EP0797726B1 - Mecanisme de distribution pour moteur a combustion interne - Google Patents

Mecanisme de distribution pour moteur a combustion interne Download PDF

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Publication number
EP0797726B1
EP0797726B1 EP95940953A EP95940953A EP0797726B1 EP 0797726 B1 EP0797726 B1 EP 0797726B1 EP 95940953 A EP95940953 A EP 95940953A EP 95940953 A EP95940953 A EP 95940953A EP 0797726 B1 EP0797726 B1 EP 0797726B1
Authority
EP
European Patent Office
Prior art keywords
shaft
gear mechanism
valve gear
rotating body
intermediate member
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
EP95940953A
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German (de)
English (en)
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EP0797726A1 (fr
Inventor
Erwin Korostenski
Armin Bertsch
Reiner Walter
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Individual
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Individual
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Publication of EP0797726A1 publication Critical patent/EP0797726A1/fr
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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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34413—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using composite camshafts, e.g. with cams being able to move relative to the camshaft
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/356—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear making the angular relationship oscillate, e.g. non-homokinetic drive
    • 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 train Internal combustion engine and in particular a valve train an internal combustion engine in which a rotating body, preferably a cam, on a shaft, preferably the Camshaft, during the rotation of the shaft cyclically is rotatable, thereby variable valve control to provide.
  • Such a valve train is for example in WO-A-96/23963 described.
  • Adjustment mechanism is shown in Fig. 23 and includes a camshaft 100 with an axis of rotation 500 on which a Cam 200 is stored. Also on camshaft 100 is mounted an inner eccentric 300, on the Axis of rotation 500 eccentric outer surface 320 External eccentric 400 is mounted. The internal eccentric 300 and the outer eccentric 400 are over one Internal eccentric ring gear 340 or one External eccentric ring gear 440 rotatable, making one on one eccentric outer surface of the outer eccentric 400 mounted intermediate link 490 in a plane perpendicular to The axis of rotation 500 is displaceable relative to the camshaft 100 is.
  • the intermediate member 490 is with the cam 200 and Drive shaft 100 coupled.
  • first transmission element 800 rotatable in the Camshaft 100 bearing axial pin 800 with a the axial pin 800 formed of the same material Sliding stone flag 810 in a slide guide a first groove 600 formed in the link 490 is trained.
  • One of the first groove 600 diametrically opposite second groove 700 of the intermediate member 490 is in engagement with a sliding stone flag 910, the same material with a second axial pin 900 is formed, which is rotatable in a bore 110 of the Cam 200 is stored.
  • the rotation of the camshaft 1 is over the first Axial pin 100 through its tab 110 and the first groove 600 transferred to the intermediate link 490 and from there on the second groove 700 and the flag 910 of the second Axial pin 900 on cam 200. Is that Intermediate member 490 in a concentric position Camshaft 100, the cam 200 rotates synchronously the camshaft 100.
  • a generic valve train is still from FR-A-2305589 or known from JP-A-05 118208.
  • the object of the invention is that described above Develop the state of the art in such a way that minimal construction volume the friction between themselves components moving towards each other and thus wear of these components is reduced.
  • a valve train has one Internal combustion engine with an adjustment mechanism a shaft having an axis of rotation, over which the Rotary movement for the valve train initiated in this is, with a rotatably mounted relative to the shaft Rotating body and with a surrounding the shaft Intermediate link, which in the axial direction next to the rotatable rotating body arranged and opposite the shaft is rotatable and with the shaft over a first Slideway and a first transmission element and with the rotating body via a second sliding guide and a second transmission element is drivingly connected.
  • At least one of the transmission elements comprises a radial pin that is substantially perpendicular to the Axis of rotation of the shaft is arranged.
  • a radial pin as a transmission element has the advantage that when force is applied Tipping moment can be reduced, which makes the overall occurring tilting moment is reduced.
  • the first transmission element is a radial pin.
  • the Radial pin in a recess in a sliding block slidably received in a bearing seat of the Intermediate link is pivotally mounted.
  • this Embodiment takes the pivotal movement between the Sliding block and the bearing seat of the intermediate link instead, while the longitudinal displacement between the radial pin and the sliding block takes place. This allows the radial pin be firmly fixed in the shaft.
  • the radial pin can be one cylindrical section and essentially one have rectangular section, the cylindrical Section is inserted into a radial bore of the shaft and the substantially rectangular section in sliding engagement with the recess of the sliding block stands. Between the cylindrical section and the im essential rectangular section of the radial pin can a paragraph may be provided with one on the shaft a positive locking element against migration of the radial pin from the Radial bore forms.
  • the diameter of the cylindrical section is preferably smaller than the larger of the two Cross-sectional edges of the substantially rectangular Section.
  • the sliding block preferably has the outer contour of a cylinder segment flattened on two sides, whereby the two rounded sides of the jacket segments Cylinders are joined together by an end face are connected.
  • the recess is preferably that of the Face opposite side of the sliding block open.
  • the sliding block has two sliding surfaces Sliding contact with two opposite one another Faces of the rectangular section of the radial pin and two shoulders to rest on a third surface of the rectangular section of the radial pin. Between A depression can be formed around the shoulders To facilitate assembly of the radial pin. If the Diameter of the cylindrical section of the radial pin is smaller than at least the larger of the two Cross-sectional edges of the substantially rectangular Section, the cylindrical section of the Radial pin through the recess into the Radial bore of the shaft are introduced.
  • the bearing seat is preferably on the rotating body facing side of the intermediate link open and has two concave side walls, the radius of curvature of which the Side faces of the sliding block correspond, as well as one End face for contact with the end face of the radial pin on. This allows the sliding block in the side Bearing seat can be used.
  • the axial fixation of the rotating body and the Intermediate link on the shaft can be via the radial pin respectively.
  • the second transmission element can be parallel to Axis of rotation mounted in a bore of the rotating body Grip axial pin.
  • the side surfaces of the sliding stone flag can become one or both sides of the axial pin over the circumference of its extend cylindrical shaft so that the Axial pin together with the sliding stone flag an L-shape or has a T-shape. This will make an enlarged one Contact surface of the sliding stone flag and thus one Reduction of the surface pressure to the groove of the Pontic and in the case of a T-shape one symmetrical application of force achieved.
  • the bore of the rotating body in which the axial pin can be stored on the side of the The pontic is turned away, closed and the Shaft can have a longitudinal bore as well as one or more of the longitudinal bore to the outer surface of the shaft have running shaft oil holes.
  • Rotary body can be arranged a rotary body oil hole be that oil from the longitudinal bore of the shaft over the Shaft oil hole and the rotating body oil hole in the Bore for storing the axial pin between these and the closed end of this hole passes through the axial pin by the oil pressure in firm contact with the End wall is pressed in the groove of the intermediate link.
  • a third sliding guide between the rotating body and the Intermediate member provided which is a support between the Rotating body and the intermediate member represents and at the same time a relative movement between the rotating body and the intermediate link in a direction perpendicular to Allows axis of rotation.
  • This third sliding guide is used by the Transfer of the rotational movement generated tilting moment on the Include pontic.
  • the support provided will be the fastest Bearing point between the intermediate link and the External eccentric relieved. Instead, the support is found against this tilting moment between the rotating body and the Intermediate link instead, which is only a minor Have relative speed to each other.
  • the free Tipping moment is about in the valve train according to the invention the large bearing between the rotating body and supported on the shaft, on which also only slight Relative speeds occur and therefore only is lightly loaded. This will make the Total system friction losses significantly reduced. In addition, the holding torque of the external eccentric becomes clear decreased.
  • the third sliding guide can be designed so that in a groove is provided in the rotary body, in which a Intermediate link trained web engages.
  • the groove runs in Circumferential direction of the rotating body, wherein by a Opening is interrupted, through which the Intermediate link with the web can be inserted in the radial direction is.
  • the free Tipping moment at the bearing between the rotating body and Shaft is supported, it is advantageous to use this Bearing point to be executed particularly wide. For this reason the rotating body can move in the direction of the bearing surface the axis of rotation be widened and have dimensions, which are wider than at least a section of the Outer contour of the rotating body.
  • the shaft is preferably a camshaft and the Rotating body a cam for actuating a Gas exchange valve. This makes it extremely compact Device for variable valve control provided.
  • the intermediate link can be designed so that its outer contour in no operating position over the Outer contour of the cam protrudes. This enables the Use of this embodiment in bucket tappet motors.
  • a as Cam-formed rotating body 10 is rotatable on a trained as a camshaft shaft 1, which at Operation of the internal combustion engine, preferably by the Crankshaft of the internal combustion engine (not shown), with half crankshaft speed is rotated.
  • an inner eccentric 91 provided, which is rotatable by a bearing block 92 to a cylinder head 93, which is only shown in a hint is fixed.
  • the outer surface of the inner eccentric 91 is an outer eccentric 90 rotatably mounted.
  • the inner eccentric 91 is over one Internal eccentric ring gear 91A rotatable during the External eccentric 90 through a coaxial to the axis of rotation D.
  • the external eccentric ring gear 90A is rotatable, which with a nose 90B in a groove 90C of the External eccentric engages.
  • an intermediate member 20 which is on an eccentric Outer surface of the outer eccentric 90 is rotatably mounted.
  • the intermediate member 20 is with the camshaft 1 and Cam 10 drivingly connected, so that a rotation of the Camshaft 1 via intermediate member 20 on cam 10 is transmitted. If depending on the position of the External eccentric 90 and the inner eccentric 91 the rotation of the intermediate member 20 concentric with the rotation of the Camshaft 1 runs, the cam 10 rotates synchronously with the camshaft 1. Is by appropriate Displacement of the external eccentric 90 and / or Inner eccentric 91 the intermediate member 20 from his concentric position radially to the camshaft 1 shifted, there is a cyclic one with every revolution Speed increase or speed reduction the speed of rotation of the cam 10 compared to that of the camshaft 1 instead.
  • the drive connection of the camshaft 1 to Intermediate member 20 takes place via a radial pin 40, which in a corresponding radial bore 4 of the camshaft 1 is introduced.
  • the camshaft 1 has a Longitudinal bore 2 and the radial bore 4 has a depth that is greater than the sum of the camshaft radius and the radius of the longitudinal bore 2.
  • the radial pin 40 has a cylindrical section 42 which is fully inserted into the camshaft 1 and a generally rectangular section 43 which protrudes from the camshaft 1. Between the cylindrical portion 42 and the rectangular portion 43 a shoulder 41 is formed. By selection suitable fit dimensions between the cylindrical part 42 of the radial pin 40 and the radial bore 4 and one corresponding stop at the closed end of the Radial bore 4, the radial pin 40 is fixed in the Camshaft 1 fixed. As an additional positive The inner eccentric 91 partially covers the fuse Radial bore 4, which due to the shoulder 41 a additional protection against migration of the Radial pin 40 is reached from the bore 4.
  • the rectangular section 43 is covered by a recess 51 a sliding block 50 slidably includes.
  • the sliding block 50 has the shape of a flattened on two sides Cylinder segment, with the two rounded Side surfaces 52, 53 are jacket segments of a cylinder, which are connected to one another by an end face 54.
  • the recess 51 is that of the end face 54 opposite side open and has two Sliding surfaces 55, 56 for sliding contact with two each other opposite faces of the rectangular portion 43 the radial pin 40 and two shoulders 57, 58 to the system to a third surface of the rectangular section 43 of the Radial pin 40 on.
  • the rectangular section 43 of the radial pin 40 and the Recess 51 of the sliding block 50 are in terms of their Dimensions matched so that the sliding block 50 can slide over the rectangular section 43.
  • the intermediate member 20 has a bearing seat 22 which the side facing the cam 10 is open.
  • the to the open side adjacent concave side walls 25, 26 of the Bearing seat 22 are the radius of the side surfaces 52, 53 of the sliding block 50 formed accordingly, so that the through the open side of the bearing seat 22 into the bearing seat 22 insertable sliding block 50 opposite the intermediate link 20 can be pivoted.
  • An end face 27 of the Bearing seat 22 serves to abut the sliding block 50 recess 27A provided in the end face 27 allows the insertion of the radial pin 40 in the Assembly.
  • axial pin 70 On the side of the bearing seat 22 opposite Intermediate member 20 has a groove 23 into which one Sliding stone flag 71 engages with the same material an axial pin 70 is formed.
  • the axial pin 70 is rotatable in a closed at one end and parallel to the axis of rotation D extending bore 13 in the cam 10 stored.
  • a rotating body oil hole provided in the cam 10 19 is at least temporarily in overlap with a shaft oil bore 3 of the camshaft 1 and opens with its opposite end in the bore 13 in one Area between that of the sliding stone flag 71st opposite end of the axial pin 70 and the closed End of the bore 13.
  • Camshaft 1 Through an appropriate groove (not shown) of the cam 10 in the area of the bearing surface Camshaft 1 can be ensured that the Rotary body oil bore 19 over the entire range of rotation Cam 10 opposite the camshaft 1 in connection with the shaft oil hole 3 is located. That way ensures that a in the longitudinal bore 2 Camshaft 1 prevailing oil pressure on the front side of the axial pin 70 is applied and the Sliding flag 71 against the end wall 24 of the groove 23 of the Intermediate member 20 presses to the game between the Sliding stone flag 71 and the groove 23 when changing the system dampen.
  • the diameter of the pin of the axial pin 70 is preferably smaller than the width of the Sliding stone flag 21 or the groove 23.
  • the length the pin of the axial pin 70 is preferably larger than half the width of the cam 1.
  • the intermediate member 20 has that end the open side of the groove 23 and the open side of the Bearing seat 22 has, via a web 21 which in runs essentially in the circumferential direction and through the groove 23 and the open side of the bearing seat 22 interrupted becomes.
  • the web 21 can be inserted radially into a Groove 11 are introduced, which on the intermediate member 20th facing side of the cam 10 is formed.
  • the groove 11 runs essentially in the circumferential direction and will interrupted by an opening 12 which the radial Inserting the web 21 allows.
  • the depth of the groove 11 and the strength of the web 21 are so on top of each other matched that a tilting moment of the intermediate member 20th can be caught and at the same time over one radial displacement and a certain extent Rotation of the intermediate member 20 relative to the cam 10 is possible.
  • the groove 11 of the cam 10 is on the intermediate member 20 facing side by an essentially in Limited circumferential web 17, the is also interrupted by the opening 12. To the Enlarge the contact surface to absorb the tilting moment, this web 17 gives way in a central region 18 in the region the line D-D in Fig. 3 from the circumferential direction. In this area is the web 17 with respect to the bottom of the Groove 11 increased, for example, in that in the Middle region 18 the upper edges of the web 17 on both Sides of the bore for the camshaft 1 parallel to each other.
  • the bottom is that on the intermediate member 20 groove 28 formed by the web 21 in one corresponding central region 29 opposite the upper edge of the web 21 lowered, for example in that this central region 29 the bottom portions of the groove 28 have a changed radius of curvature.
  • the axial pin 70 is in with its cylindrical shaft the bore 13 of the cam 10 is inserted.
  • the sliding block 50 is in from the open side of the bearing seat 22 inserted this.
  • the intermediate member 20 is of the Bore 13 and thus the cam tip opposite Side of the cam 10 forth with its web 21 in the groove 11 introduced.
  • the sliding stone flag 71 enters Groove 23.
  • the intermediate member 20 is in this position and the cam 10 axially fixed to each other.
  • the thus manufactured unit from intermediate link and cam is on the camshaft is pushed on and the recess of the Sliding block 50 with the radial bore 4 in the camshaft 1 overlapped.
  • the radial pin 40 is through the recess 51 is inserted into the radial bore 4.
  • Fig. 21 shows a third embodiment in which for two cams 10A, 10B, a common inner eccentric 91 is provided. This is on both sides of the An adjusting unit is provided for the camshaft bearing, so that Subsequent insertion of the eccentric is not possible is. For this reason are local to the eccentrics Recesses (not shown) provided around the Radial pin with complete pre-assembly unit made of cams 10A, 10B, the two intermediate links 20 and the eccentrics through the recesses 51 in the respective sliding blocks 50 in the corresponding radial bores 4 of the camshaft 1 to be able to introduce.

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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)

Claims (18)

  1. Mécanisme d'entraínement pour soupapes d'un moteur à combustion interne
    avec un arbre (1) comprenant un axe de rotation (D), la rotation pour le mécanisme d'entraínement pour soupapes étant introduite dans le même à travers le susdit arbre,
    avec un corps de rotation (10) logé de façon rotative par rapport à l'arbre (1) et
    avec un élément intermédiaire (20) entourant l'arbre (1) cet élément étant arrangé en direction axiale a côté du corps de rotation rotatif (10), rotatif par rapport à l'arbre (1) et lié de façon entraínante avec l'arbre (1) par un premier guidage à glissement (15) et un premier élément de transmission (40,50) et avec le corps de rotation (10) par un deuxième guidage à glissement (16) et un deuxième élément de transmission (70), caractérisé en ce qu'au moins un élément de transmission (40,50) comprend une tige radiale (40) disposée de façon essentiellement verticale par rapport à l'axe de rotation (D) de l'arbre (1).
  2. Mécanisme d'entraínement pour soupapes selon la revendication 1, caractérisé en ce que le premier élément de transmission (40) est contenu de façon glissante sous forme de tige radiale (40) dans un évidement (51) d'une tête coulissante (50) étant logée de façon pivotable dans un logement (22) de l'élément intermédiaire (20).
  3. Mécanisme d'entraínement pour soupapes selon la revendication 2, caractérisé en ce que la tige radiale (40) comporte une portion cylindrique (42) et une portion essentiellement rectangulaire (43), la portion cylindrique (42) étant insérée dans un alésage radial (4) de l'arbre (1) et la portion essentiellement rectangulaire (43) s'engageant de façon glissante dans l'évidement (51) de la tête coulissante (50).
  4. Mécanisme d'entraínement pour soupapes selon la revendication 3, caractérisé en ce qu'entre la portion cylindrique (42) et la portion essentiellement rectangulaire (43) de la tige radiale (40) est prévu un gradin (41) qui forme avec un élément (91) à faire glisser sur l'arbre (1) une sécurité de blocage contre une excursion de la tige radiale (40) hors de l'alésage radial (4).
  5. Mécanisme d'entraínement pour soupapes selon la revendication 3 ou 4, caractérisé en ce que le diamètre de la portion cylindrique (42) est inférieur au plus long des deux côtés de la coupe transversale (44,45) de la portion essentiellement rectangulaire (43).
  6. Mécanisme d'entraínement pour soupapes selon une des revendications précédentes, caractérisé en ce que la tête coulissante (50) a le contour extérieur d'un segment de cylindre aplati sur deux côtés, les deux parois arrondies (52,53) étant les segments d'enveloppe d'un cylindre reliés entre eux par une face (54).
  7. Mécanisme d'entraínement pour soupapes selon la revendication 6, caractérisé en ce que l'évidement (51) est ouvert vers le côté de la tête coulissante (50) qui se trouve vis-à-vis de la face (54).
  8. Mécanisme d'entraínement pour soupapes selon la revendication 7, caractérisé en ce que la tête coulissante (50) comporte deux surfaces de glissement (55,56) destinées au contact glissant avec deux surfaces opposées l'une à l'autre de la portion rectangulaire (43) de la tige radiale (40) et deux épaules (57,58) destinées au contact avec une troisième surface de la portion rectangulaire (43) de la tige radiale (40).
  9. Mécanisme d'entraínement pour soupapes selon la revendication 8, caractérisé en ce qu'entre les épaules (57,58) est formé un creux (59) pour faciliter le montage de la tige radiale (40).
  10. Mécanisme d'entraínement pour soupapes selon une des revendications précédentes, caractérisé en ce que le logement (22) est ouvert du côté orienté vers le corps de rotation (10) de l'élément intermédiaire (20) et qu'il comporte deux parois concaves (25,26), dont les rayons de courbure correspondent à celui des parois (52,53) de la tête coulissante (50), et une face (27) destinée à entrer en contact avec la face (54) de la tige radiale (40).
  11. Mécanisme d'entraínement pour soupapes selon une des revendications précédentes, caractérisé en ce que le fixage axial du corps de rotation (10) et de l'élément intermédiaire (20) sur l'arbre (1) se fait par la tige radiale (40).
  12. Mécanisme d'entraínement pour soupapes selon une des revendications précédentes, caractérisé en ce que le deuxième élément de transmission (70) comprend une tige axiale (70) logée parallèlement à l'axe de rotation (D) dans un alésage (13) du corps de rotation (10).
  13. Mécanisme d'entraínement pour soupapes selon la revendication 12, caractérisé en ce que l'une des extrémités de la tige axiale (70) est pourvue d'une queue (71) de la tête coulissante présentant deux parois parallèles et qui s'engage dans une rainure (23) de l'élément intermédiaire (20), les parois s'étendant en direction de la rainure (23) vers un ou l'autre des deux côtés de la tige axiale (70) outre sa circonférence, de manière que la tige axiale (70) présente avec la queue (71) de la tête coulissante une forme d'L ou T.
  14. Mécanisme d'entraínement pour soupapes selon la revendication 12 ou 13, caractérisé en ce que l'alésage (13) dans le corps de rotation (10) est fermé du côté qui n'est pas orienté vers l'élément intermédiaire (20), que l'arbre (1) comporte un alésage longitudinal (2) et au moins un alésage de passage d'huile pour l'arbre (3) s'étendant de l'alésage longitudinal (2) à la surface extérieure de l'arbre (1) et que le corps de rotation (10) comporte un alésage de passage d'huile pour le corps de rotation (19), à travers lequel de l'huile provenant de l'alésage longitudinal (2) passant à travers l'alésage de passage d'huile pour l'arbre (3) peut arriver dans l'alésage (13) entre son extrémité fermée et la tige axiale (70), de sorte que la tige axiale (70) est pressée en fort contact avec la face (24) de la rainure (23).
  15. Mécanisme d'entraínement pour soupapes selon une des revendications précédentes, caractérisé en ce que l'élément intermédiaire (20) est logé de façon rotative sur un excentrique périphérique (90) qui est logé de façon rotative sur une surface excentrique périphérique d'un excentrique intérieur (91) rotatif sur l'arbre (1).
  16. Mécanisme d'entraínement pour soupapes selon la revendication 15, caractérisé en ce que pour deux corps de rotation adjacents (10A, 10B) est prévu un excentrique intérieur commun (91).
  17. Mécanisme d'entraínement pour soupapes selon une des revendications précédentes, caractérisé en ce qu'entre le corps de rotation (10) et l'élément intermédiaire (20) est prévu un troisième guidage à glissement (30) formant un appui entre le corps de rotation (10) et l'élément intermédiaire (20) qui rend en même temps possible un mouvement relatif entre le corps de rotation (10) et l'élément intermédiaire (20) dans une direction perpendiculaire à l'axe de rotation (D).
  18. Mécanisme d'entraínement pour soupapes selon une des revendications précédentes, caractérisé en ce que l'arbre (1) est un arbre à cames et le corps de rotation (10) une came pour actionner une soupape d'échange du gaz.
EP95940953A 1994-12-13 1995-12-12 Mecanisme de distribution pour moteur a combustion interne Expired - Lifetime EP0797726B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE4444289 1994-12-13
DE4444289 1994-12-13
DE19529346 1995-08-09
DE19529346 1995-08-09
PCT/DE1995/001783 WO1996018807A1 (fr) 1994-12-13 1995-12-12 Mecanisme de distribution pour moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP0797726A1 EP0797726A1 (fr) 1997-10-01
EP0797726B1 true EP0797726B1 (fr) 1998-05-27

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EP95940953A Expired - Lifetime EP0797726B1 (fr) 1994-12-13 1995-12-12 Mecanisme de distribution pour moteur a combustion interne

Country Status (7)

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US (1) US5884592A (fr)
EP (1) EP0797726B1 (fr)
AT (1) ATE166698T1 (fr)
AU (1) AU4252496A (fr)
DE (2) DE19581405D2 (fr)
ES (1) ES2119503T3 (fr)
WO (1) WO1996018807A1 (fr)

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WO1996018807A1 (fr) 1996-06-20
EP0797726A1 (fr) 1997-10-01
DE59502370D1 (de) 1998-07-02
AU4252496A (en) 1996-07-03
US5884592A (en) 1999-03-23
ATE166698T1 (de) 1998-06-15
ES2119503T3 (es) 1998-10-01
DE19581405D2 (de) 1998-02-05

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