EP0723627A1 - Mecanisme de distribution pour moteur a combustion interne multicylindre - Google Patents

Mecanisme de distribution pour moteur a combustion interne multicylindre

Info

Publication number
EP0723627A1
EP0723627A1 EP94928822A EP94928822A EP0723627A1 EP 0723627 A1 EP0723627 A1 EP 0723627A1 EP 94928822 A EP94928822 A EP 94928822A EP 94928822 A EP94928822 A EP 94928822A EP 0723627 A1 EP0723627 A1 EP 0723627A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
valve
rocker arms
valves
longitudinal channel
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.)
Granted
Application number
EP94928822A
Other languages
German (de)
English (en)
Other versions
EP0723627B1 (fr
Inventor
Michael Paul
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.)
Audi AG
Original Assignee
Audi 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 Audi AG filed Critical Audi AG
Publication of EP0723627A1 publication Critical patent/EP0723627A1/fr
Application granted granted Critical
Publication of EP0723627B1 publication Critical patent/EP0723627B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0005—Deactivating valves
    • 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
    • F01L1/267—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 with means for varying the timing or the lift of the valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D17/00—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling
    • F02D17/02—Cutting-out

Definitions

  • the invention relates to a valve train for a multi-cylinder internal combustion engine according to the preamble of claim 1.
  • a valve train is known, for example, from EP 213 759 or DE 42 05 230.
  • the object of the invention is to enable cylinder deactivation for fuel saving in a simple manner in a multi-cylinder internal combustion engine with a valve train of the generic type.
  • the cylinder in question is switched off by stopping its intake valve or valves, which is achieved in that the first cams acting on these valves via the first rocker arms have a zero stroke profile, that is to say they consist of only one basic circle, and the coupling bolts are not acted upon by the pressure medium, so that no coupling of these first rocker arms to the second rocker arm or levers takes place, which interact with a cam with a cam profile, which brings about the desired valve timing and the desired valve lift.
  • the section of the longitudinal channel which is assigned to the first rocker arm of the intake valve of the cylinder to be deactivated can, according to the feature of claim 2, by Plugs are sealed off, one of which is a pressure oil
  • the coupling pin comes into its coupling position in which it connects the first rocker arm to the second rocker arm and thus the inlet valve is actuated in accordance with the contour of the cam interacting with the second rocker arm.
  • the plug provided with the pressure medium inlet bore is preferably in the
  • the camshaft for all intake valves of at least one cylinder is provided with a first cam with a zero stroke profile, and in turn these intake valves are assigned a partitioned section in the longitudinal channel, which has its own pressure medium supply, so that in the manner previously described at zero pressure or at reduced pressure there is no coupling between the first and second rocker arms and the inlet valves are shut down, while when pressure is applied there is a coupling between the first and second rocker arms and the inlet valves are actuated in accordance with the contour of the second cam (s).
  • two longitudinal channels can be provided in the axis, of which the first with the holes receiving the coupling pins in the first set of valves actuating the first rocker arm and the second with the holes receiving the coupling pins in the second set of
  • Inlet valves actuating the first rocker arm is connected, the two longitudinal channels having a partitionable section for the inlet valves of at least one cylinder, and these sections being connectable to or separable from a high pressure source. You can do this
  • Sections at at least one end may be limited by a slide which can be displaced as a function of operating parameters and which, in a first position, separates both longitudinal channels from the high pressure source, in which case all inlet valves of this cylinder are shut off, in a second position connects one of the longitudinal channels to the high pressure source , in which case the valve or valves, which are assigned to this longitudinal channel section, are actuated according to the contour of the second cam or, and in a third position connects both longitudinal channels with the high pressure source, in which case all inlet valves of the relevant cylinder according to the contour of the or the second
  • Cams are operated. Are three inlet valves and thus three first rocker arms and two interconnected second ones arranged between adjacent first rocker arms
  • FIG. 1 shows a valve train with a valve actuation mechanism according to the invention in vertical section along line 1-1 in Fig. 3,
  • FIG. 2 shows a vertical section along line 2-2 in FIG.
  • FIG. 3 is a view of the valve train for the intake valves of two cylinders in direction of arrow 3 in Fig. 1,
  • Fig. 5 is a view similar to Fig. 3 of a valve train for
  • FIG. 6 shows a section along line 6-6 in FIG. 5,
  • Fig. 7 is a section along line 7-7 in Fig. 5, and
  • 1 to 4 is a valve train for two inlet valves Tile El shown a first cylinder and two intake valves E2 of a second cylinder of a multi-cylinder internal combustion engine. Each valve E1, E2 is by a spring 1 in
  • first cams 3 with a zero stroke profile are arranged on a camshaft 2, and a second cam 4 with a cam contour corresponding to the desired valve lift is arranged between them.
  • Cam contour and between them a second cam 9 is provided with a cam contour designed for the upper speed range.
  • the cams 4 and 6 preferably have the same contour.
  • Valves E2 are each provided with a first rocker arm 7, which is arranged between valve E1 and cam 3 or valve E2 and cam 5, respectively. All first
  • Rocker arms 7 are pivotally mounted on a common axis 8. Between the first rocker arms 7 of each pair of valves E1 and E2, a second drag lever 9 is mounted on the axis 8 and cooperates with the second cam 4 and 6, respectively. Every second rocker arm 9 can be coupled to the adjacent first rocker arms 7 in the upper speed range, so that the valves in this speed range
  • each second rocker arm 9 is provided with a cross member 10 which runs in front of and at a short distance from the free ends of the first rocker arms 7.
  • radial bores 11 are provided for the pivot axis 8, which are aligned with bores 12 in the crossmember 10 when the valves are in their closed position, in each bore 11 a piston 13 is arranged, which is between a first inner position (Fig . 4) and a second outer position (Fig.1, 2) is displaceable in which it engages in the corresponding bore 12 in the cross member 10.
  • the pistons 13 thus connect the first rocker arms 7 to the second rocker arms lever 9 so that the valves E1 are actuated in accordance with the contour of the cam 4 and the second inlet valves E2 in accordance with the contour of the cam 6.
  • the displacement of the pistons 13 to the outside takes place with the aid of a pressure medium which is supplied through a channel 15 in the axis 8, which is connected to the bores 11 via openings 16 in the wall of the axis 6. If the pressure medium supply is interrupted or the pressure is reduced, the pistons 13 are each returned to their bores 11 by a spring 14, so that the second cam levers 9 can now swing freely and the valves E1 their closed cams 3 remain closed due to the zero stroke profile while the valves E2 are operated according to the contour of the cams 5.
  • the spring 14 is supported on the one hand on an insert 17 fixed in the bore 11 and on the other hand on the end 18 of a tube 19 which is fastened to the piston 13 and extends through the insert 17.
  • the second drag levers 9 are held in contact with their cams 4 and 6 by a spring 20.
  • the springs 20 are each arranged on a pipe 21 receiving a spark plug or an injection valve and are supported on the one hand on a stationary abutment 22 and on the other hand on a displaceable spring plate 23 which interacts with the extensions 24 of the second rocker arm 9 partially surrounding the pipe 21.
  • the first cams 3 are for the intake valves
  • E1 of a cylinder with a zero stroke profile is provided in order to stop these valves and thus to be able to switch off the corresponding cylinder.
  • Longitudinal channel 15 of axis 8 is provided with a partition 15a, which is assigned to these valves E1 and has an adequate supply of pressure medium. If no pressure medium or a pressure medium with reduced pressure is supplied to section 15a, the coupling bolts 13 remain in their position Fig. 4 shown decoupling position
  • the channel section 15a is delimited by plugs 25 and 26 inserted in the longitudinal channel 15.
  • a pressure medium inflow bore 27 which flows into the channel section 15a and which can be connected to a pressure medium source (not shown) by means of an electromagnetic switching valve 28 which is controlled as a function of operating parameters.
  • the plug 26 is in the range
  • the switching valve 28 has a valve body 29 which has a wide circumferential groove 30 which is connected to an inflow bore 31 in the housing of the switching valve and in the bearing point 32, which is connected to the pressure medium source.
  • valve body 29 interacts with a valve seat 31a. In the closed position of the valve body 29 shown in FIG.
  • the coupling bolts 13 assigned to the inlet valves E2 are in their uncoupling position shown in FIG. 4 when there is no pressure or only a changed pressure in the longitudinal channel 15.
  • the inlet valves E2 are then actuated by the first cams 5 via the first rocker arms 7.
  • the long channel 15 is a pressure medium high pressure according to the arrow P via a switching valve, not shown supplied, the coupling bolts 13 come into the coupling position shown in Fig. 2, in which they the first
  • Valve body 29 a channel 29a is provided, which with the channel section 15a and via a throttle point with the
  • Circumferential groove 30 is connected.
  • E1 of a cylinder is switched off and this cylinder is shut down.
  • first cams with zero stroke profile and sealed-off duct sections 15a for the intake valves of a plurality of cylinders which cams can be individually connected to a pressure medium source according to FIG. 4. This means that either several cylinders can be switched off at the same time or another cylinder can be switched off in order to avoid a longer switch off of a cylinder and the associated cooling of the same.
  • FIGS. 5 to 10 are now referred to, the same or similar parts being designated with the same reference numerals as in FIGS. 1 to 4.
  • a valve train for three intake valves E of a cylinder is shown, wherein each valve is assigned a cam 3 with a zero stroke profile and a cam 4 is arranged with a cam contour corresponding to the desired valve lift between adjacent cams 3.
  • a first rocker arm 7a, 7b or 7c is provided between each inlet valve E and its first cam 3, while the second cam 4 has a second one
  • Rocker arms 9 cooperate, the free ends of which are connected by a crossmember 10 which, in the manner described above, by coupling bolts 13 to the first rocker arms n 7 can be connected.
  • the pivot axis 8 could have a single one
  • two longitudinal channels 33, 34 are provided, which in the area of an inlet valve group have at least one cylinder sealed sections 33a, 34a and of which the channel section 33a through cutouts 35 in the axis 8 with the bores 11 in the two outer rocker arms 7a and
  • the channels 33 and 34 can be connected to a pressure medium source by switching valves, not shown, so that there is the possibility of
  • an electromagnetic switching valve 37 is provided in a bearing of axis 8, the valve body 38 of which separates a channel 39 connected to a high-pressure source in a first position (FIG. 8) from both longitudinal channels 33, 34, in a second position ( Fig. 9) the channel 39 with one
  • Channel section 33a connects and in a third position (Figy. 10). also connects to the second channel section 34a.
  • all the first rocker arms 7a, 7b, 7c are therefore decoupled from the crossmember 10, and thus all the inlet valves are closed.
  • the coupling bolts 13 of the two outer first rocker arms 7a, 7c are acted upon, whereby the two outer inlet valves are actuated in accordance with the contour of the cams 4, while the middle inlet valve remains closed.
  • the middle first rocker arm 7b is also coupled to the crossmember 10, so that all three inlet valves are now actuated in accordance with the contour of the cams 4.
  • the control slide 38 is elongated for this purpose Provide circumferential groove 40 which is constantly in communication with the inflow channel 39. At the end of the circumferential groove 40, an annular shoulder 41 is formed, which cooperates with an annular valve seat 42 in the first lung according to FIG. 8.
  • the lower end of the spool 38 is formed by an annular plate 43, which in the second
  • Longitudinal channel 46 is provided, which is connected to the recess 40 by a throttle point 47, so that a throttled pressure medium supply to both channel sections 33a and 34a takes place.
  • a throttled pressure medium supply to both channel sections 33a and 34a takes place.
  • the longitudinal channel 46 and the throttle point 47 could in the valve seat 42 or in the
  • the two outer intake valves are actuated in the position of the control slide 38 according to FIG. 9 and all three intake valves in the position shown in FIG. 10 in accordance with the contour of the second cams 4.
  • the arrangement could also be such that the channel section 33a with the bore 11 of the middle first rocker arm 7b and the channel section 34a with the holes 11 of the two outer first rocker arms 7a is connected. In this case, the
  • the invention is not limited to the exemplary embodiments shown, but can also be used with a valve train for an internal combustion engine which has only one per cylinder

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

Dans un mécanisme de distribution destiné à un moteur à combustion interne multicylindre, les soupapes d'admission (E1, E2) sont actionnées, au choix, par des premières cames d'un arbre à cames, par l'intermédiaire de premiers basculeurs (7), ou par des deuxièmes cames, par l'intermédiaire de deuxièmes basculeurs (9), les premiers et deuxièmes basculeurs étant séparés ou reliés par des axes d'accouplement (13), sur lesquels peut être appliqué un fluide sous pression passant par un canal longitudinal (15) situé dans l'axe de basculeurs (8). Afin qu'il soit possible d'interrompre le fonctionnement de cylindres individuels, les premières cames affectées aux soupapes d'admission (E1) du cylindre concerné présentent un profil correspondant à une levée nulle, et, dans ledit canal longitudinal (15), se trouve une section étanche (15a) qui peut être reliée individuellement à une source de fluide sous pression, de sorte que, lorsque l'alimentation en fluide sous pression est interrompue, les soupapes d'admission soient mises hors fonction, et que, lorsque la source de fuite sous pression est mise en communication avec ladite section, lesdites soupapes d'admission soient actionnées en fonction du contour des secondes cames.
EP94928822A 1993-10-14 1994-09-26 Mecanisme de distribution pour moteur a combustion interne multicylindre Expired - Lifetime EP0723627B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4334995 1993-10-14
DE4334995A DE4334995C2 (de) 1993-10-14 1993-10-14 Ventiltrieb für eine Mehrzylinder-Brennkraftmaschine
PCT/EP1994/003213 WO1995010694A1 (fr) 1993-10-14 1994-09-26 Mecanisme de distribution pour moteur a combustion interne multicylindre

Publications (2)

Publication Number Publication Date
EP0723627A1 true EP0723627A1 (fr) 1996-07-31
EP0723627B1 EP0723627B1 (fr) 1998-03-04

Family

ID=6500113

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94928822A Expired - Lifetime EP0723627B1 (fr) 1993-10-14 1994-09-26 Mecanisme de distribution pour moteur a combustion interne multicylindre

Country Status (4)

Country Link
US (1) US5832891A (fr)
EP (1) EP0723627B1 (fr)
DE (2) DE4334995C2 (fr)
WO (1) WO1995010694A1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19628024C2 (de) * 1996-07-11 1999-04-01 Siemens Ag Brennkraftmaschine
DE19643711A1 (de) * 1996-10-23 1998-04-30 Audi Ag Ventilbetätigungsvorrichtung für eine Brennkraftmaschine
US6293237B1 (en) 1997-12-11 2001-09-25 Diesel Engine Retarders, Inc. Variable lost motion valve actuator and method
US8820276B2 (en) 1997-12-11 2014-09-02 Jacobs Vehicle Systems, Inc. Variable lost motion valve actuator and method
US6510824B2 (en) 1997-12-11 2003-01-28 Diesel Engine Retarders, Inc. Variable lost motion valve actuator and method
US6799543B2 (en) * 2001-01-05 2004-10-05 Delphi Technologies, Inc. Valve deactivation system with free motion spring
HK1033238A2 (en) * 2001-01-20 2001-08-03 Foo Wah Lau A control device for an air valve of an internal combustion engine
DE10139289A1 (de) * 2001-08-09 2003-02-27 Ina Schaeffler Kg Brennkraftmaschine mit einem schaltbaren Ventiltriebsglied
DE10149477A1 (de) * 2001-10-08 2003-04-17 Bosch Gmbh Robert Verfahren und Vorrichtung sowie Computerprogramm zur Steuerung eines Verbrennungsmotors
DE10221015A1 (de) * 2002-05-11 2003-11-27 Daimler Chrysler Ag Brennkraftmaschine und Verfahren zum Betreiben derselben
US6938873B2 (en) * 2003-12-01 2005-09-06 Delphi Technologies, Inc. Compound valve assembly for controlling high and low oil flow and pressure
DE102005017563B4 (de) * 2005-04-16 2007-06-28 Daimlerchrysler Ag Verfahren zur Herstellung von Hohlwellen sowie Hohlwellen
US8650874B2 (en) * 2011-05-02 2014-02-18 GM Global Technology Operations LLC Engine assembly including intake boost system
DE102017107690A1 (de) 2017-04-10 2018-10-11 Schaeffler Technologies AG & Co. KG Schaltbarer Schlepphebel für einen Ventiltrieb einer Brennkraftmaschine

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4790274A (en) * 1986-07-30 1988-12-13 Honda Giken Kogyo Kabushiki Kaisha Valve operating mechanism for internal combustion engine
CA1308977C (fr) * 1986-08-27 1992-10-20 Tsuneo Konno Mecanisme d'actionnement des soupapes de moteur a combustion interne
JPH036801Y2 (fr) * 1986-11-18 1991-02-20
JPS63167016A (ja) * 1986-12-27 1988-07-11 Honda Motor Co Ltd 多気筒内燃機関の動弁装置
JPH0417705A (ja) * 1990-05-02 1992-01-22 Nissan Motor Co Ltd 多気筒エンジンの弁作動装置
JPH0482343U (fr) * 1990-11-29 1992-07-17
DE4205230A1 (de) * 1992-02-21 1993-08-26 Audi Ag Ventilbetaetigungsmechanismus fuer eine brennkraftmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9510694A1 *

Also Published As

Publication number Publication date
DE59405406D1 (de) 1998-04-09
EP0723627B1 (fr) 1998-03-04
US5832891A (en) 1998-11-10
DE4334995A1 (de) 1995-04-20
WO1995010694A1 (fr) 1995-04-20
DE4334995C2 (de) 1996-01-11

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