EP0353543B1 - Commande de soupape pour moteur à combustion interne - Google Patents

Commande de soupape pour moteur à combustion interne Download PDF

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Publication number
EP0353543B1
EP0353543B1 EP89113228A EP89113228A EP0353543B1 EP 0353543 B1 EP0353543 B1 EP 0353543B1 EP 89113228 A EP89113228 A EP 89113228A EP 89113228 A EP89113228 A EP 89113228A EP 0353543 B1 EP0353543 B1 EP 0353543B1
Authority
EP
European Patent Office
Prior art keywords
valve
operating device
cam
stem
slideway
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
EP89113228A
Other languages
German (de)
English (en)
Other versions
EP0353543A1 (fr
Inventor
Jiri Seidl
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke 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 Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP0353543A1 publication Critical patent/EP0353543A1/fr
Application granted granted Critical
Publication of EP0353543B1 publication Critical patent/EP0353543B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/08—Shape of cams
    • 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
    • F01L1/143—Tappets; Push rods for use with overhead camshafts
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/01—Absolute values
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/18—DOHC [Double overhead camshaft]

Definitions

  • the invention relates to a valve control for internal combustion engines of the type described in the preamble of claim 1.
  • valve control is shown, for example, in GB-PS 846133.
  • This valve control designed for a high-performance engine, also has control shafts with control cams for relatively large valve strokes.
  • control cams of this type are designed to achieve a sufficient filling of the cylinders in the upper speed range for relatively large control angles of over 300 ° crankshaft angles. This gives the valves a late closing point after UT and OT.
  • This opening or time cross section according to UT and / or OT is essential for the gas dynamics in the intake system of the internal combustion engine in order to achieve a high degree of filling.
  • a large time cross section of the valves between the UT and TDC position of the piston in the respective cylinder and the respective closing point has an adverse effect on smooth running and torque in the low speed range due to the backflow of the fresh gas into the suction system through the inlet valve and the relative large overlap of inlet and outlet valve.
  • the aim of the invention is to moderate in an internal combustion engine intended for normal operation Performance waiver in the upper speed range to achieve a significant gain in torque and smoothness in the low speed range in that with substantially the same total opening or opening.
  • a reduction in the control angle of the control cam in combination with an increase in the cam or valve stroke is not possible without taking into account the degree of curvature of the curved slide path of the tappet.
  • the control cam is hollow in its flanks even at low acceleration values.
  • the radius of a hollow flank of the control cam must be relatively large, but as a result, a steep increase in valve opening which is required in accordance with the aforementioned objective cannot be achieved with a small roller radius.
  • a small roller radius in connection with a control cam with a large cam or valve stroke causes a considerable, wear-promoting transverse load.
  • the transverse load is lower, but with a roller radius going towards infinity ( ⁇ ) there is a contact line of the cam tip-side flank area with the tappet slide, which is spaced far from the center of the tappet.
  • a large migration of the contact line of the control cam requires corresponding dimensions of the tappet in the direction of the cam rotation plane, with the disadvantages of large inertial forces and considerable installation space.
  • the invention is based on the object, for a generic valve control with respect to the roller radius of the tappet slideway a radius range and with regard to the control angle and the cam or To show valve stroke of the control cam limit values, the three values in combination with each other resulting in a reduced closing cross section of the valves with a steep valve stroke curve.
  • the closing time cross-section for the exhaust valve can also be reduced according to the invention.
  • a high torque is achieved due to the full time cross section between TDC and TDC in conjunction with the reduced fresh gas backflow.
  • the reduced power in the upper speed range associated with the reduced gas dynamics in the intake system by reducing the closing time cross section between UT and the closing point of the inlet valve is compensated for by means of several inlet valves per cylinder of the internal combustion engine. For this, three inlet valves form an optimal compromise between a high torque curve in the low speed range and a favorable performance level in the upper speed range.
  • the combination of these three numerical values gives, as a further advantage, a favorable measure for the migration of the contact line between the control cam and the slideway of the valve tappet without limiting a desired large valve lift by the given valve opening speed.
  • the favorable emigration dimension also results in relatively small dimensions of the tappet in the direction of the control cam rotary plane, combined with small masses in a small installation space. Lower masses enable valve acceleration corresponding to the steep course of the valve stroke without dynamic problems.
  • the mass of the valve tappet can also be reduced in addition to small dimensions by a shape of a tappet having a rectangular or oval cross section in plan view.
  • such plungers also facilitate the arrangement of a plurality of intake and exhaust valves in a cylinder of relatively small diameter.
  • the value specified in claim 2 for the roller radius of the slide of the valve tappet gives, in addition to the dimension of the contact line migration favorable for the tappet dimension, the further advantage of a radius for the tip of the control cam when the valve stroke is full between the reversal points of the reciprocating piston in the cylinder to be able to choose with which the Hertzian pressure between the cam tip and the tappet slideway is low, especially at low engine speed.
  • a radius tending toward larger numerical values at the cam tip complies with the configuration of a full valve lift curve or a fuller valve lift curve.
  • a valve control 1 in a cylinder head 2 of a reciprocating piston internal combustion engine comprises a control shaft 3 with a control cam 4, which actuates an inlet valve 6 in a combustion chamber depression 7 of the cylinder head 2 for a cylinder via a tappet 5.
  • This control cam 4 interacts with a cylindrically curved slide 8 of the plunger 5.
  • the slideway 8 is formed with a roller radius R R ⁇ 65 mm.
  • a steep valve stroke curve - solid line - is achieved in the interaction of the three specified values according to FIG Interpretation according to the dashed curve.
  • the valve stroke curve follows the solid line compared to the dashed curve a full time cross-section for torque and power.
  • the solid valve stroke curve shows a significantly reduced closing time cross-section from "reciprocating piston UT" to "inlet closes (Es)". This means that at low engine speeds, backflow of the fresh charge drawn from the cylinder into the intake system is considerably reduced, resulting in a high torque curve.
  • at least two inlet valves 6 are provided per combustion chamber 7.
  • the dimensioning of the interacting valve train elements results in a favorable value for the emigration "A" of the contact line "K" of the control cam 4 with the slideway 8 at, in particular, avoiding the production of pronounced hollow flanks of the control cams 4 with a large valve lift h V beginning engagement of the control cam tip area 9.
  • the rectangular or oval tappets 5 are conducive to a closely adjacent arrangement of the inlet valves 6 in the combustion chamber trough 7, the slideways 8 connecting guide surfaces 10 of the tappets 5 arranged at the greatest mutual distance from one another.
  • the control can be designed analogously for an exhaust valve, not shown, in order in particular to be able to additionally influence the size of the valve overlap of the intake and exhaust valve.

Landscapes

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

Claims (5)

1. Commande de soupape pour moteur à combustion interne, dans laquelle une soupape (6) est actionnée par l'intermédiaire d'un poussoir (5) par un arbre à cames (3) et une came de commande (4) de l'arbre à cames (3) coopère avec une glissière bombée (8) du poussoir (5), commande de soupape caractérisée en ce que la came de commande (4) pour une soupape (6) présente un came principale avec un angle de commande (α) d'au plus 240° d'angle d'arbre de vilebrequin lors d'une course de came ou course de soupape (hv) d'au moins 10 mm, la glissière (8) du poussoir (5) étant pourvue au moins dans une section essentielle d'un rayon de roulement (rr) compris dans la zone de valeurs 50 ≦ rr ≦ 80 mm. (RR).
2. Commande de soupape selon la revendication 1, caractérisée en ce que l'angle de commande vaut l'angle d'arbre de vilebrequin α = 236° et le rayon de roulement a pour valeur rr ≈ 65 mm.
3. Commande de soupape selon la revendication 1 et la revendication 2, caractérisée en ce que l'arbre à cames (3) est équipé de cames de commande (4) pour plusieurs soupapes (6) à chaque cylindre du moteur à combustion interne.
4. Commande de soupape selon la revendication 3, caractérisée en ce que le poussoir (5) ― vu par dessus, présente une section rectangulaire ou ovale et que la glissière (8) relie les faces de guidage (10) du poussoir (5) disposées à la plus grande distance mutuelle.
5. Commande de soupape selon les revendications 1-4, caractérisée en ce que la glissière (8) du poussoir (5) est formée de sections avec des rayons de roulement différents (RR) compris dans la zone de valeur de 50 ≦ rr ≦ 80.
EP89113228A 1988-08-03 1989-07-19 Commande de soupape pour moteur à combustion interne Expired - Lifetime EP0353543B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3826365A DE3826365A1 (de) 1988-08-03 1988-08-03 Ventilsteuerung fuer brennkraftmaschinen
DE3826365 1988-08-03

Publications (2)

Publication Number Publication Date
EP0353543A1 EP0353543A1 (fr) 1990-02-07
EP0353543B1 true EP0353543B1 (fr) 1992-01-22

Family

ID=6360159

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89113228A Expired - Lifetime EP0353543B1 (fr) 1988-08-03 1989-07-19 Commande de soupape pour moteur à combustion interne

Country Status (2)

Country Link
EP (1) EP0353543B1 (fr)
DE (2) DE3826365A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4002964A1 (de) * 1990-02-01 1991-08-08 Audi Ag Zylinderkopf fuer eine ventilgesteuerte brennkraftmaschine
DE4244287C2 (de) * 1992-04-27 2001-12-13 Iav Motor Gmbh Ventiltrieb für Ladungswechselventile, vorzugsweise Einlaßventile von Hubkolbenbrennkraftmaschinen
DE4244286C2 (de) * 1992-11-13 2001-07-05 Iav Motor Gmbh Schaltbarer Ventiltrieb für Gaswechselventile von Verbrennungsmotoren
DE4302877C2 (de) * 1993-02-02 1996-04-11 Schaeffler Waelzlager Kg Stößel
DE4413408A1 (de) * 1994-04-18 1995-10-19 Korostenski Erwin Brennkraftmaschine mit Flachstößel
DE10123963A1 (de) * 2001-05-17 2002-11-21 Ina Schaeffler Kg Stößel für einen Ventiltrieb
JP2003083017A (ja) * 2001-09-10 2003-03-19 Mitsubishi Electric Corp バルブリフト調整装置

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3073292A (en) * 1960-02-17 1963-01-15 Gen Motors Corp Composite valve lifter
BE759158A (fr) * 1969-11-20 1971-04-30 Standard Triumph Motor Cy Ltd Commande des soupapes d'un moteur a combustion
DE3234640A1 (de) * 1982-09-18 1984-03-22 Volkswagenwerk Ag, 3180 Wolfsburg Ventiltrieb, insbesondere fuer eine brennkraftmaschine
GB2133467A (en) * 1983-01-17 1984-07-25 Darren Gale Swanson Four-stroke engine valve timing
DE3306355A1 (de) * 1983-02-24 1984-08-30 Ford-Werke AG, 5000 Köln Brennkraftmaschine mit variablen ladungswechsel-steuerzeiten
DE3308550A1 (de) * 1983-03-10 1984-09-13 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg Flachstoessel fuer ventilantriebe
FR2550273B1 (fr) * 1983-08-05 1987-11-06 Peugeot Dispositif d'actionnement d'une soupape, pour distribution variable d'un moteur a combustion interne
US4637357A (en) * 1985-04-29 1987-01-20 Yamaha Hatsudoki Kabushiki Kaisha Tappet arrangement for engine valve train
DE3622143A1 (de) * 1986-07-02 1988-01-14 Daimler Benz Ag Gleitpaarung aus einem steuernocken und einem ventilbetaetigungshebel

Also Published As

Publication number Publication date
DE3826365A1 (de) 1990-02-15
EP0353543A1 (fr) 1990-02-07
DE58900757D1 (de) 1992-03-05

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