EP0779411B1 - 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
EP0779411B1
EP0779411B1 EP96116552A EP96116552A EP0779411B1 EP 0779411 B1 EP0779411 B1 EP 0779411B1 EP 96116552 A EP96116552 A EP 96116552A EP 96116552 A EP96116552 A EP 96116552A EP 0779411 B1 EP0779411 B1 EP 0779411B1
Authority
EP
European Patent Office
Prior art keywords
locking
cam
valve drive
drive according
stroke
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
EP96116552A
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German (de)
English (en)
Other versions
EP0779411A1 (fr
Inventor
Dietmar Schwarzenthal
Joachim Grünberger
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
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Filing date
Publication date
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Publication of EP0779411A1 publication Critical patent/EP0779411A1/fr
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Publication of EP0779411B1 publication Critical patent/EP0779411B1/fr
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
    • 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
    • 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
    • F01L1/26—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
    • 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
    • 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
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F01L1/462—Valve return spring arrangements

Definitions

  • the invention relates to a valve train of an internal combustion engine Internal combustion engine according to the type of the main claim.
  • Such a valve train is described for example in EP 0 515 520 B1 and has a plunger made of two concentric cup elements, of which the inner abuts with its one end face on the valve stem of the gas exchange valve.
  • the tappet interacts with the cam of a camshaft, the three part cams with has different cam tracks.
  • the two outer cam tracks have the same stroke and act on the outer cup element.
  • the middle one Partial cam has a different stroke profile with a lower stroke height and acts on the inner cup element.
  • the two concentric cup elements can by hydraulic loading of a coupling element with each other coupled or independent in a second switching position of this coupling element be moved from each other.
  • the two are in the coupled switching position Cup elements connected to each other so that the stroke of the partial cam follow with a larger stroke. About the coupling element and the inner cup element this movement is transferred to the valve stem.
  • the two cup elements are independent of one another movable. In this switch position, the valve stem works with the middle part cam together with less stroke.
  • the outer plate element follows the stroke of the outer partial cams, but no connection to the inner cup element or to the valve stem. With these plungers, however, there is a possibility that Coupling element by hydraulic loading at any time from its current Switch position is adjustable.
  • the displacement of the coupling element is in generally only given if all the partial cams interact with the associated cup element are in their base circle phase, since only in this Switch position, the coupling element is freely movable.
  • the pressurization of the Coupling element takes place independently of it, so that under certain circumstances the time for a complete adjustment of the coupling element from a switching position in the others are not enough. Unwanted edge loads can then occur high wear occur. Under certain circumstances it can also happen that the Coupling element in the event of insufficient displacement caused by the valve train acting forces is pushed back, so that the valve after a partial stroke beats back into the valve seat undamped, which is very annoying and causes additional wear.
  • a plunger for a switchable gas exchange valve which has a coupling element has, with which the associated gas exchange valve can be activated or deactivated.
  • This coupling element is longitudinally displaceable and has a bore in which in a Switch position of the valve stem can dip. In this switch position there is a Stroke movement of the tappet possible, but not transferred to the valve stem becomes. Moving the coupling element is only within defined Cam tracks possible.
  • the coupling element acts with a locking device together, which consists of a resilient locking tongue and an actuating pin.
  • the resilient locking tongue engages in the coupling element in defined positions.
  • the stylus picks up a cam contour of the associated cam and transmits it on the locking element, wherein only in predetermined cam track areas Relief of the locking element and thus a displacement of the coupling element is possible.
  • DE 37 35 156 C2 is a valve train of an internal combustion engine known, in which two gas exchange valves via rocker arms from the three-part cam be applied to a camshaft.
  • the three rocker arms are adjacent arranged to each other and stored on a common axis.
  • the two outer rocker arms work with the two outer cam tracks of the three-part Cam together
  • the middle rocker arm works with the middle cam track together with a larger valve stroke.
  • the three related rocker arms is guided a coupling element with which the three in a first switching position Rocker arms are coupled to each other so that the stroke of the middle Follow the cam track with a larger lifting height.
  • the middle rocker arm has it no influence on the valve stroke.
  • the invention has for its object a valve train of an internal combustion engine to improve the genus of the main claim so that undefined switching positions can be avoided and it is ensured that the coupling element is always safe from one its end positions can be transferred to the other end position. With that at the same time undesirable component loads due to insufficient load-bearing behavior be avoided.
  • the cam track-dependent blocking or release of the coupling element can be carried out advantageously so that a scanning element has a cam contour Scans the camshaft and transfers it to the locking element so that this in one locked the coupling element in the first cam track region and in a second Releases cam track area.
  • This scanning element can be, for example, mechanical acting component to be executed, the outer contour of the cam track or Scans the cam area.
  • the valve train according to the invention can advantageously be of different types valve lift transmission.
  • the Invention the transmission of the predetermined by the cam or the cam tracks Stroke course on the at least one gas exchange valve through stroke transmission elements in the manner of a bucket tappet with two concentric lifting elements.
  • the stroke transmission takes place through Lever elements, for example rocker arms or rocker arms.
  • the scanning element and the locking element can be used in a particularly advantageous manner be integrally formed, whereby a transmission of the scanning signal to the Locking element takes place directly without intermediate components and components and possibly also Space can be saved.
  • the coupling element has two spaced locking contours, can particularly advantageous way the locking element in each case depending on the Engage switching position in the coupling element, so that this in both switching positions (End positions) can be locked.
  • the locking element and the coupling element are coordinated with one another Shaping designed so that a positive control of the coupling element during of the switching process or at the end of the switching process.
  • This Forced control is achieved by the locking element depending on the Rotational position of the cam through interaction with the cam contour on the Locking contour of the coupling element attacks and this inevitably in one of its End positions shifted.
  • the implementation takes place through wedge-shaped locking grooves are introduced on the coupling element. This mechanical priority control overlays the hydraulic control and significantly increases the safety of such Valve train.
  • the coupling element as a cylindrical Pin is formed, which in the coupling bores of the two with each other coupling plunger elements is guided.
  • the locking contour can be as circumferential annular recess can be produced in a relatively simple manner.
  • such a shape offers considerable advantages in the Sealing of the coupling element, so that it can be directly acted upon hydraulically Piston can be used.
  • valve train shown in Fig. 1 a not shown Internal combustion engine has a cylindrical plunger 1, which is coaxial with one switchable gas exchange valve 2 is arranged and by a cam 3 one Camshaft 4 is operated.
  • the tappet 1 is in a bore 5 of a cylinder head 6 used and is supported by a compression spring 7.
  • Valve 2 gas exchange valve
  • Valve plate 9 and a valve stem 10, which is provided with a valve spring plate 11 is.
  • a valve spring 12 is located between the valve spring plate 11 and the cylinder head 6 arranged, which holds the valve 2 in the closed position.
  • the valve spring 12 opposite, the compression spring 7 is also supported on the valve spring plate 11.
  • the plunger 1 shown in FIGS. 2 and 3 has two concentric Cup elements 13, 14, each with different cam areas (Partial cams) 15 to 17 of cam 3 interact.
  • the two outer ones Cam areas 15 and 17 are of identical design, i.e. they have the same Lift height and phase position. These cam areas 15 and 17 act with the outer of the two cup elements 13 together.
  • the middle cam area 16 has compared to the two outer cam areas 15 and 17, a lower lifting height and cooperates with the inner cup element 14. This is about itself known hydraulic valve lash adjuster (HVA) 18 with the valve stem 10 of the gas exchange valve 2 together.
  • HVA hydraulic valve lash adjuster
  • the outer cup element 13 has an approximately cup-shaped housing 19, the Bottom 20 facing the cam 3. This has a continuous opening 21, which is surrounded on the inside of the bottom 20 by a peripheral edge 22.
  • the bottom 20 is parallel to its outside 23 from a bore 24 penetrated, which intersects the opening 21.
  • this opening 21 is also cup-shaped housing 25 of the inner cup element 14 used. Its bottom 26 is the middle Cam area 16 facing. The bottom 26 is covered by a bore 27 penetrated that in the working position shown in Fig. 2 of the plunger 1 and Cam 3 is aligned with the bore 24 of the outer cup element 13. In these Bore 27 opens approximately perpendicular to a bore 28 which extends from the Outside 29 of the bottom 26 goes out. This is a bore 30 smaller Diameter opposite, which also opens into the bore 27 and from the Inside 31 of the bottom 26 goes out.
  • the bottoms 20 and 26 of the two Cup elements are on their outer sides 23 and 29 in the running direction of the cam 3 barrel-shaped.
  • the housing 25 of the inner cup element 14 has a jacket section 32 extending from the bottom 26 and having a longitudinal groove 33 is provided, which is from the open end face 34 of the jacket section 32 starting from about to the middle region of the bottom 26.
  • two mutually opposite guide sleeves 36, 37 are used, that protrude to the outside of the inner cup element.
  • These guide sleeves 36 and 37 receive a coupling element 38 in the form of a cylindrical pin, whose length is the distance between the two outer end faces 39, 40 of the two Corresponds to guide sleeves 36 and 37.
  • the coupling element 38 is with two adjacent, circumferential locking grooves 41, 42 with approximately V-shaped Provide cross section.
  • These locking grooves work with a locking pin 43 together, which is guided in the bore 28.
  • This has one cylindrical section 44, the diameter of which corresponds to that of the bore 28 and whose length is greater than the length of the bore 28.
  • On the cylindrical Section 44 closes a conical section 45 with a larger one Base diameter, which is located inside the bore 27 and the Locking grooves 41, 42 facing.
  • the bottom of the cone section 45 is on the Inside 27 of the bore 28.
  • the cylindrical section 44 protrudes into a groove 46, which is formed in the base circle region of the partial cam 16.
  • the right guide sleeve 48 in FIG. 2 is approximately cup-shaped and dimensioned so that its open end face 49 to the end face 40 of the Guide sleeve 37 bumps.
  • On the inside of the bottom 50 of the guide sleeve 48 one end of a compression spring 51 is supported, the opposite end of which a piston 52 guided inside the guide sleeve 48. The face this piston 52 bears against the end face of the coupling element 38.
  • the opposite guide sleeve 47 also projects with its end face 53 to the Face 39 of the guide sleeve 36.
  • the guide sleeve 47 is on hers opposite end face by a cup-shaped insert 54 locked. Inside the guide sleeve 47, a piston 54 is longitudinally movable performed, the end face on the opposite end face of the coupling element 38 is present. In the guide sleeve 47 opens a bore 55, which follows explained way is coupled to the oil supply to the cylinder head. Through the piston 55 and the insert 54 becomes a pressure space 57 inside the guide sleeve 47 trained, in which this bore 56 opens.
  • pressure medium lubricating oil
  • Cup-shaped inserts 58 and 59 are used in the interior of the outer cup element 13 .
  • External use 58 lies with its outer mat surface 60 on the inner wall of the outer Cup element.
  • This outer insert 58 also has an inner, peripheral edge 61, the peripheral edge 22 of the outer cup element 13 is present.
  • the inner insert 59 lies with its outer surface 62 on the outer surface 60 of the outer insert and also has a peripheral edge 63, which on circumferential edge 61 of the outer insert 58 abuts. Between the two A partially circulating oil chamber 64 is formed for use.
  • an anti-twist device which comprises a longitudinally guided pin 90 in the cylinder head 6, which in the Longitudinal groove 33 of the inner cup element 14 engages.
  • the pin 90 is also on the outside with a guide head 71 provided in a longitudinal groove, not shown, in the plunger guide of the Cylinder head 6 protrudes. Through this guide head 71 is a rotation of the outer Cup element 13 and thus the entire plunger 1 relative to the cylinder head 6 prevented.
  • the rotary movement of the camshaft 4 is over the cam 3 in a stroke movement of the plunger 1 and thus the gas exchange valve 2 implemented.
  • the gas exchange valve 2 follows that generated by the central partial cam 16 Stroke. This is via the inner cup element 14 and the hydraulic Valve clearance compensation element 18 from partial cam 16 to valve stem 10 transfer.
  • the outer cup element 13 also performs a lifting movement that corresponds to the stroke curve of the partial cams 15 and 17.
  • the first switching position of the coupling element 38 are the outer and inner Cup element 13 and 14, however, not connected to each other, so that the outer cup element moves independently of the inner cup element.
  • the Compression spring 51 which acts on the piston 52, which in turn with the Coupling element 38 and the pressurizable piston 55 cooperate is so voted that if there is one for the normal oil supply of the Cylinder head of sufficient oil pressure (e.g. 0.5 bar) of the piston 52, the Coupling element 58 and the piston 55 in the first switching position shown in Fig. 3 moved or held in this.
  • the groove 46 in the partial cam 16 is approximately crescent-shaped and at the beginning of the base circle phase (in relation to the rotary movement) of the Cam 3 arranged. Is in the switching position shown in Fig. 3 Coupling element 38 of the piston 55 is subjected to switching pressure, this causes a force directed to the right in the representation selected in FIG. 3 on the Coupling element 38. As long as the locking element 43 - as in FIG. 2 shown - in cooperation with the partial cam 16 in the survey phase or the base circle phase is outside the groove 46, this is in the bore 27th pressed or held that it is in the locking groove 42 of the coupling element 38th intervenes. A displacement of the coupling element 38 is prevented.
  • the second embodiment of the shown in FIGS. 4 to 6 Tappet 1 essentially differs in that Formation of the coupling element and the locking element.
  • the locking element as Locking ball 72 formed on the one hand with the partial cams 16 and Locking groove 46 and the coupling element 73 cooperates.
  • the coupling element 73 has - as in the previous embodiment - two arranged side by side, in Cross-section V-shaped locking grooves 41, 42, which with the locking ball 72nd work together.
  • the length of the coupling element 73 corresponds to the length of the Bore 27 of the inner cup element 14.
  • the front ends of the cylindrical coupling element 73 are crowned, the Radius of curvature is smaller than the cylinder radius of the coupling element 73.
  • the middle position (FIG. 5) remains when the elevation phase of the cam 3 begins.
  • the coupling element 73 is located at the beginning of the elevation phase of the cam in a middle (not fully switched) position (see Fig. 5), the Locking ball 72 on the web 77 between the two locking grooves 41 and 42 on.
  • the partial cam 16 runs during its rotation on the Locking ball 72, so that when the accumulation phase of the inner Cup element 14 moves relative to the outer cup element.
  • the third exemplary embodiment of the joint 1 shown in FIG. 7 shows in contrast to the previously described exemplary embodiment, two separate coupling elements 78, 79, which are each provided with two locking grooves 41, 42.
  • the two Coupling elements 78, 79 simultaneously act as hydraulically actuated pistons, the pressure space 80 between its two facing end faces is trained.
  • the two coupling elements 78, 79 are - as in the Embodiments previously - arranged in the inner cup element 14. Outside Cup element 13, two pistons 81, 82 are guided, each by a compression spring 83 and 84 are acted upon and the coupling elements 78 and 79 act in the opposite direction.
  • the two coupling elements 78, 79 each act with one Locking ball 85, 86 together, which in turn has a common groove 87 cooperate in the partial cam 16.
  • the fourth embodiment of the invention shown in Fig. 8 shows in essentially a modification of the previously described embodiment, at which the coupling elements 78 and 79 in the outer cup element 13 and those with Compression springs 83 and 84 cooperating pistons 81 and 82 inside Cup element 14 are arranged. Pressurization of pistons 78 and 79 takes place on their outer end faces facing away from the inner cup element 14.
  • Each of the two coupling elements is - as in the exemplary embodiments above - with two locking grooves 41, 42, each with a locking ball 85, 86 cooperate. These locking balls 85 and 86 each act with one Locking groove 88 and 89 together, which in the two outer part cams 15 and 16 are arranged.
  • FIGS. 9 to 11 show two modifications of a fifth exemplary embodiment shown, which correspond essentially to the first embodiment and themselves in the elements to prevent rotation and the structure and arrangement of the Differentiate locking element from this.
  • the inner cup member 14 of the fifth shown in FIGS. 9 and 10 Embodiment has a narrow incision 91 starting from the bottom 26, which extends into the area of the bore 30.
  • This incision 91 partially settles continues in the guide sleeve 27 as an incision 92.
  • This incision 92 extends in this exemplary embodiment over more than 2/3 of the circumference of the guide sleeve, leaving a web 93.
  • a bow-shaped Spring element 94 inserted, one leg 95 on the underside of the Incision 91 is present.
  • the spring element 94 engages around the web 93 Guide sleeve and the coupling element 38.
  • the second leg 96 protrudes from the Outside of the bottom 26 out of the incision 91 and lies with one curved section 97 on the partial cam 16.
  • the coupling element 38 encompassing curved section 98 is formed so that by Cooperation of the spring leg 96 and the partial cam 16, the spring leg 96 is located in one of the two locking grooves 41, 42.
  • the coupling element 38 is shown, for example, in FIG. 10 Starting position shifted to the right.
  • the anti-rotation device between the inner cup element 14 and the outer Cup element 13 is carried out in this exemplary embodiment by a in FIG. 10 visible securing element 99, which in the region of the bore 24 between the both cup elements is inserted.
  • the securing element 99 has a bore 100, into which the piston 55 protrudes and thus positions the securing element 99.
  • One side of this securing element 99 lies on the curved inner circumference of the outer cup element 13.
  • the opposite side of the The securing element is flattened and is also flattened on one trained section 101 of the inner cup element 14.
  • the entire plunger 1 is secured against rotation by a pin 102, which is shown in FIG a bore 103 of the outer cup element 13 is inserted and how the Locking pin 90 of the first embodiment in one not closer shown groove of the plunger guide is.
  • FIG. 11 A modification of the anti-rotation device between the inner and outer cup element is shown in Fig. 11.
  • This anti-rotation device has a disc-shaped Securing element 104, which on the star side of the peripheral edge 22 of the inner cup element 14 is arranged.
  • This securing element 104 is in This embodiment is designed as a flat sheet and can be used as a separate one Be formed component or parts of one of the two cup-shaped inserts 58, 59 his.
  • the securing element 104 is secured against rotation with the outer cup elements 13 and has an opening 105 that the inner cup element 14th penetrates.
  • the inner cup element 14 is in this embodiment cylindrical and has two flattened side 106, 107.
  • the opening 105 of the Fuse element 104 is correspondingly circular with two flattened Sections trained. Through this shape, the angular position of the inner Cup element 14 fixed to the outer cup element 13.
  • the inner cup element 14 shown in FIGS. 12 and 13 has likewise an incision 108 starting from the bottom 26, the underside of which, for example runs perpendicular to the axial direction of the cup element.
  • the guide sleeve in this embodiment the inner cup element is in two parts formed and has a sleeve portion 110 and a second sleeve portion 111. These sleeve sections are inserted into the bore 27 so that their two opposite end faces in the region of the incision 108 a distance have something that corresponds to the width of the incision. Between the two Sleeve sections 110 and 111 and section 108 is the spring element 94 out, whose lower leg 112 runs approximately straight and on the underside 109 of the incision 108 is present.
  • the inner cup element 14 shown in FIGS. 14 and 15 differs of the previously described essentially due to the reduced width of the Incision and by a different design of the spring element.
  • the width of the Notch 112 in this modification is smaller than the diameter of the bore 27 and only penetrates the part of the bottom 26 located above the bore.
  • the spring element 94 is symmetrical and has two legs 113, 114, which encompass the coupling element. A connecting the two legs 113 and 114 Web 115 abuts the partial cam 16.
  • the spring element 94 in this modification is by the interaction with the two locking grooves 41, 42 of the Coupling element essentially raised in the axial direction of the cup element, provided that this movement is not limited by the partial cam 16.
  • the spring elements can be in the inner or in the outer cup element be arranged.
  • the camshaft acts 4 with the partial cams 15, 16 and 17 via three adjacent lever elements 116, 117 and 118 with two gas exchange valves 2 together.
  • the three lever elements 116 to 118 are designed in this embodiment as rocker arms and on one common axis 119 mounted.
  • In the middle lever element 117 is one through hole 120 formed in two aligned blind holes 121st and 122 passes.
  • the blind hole 121 is formed in the lever element 116, the Blind bore 122 is located in lever element 118.
  • In the blind bore 121 is one with a compression spring acted upon piston 52, which acts on the coupling element 38.
  • the two gas exchange valves 2 are in the Fig. 18 shown switching position of the coupling element 38 of the two Partial cams 15 and 17 actuated via the two outer lever elements 116 and 118.
  • the middle lever element 117 is freely movable. Is by pressurization of the piston 55, the coupling element depending on the rotational position of the cam 4 shifted, all three lever elements are analogous to those previously described Embodiments coupled together, so that these together the Follow the stroke of the middle cam with the largest stroke curve.
  • the Switching functions and the interlocks correspond in this embodiment those described above and are therefore not explained again.

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

Claims (19)

  1. Commande de soupape d'un moteur à combustion interne comportant au moins une soupape d'échange des gaz qui est sollicitée par une came (3) avec au moins deux voies de came (15 à 17) présentant différents parcours de course d'un arbre à came (4), comportant un premier élément de transmission de course (13 ; 116, 118) qui coopère d'une part avec une première voie de came et d'autre part avec la tige (10) de la soupe d'échange des gaz, et comportant un deuxième élément de transmission de course (14, 117) qui est disposé à proximité du premier élément et qui coopère avec une deuxième voie de came, les deux éléments de transmission de course étant accouplés entre eux dans une première position de commutation, au moyen d'un élément de couplage (38, 73, 78, 79) déplaçable hydrauliquement, et étant déplaçable indépendamment l'un de l'autre dans une deuxième position de commutation, et l'élément de couplage présentant un contour de verrouillage (41, 42) qui coopère avec un élément de verrouillage (43, 72, 85, 86, 94, 124), l'élément de couplage (38, 73, 78, 79) pouvant être verrouillé par l'élément de verrouillage (43, 72, 85, 86, 94, 124) dans sa deuxième position de commutation, et étant libéré indépendamment de la voie de came, et pouvant être déplacé dans sa première position de commutation, caractérisée en ce que l'élément de couplage (38, 73, 78, 79) présente des nervures de verrouillage (41, 42) en forme de coins, au moyen desquelles et en coopération avec l'élément de verrouillage (43, 72, 85, 86, 94, 124), l'élément de couplage (38, 73, 78, 79) peut être déplacé mécaniquement dans l'une des deux positions de commutation indépendamment de la commande hydraulique.
  2. Commande de soupape selon la revendication 1, caractérisée en ce qu'un élément de palpage (43, 72, 85, 86, 94, 124) palpe un contour de came (46) de l'arbre à came et le transmet à l'élément de verrouillage, de sorte que ce dernier verrouille l'élément de couplage (38, 73, 78, 79) dans une première zone de la voie de came et le libère dans une deuxième zone de la voie de came.
  3. Commande de soupape selon la revendication 1 ou 2, caractérisée en ce que l'élément de palpage (43, 72, 85, 86) est un doigt de palpage qui palpe le contour extérieur de la came (3) et en ce que la came présente dans la zone de palpage du doigt de palpage, un contour de déverrouillage (46) sous la forme d'un relief ou d'un creux.
  4. Commande de soupape selon l'une des revendications précédentes, caractérisée en ce que l'élément de verrouillage (48) est une broche de verrouillage déplaçable longitudinalement, qui s'engage dans le contour de verrouillage (46) sur l'élément de couplage.
  5. Commande de soupape selon l'une des revendications précédentes, caractérisée en ce que l'élément de verrouillage est un élément à ressort (94, 124).
  6. Commande de soupape selon la revendication 5, caractérisée en ce que l'élément à ressort (94) est guidé dans une entaille (91, 108, 112, 123) du deuxième élément de transmission de course.
  7. Commande de soupape selon l'une des revendications précédentes, caractérisée en ce que l'élément de verrouillage est une bille de verrouillage qui s'engage dans le contour de verrouillage (46) sur l'élément de couplage.
  8. Commande de soupape selon l'une des revendications précédentes, caractérisée en ce que le contour de verrouillage (41, 42) sur l'élément de couplage (38, 73, 78, 79) présente des surfaces latérales inclinées.
  9. Commande de soupape selon l'une des revendications précédentes, caractérisée en ce que l'élément de palpage et l'élément de verrouillage sont réalisés d'un seul tenant.
  10. Commande de soupape selon l'une des revendications précédentes, caractérisée en ce que les éléments de transmission de course (13, 14) sont disposés coaxialement l'un par rapport à l'autre et sont construits à la manière d'un poussoir en cloche en deux parties, dont les fonds de cloche (20, 26) sont sollicités par la came, et en ce que l'élément de verrouillage est guidé dans les fonds de cloche.
  11. Commande de soupape selon l'une des revendications précédentes, caractérisée en ce que les éléments de transmission de course sont réalisés en tant qu'éléments à levier (116, 117, 118) (levier d'entraínement ou levier basculant).
  12. Commande de soupape selon l'une des revendications précédentes, caractérisée en ce que pour chaque came (4) trois éléments à levier (116, 117, 118), disposés côte à côte, coopèrent avec la ou les soupape(s) d'échange des gaz (2).
  13. Commande de soupape selon la revendication 12, caractérisée en ce que les deux éléments à levier (116, 118) extérieurs coopèrent avec des voies de came (15, 17) qui présentent chacune le même parcours de course.
  14. Commande de soupape selon l'une des revendications précédentes, caractérisée en ce que l'élément de couplage présente deux contours de verrouillage (41, 42) espacés dans lesquels s'engage l'élément de verrouillage, toujours en fonction de la position de commutation, ce qui fait que l'élément de couplage peut être verrouillé dans les deux positions de commutation.
  15. Commande de soupape selon l'une des revendications précédentes, caractérisée en ce que les éléments de transmission de course présentent des perçages de couplage (27, 24 ; 120, 121, 122) qui sont alignés dans des dispositions de rotation définies de l'arbre à came, et en ce que l'élément de couplage est réalisé en tant que broche cylindrique (38) qui est guidée dans les perçages de couplage.
  16. Commande de soupape selon la revendication 10, caractérisée en ce que l'élément de couplage (38) est guidé dans l'élément de transmission de course disposé à l'intérieur, lorsque la position de commutation n'est pas accouplée.
  17. Commande de soupape selon la revendication 11, caractérisée en ce que l'élément de couplage (78, 79) est constitué de deux éléments coulissants de type piston.
  18. Commande de soupape selon l'une des revendications précédentes, caractérisée en ce que l'élément de couplage (38, 73) est déplaçable sous l'action d'un piston (55) sollicité hydrauliquement, qui est guidé dans une portion des perçages de couplage.
  19. Commande de soupape selon l'une des revendications précédentes, caractérisée en ce que l'élément de couplage présente une zone terminale inclinée ou courbée, sur au moins un côté frontal.
EP96116552A 1995-12-13 1996-10-16 Commande de soupape pour moteur à combustion interne Expired - Lifetime EP0779411B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19546437 1995-12-13
DE19546437 1995-12-13
DE19622174A DE19622174A1 (de) 1995-12-13 1996-06-01 Ventiltrieb einer Brennkraftmaschine
DE19622174 1996-06-01

Publications (2)

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EP0779411A1 EP0779411A1 (fr) 1997-06-18
EP0779411B1 true EP0779411B1 (fr) 2001-05-23

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EP96116552A Expired - Lifetime EP0779411B1 (fr) 1995-12-13 1996-10-16 Commande de soupape pour moteur à combustion interne

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EP (1) EP0779411B1 (fr)
JP (1) JPH09184409A (fr)
KR (1) KR970044042A (fr)
DE (2) DE19622174A1 (fr)

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DE19648141A1 (de) * 1996-11-21 1998-05-28 Schaeffler Waelzlager Ohg Stößel für einen Ventiltrieb einer Brennkraftmaschine
DE19652180A1 (de) * 1996-12-14 1998-06-18 Schaeffler Waelzlager Ohg Stößel für einen Ventiltrieb einer Brennkraftmaschine
DE19717537C1 (de) * 1997-04-25 1998-12-24 Porsche Ag Ventiltrieb einer Brennkraftmaschine
DE19721208A1 (de) * 1997-05-21 1998-11-26 Schaeffler Waelzlager Ohg Nockenfolger eines Ventiltriebs einer Brennkraftmaschine
DE19742777A1 (de) 1997-09-27 1999-04-01 Schaeffler Waelzlager Ohg Stößel für einen Ventiltrieb einer Brennkraftmaschine
DE19744253A1 (de) * 1997-10-07 1999-04-08 Schaeffler Waelzlager Ohg Stößel
DE19801603A1 (de) 1998-01-17 1999-07-22 Schaeffler Waelzlager Ohg Auf unterschiedliche Hübe für wenigstens ein Gaswechselventil schaltbarer Nockenfolger eines Ventiltriebs einer Brennkraftmaschine
DE19930572A1 (de) * 1999-07-02 2001-01-04 Schaeffler Waelzlager Ohg Ventiltrieb einer Brennkraftmaschine
DE10002287A1 (de) 2000-01-20 2001-07-26 Schaeffler Waelzlager Ohg Schaltbarer Flach- oder Rollenstössel
US6854432B2 (en) 2000-04-10 2005-02-15 Honda Giken Kogyo Kabushiki Kaisha Valve gear of internal combustion engine
DE10136353B4 (de) * 2001-07-26 2017-08-17 Volkswagen Ag Ventiltrieb einer Brennkraftmaschine für ein desaktivierbares Gaswechsel-Hubventil
EP1447547B1 (fr) * 2003-02-17 2006-04-19 Ford Global Technologies, LLC Moteur à combustion interne ayant un dispositif de variation de la course des soupapes
DE102004043182A1 (de) * 2004-09-07 2006-03-30 Ina-Schaeffler Kg Schaltbarer Schlepphebel
JP4583229B2 (ja) * 2005-04-19 2010-11-17 本田技研工業株式会社 内燃機関の動弁装置
DE102008028513A1 (de) * 2008-06-16 2009-12-24 Audi Ag Ventilbetrieb für Gaswechselventile einer Brennkraftmaschine mit doppelt abgestützten Nockenträgern
JP2010180805A (ja) * 2009-02-06 2010-08-19 Hitachi Automotive Systems Ltd 内燃機関の弁停止装置及びその製造方法
JP2014152694A (ja) * 2013-02-07 2014-08-25 Toyota Motor Corp 内燃機関の可変動弁装置
CN105041403B (zh) * 2015-08-11 2018-08-21 莫嘉林 汽车发动机缓速系统

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DE3735156A1 (de) 1986-10-16 1988-05-26 Honda Motor Co Ltd Einrichtung zur ventilbetaetigung in einer brennkraftmaschine
EP0515520B2 (fr) 1990-02-16 1998-04-29 Group Lotus Limited Moyen de commande de soupape
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DE4213855A1 (de) * 1992-04-27 1993-10-28 Iav Motor Gmbh Ingenieurgesell Ventiltrieb für veränderbare Öffnungscharakteristik bei Ventilen, vorzugsweise Einlaßventilen, von Brennkraftmaschinen
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DE4405189C2 (de) 1994-02-18 1996-07-11 Porsche Ag Stößel für ein abschaltbares Ventil einer Brennkraftmaschine

Also Published As

Publication number Publication date
DE59606950D1 (de) 2001-06-28
EP0779411A1 (fr) 1997-06-18
JPH09184409A (ja) 1997-07-15
DE19622174A1 (de) 1997-06-26
KR970044042A (ko) 1997-07-26

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