EP2009255B1 - Valve d'étranglement pour un moteur à combustion interne doté d'une commande de soupape hydroélectrique - Google Patents

Valve d'étranglement pour un moteur à combustion interne doté d'une commande de soupape hydroélectrique Download PDF

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Publication number
EP2009255B1
EP2009255B1 EP08156892A EP08156892A EP2009255B1 EP 2009255 B1 EP2009255 B1 EP 2009255B1 EP 08156892 A EP08156892 A EP 08156892A EP 08156892 A EP08156892 A EP 08156892A EP 2009255 B1 EP2009255 B1 EP 2009255B1
Authority
EP
European Patent Office
Prior art keywords
valve
chamber
stop surface
section
cross
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.)
Not-in-force
Application number
EP08156892A
Other languages
German (de)
English (en)
Other versions
EP2009255A1 (fr
Inventor
Calin Petru Itoafa
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co 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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP2009255A1 publication Critical patent/EP2009255A1/fr
Application granted granted Critical
Publication of EP2009255B1 publication Critical patent/EP2009255B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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 an electrohydraulic valve control system for the variable actuation of a gas exchange valve spring-loaded in the closing direction of an internal combustion engine, comprising a gas exchange valve far drive side with a hydraulic first chamber and a gas exchange valve close output side with a hydraulic second chamber which communicates hydraulically with the first chamber via a main flow path and a Maustrompfad, and having a fixedly inserted in the secondary flow path throttle valve with a hubbeweglich between a stationary extending from the first chamber first stop surface and a second chamber extending stationary second stop surface arranged valve body which releases a limited from the first stop surface inflow cross section when contacting the second stop surface and a limited by the second stop surface flow cross-section only partially obscured, so that the Hydraulikmi largely flow unthrottled into the second chamber can, and closes at investment on the first stop surface of the limited of this inflow cross section to a throttle cross-section.
  • While hydraulic valve brakes are known in various structural configurations in the prior art, serving as a hydraulic valve brake throttle valve of the type mentioned is considered from the considered generic US 5,577,468 out.
  • the throttle valve used there in the secondary flow path is the throttled emptying of the slave chamber in the final closing phase of the gas exchange valve by then both the main flow and the inflow cross section in the secondary flow path are closed except for a remaining throttle cross-section through which the hydraulic fluid can escape from the slave chamber.
  • the throttle valve allows in the initial opening phase of the gas exchange valve in favor of its high opening acceleration to a low-throttle and thus fast filling of the slave chamber by then the inflow cross-section is already open before opening the main flow path.
  • the central component of the proposed in the cited document throttle valve is designed as a plate valve body, wherein the throttle cross-section is formed either by a central bore through the plate or by a local bead on the surface thereof.
  • the indentation provided on the plate surface as an alternative to the bore has the disadvantage that the plate is always in the correct orientation, i. must be mounted with the indentation opposite to the encoder chamber-side stop surface, since the opposite surface of the plate with significantly larger indentations, which form the flow cross section to the slave chamber, is provided. Consequently, the hydraulic valve brake function would not be given in a faulty mounting of the plate also.
  • the throttle cross-section should be formed by one or more bead-like recesses in the encoder chamber side stop surface.
  • the invention is based on the idea, the throttle cross section not in the valve body itself, but on the encoder chamber side stop surface, i. on the first abutment surface on the part of the first chamber in the form of the bead-like, i. to arrange recessed recesses.
  • a significant advantage over the well known in the cited prior art bore in the plate is the significantly lower sensitivity of the moldings with regard to clogging or clogging with dirt particles, since the indentations also in contact with the valve body at the second chamber side chamber, i. when the inflow cross section is released through the then into the receiving chamber, i. in the second chamber entering hydraulic fluid are acted upon. Consequently, dirt particles that may accumulate during the final closing phase of the gas exchange valve in the recesses, be flushed out of the recesses during the subsequent opening phase of the gas exchange valve.
  • the throttle cross section formed in the geberhunt Schoen stop surface has over the known plate with throttle cross section on the surface especially the advantage that the valve body formed symmetrically and in the case of a plate with identical surfaces and consequently with arbitrary Orientation can be mounted.
  • the geometry of the valve body is freely selectable within wide limits, so that instead of the known plate, for example, a ball or a conical valve body can be used.
  • the indentations have a substantially circular segment-shaped cross section with a depth of 0.03 mm to 0.09 mm and preferably from 0.05 mm to 0.07 mm.
  • this design of the indentations is particularly advantageous if the indentations are made without cutting by embossing.
  • the throttle valve should be formed as the valve body and a valve housing with the stop surfaces extending therein comprehensive unit.
  • the valve housing is formed in two parts with a valve carrier and a socket, wherein the socket is inserted in a receiving chamber-side hollow cylindrical recess of the valve carrier.
  • the encoder chamber-side abutment surface are formed by a bottom of the recess and the receiving chamber side abutment surface by a bottom facing annular end face of the socket.
  • the bush for axial positional fixation in the valve housing should be provided with a collar which bears against an end face of the valve carrier facing the slave chamber.
  • a sufficient flow cross-section for the inflowing into the receiving chamber hydraulic fluid can be produced particularly easily produced, if the valve body is formed as a flat plate and only partially covered when applied to the annular end face of the bushing limited by the annular end face flow cross-section.
  • the plate as a simple stamped part and on the other hand, the annular end face of the socket be made completely flat, so that despite the sealing effect in the contact region of these two parts required for a fast filling of the slave chamber flow cross section remains.
  • a preferred form of the plate substantially corresponds to a rectangle with opposite thereto adjacent circle segments.
  • FIG. 1 is an essential for the understanding of the invention section of an electro-hydraulic valve control 1 for the variable actuation of a spring-loaded in the closing direction gas exchange valve 2 disclosed.
  • the slave housing 5 serves for the longitudinally movable mounting of an elongate working piston 6 of an otherwise known hydraulic valve clearance compensation device 7, which contacts the shaft end of the gas exchange valve 2.
  • valve clearance compensation device 7 via a connected to the lubricant circuit of the engine supply bore 8 and a tap hole 9 in the actuator housing 3, an outer annular groove 10 and with this - not visible here - connected inner annular groove 11 in the slave housing 5 and a transverse bore 12 in the working piston 6.
  • a co-moving with the working piston 6 slave piston 13 is limited with its gas exchange valve 2 end face 14 a hydraulic slave chamber 15 whose volume in the closed position of the gas exchange valve 2 shown here only the interior of a - here not shown in section - throttle valve 16 corresponds.
  • the known to be located on the gas exchange valve near output side of the valve control 1 slave chamber 15 is connected via a main flow path 17 in the form of holes 18 in the slave housing 5 and a Maustrompfad 19 in the form of the throttle valve 16 and a recess 4 for receiving bore 4 in the actuator housing 3 to a on the Gas monventilfernen drive side of the valve control 1 extending donor chamber 21 connected.
  • This is visible here only in the form of an inlet bore 22 in the actuator housing 3 and an annular chamber 23 between the actuator housing 3 and the slave housing 5.
  • the throttle valve 16 is formed as a structural unit and comprises a two-part valve housing 24 with a valve carrier 25 and a bushing 26 which is inserted in a slave chamber side hollow cylindrical recess 27 of the valve carrier 25, and a valve body 28 formed here as a flat plate, in the flow direction of the hydraulic fluid between a receiving chamber-side stop surface 29 and a geberhunt principleen stop surface 30 is arranged to be movable.
  • the encoder chamber side abutment surface 30 are formed by a bottom 31 of the recess 27 and the receiving chamber side abutment surface 29 by a bottom 31 facing annular end face 32 of the bushing 26.
  • the sleeve 26 is provided with a collar 33 which rests against one of the slave chamber 15 facing end face 34 of the valve carrier 25.
  • the valve carrier 25 also has a radially outwardly directed collar 35, so that the throttle valve 16, as in FIG. 1 recognizable, between the gas exchange valve remote end face 36 of the slave housing 5 and a shoulder 37 of the receiving bore 4 can be clamped.
  • FIG. 2 illustrated abutment position of the plate 28, in which this abuts the receiving chamber-side abutment surface 29, a limited by the encoder chamber-side stop surface 30 inlet cross-section 38 is released.
  • the hydraulic fluid in this position of the plate 28 largely unthrottled to flow into the slave chamber 15 by the plate 28 only partially obscured by the annular end face 32 of the sleeve 26 flow cross-section 39.
  • the plate 28 has a shape corresponding to a rectangle with opposite thereto adjoining and flush with the annular end face 32 flush circle segments.
  • FIG. 3 illustrated bottom view of the valve carrier 25 is formed by the bottom 31 of the recess 27 formed geberhunt worne stop surface 30 with two diametrically opposite bead-like indentations 40.
  • FIG. 4 As can be seen, in the case of the voltage applied to the encoder chamber side abutment surface 30 plate 28 of the inflow cross section 38 is closed in the valve carrier 25 to a throttle cross section formed by the indentations 40. This state occurs at closing gas exchange valve 2, wherein the hydraulic means located in the slave chamber 15 is initially mainly displaced via the bores 18 in the slave housing 5 and then, when the holes 18 are closed by the slave piston 13, only by the indentations 40 in the Donor chamber 21 can escape with a corresponding delay of the gas exchange valve 2.

Landscapes

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

Claims (8)

  1. Commande de soupape électrohydraulique (1) pour l'actionnement variable d'une soupape d'échange de gaz (2) d'un moteur à combustion interne, sollicitée par une force de ressort dans une direction de fermeture, présentant un côté d'entraînement éloigné de la soupape d'échange de gaz avec une première chambre hydraulique (21) et un côté de sortie proche de la soupape d'échange de gaz avec une deuxième chambre hydraulique (15), qui communique par voie hydraulique par le biais d'un chemin de flux principal (17) et d'un chemin de flux secondaire (19) avec la première chambre (21), et présentant une soupape d'étranglement (16) insérée fixement dans le chemin de flux secondaire (19) avec un corps de soupape (28) disposé avec une course de déplacement entre une première surface de butée (30) s'étendant fixement du côté de la première chambre (21) et une deuxième surface de butée (29) s'étendant fixement du côté de la deuxième chambre (15), lequel, lors de l'application contre la deuxième surface de butée (29), libère une section transversale d'afflux (38) limitée par la première surface de butée (30) et ne recouvre que partiellement une section transversale de passage (39) limitée par la deuxième surface de butée (29), de sorte que l'agent hydraulique puisse affluer essentiellement sans étranglement dans la deuxième chambre (15), et lequel, lors de l'application contre la première surface de butée (30), ferme la section transversale d'afflux (38) limitée par celle-ci à l'exception d'une section transversale d'étranglement, caractérisée en ce que la section transversale d'étranglement est formée par une ou plusieurs formations en forme de moulure (40) dans la première surface de butée (30).
  2. Commande de soupape électrohydraulique (1) selon la revendication 1, caractérisée en ce que les formations (40) présentent une section transversale essentiellement en forme de segment de cercle avec une profondeur de 0,03 mm à 0,09 mm et de préférence de 0,05 mm à 0,07 mm.
  3. Commande de soupape électrohydraulique (1) selon la revendication 1, caractérisée en ce que la soupape d'étranglement (16) est réalisée sous forme d'unité constructive comprenant le corps de soupape (28) et un boîtier de soupape (24) avec les surfaces de butée (29, 30) s'étendant à l'intérieur.
  4. Commande de soupape électrohydraulique (1) selon la revendication 3, caractérisée en ce que les formations (40) sont fabriquées sans enlèvement de copeaux par gaufrage du boîtier de soupape (24).
  5. Commande de soupape électrohydraulique (1) selon la revendication 3, caractérisée par un boîtier de soupape en deux parties (24) avec un support de soupape (25) et une douille (26), qui est insérée dans un évidement cylindrique creux (27) du support de soupape (25) s'étendant du côté de la deuxième chambre (15), la première surface de butée (30) étant formée par un fond (31) de l'évidement (27) et la deuxième surface de butée (29) étant formée par une surface frontale annulaire (32) de la douille (26) tournée vers le fond (31).
  6. Commande de soupape électrohydraulique (1) selon la revendication 5, caractérisée en ce que la douille (26) est pourvue d'un épaulement (33) qui s'applique contre une surface frontale (34) du support de soupape (25) tournée vers la deuxième chambre (15).
  7. Commande de soupape électrohydraulique (1) selon la revendication 5, caractérisée en ce que le corps de soupape (28) est réalisé sous forme de plaque plane et lors de l'application contre la surface frontale annulaire (32) de la douille (26), ne recouvre que partiellement la section transversale de passage (39) limitée par la surface frontale annulaire (32).
  8. Commande de soupape électrohydraulique (1) selon la revendication 7, caractérisée en ce que la forme de la plaque (28) correspond essentiellement à un rectangle avec des segments de cercle s'y raccordant les uns en face des autres.
EP08156892A 2007-06-29 2008-05-26 Valve d'étranglement pour un moteur à combustion interne doté d'une commande de soupape hydroélectrique Not-in-force EP2009255B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007030215A DE102007030215A1 (de) 2007-06-29 2007-06-29 Drosselventil für eine Brennkraftmaschine mit elektrohydraulischer Ventilsteuerung

Publications (2)

Publication Number Publication Date
EP2009255A1 EP2009255A1 (fr) 2008-12-31
EP2009255B1 true EP2009255B1 (fr) 2010-09-15

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP08156892A Not-in-force EP2009255B1 (fr) 2007-06-29 2008-05-26 Valve d'étranglement pour un moteur à combustion interne doté d'une commande de soupape hydroélectrique

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Country Link
EP (1) EP2009255B1 (fr)
CN (1) CN201326424Y (fr)
DE (2) DE102007030215A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010048135A1 (de) 2010-10-11 2012-04-12 Schaeffler Technologies Gmbh & Co. Kg Aktuator eines elektrohydraulischen Gaswechselventiltriebs einer Brennkraftmaschine
DE102011004403A1 (de) 2011-02-18 2012-08-23 Schaeffler Technologies Gmbh & Co. Kg Hydraulischer Ventiltrieb einer Brennkraftmaschine
DE102014201910A1 (de) 2014-02-04 2015-08-06 Schaeffler Technologies AG & Co. KG Aktuator für einen elektrohydraulischen Gaswechselventiltrieb einer Brennkraftmaschine
DE102019104459B4 (de) * 2019-02-21 2023-01-05 Schaeffler Technologies AG & Co. KG Aktuator eines hydraulischen Ventiltriebs einer Brennkraftmaschine

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69122411T2 (de) 1991-11-29 1997-02-06 Caterpillar Inc Hydraulischer brennkraftmaschinenventilsitzdaempfer
KR20010032345A (ko) * 1997-11-21 2001-04-16 디이젤 엔진 리타더스, 인코포레이티드 한정된 로스트 모션 태핏에서 밸브 시팅 속도를 한정하는장치
WO2000012895A2 (fr) * 1998-08-26 2000-03-09 Diesel Engine Retarders, Inc. Dispositif de commande de la vitesse d'obturation des soupapes au moyen d'un orifice a diametre variable
US6769385B1 (en) * 2003-03-12 2004-08-03 Caterpillar Inc System for controlling engine valve seating velocity
US7318398B2 (en) * 2003-08-15 2008-01-15 Caterpillar Inc. Engine valve actuation system

Also Published As

Publication number Publication date
CN201326424Y (zh) 2009-10-14
DE502008001290D1 (de) 2010-10-28
DE102007030215A1 (de) 2009-01-08
EP2009255A1 (fr) 2008-12-31

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