WO2003102384A1 - Mecanisme de distribution variable, a actionnement hydraulique, pour moteur a combustion interne - Google Patents

Mecanisme de distribution variable, a actionnement hydraulique, pour moteur a combustion interne Download PDF

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Publication number
WO2003102384A1
WO2003102384A1 PCT/EP2003/005014 EP0305014W WO03102384A1 WO 2003102384 A1 WO2003102384 A1 WO 2003102384A1 EP 0305014 W EP0305014 W EP 0305014W WO 03102384 A1 WO03102384 A1 WO 03102384A1
Authority
WO
WIPO (PCT)
Prior art keywords
bore
piston
slave piston
compensation element
valve
Prior art date
Application number
PCT/EP2003/005014
Other languages
German (de)
English (en)
Inventor
Martin Rauch
Michael Haas
Original Assignee
Ina-Schaeffler Kg
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 Ina-Schaeffler Kg filed Critical Ina-Schaeffler Kg
Priority to AU2003232767A priority Critical patent/AU2003232767A1/en
Priority to EP03755929A priority patent/EP1509686B1/fr
Priority to DE50303590T priority patent/DE50303590D1/de
Publication of WO2003102384A1 publication Critical patent/WO2003102384A1/fr
Priority to US10/999,247 priority patent/US7080614B2/en

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
    • 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
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • 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
    • 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
    • F01L1/2411—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the valve stem and rocker arm
    • 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 hydraulically operated, preferably variable valve train of an internal combustion engine, with a housing built into a receptacle of a cylinder head, in the bore of which an axially movable slave piston runs, which delimits a pressure space for the hydraulic medium on one end face and a hydraulic one on its other end face
  • Backlash compensation element having a check valve, which backlash compensation element acts at least indirectly on a gas exchange valve on its side remote from the housing, the housing being cut by at least one path for hydraulic medium which is in front of a channel of the slave piston or backlash compensation element for forwarding the hydraulic medium to a storage space of the backlash compensation element communicates with the check valve.
  • valve train is evident from WO 89/02975, which is considered to be generic.
  • this is relatively complex. So the master and slave pistons have a common housing. This is accompanied by the fact that this valve train may be built relatively high or its variability in use is limited.
  • the hydraulic lash adjuster used is in permanent hydraulic medium contact with a supply line from the cylinder head. Because of this constant supply of hydraulic fluid, it can in the worst case happen that the play compensation element unnecessarily "pumps up" outside of cam base circle phases and thus undesirable stroke changes occur on the gas exchange valve.
  • the object of the invention is therefore to provide a valve train with a slave piston of the aforementioned type, in which the disadvantages cited are eliminated.
  • this object is achieved in that the housing installed in the cylinder head is manufactured as a separate component for forming only one slave unit, the channel being hydraulically connected to the path only outside a stroke phase of the slave piston.
  • a stop part can be installed on the face side in the slave piston, which is overlapped in sections by a housing of the play compensation element in the event of compensation. It is intended to form an outer jacket of the stop part as a sliding surface for a bore of a housing of the play compensation element and at the same time form an annular space / channel for hydraulic medium between the outer casing and the bore of the housing of the slave piston for supply to a storage space of the play compensation element.
  • this annular space communicates with a path for supplying the hydraulic medium through the housing only when the basic circuit is being passed through, ie outside a lifting phase of the slave piston. Possibly. the annular space can also be in fluid communication with the path immediately at the start of the stroke or before the end of the stroke.
  • the slave piston at the stroke end in the available base circle interval is sufficiently quick, i.e. Even at high speeds of the internal combustion engine, due to its absolute end position, this need not be changed.
  • the compression spring present in the play compensation element and at the same time an external spring can be used as the spring assembly, the latter on the one hand sitting on an axial extension of the pressure piston of the play compensation element extending in the valve direction and on the other hand acting against a facing end face of the slave piston.
  • the check valve of the play compensation element can, according to a further invention proposal, also in a bottom of the end bore of the Slave piston be applied, wherein the pressure piston between the bottom and its facing end face encloses the high pressure space of the play compensation element.
  • the path through the housing for supplying the hydraulic medium opens out radially on the inside into an annular groove.
  • the slave piston cannot be secured against rotation.
  • the annular groove can also be arranged on the outer jacket of the slave piston.
  • servo means Any type of servo means is conceivable and envisaged as hydraulic means for acting on the valve train.
  • engine oil is thought of, which is already present in the internal combustion engine circuit, but servo means such as brake fluid or the like are also conceivable.
  • the housing which disadvantageously guides the master and slave pistons at the same time, is arranged in the cylinder head via an interference fit or the like.
  • FIGS. 1 to 3 show a variable valve train of an internal combustion engine with views of slave units designed according to the invention.
  • a cylinder head 2 with a receptacle 1 is indicated in FIG. 3.
  • the housing 3 has a bore 4 in which a slave piston 5 is received.
  • the slave piston 5 delimits a pressure chamber 7 for hydraulic medium in the region of its one end face 6. On its other end face 8, it has a bore 16 into which a stop part 17 is installed. This protrudes from the bore 16.
  • An annular space 24 for hydraulic medium is formed between its outer casing 20 and the bore 4.
  • an edge region of a surface 18 of the stop part 17 has a recess 23 for the hydraulic medium for the direct supply thereof to a storage space 14 of a play compensation element 9.
  • Figure 1 can also be seen that within a bore 21 of the housing
  • a pressure piston 19 runs, which encloses the aforementioned storage space 14 and always abuts the surface 18 on the end face.
  • the pressure piston 19 engages over the outer jacket 20 of the stop part 17.
  • the slave piston 5 and the play compensation element 9 according to FIG. 1 are manufactured as completely separate components. However, this is not the case with the embodiment according to FIG. 2.
  • the slave piston 5 has a bore 25 extending from its other end face 8.
  • the pressure piston 19 of the play compensation element 9 runs in this bore 9.
  • a leakage gap for the hydraulic medium is formed between the bore 25 and an outer jacket of the pressure piston 19.
  • the pressure piston 19 (in one or more parts) is towered over by an extension piece 27 in the valve direction.
  • the latter has a radial extension 28 on the valve side, which here is integrally connected to the extension piece 27, on which a compression spring 29 is supported at one end.
  • the compression spring 29 acts at the other end against the end face 8 of the slave piston 5. This effectively enables the return movement of the slave piston 5 at the stroke end to its defined end position. Possibly. If the force of the compression spring 35 assigned to the play compensation element 9 is sufficient, such a separate compression spring 29 can be dispensed with.
  • the hydraulic medium is in turn supplied through at least one path 12 through the housing 3, which opens radially on the inside into the annular groove 33.
  • the path 12 communicates with the annular groove 33 with a channel 13 in the slave piston 5 which is designed as a radial passage the check valve 9a.
  • the slave piston 5 likewise has a bore 25 on its other end face 8.
  • the pressure piston 19 is installed in the bore 25.
  • the leakage gap 26 for the hydraulic medium is in turn formed between the bore 25 of the slave piston 5 and an outer jacket of the pressure piston 19.
  • the check valve 9a is arranged here at a base of the bore 25 is.
  • a supply line for the hydraulic medium up to immediately before the check valve 9a, which opens here in the valve direction, is in turn realized via at least one path 12 with a radially inner annular groove 33 extending radially through the housing 3.
  • the slave piston 5 For the transmission of the hydraulic medium from the annular groove 33, the slave piston 5 has a channel 13, which is produced on the outer surface of the slave piston 5, on the side of the path 12, as a longitudinal groove. A radial section branches off from the longitudinal groove, which in turn goes into an axial channel, which is designated here as “storage space 14”.
  • the pressure piston 19 is enclosed by a compression spring 32 which acts at one end against a radial extension 31 designed here as a locking ring and at the other end is supported on the other end face 8 of the slave piston 5.
  • the slave piston 5 is shown in its valve stroke position, which can be the maximum stroke.

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)

Abstract

Mécanisme de distribution de préférence variable, à actionnement hydraulique, pour un moteur à combustion interne, qui possède une unité réceptrice (15) conçue en tant qu'élément structural séparé par rapport à une unité émettrice. Selon la présente invention, l'unité réceptrice est pourvue d'un élément hydraulique (9) de rattrapage de jeu qui n'est relié à un passage (12) d'amenée de milieu hydraulique qu'en dehors d'une phase de levage d'un piston émetteur. On obtient ainsi d'une part un mécanisme de distribution de structure simple pourvu d'une unité réceptrice (15). D'autre part, l'action susmentionnée du milieu hydraulique empêche un </= POMPAGE >/= inutile de l'élément de rattrapage de jeu (9) pendant les phases de levage du piston récepteur (5).
PCT/EP2003/005014 2002-05-31 2003-05-14 Mecanisme de distribution variable, a actionnement hydraulique, pour moteur a combustion interne WO2003102384A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
AU2003232767A AU2003232767A1 (en) 2002-05-31 2003-05-14 Hydraulically actuated, variable valve drive of an internal combustion engine
EP03755929A EP1509686B1 (fr) 2002-05-31 2003-05-14 Mecanisme de distribution variable, a actionnement hydraulique, pour moteur a combustion interne
DE50303590T DE50303590D1 (de) 2002-05-31 2003-05-14 Hydraulisch betätigter, variabler ventiltrieb einer brennkraftmaschine
US10/999,247 US7080614B2 (en) 2002-05-31 2004-11-30 Hydraulically actuated, variable valve drive of an internal combustion engine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10224039A DE10224039A1 (de) 2002-05-31 2002-05-31 Hydraulisch betätigter, variabler Ventiltrieb einer Brennkraftmaschine
DE10224039.6 2002-05-31

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US10/999,247 Continuation US7080614B2 (en) 2002-05-31 2004-11-30 Hydraulically actuated, variable valve drive of an internal combustion engine

Publications (1)

Publication Number Publication Date
WO2003102384A1 true WO2003102384A1 (fr) 2003-12-11

Family

ID=29432458

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2003/005014 WO2003102384A1 (fr) 2002-05-31 2003-05-14 Mecanisme de distribution variable, a actionnement hydraulique, pour moteur a combustion interne

Country Status (4)

Country Link
EP (1) EP1509686B1 (fr)
AU (1) AU2003232767A1 (fr)
DE (2) DE10224039A1 (fr)
WO (1) WO2003102384A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT500679B8 (de) * 2004-06-16 2007-02-15 Ge Jenbacher Gmbh & Co Ohg Ventilantrieb
DE602004003936T2 (de) * 2004-09-14 2007-06-06 CRF Società Consortile per Azioni, Orbassano Brennkraftmaschine mit variabel angesteuerten Ventilen, welche jeweils mit einem hydraulischen Stößel außerhalb des jeweiligen Aktors versehen sind

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989002975A1 (fr) * 1987-10-02 1989-04-06 Siemens Aktiengesellschaft Poussoir de soupape de moteur hydraulique
EP0535275A1 (fr) * 1990-06-18 1993-04-07 FEULING ENGINEERING, Inc. Dispositif de variation de calage de soupape électrohydraulique
EP0803642A1 (fr) * 1996-04-24 1997-10-29 C.R.F. Società Consortile per Azioni Moteur à combustion interne avec soupapes à commande variable
WO1999010629A2 (fr) * 1997-08-28 1999-03-04 Diesel Engine Retarders, Inc. Dispositif d'actionnement d'une soupape de moteur avec commande de la vitesse d'obturation
US5954020A (en) * 1993-08-24 1999-09-21 Ina Walzlager Schaeffler Kg Cup-shaped tappet
EP1091097A1 (fr) * 1999-10-06 2001-04-11 C.R.F. Società Consortile per Azioni Ameliorations d'un dispositif de commande de soupape variable pour moteur à combustion interne
EP1245799A2 (fr) * 2001-03-23 2002-10-02 C.R.F. Società Consortile per Azioni Moteur à combustion interne à commande variable de soupapes et poussoir hydraulique auxiliaire

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4258672A (en) * 1978-10-20 1981-03-31 Hietikko Calvin N Variable lift camming apparatus and methods of constructing and utilizing same
DE4224988A1 (de) * 1991-08-02 1993-02-04 Elsbett L Hydrostatische ventilbetaetigung

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989002975A1 (fr) * 1987-10-02 1989-04-06 Siemens Aktiengesellschaft Poussoir de soupape de moteur hydraulique
EP0535275A1 (fr) * 1990-06-18 1993-04-07 FEULING ENGINEERING, Inc. Dispositif de variation de calage de soupape électrohydraulique
US5954020A (en) * 1993-08-24 1999-09-21 Ina Walzlager Schaeffler Kg Cup-shaped tappet
EP0803642A1 (fr) * 1996-04-24 1997-10-29 C.R.F. Società Consortile per Azioni Moteur à combustion interne avec soupapes à commande variable
WO1999010629A2 (fr) * 1997-08-28 1999-03-04 Diesel Engine Retarders, Inc. Dispositif d'actionnement d'une soupape de moteur avec commande de la vitesse d'obturation
EP1091097A1 (fr) * 1999-10-06 2001-04-11 C.R.F. Società Consortile per Azioni Ameliorations d'un dispositif de commande de soupape variable pour moteur à combustion interne
EP1245799A2 (fr) * 2001-03-23 2002-10-02 C.R.F. Società Consortile per Azioni Moteur à combustion interne à commande variable de soupapes et poussoir hydraulique auxiliaire

Also Published As

Publication number Publication date
AU2003232767A1 (en) 2003-12-19
EP1509686B1 (fr) 2006-05-31
DE50303590D1 (de) 2006-07-06
DE10224039A1 (de) 2003-12-11
EP1509686A1 (fr) 2005-03-02

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