[go: up one dir, main page]

EP0560812B1 - Installation pour l'actionnement simultane de deux soupapes de cylindre d'un moteur a combustion interne - Google Patents

Installation pour l'actionnement simultane de deux soupapes de cylindre d'un moteur a combustion interne Download PDF

Info

Publication number
EP0560812B1
EP0560812B1 EP91920515A EP91920515A EP0560812B1 EP 0560812 B1 EP0560812 B1 EP 0560812B1 EP 91920515 A EP91920515 A EP 91920515A EP 91920515 A EP91920515 A EP 91920515A EP 0560812 B1 EP0560812 B1 EP 0560812B1
Authority
EP
European Patent Office
Prior art keywords
bridge
cylinder head
end regions
gas exchange
exchange valves
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
EP91920515A
Other languages
German (de)
English (en)
Other versions
EP0560812A1 (fr
Inventor
Walter Speil
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.)
INA Waelzlager Schaeffler OHG
Original Assignee
INA Waelzlager Schaeffler OHG
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 Waelzlager Schaeffler OHG filed Critical INA Waelzlager Schaeffler OHG
Publication of EP0560812A1 publication Critical patent/EP0560812A1/fr
Application granted granted Critical
Publication of EP0560812B1 publication Critical patent/EP0560812B1/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
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • 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
    • F01L2305/00—Valve arrangements comprising rollers
    • F01L2305/02—Mounting of rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
    • F02F1/4214—Shape or arrangement of intake or exhaust channels in cylinder heads specially adapted for four or more valves per cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F2001/244—Arrangement of valve stems in cylinder heads
    • F02F2001/247—Arrangement of valve stems in cylinder heads the valve stems being orientated in parallel with the cylinder axis

Definitions

  • the invention relates to a device for the simultaneous actuation of two gas exchange valves of an internal combustion engine, consisting of a bar-shaped bridge which is guided over at least one column and has end play compensation elements which are in contact with valve stem ends of the gas exchange valves, the bridge over the column in the cylinder head Internal combustion engine is guided parallel to the axes of the gas exchange valves and has a rotatably mounted roller in the middle between the two play compensation elements, against which a control cam runs directly.
  • Such a device is previously known from FR-A-484 035.
  • This generic device also consists of a bar-shaped bridge for the simultaneous actuation of two gas exchange valves.
  • a roller which projects in the direction of the camshaft and against which a control cam runs.
  • the bridge is guided parallel to the longitudinal axis of the gas exchange valves with a telescopic guide, which extends in a direction facing away from the control cam and is hollow-cylindrical.
  • the valve stem ends are provided with a thread for valve clearance adjustment, but only between the roller and the base circle of the control cam. This thread is provided in the bridge in the area of the end jaws. For the purpose of adjusting the valve clearance, these clamping jaws have to be released in a complex manner while the internal combustion engine is at a standstill and the valve stem has to be turned relative to the bridge.
  • a disadvantage of this solution is that, on the one hand, no automatic valve clearance compensation is realized and, on the other hand, the cylinder head for telescoping the bridge is relatively complicated. Furthermore, due to the role of the bridge and the hub-like approach, a relatively large amount of installation space is required.
  • a rocker arm actuates two gas exchange valves simultaneously via a bridge.
  • a spherical end piece of the rocker arm sits in a dome-shaped receptacle arranged centrally in the bridge.
  • Hydraulically acting means for adjusting the valve clearance are provided in the end regions of the bridge.
  • such a valve train via rocker arms proves to be unfavorable in terms of the number of parts and rigidity.
  • a relatively large amount of installation space is again required.
  • There is also an additional screw for adjusting the rocker arm with respect to the bridge It is also disadvantageous that complex measures for supplying oil to the hydraulically acting play compensation elements via a longitudinal bore in the rocker arm and the above-mentioned adjusting screw are required.
  • the invention is therefore based on the object of providing a device for the simultaneous actuation of two gas exchange valves, in which the disadvantages shown are eliminated and in particular the valve clearance is compensated for automatically and with simple means, taking up little space.
  • this object is achieved according to the characterizing part of claim 1 in that a valve clearance occurring between the bridge and the valve stem ends of the gas exchange valves is compensated for by automatically hydraulically acting clearance compensation elements, with a bore opening in its lower end in an oil channel of the cylinder head in at least one column is provided and the bore with at least one transverse bore for the oil supply to the Game compensation elements is provided. Because of this design, there is no mechanical adjustment of the valve clearance during the entire operating time of the internal combustion engine.
  • the oil supply described here can be implemented with simple and inexpensive means on cylinder heads that have already been implemented, the columns simultaneously allowing the bridge to be guided exactly parallel to the axes of the gas exchange valves.
  • the bridge is advantageously formed from a lightweight material such as aluminum, plastic or fiber-reinforced plastic, but can also consist of solid steel or a composite of pressed sheet metal parts.
  • roller is arranged so that it does not project beyond the outer contour of the bridge in the direction of the control cam.
  • the overall height of the internal combustion engine is influenced favorably by this measure.
  • At least one of the columns has a circular cross section and at least one of the columns has a flattened area to prevent rotation. It is inexpensive and technically simple to use such material as rod material.
  • the bridge is integrally connected to at least one of the columns and engages in bores of the cylinder head.
  • groove-shaped recesses are provided in the bridge for receiving the end regions of the bolt used to support the roller.
  • This training can be easily implemented in terms of production technology.
  • the bolt can, as stated in claim 6, also secure against rotation by a Experience caulking in the bridge.
  • This variant proves to be inexpensive in terms of material and assembly.
  • the manufacturing expense for the caulking mentioned above is eliminated.
  • Claim 8 provides an attachment of the end regions of the bolt in bearing elements inserted separately into the bridge. Here it is possible to first connect the bearing element to the end areas and then insert it together into the bridge.
  • the claim 9 describes the leadership of the bridge directly in a recess in the cylinder head. If this is now designed so that it surrounds the bridge at least in a partial area of its outer surface and has a complementary shape to it, the separate columns for guiding the bridge can be dispensed with.
  • a device in longitudinal section, in which two gas exchange valves 2 arranged side by side, which are slidably mounted in valve guides 3 in a conventional manner, are held in a closed position by valve springs 4 in a cylinder head 1.
  • These two gas exchange valves 2 are actuated simultaneously in that, for example, hydraulic lash adjusters 5 rest against their valve stem ends, which are arranged so as to be longitudinally displaceable in opposite ends of a bar-shaped bridge 6.
  • the right game compensation element is shown in section. Since the internal structure of these known play compensation elements is not important for the invention, a detailed description is unnecessary.
  • a roller 8 is rotatably mounted on a bolt 7 with the interposition of cylindrical rolling elements 9, against which a control cam 10 of a camshaft 11 runs, which in turn is mounted in a known manner on the cylinder head.
  • the hydraulic play compensation elements will compensate for any play.
  • the bridge 6 will be moved down evenly and at the same time open the two gas exchange valves 2 by the same amount in each case. The prerequisite for this is that the bridge 6 is guided exactly parallel to the axes of the gas exchange valves 2.
  • the bridge 6 is trough-shaped in its outer surface 11 a surrounding the roller 8 and facing the control cam 10.
  • This design is provided as an oil reservoir for better lubrication of the roller 8 with the bolt 7 and the rolling elements 9.
  • the bolt 7 is fastened with its two axial end regions 11 b in a receptacle 11 c of the bridge 6. Further embodiments of the attachment can be found in the following description of the figures.
  • This receptacle 11 c can also consist of separately caulked and unspecified holding segments.
  • FIGS. 7 to 9 show some possibilities for mounting the bolt 7 for the roller 8.
  • the guidance of the bridge 6 can be seen from FIGS. 2 and 3 . It is carried out using two pillars.
  • the lower end of the column 12, which is designed as a hollow column closed on one side, is fastened in the cylinder head 1. It engages in a continuous longitudinal bore 13 of the bridge 6.
  • These two pillars 12 and 15 ensure perfect parallel guidance of the bridge 6. It has proven to be advantageous for fastening the columns 12 and 15 to an adjacent part by fastening them there by pressing them in or by means of a screw thread.
  • Another variant provides for the columns 12 and 15 to be fastened in the bridge 6 and to be guided in bores 15 a of the cylinder head 1.
  • the hollow column 12 also serves to supply oil from the engine oil circuit to the hydraulic lash adjusters 5.
  • an oil channel 16 through which engine oil is supplied, opens into its lower end. The oil rises in the bore 20 of the column 12 and reaches the two hydraulic play compensation elements 5 via cross bores 17 and distributor bores 18 in the bridge 6.
  • FIGS. 4 and 5 show an embodiment in which two bridges 6 working side by side are guided in the same way as in the previous figures. However, only a single column 15 is required, which can be used to guide both bridges 6. Otherwise, the type of guidance is completely the same as that shown in FIGS. 2 and 3, so that a separate description of this is not necessary.
  • the arrangement of the hydraulic lash adjuster elements and thus also the gas exchange valves with respect to the arrangement of the camshaft is different in this case from that previously shown. While in the embodiment according to FIGS. 1 to 3 an imaginary connecting line between the two jointly operated gas exchange valves 2 runs parallel to the camshaft 11, this imaginary line runs in the embodiment according to FIGS. 4 and 5 at right angles to the axis of the camshaft 11.
  • Such an arrangement has the advantage that the intake and exhaust valves of a cylinder of an internal combustion engine can be actuated by a common camshaft.
  • FIG. 6 shows a plan view of a bridge 6, which has mutually opposite prism surfaces 19 which are inclined at right angles, which interact with corresponding counter surfaces of the cylinder head 1 and thus ensure an exact guidance of the bridge 6.
  • FIG. 7 it is provided to receive the bolt 7 with its end regions 11 b in a groove-shaped recess 21 in the bridge 6. wherein the groove base 22 is semicircular.
  • the width of the groove-shaped recess is expediently chosen so that it corresponds approximately to the diameter of the bolt. However, it could also be slightly smaller in order to achieve a press connection.
  • FIG. 8 shows a recording of the end regions 11b of the bolt 7 according to FIG. 7, but here the bolt 7 is fixed in position and secured against twisting by caulking 23 in the bridge 6.
  • the end regions 11b of the bolt 7 can be mounted in a holding part which is inserted separately into the bridge 6.
  • This holding part is designed here as a semicircular bearing element 25, in which a bore 26 is provided for receiving the end region 11b.
  • the bearing element 25 is supported in a complementary pocket 27 of the bridge 6.
  • This bearing element 25 can also be box-shaped or of another geometry.
  • the bore 26 in the disk 25 is arranged eccentrically. This may be necessary in order to optimally integrate the roller 8 into the free space of the bridge 6.
  • FIGS. 12 and 13 show different embodiments of the bearing element 25.
  • This can advantageously be provided with a sleeve-shaped section 28.
  • This section 28 forms a sliding bearing for the bolt 7. If section 28 is worn over the life of the device according to the invention, this section can be easily replaced with a new section 28.
  • FIG. 14 shows an advantageous development of the bearing element (25) according to FIGS. 11 to 13. To fix the position axially, this can have a bent end region 29. This end region (29) forms a precise stop for the bearing element (25) during the assembly process.
  • the guide for the play compensation element 5 can at the same time be designed as a preferably pressed-in receptacle 30 for mounting the bolt 7.
  • the open and ring-shaped region 31 of the receiving bush 30 facing away from the control cam 10, which is not shown here, is provided with a flange 32, which is supported on the bridge 6, for fixing the position.
  • FIG. 17 shows a receiving bush 30 according to FIG. 16, but this is supported with its closed axial end region 33 on a closed section 34 of the bridge 6. Because of these possibilities of designing the receiving bush 30, which can be seen in FIGS. 15 to 17 , the longitudinal bore 13 for receiving the play compensation element 5 does not require any subsequent fine machining during production.
  • the receiving sleeve 30 can compensate to a certain extent for the surface roughness and manufacturing tolerances that occur.
  • FIGS. 18-20 show possibilities for forming the bridge 6 in the area of the roller 8 facing the control cam 10.
  • the solution described in FIG. 18 represents a simple solution.
  • the roller 8 in the area of the bridge 6 is open. If a support surface for the roller 8 is now required, for example during assembly, it is possible to make the bridge 6 semicircular in the region of the roller 8 or, as shown in FIG. 20, rectangular.

Landscapes

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

Abstract

Dans une installation pour l'actionnnement simultané de deux soupapes de cylindre (2) d'un moteur à combustion interne, constituée d'un pont (6) en forme de barre qui présente à ses extrémités des éléments hydrauliques de compensation du jeu (5) qui sont au contact des extrémités des tiges des soupapes de cylindre (2), le pont (6) étant guidé dans la tête de cylindre (1) du moteur à combustion interne parallèlement aux axes des soupapes de cylindre (2) et des éléments actionnant les soupapes étant appliqués au centre du pont entre les deux éléments de compensation du jeu (5), on obtient, par rapport aux modes de réalisation connus, une construction moins importante, et donc moins encombrante avec également un frottement réduit, par le fait qu'on dispose, au centre du pont (6), un galet (8) monté pivotant contre lequel s'appuie directement une came radiale (10).

Claims (9)

  1. Dispositif d'actionnement simultané de deux soupapes (2) de remplacement des gaz d'un moteur à combustion interne, comprenant un pont (6) en forme de poutre guidé par au moins une colonne (12 ou 15) qui, dans ses régions terminales, comprend des éléments de compensation de jeu (5) qui sont en contact avec des extrémités des tiges des soupapes (2) de remplacement des gaz, le pont (6) étant guidé par au moins l'une (12 ou 15) des colonnes dans la tête de cylindre (1) du moteur à combustion interne parallèlement aux axes des soupapes (2) de remplacement des gaz, ledit pont (6) comprenant à son centre, entre les deux éléments de compensation de jeu (5), un galet (8) monté en rotation et contacté directement par une came de commande (10), caractérisé en ce qu'un jeu qui se produit entre le pont (6) et les extrémités des tiges des soupapes (2) de remplacement des gaz est compensé par des éléments hydrauliques de compensation de jeu (5) à action automatique, il étant prévu dans au moins l'une (12 ou 15) des colonnes, un alésage (20) dont l'extrémité inférieure débouche dans un conduit d'huile (16) de la tête de cylindre (1), cet alésage (20) comprenant, pour le transfert d'huile aux éléments de compensation de jeu (5), au moins un alésage transversal (17).
  2. Dispositif selon la revendication1 1, caractérisé en ce que le galet (8) est agenceé de manière à ne pas s'étendre au-delà du contour extérieur du pont (6) vers la came de commande (10).
  3. Dispositif selon la revendication 1, caractérisé en ce qu'au moins l'une des colonnes (12 ou 15) possède une section transversale circulaire, et en ce qu'au moins l'une des colonnes (12 ou 15) comprend un aplatissement (38) qui sert de dispositif anti-torsion.
  4. Dispositif selon la revendication 1, caractérisé en ce que le pont (6) est réalisé en une seule pièce avec au moins l'une des colonnes (12 ou 15) et s'engage dans des alésages (15a) de la tête de cylindre.
  5. Dispositif selon l'une des revendications précédentes, caractérisé en ce que le pont (6) comprend des évidements (21) en forme de rainures pour loger les régions terminales (11b) du goujon (7) qui sert au montage du galet (8).
  6. Dispositif selon la revendication 5, caractérisé en ce qu'une fixation de position et/ou une immobilisation en rotation des régions terminales (11b) du goujon (7) est réalisée par au moins un matage (23) dans le pont (6) dans la région de l'évidement (21).
  7. Dispositif selon la revendication 5, caractérisé en qu'une fixation de position et/ou une immobilisation en rotation des régions terminales (11b) du goujon (7) est réalisée par au moins une pièce (24) qui a une forme complémentaire à l'évidement (21) et qui ferme celui-ci.
  8. Dispositif selon l'une des revendications précédentes, caractérisé en ce que les régions terminales (11b) du goujon (7) sont montées dans des éléments de montage (25) séparés qui sont fixés dans le pont (6).
  9. Dispositif selon la revendication 1, caractérisé en ce que le pont (6) comprend des surfaces de prisme (19) qui sont inclinées, l'une par rapport à l'autre, et en ce que chaque surface de prisme (19) coopère avec une contre-surface (19a) correspondante de la tête de cylindre.
EP91920515A 1990-12-08 1991-11-27 Installation pour l'actionnement simultane de deux soupapes de cylindre d'un moteur a combustion interne Expired - Lifetime EP0560812B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4039256 1990-12-08
DE4039256A DE4039256C2 (de) 1990-12-08 1990-12-08 Einrichtung zur gleichzeitigen Betätigung zweier Gaswechselventile einer Brennkraftmaschine
PCT/EP1991/002245 WO1992010650A1 (fr) 1990-12-08 1991-11-27 Installation pour l'actionnement simultane de deux soupapes de cylindre d'un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP0560812A1 EP0560812A1 (fr) 1993-09-22
EP0560812B1 true EP0560812B1 (fr) 1995-05-10

Family

ID=6419907

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91920515A Expired - Lifetime EP0560812B1 (fr) 1990-12-08 1991-11-27 Installation pour l'actionnement simultane de deux soupapes de cylindre d'un moteur a combustion interne

Country Status (6)

Country Link
US (1) US5261361A (fr)
EP (1) EP0560812B1 (fr)
JP (1) JP3323196B2 (fr)
BR (1) BR9107154A (fr)
DE (2) DE4039256C2 (fr)
WO (1) WO1992010650A1 (fr)

Families Citing this family (41)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4226760A1 (de) * 1992-08-13 1994-02-17 Opel Adam Ag Ventiltrieb für zumindest zwei gleichzeitig betätigbare Hubventile
DE4228796A1 (de) * 1992-08-29 1994-03-03 Porsche Ag Ventilantriebsanordnung für eine Brennkraftmaschine
DE4230227A1 (de) * 1992-09-10 1994-03-17 Porsche Ag Ventiltrieb für Brennkraftmaschinen
US5361733A (en) * 1993-01-28 1994-11-08 General Motors Corporation Compact valve lifters
DE4309602C2 (de) * 1993-03-24 1997-01-09 Bayerische Motoren Werke Ag Ventilstößel für zumindest zwei Brennkraftmaschinen-Hubventile
DE4338845C2 (de) * 1993-11-13 1998-03-26 Schaeffler Waelzlager Kg Vorrichtung zum gleichzeitigen Betätigen zweier Gaswechselventile
GB9401248D0 (en) * 1994-01-24 1994-03-23 Lotus Car Cam mechanisms
DE4410122C2 (de) * 1994-03-24 2003-05-08 Ina Schaeffler Kg Verbindung einer Führungsschiene einer Ventilbetätigungseinrichtung mit einem Nockenwellenlager
DE4410123C2 (de) * 1994-03-24 2003-02-20 Ina Schaeffler Kg Ölversorgung bei einer Ventilbetätigungseinrichtung
DE9405442U1 (de) * 1994-03-31 1995-08-03 FEV Motorentechnik GmbH & Co. KG, 52078 Aachen 4-Ventil-Kolbenbrennkraftmaschine
DE9406190U1 (de) * 1994-04-14 1994-06-09 INA Wälzlager Schaeffler KG, 91074 Herzogenaurach Vorrichtung zur gleichzeitigen Betätigung von zumindest zwei Gaswechselventilen
DE4415270A1 (de) * 1994-04-30 1995-11-02 Opel Adam Ag Einrichtung zur gleichzeitigen Betätigung zweier Gaswechselventile einer Brennkraftmaschine
DE9411680U1 (de) * 1994-07-19 1994-09-15 INA Wälzlager Schaeffler KG, 91074 Herzogenaurach Einrichtung zur gleichzeitigen Betätigung von zumindest zwei Gaswechselventilen
DE19519399A1 (de) * 1995-05-26 1996-11-28 Schaeffler Waelzlager Kg Ventiltrieb einer Brennkraftmaschine
US5606939A (en) * 1995-10-30 1997-03-04 General Motors Corporation Valve actuation assembly
US5921209A (en) * 1997-08-29 1999-07-13 Chrysler Corporation Roller arrangement for valve train mechanism
DE19749079B4 (de) * 1997-11-06 2007-12-20 Schaeffler Kg Nockenfolger eines Ventiltriebs einer Brennkraftmaschine
DE19803246A1 (de) * 1998-01-28 1999-08-05 Meta Motoren Energietech Vorrichtung zum Betätigen wenigstens eines Ladungswechselventils einer Brennkraftmaschine
US5931133A (en) * 1998-05-18 1999-08-03 General Motors Corporation Roller cam follower bearing shaft retention
US7263956B2 (en) * 1999-07-01 2007-09-04 Delphi Technologies, Inc. Valve lifter assembly for selectively deactivating a cylinder
DE19958314A1 (de) * 1999-12-03 2001-06-07 Mahle Ventiltrieb Gmbh Rollenstößel
DE10146129A1 (de) 2001-09-19 2003-04-03 Ina Schaeffler Kg Schaltelement für einen Ventiltrieb einer Brennkraftmaschine
ATE300665T1 (de) 2002-02-06 2005-08-15 Ina Schaeffler Kg Schaltelement für einen ventiltrieb einer brennkraftmaschine
US6871622B2 (en) 2002-10-18 2005-03-29 Maclean-Fogg Company Leakdown plunger
US7028654B2 (en) 2002-10-18 2006-04-18 The Maclean-Fogg Company Metering socket
US7191745B2 (en) 2002-10-18 2007-03-20 Maclean-Fogg Company Valve operating assembly
US7273026B2 (en) 2002-10-18 2007-09-25 Maclean-Fogg Company Roller follower body
US7128034B2 (en) 2002-10-18 2006-10-31 Maclean-Fogg Company Valve lifter body
JP2008115818A (ja) * 2006-11-07 2008-05-22 Otics Corp ロッカアーム
US8161929B2 (en) 2007-11-21 2012-04-24 Schaeffler Kg Switchable tappet
US8196556B2 (en) * 2009-09-17 2012-06-12 Delphi Technologies, Inc. Apparatus and method for setting mechanical lash in a valve-deactivating hydraulic lash adjuster
DE102012219506A1 (de) * 2012-10-02 2014-04-03 Schaeffler Technologies Gmbh & Co. Kg Hebelartiger Nockenfolger
AU2014295818B2 (en) * 2013-07-26 2018-08-23 Ibos Innovations Pty Ltd Piston machine
CN104791036B (zh) * 2015-03-27 2017-04-05 安徽江淮汽车集团股份有限公司 一种发动机配气机构
WO2020030299A1 (fr) * 2018-08-08 2020-02-13 Eaton Intelligent Power Limited Système hybride d'actionnement variable de soupapes
US11053819B2 (en) 2018-11-06 2021-07-06 Jacobs Vehicle Systems, Inc. Valve bridge systems comprising valve bridge guide
EP3877631B1 (fr) * 2018-11-06 2025-04-02 Jacobs Vehicle Systems, Inc. Systèmes de pont de soupapes comprenant un guide de pont de soupapes
US11319842B2 (en) * 2018-11-06 2022-05-03 Jacobs Vehicle Systems, Inc. Valve bridge comprising concave chambers
US11220933B2 (en) 2020-05-04 2022-01-11 Caterpillar Inc. Valve lifter anti-rotation device having cantilever bridge
US11236642B2 (en) 2020-05-04 2022-02-01 Caterpillar Inc. Valve lifter anti-rotation device and valve lifter assembly in valve actuation system
CN114704391B (zh) * 2022-05-06 2023-03-21 潍柴动力股份有限公司 一种发动机停缸控制装置及控制方法

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR484035A (fr) * 1916-03-03 1917-08-28 Des Anciens Etablissements Panhard Et Levassor Commande de soupapes
FR495639A (fr) * 1917-09-29 1919-10-14 Alessandro Anzani Commande de soupapes pour moteurs à explosions
FR555853A (fr) * 1922-09-11 1923-07-07 Aviation Louis Breguet Sa Commande de distribution pour moteur à soupapes
GB465540A (en) * 1936-01-31 1937-05-10 Fairey Aviat Co Ltd Improvements in or relating to valve mechanism for internal combustion engines
US2380051A (en) * 1943-04-22 1945-07-10 Gen Motors Corp Hydraulic valve adjusting means
US4677723A (en) * 1976-09-08 1987-07-07 Precision Screw Machine Company Valve bridge construction method
US4231267A (en) * 1978-11-01 1980-11-04 General Motors Corporation Roller hydraulic valve lifter
FR2553823B3 (fr) * 1983-10-25 1986-01-03 Renault Poussoir de soupape pour moteurs a combustion interne et arbres a cames en tete
DE3624108A1 (de) * 1986-07-17 1988-01-28 Opel Adam Ag Ventiltrieb fuer zumindest zwei gleichzeitig zu betaetigende ventile
IT1195192B (it) * 1986-10-07 1988-10-12 Fiat Auto Spa Comando valvole per motori ad alberi a camme in testa
US4924821A (en) * 1988-12-22 1990-05-15 General Motors Corporation Hydraulic lash adjuster and bridge assembly
DE59200059D1 (de) * 1991-03-12 1994-03-17 Avl Verbrennungskraft Messtech Zylinderkopf einer Brennkraftmaschine.
JP3119509U (ja) 2005-12-07 2006-03-02 荘平 高井 緩衝面付角底袋

Also Published As

Publication number Publication date
BR9107154A (pt) 1994-04-19
US5261361A (en) 1993-11-16
DE59105475D1 (de) 1995-06-14
JP3323196B2 (ja) 2002-09-09
DE4039256A1 (de) 1992-06-11
WO1992010650A1 (fr) 1992-06-25
JPH06503142A (ja) 1994-04-07
DE4039256C2 (de) 1996-05-09
EP0560812A1 (fr) 1993-09-22

Similar Documents

Publication Publication Date Title
EP0560812B1 (fr) Installation pour l'actionnement simultane de deux soupapes de cylindre d'un moteur a combustion interne
DE19509604A1 (de) Ventiltrieb einer Brennkraftmaschine
DE4302877C2 (de) Stößel
DE4220816A1 (de) Variable Ventilsteuerung mittels Änderung der Hebelverhältnisse bei Kipp- oder Schlepphebeln von Ventiltrieben
DE2654528A1 (de) Ventilbetaetigungshebel
DE102007010157A1 (de) Ventiltrieb einer Brennkraftmaschine mit dreistufigen Nockenprofilgruppen und axial beweglichen Kulissen- oder Eingriffselementen
DE4410122C2 (de) Verbindung einer Führungsschiene einer Ventilbetätigungseinrichtung mit einem Nockenwellenlager
DE69612087T2 (de) Kipphebelvorrichtung für brennkraftmaschine
DE4494320C1 (de) Schlepphebel für die Betätigung von Gaswechselventilen
EP0907008B1 (fr) Culasse avec commande de soupape pour moteur à combustion interne
WO1996002739A1 (fr) Dispositif d'actionnement simultane d'au moins deux soupapes a deux voies pour gaz
DE9405694U1 (de) Schlepphebel für einen Ventiltrieb einer Brennkraftmaschine
WO1993005277A1 (fr) Poussoir hydraulique a galet
DE19701203A1 (de) Variable Ventilsteuerung für Brennkraftmaschinen
EP1205643A1 (fr) Dispositif d'actionnement de soupapes de moteur à combustion interne
EP0468202A1 (fr) Poussoir à galet avec compensateur de jeu hydraulique
DE10006015B4 (de) Variabler Ventiltrieb zur Laststeuerung einer fremdgezündeten Brennkraftmaschine
DE10235400A1 (de) Zylinderkopf für eine Brennkraftmaschine mit einem hubvariablen Ventiltrieb
EP1590554B1 (fr) Entrainement mecanique de soupape entierement variable destine a moteur a combustion interne a piston alternatif a equilibre de jeu de soupapes reglable
DE19720900B4 (de) Brennkraftmaschine mit einem Ventiltrieb für Hubventile
DE9316125U1 (de) Einrichtung zur gleichzeitigen Betätigung zweier Gaswechselventile einer Brennkraftmaschine
DE4309602C2 (de) Ventilstößel für zumindest zwei Brennkraftmaschinen-Hubventile
DE29916363U1 (de) Ventiltrieb, insbesondere für Brennkraftmaschinen
DE4433278B4 (de) Schmierung des Ventiltriebes
DE10206465A1 (de) Steuereinrichtung für Gaswechselventile eines Verbrennungsmotors

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

17P Request for examination filed

Effective date: 19930408

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 19941018

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

ITF It: translation for a ep patent filed
AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19950516

REF Corresponds to:

Ref document number: 59105475

Country of ref document: DE

Date of ref document: 19950614

ET Fr: translation filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19951018

Year of fee payment: 5

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

Ref country code: FR

Payment date: 19951107

Year of fee payment: 5

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19961127

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19961127

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

Ref country code: FR

Effective date: 19970731

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

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

Ref country code: DE

Payment date: 20021127

Year of fee payment: 12

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: 20040602

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;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20051127