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EP2841722B1 - Arbre à cames réglables pouvant être remplies d'huile sous pression - Google Patents

Arbre à cames réglables pouvant être remplies d'huile sous pression Download PDF

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Publication number
EP2841722B1
EP2841722B1 EP13714252.7A EP13714252A EP2841722B1 EP 2841722 B1 EP2841722 B1 EP 2841722B1 EP 13714252 A EP13714252 A EP 13714252A EP 2841722 B1 EP2841722 B1 EP 2841722B1
Authority
EP
European Patent Office
Prior art keywords
cam
outer shaft
oil
oil groove
shaft
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
EP13714252.7A
Other languages
German (de)
English (en)
Other versions
EP2841722A1 (fr
Inventor
Uwe Dietel
Bernd Mann
Jürgen MEUSEL
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Publication of EP2841722A1 publication Critical patent/EP2841722A1/fr
Application granted granted Critical
Publication of EP2841722B1 publication Critical patent/EP2841722B1/fr
Active legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—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
    • 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
    • F01L2013/0052—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 with cams provided on an axially slidable sleeve
    • 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
    • F01L2810/00—Arrangements solving specific problems in relation with valve gears
    • F01L2810/02—Lubrication

Definitions

  • the present invention relates to an adjustable camshaft for the valve train of an internal combustion engine with an outer shaft, on which at least one first cam is arranged and connected rotationally fixed thereto, and with an outer shaft extending through the inner shaft, with which at least one second cam is rotationally connected, wherein the second cam rotationally fixed to the inner shaft has a cam bore and is rotatably mounted on a setting point on the outer shaft.
  • Adjustable camshafts for the valve trains of internal combustion engines with phase-shiftable cams allow control of intake valves and exhaust valves of the engine at different timing without requiring an intake camshaft for the intake valves and a separate exhaust camshaft for the exhaust valves.
  • the nested waves rotate around a common Rotation axis in the cylinder head and can be adjusted to each other via a control element in their phase position.
  • an adjustable camshaft for the valve train of an internal combustion engine with an outer shaft and with an inner shaft which extends through the outer shaft.
  • cams are arranged with this rotationally fixed, and further cams are rotationally connected to the inner shaft.
  • oil is passed through a central bore in the inner shaft, and the oil passes through radially extending openings from the central bore in the inner shaft in the gap between the inner shaft and the outer shaft.
  • the DE 10 2005 014 680 A1 shows a further adjustable camshaft for the valve train of an internal combustion engine with an outer shaft on which at least one first cam is arranged and connected rotationally fixed, and with an extending through the outer shaft inner shaft, with which at least one second cam is rotationally connected.
  • a feed channel in the outer shaft is shown by way of example, which is located in a section of the outer shaft into which the inner shaft does not extend.
  • This oil can pass through a filter shown by way of example in the gap between the inner shaft and the outer shaft, for example, an oil injection nozzle can be used as an oil supply device.
  • the invention includes the technical teaching that at least one oil groove is introduced at the settling point in the outer shaft and / or in the inner wall of the cam bore, into the oil from a gap between the outer shaft and the inner shaft through at least one passage extending through the outer shaft is guided.
  • the invention makes use of the possibility of supplying the slide bearing of the cams on the outer side of the outer shaft with oil from the gap between the inner shaft and the outer shaft. Since the oil in the gap between the inner shaft and the outer shaft is always guided under pressure through the gap, the oil can pass through the passage in the outer shaft due to the overpressure to finally lubricate the designed as a slide bearing arrangement of the second cam on the outer shaft ,
  • oil can pass through the passage in the outer shaft to the at least one oil groove, thus at the settling point in the outer shaft and / or disposed in the inner wall of the cam bore, that the oil, which is guided through the passage in the oil groove, passes into the lubricating gap between the outer shaft and the cam bore.
  • a lubrication arrangement is created, as it is used in hydrostatic sliding bearings, and the transported with at least slight overpressure in the oil groove oil passes automatically into the lubrication gap between the outer shaft and the cam bore.
  • connection of the second cam with the inner shaft may be formed by a bolt which also pivots with the rotation of the inner shaft relative to the outer shaft.
  • an at least circumferentially elongated bolt hole is provided in the outer shaft, and the passage for guiding the oil from the gap between the inner shaft and the outer shaft to the at least one oil groove may be formed by the bolt hole itself.
  • a passage may be provided as a single bore, which extends radially through the outer shaft and opens in the setting for the arrangement of the second cam. The single bore extends radially through the outer shaft and the oil can pass from the gap between the inner shaft and the outer shaft in the sliding bearing of the second cam on the outside of the outer shaft.
  • the provision of the oil in the circumferential gap between the inner shaft and the outer shaft can as shown in DE 197 57 540 B4 known to be provided via an axial central bore and branched off from this separate radial bores, which may be in the outer shaft in coincidence with the executed as a single bore radial passage. Furthermore, there is the possibility that the bore in the inner shaft, in which the bolt is received, has at least one bypass, passes through the oil from the axial central bore in the gap between the inner shaft and the outer shaft. If the oil supply through a central bore, so the bolt can also be designed by a central interruption in two parts, so as not to interrupt an axial oil flow through the central bore through the bolt.
  • the introduced at the settling point in the outer shaft oil groove can be brought to the passage fluidly communicating, wherein the passage in particular relates to the bolt opening for passage of the bolt through the outer shaft.
  • the oil can pass through the passage directly into the oil groove, wherein the second cam can extend in width across the passageway.
  • the second cam may be designed as a collar cam with a cam collar, and the cam collar extends as a portion of the cam body over the passage in the outer shaft, and for example, the bolt between the inner shaft and the second cam may be inserted in the cam collar. If now oil from the gap between the inner shaft and the outer shaft through the passage, this is also set under oil pressure and the oil can continue to get into the oil groove, which is brought to the passage and thus formed with this fluidly communicating.
  • the oil groove may be formed as an extended part or extended portion of the bolt hole.
  • the bolt opening may have both an elongated extension in the circumferential direction of the outer shaft and also an elongated extension in the direction of the axis of rotation of the camshaft.
  • a degenerate oil groove is formed, which is carried out uniformly with the corresponding enlarged and, for example, approximately rectangular bolt opening.
  • the oil groove which may be introduced in the outer side of the outer shaft or in the inner wall of the cam bore of the second cam, may extend in its longitudinal extent parallel to the axis of rotation of the camshaft or the oil groove extends obliquely to the axis of rotation.
  • the oil groove may be configured so that the sliding gap between the outer shaft and the cam hole in the cam is not supplied with pressure oil only at a position.
  • a circumferential oil groove may be incorporated in the outer shaft and / or in the cam bore.
  • the groove running in the circumferential direction can communicate fluidically, for example, with at least one oil groove running longitudinally or obliquely to the axis of rotation, for example, the oil groove can communicate in the oil groove extending in the circumferential direction pass.
  • a first oil groove is supplied with oil from the gap between the inner shaft and the outer shaft, the oil first passes through the passage in the outer shaft into the first oil groove and from there into the further oil groove extending in the circumferential direction.
  • the oil groove in the context of the invention may also be formed directly by the groove extending in the circumferential direction, which is then supplied directly from the passage in the outer shaft without the interposition of at least one longitudinal or transverse to the axis of rotation extending first groove.
  • the oil can be pressed under pressure into the gap between the outer shaft and the inner shaft, in particular, the pressurized oil can flow along the longitudinal direction of the axis of rotation or the oil can from a central bore in the inner shaft and at least one radial passage in the inner shaft in be guided the gap.
  • the oil supply of the gap as in the DE 197 57 504 B4 be executed.
  • the second cam may have a cam collar into which the oil groove may at least partially extend.
  • the cam collar may form a cylindrical extension on a side surface of the second cam, so that increased by the larger width, the contact surface for forming the sliding bearing between the outer shaft and the cam bore.
  • the bolt for connecting the second cam to the inner shaft may be preferably incorporated in the cam collar, so that the bolt opening in the outer shaft with respect to the setting point is preferably arranged in the portion of the cam bore formed by the cam collar.
  • the oil groove may extend into the cam collar so that the oil passes from the bolt hole into the oil groove extending at least from the area of the cam flange into the area of the cam hole which is below the actual cam.
  • the oil groove can be introduced at the position in the cam bore, which is located below the cam tip, since at this position an oil supply for lubricating the sliding gap is particularly required.
  • a plurality of oil grooves may be provided in the setting of the outer shaft and / or in the cam bore, for example, a bolt for connecting the second cam with the inner shaft by two itself extending in the outer shaft located opposite bolt holes, and through each bolt opening, oil can get into a respective associated oil groove.
  • FIG. 1 shows a portion of an adjustable camshaft 1 in a cross-sectional view.
  • the camshaft 1 serves for the valve drive of an internal combustion engine and has a tubular outer shaft 10.
  • an inner shaft 12 extends, so that between the inner shaft 12 and the outer shaft 10, a circumferential gap 25 is formed.
  • the gap 25 is fully formed between the outer shaft 10 and the inner shaft 12, and in the gap 25 is pressed in a manner not shown in detail under pressure oil, as indicated by arrows.
  • the oil can flow along the gap 25 and provide a lubricating action between the outer shaft 10 and the inner shaft 12.
  • first cams are arranged, of which a first cam 11 is shown by way of example.
  • a first cam 11 is shown by way of example.
  • an exhaust valve of the internal combustion engine can be controlled.
  • 10 second cams are arranged on the outer shaft, of which a second cam 13 is shown by way of example.
  • the first cam 11 is rotationally connected to the outer shaft 10, for example by being pressed onto the outer shaft 10 or connected by a cohesive method with the outer shaft 10.
  • the second cam 13 is rotationally connected to the inner shaft 12, and when the inner shaft 12 is rotated relative to the outer shaft 10 in its phase position, at the same time the second cam 13 is rotated relative to the first cam 11.
  • the adjustable camshaft 1 rotate about its axis of rotation 27, wherein the angular position of the outer shaft 10 relative to the angular position of the inner shaft 12 can be adjusted.
  • the timing of the intake valve may be changed from the timing of the exhaust valve by changing the angular position of the second cam 13 with respect to the first cam 11.
  • a bearing ring 28 which is arranged firmly seated on the outside of the outer shaft 10.
  • a bolt 26 which extends through the inner shaft 12 transversely to the axis of rotation 27 serves. With its end sides, the bolt 26 is connected to the second cam 13. there the bolt 26 extends through bolt openings 23 that form respective passages in the outer shaft 10.
  • the bolt openings 23 are elongated in the circumferential direction of the outer shaft 10, so that the bolt 26 can pivot in the elongated bolt openings 23 when the inner shaft 12 is adjusted relative to the outer shaft 10 in its phase position about the rotation axis 27.
  • the second cam 13 is mounted for this purpose by a sliding bearing on the outer shaft 10 and pivots so on the outer shaft slidably with the inner shaft 12th
  • the outer shaft 10 is executed according to the embodiment shown with passages 22 which are formed as separate passages and which are located in the region of the outer shaft 10 on which the second cam 13 is rotatably received.
  • passages 22 which are formed as separate passages and which are located in the region of the outer shaft 10 on which the second cam 13 is rotatably received.
  • the pressure oil can pass from the gap 25 between the inner shaft 12 and the outer shaft 10 and get into oil grooves 16 which are introduced at the settling point of the second cam 13 in the outer shaft 10. This creates a hydrostatic lubricating effect of the sliding bearing gap of the second cam 13 on the outside of the outer shaft 10. Subsequently, the pressure oil can escape laterally from the sliding gap of the second cam 13 and the outer shaft 10.
  • the wear of the settling point on which the second cam 13 is disposed on the outer shaft 10 can be minimized.
  • the periodic pressure load of the cam 13 by the contact of the cam tip with a tap element results in increased wear, which can be minimized by the improved lubrication.
  • FIG. 2 shows a perspective view of a portion of the outer shaft 10 according to the embodiment in FIG. 1 into which a passage 23 is introduced, which serves as a bolt opening 23 for the passage of the bolt 26. Also shown is a passage 22 which is formed separately from the bolt hole 23 separately and which opens into an oil groove 16 which is inserted in the outside of the outer shaft 10 and which extends along the axis of rotation 27 along.
  • the oil groove 16 is arranged in the region of the setting point 15 in the outer shaft 10, in which the second cam 13 is arranged and has a correspondingly large need for lubricating oil.
  • FIG. 3 shows an embodiment of an adjustable camshaft 1 with an outer shaft 10 and an inner shaft 12, wherein only a second cam 13 is shown by way of example, which is connected via the bolt 26 rotationally fixed to the inner shaft 12.
  • the outer shaft 10 has two bolt openings 23, and according to the Aus colgungsbeispiel shown pressure oil from the gap 25 can pass through the bolt holes 23 in oil grooves 16, so that the bolt hole 23 already serves as a passage 23 for oil supply of the oil grooves 16, without requiring separate passages in the outer shaft 10.
  • FIG. 4 shows in a perspective view a portion of the outer shaft 10 according to the embodiment in FIG. 3 , And the groove 16 is brought up to the edge of the bolt opening 23, which serves as a passage 23 for oil supply to the oil groove 16.
  • the illustrated arrangement of the oil groove 16 with the bolt hole 23 may also be provided on the opposite side in the outer shaft 10, as in FIG FIG. 3 already shown.
  • FIG. 5 shows a portion of another embodiment of a camshaft 1 with an outer shaft 10 and an inner shaft 12, wherein again only a second cam 13 is shown by way of example.
  • the second cam 13 is rotationally connected to the inner shaft 12 via the bolt 26, wherein the bolt 26 passes through the outer shaft 10 with both ends through respective bolt openings 24.
  • the bolt openings 24 are also used in this embodiment as passages 24, can pass through the pressure oil from the gap 25 into the sliding gap between the outer shaft 10 and the second cam 13.
  • the bolt opening 24 is dimensioned in dimensions such that a first region of the bolt opening 24 serves for passage of the bolt 26, and a further region of the bolt opening 24 serves as an oil groove 17 for distributing the pressure oil in the sliding gap between the outer shaft 10 and the cam thirteenth
  • the enlarged bolt hole 24 thus forms a degenerate oil groove 17, as the bolt hole 24 extends below the second cam 13.
  • FIG. 6 shows a perspective view of a portion of the outer shaft 10 with a bolt hole 24 according to the embodiment in FIG. 5 that at the same time the oil groove 17 forms, so that the larger-sized bolt opening 24 serves both for passage of the bolt and to form an oil groove 17 for oil supply.
  • FIG. 7 shows a further embodiment of an adjustable camshaft 1 with an outer shaft 10 and an inner shaft 12, and a bolt 26 is passed through passages 23 in the outer shaft 10.
  • Shown is an oil groove 17, which is in direct fluidic contact with the passage 23, and which is formed as a lateral, pocket-like recess of the bolt opening 23.
  • the thus formed oil groove 17 extends to below the second cam 13, so that the pressure oil passes through the bolt hole 23 and the oil groove 17 in the sliding gap between the outer shaft 10 and the second cam 13.
  • FIG. 8 shows a perspective view of a portion of the outer shaft 10 with a bolt hole 23 according to the embodiment in FIG. 7 , and in the boundary of the bolt opening 23, the oil groove 17 is inserted as a pocket-like recess which forms a bulge in the bolt opening extending in the direction of the axis of rotation 27.
  • FIG. 9 shows a further embodiment of an adjustable camshaft 1 in a cross-sectional view, and the cam 13 is connected via the pin 26 with the inner shaft 12 and mounted on the outside of the outer shaft 10.
  • no oil groove is introduced, wherein the illustrated embodiment of the second cam 13 can be combined with an introduced in the cam bore 14 oil groove 18 with an introduced in the outer shaft 10 and above oil groove 16 and / or oil groove 17.
  • the second cam 13 is formed with a cam collar 13a in which the bolt 26 is inserted.
  • the oil groove 18 protrudes beyond the bolt opening 23 at least with one section, so that the pressure oil can pass from the gap 25 via the bolt opening 23 into the oil groove 18 introduced into the cam bore 14.
  • the embodiment further shows an oil groove 21, the circumferential in the Cam bore 14 is introduced, as in FIG. 10c shown closer. If pressure oil on the oil groove 18 in the oil groove 21, so the sliding bearing between the outer shaft 10 and the cam bore 14 can be supplied with oil evenly.
  • FIG. 10a shows in a perspective view a second cam 13 which has a cam collar 13a and thus forms a so-called collar cam.
  • the cam collar 13a serves to receive the bolt 26, for which purpose bolt holes 29 are made. Adjacent to the bolt holes 29 are provided in the longitudinal axis extending oil grooves 18 in the inside of the cam bore 14 is introduced. Due to the adjacent arrangement of the oil grooves 18 to the pin bore 29 equally created an adjacent arrangement of the oil grooves 18 to the bolt hole 23 when the second cam 13 is disposed on the outer shaft 10. Consequently, the pressure oil can pass through the bolt opening 23 in the oil grooves 18 and these can extend in the direction of the longitudinal axis of the cam 13 from the cam collar 13a to below the actual cam area.
  • FIG. 10b shows a variant of a second cam 13 without cam collar 13a, and by way of example, an oil groove 19 is provided, which is introduced in the inner wall of the cam bore 14 adjacent to the pin bore 29.
  • Cams 13 of this type can also be connected with a bolt to the inner shaft 12, wherein the bolt can be inserted into a through hole in the cam belt and in an inner blind bore below the cam tip.
  • FIG. 10c shows finally a further cam 13 with a cam collar 13a, and adjacent to the pin bore 29, an oil groove 18 is shown. Furthermore, in the cam bore 14, a circumferential oil groove 21 is introduced, which is in fluid communication with the longitudinally extending oil groove 18. If pressure oil is pressed via the oil groove 18 into the circumferential oil groove 21, then an improved, full-scale oil supply of the bearing gap for lubricating the cam 13 on the outer shaft can be ensured.
  • FIG. 11 shows an embodiment of a camshaft 1 with an outer shaft 10 and an inner shaft 12 and in the manner already described is a second Cam 13 with a cam collar 13a via a bolt 26 rotationally connected to the inner shaft 12.
  • oil grooves 18 are introduced, which extend from the cam portion into the cam collar 13a.
  • the oil grooves 18 cover the bolt openings 23 in the outer shaft 10 and can thus be supplied with pressure oil.
  • the embodiment further shows an oil groove 20, which is located in the outside of the outer shaft 10 and extends in the circumferential direction.
  • the oil groove 20 can be supplied with pressure oil via the oil groove 18 and also distributed over the circumference in the cam bore 14 a plurality of oil grooves 18 may be introduced, which in turn transport the oil from the oil groove 20 into the lubrication gap between the outer shaft 10 and the cam 13.
  • further structuring for example, introduced by blasting with glass beads or other particles or by laser structuring, may be provided in the cam bore 14, which is a reservoir for the under Make cam 13 guided oil.
  • the structures may have a prismatic or dome-shaped shape.
  • the oil groove 18 may be open to the end of the cam 13 or end in this, it would be preferable, however, that the oil groove 18 is closed with the advantage that a drainage of the oil from the groove 18 is difficult.
  • FIG. 12 shows in a cross-sectional partial view of an embodiment of the camshaft 1 with an inner shaft 12 in which a central channel 30 is introduced to the oil supply, which extends along the axis of rotation 27. Oil from the central channel 30 can flow under pressure along the axis of rotation 27, in particular because the pin 26 is divided and divided into a first pin member 26a and a second pin member 26b, so that the central channel 30 is formed continuously and not by a continuous bolt 26 is interrupted.
  • the oil can then enter the gap 25 from the central channel 30 into a gap between the bolt parts 26a, 26b and the bore, in which the bolt parts 26a, 26b are introduced in the inner shaft 12, and exemplarily via a passage 22 and an oil groove 16 Seat Lubricate the second cam 13 on the outer shaft 10, and distribute further through the bolt hole 23 under the cam 13.
  • FIG. 13a shows an outer shaft 10 with a bolt opening 23 by way of example, wherein in FIG. 13a an oil groove 20 is inserted adjacent to the bolt hole 23 in the outside of the outer shaft 10, which according to the arrangement in FIG. 11 can be supplied with an oil groove 18 with oil.
  • the oil groove 20 extends over a partial circumference of the outer shaft 10.
  • FIG. 13b shows an outer shaft 10 with an oil groove 20 'which extends over the full circumference of the outer shaft 10 and can be supplied in the same way with pressurized oil through the oil groove 18, as in FIG. 11 shown.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Claims (8)

  1. Arbre à cames réglable (1) pour la commande des soupapes d'un moteur à combustion interne comprenant un arbre extérieur (10) sur lequel est disposée au moins une première came (11) qui est connectée de manière solidaire en rotation à celui-ci, et comprenant un arbre intérieur (12) s'étendant à travers l'arbre extérieur (10), avec lequel au moins une deuxième came (13) est connectée de manière solidaire en rotation, la deuxième came (13) connectée de manière solidaire en rotation à l'arbre intérieur (12) présentant un alésage de came (14) et étant supportée de manière à pouvoir tourner sur l'arbre extérieur (10) au niveau d'un point d'assujettissement (15), caractérisé en ce qu'au moins une rainure d'huile (16, 17, 18, 19, 20, 20', 21) est réalisée au niveau du point d'assujettissement (15) dans l'arbre extérieur (10) et/ou dans la paroi intérieure de l'alésage de came (14), dans laquelle de l'huile provenant d'un interstice (25) entre l'arbre extérieur (10) et l'arbre intérieur (12) est guidée à travers au moins un passage (22, 23, 24) s'étendant à travers l'arbre extérieur (10).
  2. Arbre à cames réglable (1) selon la revendication 1, caractérisé en ce que la connexion de la deuxième came (13) à l'arbre intérieur (12) est formée par un boulon (26) qui s'étend à travers au moins une ouverture de boulon (23) dans l'arbre extérieur (10), le passage (23) pour le guidage d'huile au niveau de l'au moins une rainure d'huile (16, 17, 18, 19, 20, 20', 21) étant formé à travers l'ouverture de boulon (23).
  3. Arbre à cames réglable (1) selon la revendication 2, caractérisé en ce que la rainure d'huile (16) réalisée au niveau du point d'assujettissement (15) dans l'arbre extérieur (10) est amenée jusqu'au passage (22, 23), en particulier jusqu'à l'ouverture de boulon (23), de manière à communiquer fluidiquement avec celui-ci, et/ou en ce que la rainure d'huile (18, 19) réalisée dans la paroi intérieure de l'alésage de came (14) dépasse au moins en partie au-delà du passage (22, 23), en particulier de l'ouverture de boulon (23).
  4. Arbre à cames réglable (1) selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la rainure d'huile (17) est réalisée sous forme de partie élargie de l'ouverture de boulon (23, 24).
  5. Arbre à cames réglable (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que la rainure d'huile (16, 17, 18) s'étend le long de l'axe de rotation (27) de l'arbre à cames (1) ou en ce que la rainure d'huile (19) est réalisée dans l'arbre extérieur (10) et/ou dans la paroi intérieure de l'alésage de came (14) de manière à s'étendre obliquement par rapport à l'axe de rotation (27).
  6. Arbre à cames réglable (1) selon l'une quelconque des revendications précédents, caractérisé en ce qu'une rainure d'huile (20, 20') s'étendant dans la direction périphérique est réalisée dans l'arbre extérieur (10) et/ou une rainure d'huile (21) s'étendant dans la direction périphérique est réalisée dans l'alésage de came (14), laquelle communique fluidiquement notamment avec une rainure d'huile (16, 17, 18, 19) s'étendant le long de l'axe de rotation (27) ou obliquement par rapport à celui-ci.
  7. Arbre à cames réglable (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que l'huile est pressée sous pression dans l'interstice (25) entre l'arbre extérieur (10) et l'arbre intérieur (12), en particulier en ce que l'huile s'écoule sous pression dans la direction longitudinale de l'axe de rotation (27) ou en ce que l'huile est guidée dans l'interstice (25) à partir d'un alésage central dans l'arbre intérieur (12) et par le biais d'au moins un canal radial dans l'arbre intérieur (12).
  8. Arbre à cames réglable (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que la deuxième came (13) présente un épaulement de came (13a), la rainure d'huile (18, 19) s'étendant au moins en partie dans l'épaulement de came (13a).
EP13714252.7A 2012-04-24 2013-03-27 Arbre à cames réglables pouvant être remplies d'huile sous pression Active EP2841722B1 (fr)

Applications Claiming Priority (2)

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DE102012103581A DE102012103581A1 (de) 2012-04-24 2012-04-24 Nockenwelle mit durch Drucköl beölbare, verstellbare Nocken
PCT/EP2013/056464 WO2013160051A1 (fr) 2012-04-24 2013-03-27 Arbre à cames réglables pouvant être remplies d'huile sous pression

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WO (1) WO2013160051A1 (fr)

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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
DE102013113255A1 (de) 2013-11-29 2015-06-03 Thyssenkrupp Presta Teccenter Ag Verstellbare Nockenwelle
DE102014104994A1 (de) * 2014-04-08 2015-10-08 Thyssenkrupp Presta Teccenter Ag verstellbare Nockenwelle
DE102014109752B4 (de) * 2014-07-11 2024-10-10 Thyssenkrupp Presta Teccenter Ag Verfahren zur Montage einer verstellbaren Nockenwelle
DE102014116252A1 (de) * 2014-11-07 2016-05-12 Thyssenkrupp Presta Teccenter Ag Nockenwelle mit einem axial geführten Schiebeelement
DE102015215292A1 (de) * 2015-08-11 2017-02-16 Thyssenkrupp Ag Verfahren und Vorrichtung zur Montage einer verstellbaren Nockenwelle
DE102015113356A1 (de) * 2015-08-13 2017-02-16 Thyssenkrupp Ag Verstellbare Nockenwelle mit einem Phasenteller
CN110848365B (zh) * 2018-08-21 2022-03-11 上海汽车集团股份有限公司 一种滑移凸轮机构

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JPS61126007U (fr) * 1985-01-29 1986-08-07
US5664463A (en) * 1993-03-03 1997-09-09 Amborn; Peter Camshaft assembly with shaft elements positioned one inside the other and method of producing same
DE4416505A1 (de) 1994-05-10 1995-11-16 Bayerische Motoren Werke Ag Nockenwelle mit verdrehbaren Nocken
DE19638331A1 (de) 1995-09-28 1997-04-03 Volkswagen Ag Nockenanordnung für eine Brennkraftmaschine
DE19757504B4 (de) 1997-12-23 2005-03-31 Daimlerchrysler Ag Gebaute Nockenwelle für eine Brennkraftmaschine
DE102005040934A1 (de) * 2005-02-03 2006-08-17 Mahle International Gmbh Verstellbare Nockenwelle, insbesondere für Verbrennungsmotoren von Kraftfahrzeugen, mit einer hydraulischen Stelleinrichtung
DE102005014680A1 (de) 2005-02-03 2006-08-10 Mahle International Gmbh Nockenwelle mit gegeneinander verdrehbaren Nocken für insbesondere Kraftfahrzeuge
DE102008062041A1 (de) 2008-12-12 2010-06-17 Thyssenkrupp Presta Teccenter Ag Verstellbare Nockenwellenanordnung
DE102009039733A1 (de) * 2009-09-02 2011-03-10 Thyssenkrupp Presta Teccenter Ag Ventiltrieb für Gaswechselventile einer Brennkraftmaschine mit axial verschiebbaren Nockeneinheiten

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CN104411924B (zh) 2018-05-08
WO2013160051A1 (fr) 2013-10-31
EP2841722A1 (fr) 2015-03-04
US20150090208A1 (en) 2015-04-02
DE102012103581A1 (de) 2013-10-24
US9273571B2 (en) 2016-03-01
CN104411924A (zh) 2015-03-11

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