EP2286067B1 - Système d'arbre à cames ajustable - Google Patents

Système d'arbre à cames ajustable Download PDF

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Publication number
EP2286067B1
EP2286067B1 EP09753605A EP09753605A EP2286067B1 EP 2286067 B1 EP2286067 B1 EP 2286067B1 EP 09753605 A EP09753605 A EP 09753605A EP 09753605 A EP09753605 A EP 09753605A EP 2286067 B1 EP2286067 B1 EP 2286067B1
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EP
European Patent Office
Prior art keywords
inner shaft
connecting element
cam
shaft
head part
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.)
Active
Application number
EP09753605A
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German (de)
English (en)
Other versions
EP2286067A1 (fr
Inventor
Guido Scherzinger
Bernd Mann
Gunther Martin Lugauer
Mario Wolfinger
Frank Altag
Peter Wiesner
Jürgen MEUSEL
Manfred Muster
Alex Meier
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.)
Thyssenkrupp Dynamic Components Teccenter AG
Original Assignee
ThyssenKrupp Presta TecCenter AG
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Publication of EP2286067A1 publication Critical patent/EP2286067A1/fr
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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
    • F01L1/047—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
    • F01L1/34—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
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0471—Assembled camshafts
    • F01L2001/0473—Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod

Definitions

  • the invention relates to a camshaft arrangement for a drive, in particular for a motor vehicle engine.
  • the camshaft assembly comprises two coaxially arranged waves, wherein a hollow outer shaft and an inner shaft are arranged rotatable relative to each other. Both shafts each carry a plurality of cams, wherein the outer shaft cams carried by the outer shaft are non-rotatably mounted on the outer shaft, while the inner shaft cams carried by the inner shaft are non-rotatably mounted on the inner shaft. If the inner shaft and outer shaft are rotated against each other, an adjustment of the cams to each other.
  • Such adjustable camshaft arrangements are increasingly used in valve-controlled internal combustion engines for selectively influencing the control times of the valves of the engine in terms of power and torque development, fuel consumption and exhaust emission application.
  • These camshaft arrangements are, for example, built-up camshaft systems with an outer shaft and an inner shaft arranged coaxially therein. The two shafts are rotatable relative to each other by means of an adjusting device. On the outer shaft alternately fixed to the outer shaft and connected to the outer shaft rotatably mounted cam elements are arranged. The rotatably mounted cam elements are fixedly attached to the inner shaft, but rotatable by a defined circumferential angle relative to the outer shaft.
  • the rotation of the inner shaft to the outer shaft for example, by means of a Phaser, which allows an adjustment of the outer shaft fixedly connected to the outer shaft cam to the inner shaft fixedly connected inner shaft cam or vice versa, so as to achieve a phase shift of the valve timing.
  • these cams and the inner shaft usually have holes into which corresponding connecting elements are introduced. These can be pins, bolts or screws.
  • the cam elements can be designed accordingly to allow the insertion of a connecting element.
  • German Offenlegungsschrift discloses DE 197 57 504 A1
  • a camshaft with such a connecting element in the form of a cylindrical pin.
  • the cylinder pin is press-fitted into a through hole in the inner shaft and with a clearance fit in the associated cam.
  • the cam has for this purpose an outwardly cylindrical region in which there is a bore, in which the cylinder pin is introduced. Through the cylindrical portion, the bore should be routed away from the contact surface of the cam so as to achieve a continuous contact surface of the cam with the outer shaft.
  • a camshaft with mutually rotatable cam in which a connecting element is made in two parts.
  • a first part of the connecting element is hollow and protrudes into a radial bore in the inner shaft.
  • a second connecting part is inserted from the other side into the hollow first connecting part so that it widens and a tight fit is produced.
  • the two connecting parts may for example be designed as a screw with complementary threaded hole.
  • German patent DE 28 22 147 C3 further discloses a camshaft assembly, wherein the connection between the inner shaft and cam via a driver, which is fastened with a screw on the inner shaft.
  • the outer shaft has a recess for the passage of the driver.
  • the driver further protrudes into an inner groove, which is located at the joint diameter of the associated cam. The cam is pushed with the groove from the side on the driver and secured on the right and left with rings in its axial position.
  • connection between the inner shaft cam and the inner shaft is designed as a fixed connection due to the camshaft alternating load
  • a press fit of the connecting elements used in both cam and in the inner shaft is expediently used.
  • This has the disadvantage, in particular in the case of the known connecting elements with a constant cross section, that the cross section of the connecting element required for achieving the interference fit must be joined over a plurality of component bores in the cam and inner shaft.
  • an undefined influence on the press coverage and thus the safety of the press connection occur.
  • such joint connections may not have sufficient bond strength.
  • the object of the invention is therefore to provide a built camshaft assembly which is easy to add and provides a secure and sufficient strength having connection between the inner shaft and inner shaft cam.
  • the camshaft assembly according to the preamble of claim 1 is characterized according to the invention in that the respective connecting element is inserted into a receptacle in the inner shaft such that a part of the connecting element protrudes from the receptacle, and that the protruding part is at least partially introduced into a recess , which is located at the joint diameter of the respective inner shaft cam.
  • this recess is open towards at least one end face of the inner-shaft cam, and the protruding part has at least two opposite side surfaces, which bear tightly against two corresponding inner surfaces of the recess of the respective inner shaft cam.
  • the connecting element is a feather key
  • the receptacle in the inner shaft is designed as a feather key receptacle.
  • the connecting element has a shaft and a head part, wherein the shaft is introduced into a receptacle in the inner shaft, while the head part at least partially introduced into a recess which is located at the joint diameter of the respective inner shaft cam.
  • this recess is open towards at least one end face of the inner shaft cam
  • the head part has at least two opposite side surfaces, which bear tightly against two corresponding inner surfaces of the recess of the respective inner shaft cam.
  • the connecting element may have a shaft and a head part, wherein the shaft is introduced with a tight fit in the receptacle, while the head part is at least a part of the protruding part of the connecting element.
  • the head part of the connecting element is completely outside the outer shaft.
  • a can Head part only partially in the recess in the respective inner shaft cam and partially in the recess in the outer shaft.
  • the head part may also be partially in the receptacle in the inner shaft, extending through the recess in the outer shaft and then project into the recess in the inner shaft cam.
  • the inner shaft may have as receiving a stepped bore into which the head part of the connecting element partially protrudes, while the lower portion of the bore receives the shank of the connecting element.
  • This stepped bore is designed, for example, as a stepped cylindrical bore with two diameters. The larger, outer diameter accommodates a part of the head part of the connecting element.
  • the section of the head part arranged in this widened part of the stepped bore is adapted to the diameter of the widened region of the stepped bore, so that a cylindrical head part has a larger cross section in this region.
  • a stepped bore can be provided as a receptacle in the inner shaft and a stepped recess.
  • this stepped recess has a cylindrical portion in which the shank of the interference fit member is disposed and a non-cylindrical portion which receives the non-cylindrical head portion. Due to the non-cylindrical shape is advantageously achieved that a positionally accurate alignment of the head portion is made possible relative to the longitudinal axis of the camshaft assembly, so that the inner shaft cam can be added exactly in the correct desired position.
  • the shaft of the connecting element can be cylindrical and easily inserted into the cylindrical portion of the stepped recess.
  • the shaft of the connecting element can extend through the body of the inner shaft through into a second recess in the outer shaft.
  • An inner shaft cam can also be connected by two opposing connecting elements with the inner shaft such that a torque transmission is ensured.
  • the shafts of two connecting elements can be introduced into a common receptacle in the inner shaft.
  • the recess for the passage of the connecting element through the outer shaft extends over a portion of the circumference of the outer shaft, that a movement of the connecting element and thus the inner shaft relative to the outer shaft by an adjustment angle ⁇ is possible.
  • the head part of a connecting element may be formed at right angles to the shaft part of the connecting element. Further, the two side surfaces of the head portion and the two inner surfaces of the recess may each be parallel or conical to each other to facilitate the insertion of the connecting part into the recess or the sliding of the inner shaft cam on the head part and to produce a press fit.
  • the two side surfaces of the head part and / or the two inner surfaces of the recess in the inner shaft cam may also have a profiled surface.
  • the recess in the inner shaft cam may be formed in both embodiments of the invention as extending over the entire width of the inner shaft cam groove.
  • this recess is preferably located centrally below the elevation of the inner shaft cam, and the connecting element is preferably formed as a one-piece component.
  • An advantage of the first embodiment of the invention, in which a key is used as a connecting element, is that keyways are inexpensive mass components that are available at any time.
  • the feather key connection technology is well mastered in terms of manufacturing technology.
  • the total cam width, i. the cam thickness in the axial direction, the inner shaft cam for the formation of the interference fit between feather key and inner shaft cam are utilized, whereby a particularly large joint surface for the formation of the press connection between inner shaft cam and connecting element is provided.
  • This causes a particularly strong connection, which in turn allows the radial height of the inner shaft cam can be minimized, allowing a space and weight savings.
  • This embodiment of the camshaft arrangement according to the invention with feather key can thus be used particularly advantageously for smaller car camshafts.
  • Another advantage of the invention and in particular the second embodiment of the camshaft assembly according to the invention is that the cross section of the connecting element for the required tight fit of the connection between the connecting element and inner shaft or between the connecting element and inner shaft cam does not have to be joined over the entire connecting element. Rather, a tight fit for the connection between the connecting element and inner shaft cam is added over the cross section of the shank for the connection between the connecting element and inner shaft and separated from it via the side surfaces of the head part. This leads to an increased safety of the respective fixed seats.
  • an inner shaft cam is easy to connect to the inner shaft by first the connecting element is introduced into the inner shaft and then the inner shaft cam is pushed from the side on the head part of the connecting element.
  • FIG. 1 schematically an embodiment of a generic camshaft assembly 10 is shown, in which an inner shaft 30 is disposed coaxially in an outer shaft 20, wherein the shaft body are shown shortened.
  • the two shafts are rotatably supported by bearings, also not shown to each other.
  • the adjustment of the two shafts to each other by a twist angle ⁇ can be done for example by an adjusting device, also not shown in the form of a phase adjuster.
  • the inner shaft may be designed as a solid or hollow shaft, wherein in the embodiment of the Figures 1-8 a full wave was chosen.
  • outer shaft cam 21 On the outer surface of the outer shaft 20 a plurality of outer shaft cam 21 are non-rotatably mounted.
  • the attachment of these external shaft cam elements can be done in a known manner, for example by shrinking, wherein a press fit is generated.
  • the joint diameter of the cam is selected so that it is less than the outer diameter of the outer shaft at ambient temperature by a certain "overlap". If the cam element is heated, the inner diameter widens and the cam element can be threaded onto the outer shaft and positioned.
  • the surface of the outer shaft is previously processed or treated in the region of the cam. For example, a profiling can be provided.
  • the outer shaft can be additionally cooled so as to achieve a reduction in the diameter of the outer shaft. Also intermediate elements such as sockets can optionally be provided between the outer shaft and the respective cam member. Upon cooling of the cam member shrinking of the cam on the shaft, wherein the overlap prevents movement of the cam on the outer shaft.
  • any suitable method can be used for the rotationally fixed attachment of the cam 21 on the outer shaft 20.
  • the outer shaft cams on the outer shaft to be welded, or in the areas in which the cams are to be attached, are created by rolling tools tools produced by material displacement beads or webs.
  • the cams are provided for example with a chamfered inner recess and are pushed with this recess over the beads. These are thereby deformed in the outer region and thus squeezed into the recess, whereby the cam is positively and non-positively held on the outer shaft.
  • the outer shaft 20 also carries a plurality of inner shaft cam 31, which are rotatably mounted on the outer shaft, but rotatably connected to the inner shaft 30.
  • inner shaft cam members 31 are rotatably mounted on the outer shaft, but rotatably connected to the inner shaft 30.
  • clearance is provided between the inner diameter of the inner shaft cam members 31 and the outer diameter of the outer shaft 20 to permit rotation of the inner shaft cams 31 about the longitudinal axis of the cam assembly.
  • the inner shaft cams 31 are fixedly connected via a pin-shaped connecting element with the inner shaft 30, as shown schematically in FIG Fig. 1 is shown.
  • the connecting element preferably comprises a shaft 41 and a head part 42.
  • the shaft 41 of the connecting element is press-fitted into a bore in the inner shaft 30, while the head part is press-fitted into a groove in the inner shaft cam element 31.
  • Between the bore and the shaft 41, or between the groove and the head part 42 is a corresponding dimensional overlap in order to ensure a tight fit.
  • the shape of the head part 42 is adapted to the shape of the groove 32 and vice versa. Both fixed seats are independent of each other.
  • Fig. 2 shows a longitudinal section through an embodiment of the camshaft assembly according to the invention with a continuous connecting element 40th
  • the connecting element of shaft 41 and head part 42 is preferably formed in one piece.
  • a shaft part 41 and a head part 42 can also be joined together to form a two-piece connecting element.
  • This connection can be made for example via a screw or pin connection.
  • the shaft 41 may have a circular, rectangular or other geometric shaft cross-section have, which is adapted to the cross section of the associated receptacle in the inner shaft 30.
  • a round shaft cross-section for example, has the advantage that the shaft 41 and the associated bore 37 in the inner shaft 30 can be made simpler than with other shaft cross-sections.
  • the head part 42 is preferably formed at right angles to the shaft 41 and may for example be cuboid.
  • the connecting element 40 is thus preferably enlarged by the head part upwards.
  • the head part is smaller than the shaft and, for example, mounted as a cuboid on the upper surface of a pin.
  • the head part 42 always has at least two side surfaces 43 and 44 (see FIG. Fig. 5 ), which run parallel or conical to each other. These side surfaces 43 and 44 of the head part 42 may have a profiling.
  • the side surfaces 43 and 44 of the head portion 42 of the connecting element 40 are snugly against the inner surfaces 34 and 35 of the groove 32 so as to establish a firm connection (see. Fig. 5 )
  • the shank 41 has a round cross section, while the head part 42 formed at right angles to this pin is cuboid and sits on the shank end.
  • the shaft 41 of the connecting element 40 is inserted in the assembled state of the assembled camshaft assembly 10 in a preferably radial receptacle 37 in the inner shaft 30.
  • This receptacle 37 is, for example, a round bore, which is introduced radially into the material of the inner shaft 30.
  • the round shaft 41 of the connecting element 40 is preferably inserted with a press fit into this bore 37.
  • a recess 50 is provided in the outer shaft 20 to allow the connecting element 40 to project from the inner shaft 30 to the inner shaft cam element 31 to allow.
  • the connecting element 40 is guided through the recess 50 and the head part 42 of the connecting element is inserted into a recess 32 at the joint diameter of the inner shaft cam 31.
  • the recess 32 is preferably a groove which extends in the direction of the axis of the camshaft assembly 10 and is open towards at least one end face of the inner shaft cam 31.
  • a through-groove 32 which is easier to manufacture and has two parallel or conically tapering inner surfaces 34 and 35 is provided. These inner surfaces may be provided with a profiling, like the side surfaces of the head part 42 of the connecting element 40.
  • the groove 32 is preferably located centrally below the elevation 36 of the cam 31. However, it can also be arranged offset to this, if the material thickness of the cam allows this.
  • the shaft 41 is inserted in each case a connecting element 40 with tight fit in the associated bore 37 in the inner shaft.
  • the associated head part 42 is aligned in the direction of the camshaft axis, that an inner shaft cam 31 is threaded onto the outer shaft 20 and pushed with its groove 32 from the side to the projecting beyond the outer shaft 20 head portion 42 and joined with interference fit into the groove 32 can.
  • This is in Fig. 3 represented, wherein the mechanical joining process can be supplemented by conventional joining methods such as shrinking. If the side surfaces 43 and 44 of the head part 42 and the inner surfaces 34 and 35 of the groove 32 taper conically, the inner shaft cam 31 is pushed over the head part so that the shape of the head part 40 is congruent with the shape of the groove 32.
  • the connecting element 40 is a continuous component which projects through a through hole in the inner shaft 30 through into a second recess 50 'in the outer shaft.
  • the two recesses 50 and 50 'in the outer shaft 20 a rotation of the inner shaft 30 within the Enable external shaft.
  • the recesses 50 and 50 ' limit a maximum possible angle of rotation ⁇ of the inner shaft 30 to the outer shaft 20 and vice versa.
  • Fig. 5 does not protrude the connecting element 40 through a through hole in the inner shaft 30 through into a recess 50 in the outer shaft 20, but it is a shorter connecting pin which is inserted into a blind hole. In this case, only one recess 50 in the outer shaft 20 is required for a rotation of the inner shaft 30 to the outer shaft 20.
  • the connecting element 40 can have any length and, in a further exemplary embodiment, for example, can also project completely through the inner shaft 30, but not into the outer shaft 20.
  • Fig. 6 is another embodiment of the invention shown in which two connecting elements 40 and 40 'are used, which are inserted from opposite sides into a through hole 37 in the inner shaft 30.
  • the inner shaft cam member 31 has two likewise opposite grooves 32 and 33, in which the head parts of the two connecting elements are pushed.
  • two recesses 50 and 50 'are provided in which the two connecting elements can be moved with rotation of the inner shaft to the outer shaft with play.
  • an inner shaft cam element has a sufficient hub wall thickness in the base circle region.
  • the head part of the connecting element below the cam lobe 36 preferably projects further into the material of the inner shaft cam 31 than the head part of the opposite connecting element.
  • both head parts can be connected, for example by screw or pin connections with the shaft, or the shaft is integrally formed with a head part, while the opposite head part is connected by inserting the shaft into the bore of the inner shaft with the shaft.
  • Fig. 7 is a camshaft arrangement shown, in which a rotation of the inner shaft 30 is carried out relative to the outer shaft 20.
  • the connecting members 40 and 40 'of the associated inner shaft cam 31 is taken so that it rotates about the outer shaft 20 on which it is mounted with play.
  • Between the bottom of the head portion of a connecting element and the outer surface of the outer shaft is thus preferably a defined game before.
  • the underside of the head part can be adapted to the outer contour of the outer shaft 20 and, for example, slightly curved concave executed.
  • the head portion 42 of a connecting element 40 is not completely outside the outer shaft, but is partially disposed in the recess 50 or 50 'within the outer shaft.
  • This embodiment has, for example, the advantage that no defined clearance between the underside of the head part and the outer surface of the outer shaft has to be set.
  • the connecting element 40 (and / or 40 ') only has to be introduced into the inner shaft so far that the groove 32 of an inner shaft cam element 31 can be joined over the region of the head part which protrudes from the outer shaft.
  • This embodiment may be chosen for any forms of fasteners and is not limited to those in Figs Fig. 8 illustrated embodiment limited with two opposite connecting elements.
  • bore 37 may also be designed as a single-sided or double stepped bore, and the head part may partially protrude into the stepped bore. This embodiment is in Fig. 8 but not shown.
  • a connecting element can also be formed by a continuous connecting pin with a quadrangular cross-section, the cross-sectional shape of which does not change over the length.
  • the pin has a lower shaft region, which is introduced into a recess in the inner shaft 30.
  • the dimensions of the upper head area are chosen so that the groove 32 of an inner shaft cam 31 can be pushed from the side over the head area.
  • the connecting pin is also set a tight fit, which can be ensured by a suitable dimensional overlap between the groove of the inner shaft cam and the head area.
  • the side surfaces of the connecting element may be profiled in the head region in order to improve the tight fit with the inner shaft cam element 31.
  • a connecting element of a shaft and a rectangularly shaped head portion may be more advantageous, since the shape and dimensions of the shaft can be chosen so that it can be easily introduced into a recess in the inner shaft, while the shape and the dimensions of the head part can be adapted to the requirements for receiving in the groove of a réelleweHen cam.
  • another shape may be advantageous for the shaft than for the head part of a connecting element.
  • FIG. 9 and Fig. 10 Another embodiment of the invention is in Fig. 9 and Fig. 10 shown, in which a connecting element is designed as a key 60 which is inserted into a keyway in the inner shaft 30.
  • the side surfaces of the key 60 are also tight against the lateral inner surfaces of the groove 32 in the inner shaft cam 31 at.
  • the key 60 extends at least over the entire length of the groove 32.
  • the side surfaces of the key can be parallel or conical to each other. Furthermore, these side surfaces of the key 60 can be made profiled.
  • a further key 61 may be provided, which is introduced into a second keyway 37 'in the inner shaft, as in Fig. 10 is shown.
  • both feather keys are designed differently, so that the feather key 60 below the elevation 36 of the inner shaft cam 31 is higher than the opposite key 61.
  • the groove 37 'on the opposite side is made flatter and the feather key 61 protrudes to a lesser extent in the material of the inner shaft cam 31.
  • the recess 32 may be provided in the inner shaft cam 31 with support points, which limit a radial movement of the respective connecting element, if such a radial movement occurs undesirable.
  • these support points can also be located on the upper side of the respective connecting element

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

Claims (17)

  1. Système d'arbres à cames pour un dispositif d'entraînement, en particulier pour un moteur de véhicule automobile, qui comprend deux arbres (20, 30), disposés coaxialement l'un par rapport à l'autre, et dans lequel un arbre extérieur creux (20) et un arbre intérieur (30) sont agencés de sorte à pouvoir tourner l'un par rapport à l'autre, les deux arbres (20, 30) portant chacun plusieurs cames (21; 22, 31), sachant que les cames (21, 22) portées par l'arbre extérieur (20) sont montées solidaires en rotation sur l'arbre extérieur (20), tandis que les cames (31), portées par l'arbre intérieur (30), sont agencées solidaires en rotation sur l'arbre intérieur (30), chacune par l'intermédiaire d'au moins un élément de liaison (40; 40; 60), sachant que ledit élément de liaison (40; 40') fait saillie, avec jeu, dans l'arbre extérieur (20), par un évidement (50; 50'), et est fixé à la came d'arbre intérieur (31) respective, qui peut tourner sur l'arbre extérieur (20), caractérisé en ce que chaque élément de liaison (40; 40'; 60) est agencé dans un réceptacle (37), dans l'arbre intérieur (30), de sorte qu'une partie (42) dudit élément de liaison (40; 40'; 60) fasse saillie hors du réceptacle (37) et que ladite partie en saillie (42) soit logée, au moins partiellement, dans un évidement (32), qui est situé sur le diamètre d'assemblage de la came d'arbre intérieur (31) respective, sachant que cet évidement (32) est ouvert, au moins vers un côté frontal de la came d'arbre intérieur (31) et que la partie (42) en saillie vers l'extérieur présente au moins deux faces latérales opposées (43; 44), qui portent, à ajustage serré, contre deux faces intérieures correspondantes (34; 35) de l'évidement (32) de la came d'arbre intérieur (31) respective.
  2. Système d'arbres à cames selon la revendication 1, caractérisé en ce que l'élément de liaison (60) est une clavette et que le réceptacle (37) est réalisé en tant que logement de clavette
  3. Système d'arbres à cames selon la revendication 1, caractérisé en ce que l'élément de liaison (40; 40') est doté d'une tige (41) et d'une tête (42), sachant que la tige (41) est logée, dans un réceptacle (37), dans l'arbre intérieur (30), tandis que la tête (42) est logée, au moins partiellement, dans un évidement (32), qui est situé sur le diamètre d'assemblage de la came d'arbre intérieur (31) respective, sachant que cet évidement (32) est de conception ouverte, au moins vers un côté frontal de la came d'arbre intérieur (31), et que la tête (42) présente au moins deux faces latérales opposées (43; 44), qui portent, à ajustage serré, contre deux faces intérieures correspondantes (34; 35) dudit évidement (32) de la came d'arbre intérieur (31) respective.
  4. Système d'arbres à cames selon revendication 1 ou 3, caractérisé en ce que l'élément de liaison (40; 40') est doté d'une tige (41) et d'une tête (42), sachant que la tige (41) est logée, à ajustage serré, dans le réceptacle (37), tandis que la tête (42) est au moins un composant de la partie en saillie (42) de l'élément de liaison (40; 40').
  5. Système d'arbres à cames selon l'une des revendications 3 et 4, caractérisé en ce que la tête (42) de l'élément de liaison (40; 40') est située entièrement à l'extérieur de l'arbre extérieur (20).
  6. Système d'arbres à cames selon l'une des revendications 3 et 4, caractérisé en ce que la tête (42) est partiellement située, dans l'évidement (32), dans la came d'arbre intérieur (31) respective, et, partiellement, dans l'évidement (50: 50'), dans l'arbre extérieur (20).
  7. Système d'arbres à cames selon la revendication 6, caractérisé en ce que l'arbre intérieur (30) est doté d'un alésage étagé, sachant que la tête (42) fait partiellement saillie dans ledit alésage étagé.
  8. Système d'arbres à cames selon l'une des revendications 3 à 7, caractérisé en ce que la tête (42) de l'élément de liaison (40; 40') s'étend à travers le corps de l'arbre intérieur (30), jusqu'à un deuxième évidement (50') de l'arbre extérieur (20).
  9. Système d'arbres à cames selon l'une des revendications 1 à 8, caractérisé en ce qu'une came d'arbre intérieur (31) est reliée à l'arbre intérieur (30), par deux éléments de liaison (40; 40') opposés, de sorte qu'une transmission de couple de rotation est assurée.
  10. Système d'arbres à cames selon la revendication 9, caractérisé en ce que les tiges de deux éléments de liaison (40; 40') sont logés dans un réceptacle (37) commun, dans l'arbre intérieur (30).
  11. Système d'arbres à cames selon l'une des revendications 1 à 10, caractérisé en ce que l'évidement (50 ; 50'), prévu pour le passage de l'élément de liaison (40; 40') à travers l'arbre extérieur (20), s'étend sur une partie de la périphérie de l'arbre extérieur (20) de sorte qu'un mouvement, d'un angle de déplacement α, de l'élément de liaison (40; 40') et, de ce fait, de l'arbre intérieur (30) par rapport à l'arbre extérieur (20), soit possible.
  12. Système d'arbres à cames selon l'une des revendications 3 à 11, caractérisé en ce que la tête (42) est formée à angle droit par rapport à la tige (41) de l'élément de liaison (40; 40').
  13. Système d'arbres à cames selon l'une des revendications 3 à 12, caractérisé en ce que les deux faces latérales (43; 44) de la tête (42) et les deux faces intérieures (34; 35) de l'évidement (32) s'étendent, respectivement, parallèlement ou en forme de cône les unes par rapport aux autres.
  14. Système d'arbres à cames selon l'une des revendications 3 à 13, caractérisé en ce que les deux faces latérales (43 ; 44) de la tête (42) et / ou les deux faces intérieures (34 ; 35) de l'évidement (32), dans la came d'arbre intérieur (31), présentent une surface profilée.
  15. Système d'arbres à cames selon l'une des revendications 1 à 14, caractérisé en ce que l'évidement (32) est réalisé sous la forme d'une rainure, qui s'étend sur la largeur totale de la came d'arbre intérieur (31).
  16. Système d'arbres à cames selon l'une des revendications 1 à 15, caractérisé en ce que l'évidement (32) est situé centralement, au-dessous du bossage (36) de la came d'arbre intérieur (31).
  17. Système d'arbres à cames selon l'une des revendications 1 à 16, caractérisé en ce que l'élément de liaison (40; 40') est fait d'une pièce.
EP09753605A 2008-05-29 2009-05-04 Système d'arbre à cames ajustable Active EP2286067B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008025781A DE102008025781A1 (de) 2008-05-29 2008-05-29 Verstellbare Nockenwellenanordnung
PCT/EP2009/003173 WO2009143950A1 (fr) 2008-05-29 2009-05-04 Système d'arbre à cames ajustable

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EP2286067A1 EP2286067A1 (fr) 2011-02-23
EP2286067B1 true EP2286067B1 (fr) 2011-10-12

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US (1) US8495980B2 (fr)
EP (1) EP2286067B1 (fr)
CN (1) CN102046930B (fr)
AT (1) ATE528486T1 (fr)
DE (1) DE102008025781A1 (fr)
WO (1) WO2009143950A1 (fr)

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DE102011051480B4 (de) * 2011-06-30 2014-11-20 Thyssenkrupp Presta Teccenter Ag Nockenwelle mit axial verschiebbarem Nockenpaket
DE102011052822A1 (de) * 2011-08-18 2013-02-21 Thyssenkrupp Presta Teccenter Ag Nockenwelle, insbesondere für Kraftfahrzeugmotoren
DE102013007741A1 (de) * 2013-05-07 2014-11-13 Thyssenkrupp Presta Teccenter Ag Nockenwelle
DE102013106747A1 (de) * 2013-06-27 2014-12-31 Thyssenkrupp Presta Teccenter Ag Verstellbare Nockenwelle
DE102013106746A1 (de) * 2013-06-27 2014-12-31 Thyssenkrupp Presta Teccenter Ag Verstellbare Nockenwelle
CN103742219B (zh) * 2013-12-30 2016-05-11 长城汽车股份有限公司 用于发动机的配气机构及具有其的车辆
CN103758605B (zh) * 2014-01-23 2016-04-13 长城汽车股份有限公司 用于发动机的配气机构及具有其的车辆
CN103790669B (zh) * 2014-01-23 2017-07-28 长城汽车股份有限公司 用于发动机的配气机构及具有其的车辆
CN103775159B (zh) * 2014-01-23 2017-02-01 长城汽车股份有限公司 用于发动机的配气机构及具有其的车辆
CN103758604B (zh) * 2014-01-23 2017-02-01 长城汽车股份有限公司 用于发动机的配气机构及具有其的车辆
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CN103758597A (zh) * 2014-02-12 2014-04-30 太仓斯普宁精密机械有限公司 一种新型凸轮轴
DE102014107459A1 (de) * 2014-05-27 2015-12-03 Thyssenkrupp Presta Teccenter Ag Ventilsteuersystem mit einer verstellbaren Nockenwelle
CN104405463A (zh) * 2014-12-08 2015-03-11 重庆市银钢一通科技有限公司 一种凸轮轴
DE102015006375B3 (de) * 2015-05-20 2016-09-15 Audi Ag Brennkraftmaschine
DE102015224905A1 (de) 2015-12-10 2017-06-14 Thyssenkrupp Ag Verfahren zur dauerhaften Befestigung von Nocken auf einem Trägerrohr
EP3378760A1 (fr) * 2017-03-24 2018-09-26 Airbus Operations GmbH Aile pour aéronef
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Publication number Publication date
CN102046930B (zh) 2013-07-17
EP2286067A1 (fr) 2011-02-23
CN102046930A (zh) 2011-05-04
ATE528486T1 (de) 2011-10-15
US8495980B2 (en) 2013-07-30
US20110120401A1 (en) 2011-05-26
DE102008025781A1 (de) 2009-12-10
WO2009143950A1 (fr) 2009-12-03

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