EP0595060B1 - 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
EP0595060B1
EP0595060B1 EP93115881A EP93115881A EP0595060B1 EP 0595060 B1 EP0595060 B1 EP 0595060B1 EP 93115881 A EP93115881 A EP 93115881A EP 93115881 A EP93115881 A EP 93115881A EP 0595060 B1 EP0595060 B1 EP 0595060B1
Authority
EP
European Patent Office
Prior art keywords
drive according
camshaft
cam
transmission member
sliding cam
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
EP93115881A
Other languages
German (de)
English (en)
Other versions
EP0595060A1 (fr
Inventor
Winfried Krebs
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.)
Dr Ing HCF Porsche AG
Original Assignee
Dr Ing HCF Porsche 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 Dr Ing HCF Porsche AG filed Critical Dr Ing HCF Porsche AG
Publication of EP0595060A1 publication Critical patent/EP0595060A1/fr
Application granted granted Critical
Publication of EP0595060B1 publication Critical patent/EP0595060B1/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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/185—Overhead end-pivot rocking arms
    • 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
    • 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
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • 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
    • 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
    • F01L1/047—Camshafts
    • F01L2001/0475—Hollow 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
    • 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
    • F01L1/047—Camshafts
    • F01L2001/0476—Camshaft bearings
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2102—Adjustable

Definitions

  • the invention relates to a valve drive for an internal combustion engine according to the preamble of claim 1.
  • DE-OS 20 37 705 discloses a generic valve drive with a hydraulically axially displaceable camshaft on which fixed cams with two different elevation curves are arranged.
  • gas exchange valves with a larger valve stroke are actuated in one end position of the camshaft, while when the oil pressure is switched off the camshaft is spring-loaded and moved to a second end position, the valves are actuated with a smaller valve stroke.
  • the disadvantage here is the simultaneous axial displacement of all cams.
  • the angular offset of the cams to one another means that no position of the camshaft can be found in which all the cams run simultaneously on their base circle, as would be necessary for an axial displacement.
  • the cams assigned to the exhaust valves are also displaced.
  • a valve train with axially spirally displaceable and rotatable cams on the camshaft is known.
  • the cams are held on the camshaft by means of a form fit by means of a spiral thread.
  • Axially displaceable shafts run parallel to the camshaft, which engage the cams from the outside by means of drivers and rotate them relative to the camshaft in order to set optimal timing times.
  • the cams actuate gas exchange valves with the interposition of transmission elements designed as rocker arms. This arrangement takes up a considerable amount of space due to the axially displaceable shafts, is heavy and susceptible to wear due to the sliding contact between rotating cams and drivers.
  • a spiral toothing on the camshaft is expensive to manufacture.
  • valve drive with the features of the main claim has the advantage that gas exchange valves of all cylinders in a row of cylinders can be operated with this valve drive.
  • the sliding cams are axially biased against the stops as long as they run on this stop with their sections of their end face limited by the elevation curves. If the base circle of each slide cam reaches the transmission element, the slide cams are displaced and run with their elevation curve on the transmission element.
  • This valve drive can be used, for example, in the case of directly actuated valves, it being possible for the transmission element to be designed as a bucket tappet provided with hydraulic valve clearance compensation.
  • the valve drive can be used with valve drives provided with levers.
  • the transmission element is designed as a rocker arm, rocker arm or the like.
  • the sliding cams can be provided with two elevation curves, the portion abutting the stop being formed between the two elevation curves.
  • the different elevation curves running on the transmission element can have an angular offset to one another, so that there is a phase shift.
  • This phase shift can be used together with the variation of the valve lift or instead of this.
  • a valve drive of an internal combustion engine has a camshaft 2 held in bearings 1, which is driven in the usual way by a crankshaft.
  • a non-rotatable cam which is displaceable in a longitudinal direction L and is designed as a sliding cam 3.
  • This sliding cam 3 is displaceable along a guide 4 which positively connects it and the camshaft 2 from a first S1 to a second position S2.
  • the sliding cam 3 actuates two gas exchange valves designed as inlet valves 6 with the interposition of a transmission element 5.
  • a stop 7 is formed between the sliding cam 3 and the transmission element 5.
  • the sliding cam 3 is axially biased with one of its end faces 8.
  • the axial preload is applied either by a compression spring 9 or a hydraulically actuated piston 10.
  • This piston 10 is slidably inserted in a sleeve 11, which in turn is arranged between the bearing 1 and the camshaft 2. Via a central channel 12 of the camshaft 2 and radial bores 13 branching therefrom, the piston 10 is connected to a hydraulic circuit, not shown, which acts on the central channel 12 with pressure oil depending on parameters of the internal combustion engine or keeps it free of oil pressure.
  • a fixed cam 15 is arranged centrally on the camshaft 2 between two sliding cams 3 which can be displaced in relation to one another.
  • a compression spring 9 is supported on this on both sides which hold the slide cams 3 in the first position S1 when the oil pressure is switched off.
  • All cams 3, 15 have a base circle 16 and the fixed cam 15 has a first elevation curve 17, which has a shorter stroke than the second elevation curve 18 of the sliding cams 3.
  • the transmission element 5 has on the sliding cams 3 facing end faces 19 designed as a stepped recess 20 stops 7.
  • valves 6 When the internal combustion engines are operating, the valves 6 are first actuated by the fixed cam 15 according to their elevation curve 17 when the central channel 12 is free of oil pressure.
  • the sliding cam 3 run together with the fixed cam 15 without running onto the transmission element 5, since the clearance 20 provides sufficient clearance for the second elevation curves 18.
  • the pistons 10 press on the other end 8 of the sliding cam 3 facing away from the compression spring 9 and try to move it in the direction of the fixed cam 15. If the slide cams 3 run during the pressure oil connection with a section 21 of their one end face 8 limited by their elevation curve 18 in the recess 20, the slide cams 3 bear positively on the stop 7 due to the hydraulic prestress.
  • two sliding cams 3 which can be displaced in relation to one another each have a first and a second elevation curve 17 and 18.
  • both sliding cams 3 are spring-loaded in the first position S1 and act on the transmission element 5 with the first elevation curves 17.
  • the recess 20 in turn provides sufficient clearance for the elevation curves 18 provided with a larger stroke.
  • the sliding cams 3 are again in contact with the section 21 at the stop 7, before they are moved during their base circle 16 into the second position S2 shown in dashed lines in FIG. 4, in which they press the valves 6 with the second elevation curves 18 act.
  • the third embodiment according to FIG. 5 has a single sliding cam 3 with two elevation curves 17, 18.
  • the sleeve 11 is arranged adjacent to a bearing 1 on the camshaft 2 separately.
  • the transmission element 5 has a roller 22 which evenly distributes the transmitted forces, one side surface 23 of which forms the stop 7 for the section 21. In the first position S1, the roller 22 is in contact with the elevation curve 17, in the second position S2 with the elevation curve 18.
  • Fig. 6 shows the positive connection used in all embodiments between the sliding cam 3 and the camshaft 2 by the guide 4 running in the longitudinal direction L, which is formed, for example, by keys 24 inserted in grooves.
  • a phase shift between the first and second elevation curves can be achieved by these curves relative to one another are arranged offset in angle. This angular offset can also be realized without varying the stroke, so that the valve drive acts as a phase converter.
  • a line 26 shows the congruent main axes of the in-phase elevation curves 17 and 18, while a dashed line 27 shows the main axis of an out-of-phase elevation curve.

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 (10)

  1. Commande de soupape pour un moteur à combustion interne, comportant un arbre à cames maintenu dans des paliers et au moins une came déplaçable axialement, qui, par insertion d'un élément de transmission, actionne au moins une soupape d'échange de gaz, caractérisée en ce que la came est configurée en came coulissante (3) solidaire en rotation, déplaçable par rapport à l'arbre à came (2), et, précontrainte axialement, elle s'applique, dans une première position (S1), par concordance de forme, contre une butée (7) réalisée entre la came coulissante (3) et l'élément de transmission (5).
  2. Commande selon la revendication 1, caractérisée en ce que la came coulissante (3) s'applique avec une portion (21), limitée par sa courbe de relief (18), de l'une de ses faces frontales (8), contre la butée (7).
  3. Commande selon la revendication 2, caractérisée en ce que la butée (7) est formée par un évidement (20) étagé, placé sur l'élément de transmission (5).
  4. Commande selon la revendication 3, caractérisée en ce que sur l'élément de transmission (5) sont formées deux butées (7) se faisant face dans la direction longitudinale (L) de l'arbre à cames (2), agissant en sens opposé.
  5. Commande selon la revendication 2, caractérisée en ce que la butée (7) est formée par une surface latérale (23), tournée vers la portion (21), de l'élément de transmission (5).
  6. Commande selon les revendications 3 ou 5, caractérisée en ce que la portion (21) sépare l'une de l'autre deux courbes de relief (17, 18) formées sur une came coulissante (3).
  7. Commande selon la revendication 6, caractérisée en ce que la came coulissante (3) passe sur l'élément de transmission (5), dans une première position (S1) avec une courbe de relief (17, 18) et dans une seconde position (S2), avec l'autre courbe de relief (17, 18).
  8. Commande selon la revendication 3, caractérisée en ce que des deux côtés, au voisinage d'une came fixe (15) sur l'arbre à cames (2) sont prévues des cames coulissantes (3), pourvues d'une seule courbe de relief, qui dans la première position (S1) agissent sur l'élément de transmission (5).
  9. Commande selon une ou plusieurs des revendications précédentes, caractérisée en ce que la came coulissante (3), sollicitée par un piston (10) actionné hydrauliquement, est déplacée de l'une des positions (S1, S2) dans l'autre position (S2, S1).
  10. Commande selon une ou plusieurs des revendications précédentes, caractérisée en ce qu'entre l'arbre à cames (2) et la came coulissante (3) est prévu un guidage (4) par concordance de forme et solidaire en rotation, s'étendant dans la direction longitudinale (L).
EP93115881A 1992-10-30 1993-10-01 Commande de soupape pour moteur à combustion interne Expired - Lifetime EP0595060B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4236655 1992-10-30
DE4236655A DE4236655A1 (de) 1992-10-30 1992-10-30 Ventilantrieb für eine Brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP0595060A1 EP0595060A1 (fr) 1994-05-04
EP0595060B1 true EP0595060B1 (fr) 1995-12-13

Family

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Family Applications (1)

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EP93115881A Expired - Lifetime EP0595060B1 (fr) 1992-10-30 1993-10-01 Commande de soupape pour moteur à combustion interne

Country Status (4)

Country Link
US (1) US5359970A (fr)
EP (1) EP0595060B1 (fr)
JP (1) JPH06212923A (fr)
DE (2) DE4236655A1 (fr)

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Also Published As

Publication number Publication date
JPH06212923A (ja) 1994-08-02
DE59301164D1 (de) 1996-01-25
US5359970A (en) 1994-11-01
DE4236655A1 (de) 1994-05-05
EP0595060A1 (fr) 1994-05-04

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