • the inner part 8 is limited with stroke 9 plus a game 9a by stop ring 8a in a tappet outer part 7 of the outlet valve tappet 1.
  • the first pressure chamber 19 can be connected via the bores 18 to the pressure source 11 shown in FIG. 1.
  • the compression spring 13 is first compressed by the piston 12 until the stroke limitation 14 on the inner part 8 comes to a stop.
  • the ball 24 is pressed into a seat 25 by the spring 23 and initially closes the first bore 20.
  • the force of the spring 23 is now designed so that the ball 24 can still open due to the pressure building up in the first pressure chamber 19 and opens the path of the pressure fluid via the first bore 20 and the second bore 21 to the second pressure chamber 22. Due to the force exerted by the second pressure chamber 22 on the inner part 8, the latter is lifted together with the push rod 3 (FIG. 1) mounted in the spherical cap 16 and moved until the stroke 9 (FIG. 2) is exhausted.
  • the stroke 9 results as a function of the amount of oil delivered by the pressure source 11. This represents a constant since the pressure source 11 (FIG. 1) is designed as a positive displacement pump.
  • the outlet valve 4 (FIG. 1) is opened in accordance with the distance of the stroke 9. Under normal operating conditions, a play 9a remains between the inner part 8 and the stop ring 8a.
  • first and second regulating bores 26, 27 are provided in the inner part 8, which are connected to one another via an overflow channel 28.
  • the hydraulic pressure supplied by the bore 18 can act on its side facing the first pressure chamber 19 and move it against the restoring force of the compression spring 13.
  • hydraulic fluid can flow into the space filled by the compression spring 13 via the overflow channel 28 and the second regulating bore 27.
  • This room is over a relief bore 30 is connected to the environment for pressure equalization, whereby a further movement of the piston 12 is stopped.
  • the functions of the other parts are similar to the embodiment according to FIGS. 2 and 3 and have been explained in detail there.
  • the advantage of this tappet design is that the pressure relief valve can be dispensed with.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Claims (4)

  1. Procédé pour actionner un poussoir de soupape d'échappement quand un moteur à combustion interne est en fonctionnement de freinage, moteur dans lequel le poussoir de soupape (1) est monté entre une came d'échappement (6) et une tige de poussoir (3) d'un mécanisme de soupape d'échappement, le poussoir de soupape (1) étant essentiellement formé d'une partie externe de poussoir (7) et d'une partie interne (8) pouvant être actionnée par une source de pression et se déplacer axialement dedans, tandis que la partie interne (8) est guidée dans la partie externe (7) du poussoir en se déplaçant axialement avec du jeu, la partie interne (8) présentant un piston (12) maintenu en position de départ au moyen d'un ressort de pression (13) dont on peut limiter le mouvement axial en direction de la tige de poussoir (3) par un limiteur de course et, à l'extrémité opposée au ressort de pression (13), par un mandrin (15), le mandrin (15) appuyant sur une bille (24) qui peut être comprimée dans le sens du piston (12) par un ressort (23) de telle manière qu'une deuxième chambre de pression (22) se trouvant entre la partie externe (7) du poussoir et la partie interne (8), puisse être reliée par des alésages (18), un premier et un second alésages (20, 21) et un siège de soupape (25) à la source externe de pression (11), puis ensuite, par une pression croissante dans une première chambre de pression (19), le piston (12) libéré par la source externe de pression (11), se déplace à l'encontre du ressort de pression (13) et, de cette façon, la bille (24) est libérée, la bille (24) bloquant par le ressort (23) la deuxième chambre de pression (22) par rapport à la première chambre de pression (19) et le ressort (23) étant déterminé de telle façon que la pression de la source de pression (11) soit d'abord suffisante pour soulever la bille (24) du siège de soupape (25), l'huile s'écoulant dans la deuxième chambre de pression (22) soulevant la partie intérieure (8) et ouvrant de cette façon la soupape d'échappement (4), et de telle façon que quand la pression est croissante à partir de la force de la tige de poussoir (3) qui est exercée sur la partie interne (8) par la pression croissante, qui en résulte dans la deuxième chambre de pression (22), la bille (24) bloque la chambre de pression (22) au moyen du siège de soupape (25) et relie le courant de retour provenant de la seconde chambre de pression (22) à la source externe de pression (11) en fermant le siège de soupape (25) et, après abaissement de la pression, par la source externe de pression le ressort de pression (13) ramène le piston (12) contre la bille (24) à sa position de départ, grâce à quoi le siège de soupape (25) s'ouvre, l'huile s'écoule de la deuxième chambre de pression (22) et la course de la partie interne (8) et de cette façon de la soupape d'échappement (4) se termine, procédé caractérisé en ce que la source de pression (11) constituée par une pompe à déplacement refoule, pendant le cycle de compression du moteur à combustion interne, un débit d'huile en permanence constant dans la seconde chambre de pression (22), grâce à quoi la partie interne (8) ouvre en partie la soupape d'échappement (4) au moyen de la tige de poussoir (3), et en ce que la pression appliquée par la source de pression (11) décroît vers la fin du cycle de compression, de l'huile pouvant couler en arrière à partir de la seconde chambre de pression (22), vers la source de pression (11).
  2. Procédé selon la revendication 1, caractérisé en ce que la course du piston (12) est limitée par une butée (14) qui est reliée de façon rigide au piston (12) .
  3. Procédé selon la revendication 1, caractérisé en ce que la course (9) est limitée par un premier et un second alésages de réglage (26, 27), le premier alésage de réglage (26) étant localisé dans la partie interne (8), de telle façon que, dans la position terminale voulue du piston (12), ce piston libère le premier alésage de réglage (26), si bien que celui-ci communique avec l'atmosphère environnante.au moyen d'un canal de trop plein (28), du deuxième alésage de réglage (27) et d'un alésage de décharge (30)
  4. Procédé selon la revendication 1, caractérisé en ce que la course (9) est déterminée de telle façon que quand le moteur fonctionne régulièrement il y ait un jeu (9a) entre la partie interne du poussoir (8) et la bague de butée (8a) . quand la course additionnelle est maximale, course qui est déclenchée par l'unité de pompe hydraulique de la source de pression (11).
EP92100960A 1991-01-29 1992-01-22 Procédé pour actionner un poussoir de soupape d'échappement d'un moteur en mode frein moteur Expired - Lifetime EP0497194B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4102537 1991-01-29
DE4102537A DE4102537A1 (de) 1991-01-29 1991-01-29 Auslass-ventilstoessel fuer eine brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP0497194A1 EP0497194A1 (fr) 1992-08-05
EP0497194B1 true EP0497194B1 (fr) 1995-04-05

Family

ID=6423904

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92100960A Expired - Lifetime EP0497194B1 (fr) 1991-01-29 1992-01-22 Procédé pour actionner un poussoir de soupape d'échappement d'un moteur en mode frein moteur

Country Status (5)

Country Link
US (1) US5161500A (fr)
EP (1) EP0497194B1 (fr)
JP (1) JPH04311615A (fr)
DE (2) DE4102537A1 (fr)
ZA (1) ZA92569B (fr)

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US5253621A (en) * 1992-08-14 1993-10-19 Group Lotus Plc Valve control means
DE4209775A1 (de) * 1992-03-26 1993-09-30 Man Nutzfahrzeuge Ag Vorrichtung zur Steuerung eines Auslaßventils im Motor-Bremsbetrieb
US5233951A (en) * 1992-09-25 1993-08-10 Hausknecht Louis A Flow restriction controlled variable engine valve system
US5327858A (en) * 1992-09-25 1994-07-12 Hausknecht Louis A Flow restriction controlled variable engine valve system
DE4238325C2 (de) * 1992-11-13 1999-09-09 Iav Motor Gmbh Schaltbarer Ventiltrieb mit Kipphebel und untenliegender Nockenwelle für Gaswechselventile von Verbrennungsmotoren
DE4334006C2 (de) * 1993-10-06 1996-10-10 Man Nutzfahrzeuge Ag Vorrichtung zur Erhöhung der Motorbremsleistung einer Brennkraftmaschine
US5372114A (en) * 1993-10-29 1994-12-13 Cummins Engine Company, Inc. Dampened pressure regulating and load cell tappet
DE9319435U1 (de) * 1993-12-17 1994-02-10 INA Wälzlager Schaeffler KG, 91074 Herzogenaurach Schaltbares Abstützelement
US5647318A (en) 1994-07-29 1997-07-15 Caterpillar Inc. Engine compression braking apparatus and method
US5540201A (en) 1994-07-29 1996-07-30 Caterpillar Inc. Engine compression braking apparatus and method
US5526784A (en) 1994-08-04 1996-06-18 Caterpillar Inc. Simultaneous exhaust valve opening braking system
DE4443137A1 (de) * 1994-12-03 1996-06-05 Bosch Gmbh Robert Verfahren zur Ermittlung der Federkraft einer Schließfeder beim Öffnen eines Ventiles, insbesondere eines Brennstoffeinspritzventiles, und Vorrichtung zur Durchführung des Verfahrens
DE19515434A1 (de) * 1995-04-27 1996-10-31 Schaeffler Waelzlager Kg Hydraulische Spielausgleichsvorrichtung
WO1999039092A1 (fr) * 1998-02-02 1999-08-05 Diesel Engine Retarders, Inc. Piston asservi auto-limitateur a rattrapage de jeu pour ralentisseur sur moteur a commande de decompression
US6085721A (en) * 1998-04-03 2000-07-11 Diesel Engine Retarders, Inc. Bar engine brake
WO2000011336A1 (fr) 1998-08-19 2000-03-02 Diesel Engine Retarders, Inc. Piston a course limitee, a securite integree, a commande hydraulique
US5964193A (en) * 1998-08-20 1999-10-12 Ford Global Technologies, Inc. Synchronous hydraulic lash adjuster
KR100510751B1 (ko) * 2003-07-29 2005-08-26 김용구 유압잭과 에어부스터로 구성된 에어작기
DE102004053202A1 (de) 2004-11-04 2006-06-01 Schaeffler Kg Ventiltrieb einer Brennkraftmaschine
DE102004053203A1 (de) 2004-11-04 2006-06-01 Schaeffler Kg Variabler Ventiltrieb einer Brennkraftmaschine
DE102007014248A1 (de) * 2007-03-24 2008-09-25 Schaeffler Kg Hubkolbenbrennkraftmaschine mit Motorbremseinrichtung
DE102010018208A1 (de) * 2010-04-26 2011-10-27 Schaeffler Technologies Gmbh & Co. Kg Hydraulisches Ventilspiel-Ausgleichselement für Hubkolbenbrennkraftmaschinen
CN109296788B (zh) * 2018-11-17 2021-12-21 徐州启峰智能科技有限公司 排气装置

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Also Published As

Publication number Publication date
DE59201799D1 (de) 1995-05-11
EP0497194A1 (fr) 1992-08-05
US5161500A (en) 1992-11-10
ZA92569B (en) 1992-10-28
DE4102537A1 (de) 1992-07-30
JPH04311615A (ja) 1992-11-04

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