EP1963629B1 - Nockenwellenversteller - Google Patents

Nockenwellenversteller Download PDF

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Publication number
EP1963629B1
EP1963629B1 EP06830088A EP06830088A EP1963629B1 EP 1963629 B1 EP1963629 B1 EP 1963629B1 EP 06830088 A EP06830088 A EP 06830088A EP 06830088 A EP06830088 A EP 06830088A EP 1963629 B1 EP1963629 B1 EP 1963629B1
Authority
EP
European Patent Office
Prior art keywords
lubricant
camshaft
camshaft adjuster
flow
duct
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 - Fee Related
Application number
EP06830088A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1963629A1 (de
Inventor
Mike Kohrs
Jens Schäfer
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.)
IHO Holding GmbH and Co KG
Original Assignee
Schaeffler KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler KG filed Critical Schaeffler KG
Publication of EP1963629A1 publication Critical patent/EP1963629A1/de
Application granted granted Critical
Publication of EP1963629B1 publication Critical patent/EP1963629B1/de
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • F01L1/352—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 bevel or epicyclic 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
    • 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
    • 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
    • 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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34436—Features or method for avoiding malfunction due to foreign matters in oil
    • 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 invention relates to a camshaft adjuster for an internal combustion engine in which lubrication takes place via a lubricant stream, in particular according to the preamble of claim 1.
  • the adjustment energy can take the form of a provision by a drive and / or a braking power and by utilizing power losses of the shaft system (eg friction) and / or inertias and / or centrifugal forces.
  • a braking preferably in the adjustment "late” can also be done with full utilization or shared use of the friction of the camshaft.
  • a camshaft adjuster may be equipped with or without a mechanical limitation of the adjustment range.
  • a transmission in a camshaft phaser find one or more stages three-shaft gearbox and / or multi-joint or coupling gear use, for example in the form of a swash plate gear, eccentric, planetary gear, wave gear, cam gear, Mehrgelenk- or Koppfelgetriebe or combinations of the individual designs in one multi-level training.
  • camshaft adjusters For an operation of the camshaft adjuster, a supply of a lubricant to lubrication points, in particular bearing points and / or rolling toothing, is required, wherein the lubricant lubrication and / or Cooling relative to each other moving components of the camshaft adjuster is used.
  • camshaft adjusters have a lubricant circuit which can be coupled, for example, to the lubricant circuit of the internal combustion engine.
  • the invention initially eliminates the prejudice that a supply of lubricant is required for each angular position of the camshaft and thus a continuous supply of lubricant. Rather, the invention uses a discontinuous lubricant supply.
  • Such a discontinuous lubricant supply can be created according to the invention in a particularly simple manner, u. U. without a particularly complex control or regulating unit, an actuator or a valve is required: According to the invention, a release or blocking the lubricant supply movement controlled by the relative movement of the components of the camshaft adjuster, which include the feed channel and the receiving channel.
  • a transfer of lubricant takes place only when the supply channel and the receiving channel are approximately aligned with each other.
  • leakage with reduced delivery volume can result in transmission.
  • a groove which does not completely encircle the peripheral surface can be provided in the region of the feed channel and / or receiving channel, whereby the time duration of a transmission of the lubricant is prolonged.
  • a passage cross-section which increases with time can be formed, which drops back to zero after reaching a maximum (aligned holes), whereby the temporal signal of the transfer volume flow can be predetermined.
  • the width of a not completely circumferential circumferential groove can be made suitable for influencing the signal of the transfer volume flow.
  • the delivery rate of the lubricant can be reduced compared to a continuous supply of lubricant. Furthermore, there are pulsations of the lubricant flow in the camshaft adjuster, which can lead to improved lubrication and improved distribution of the lubricant.
  • the embodiment of the invention is not limited to embodiments according to the aforementioned prior art, in which the supply via a camshaft bearing. Rather, supply channel and receiving channel can be arranged to bring about a discontinuous lubricant flow in any components that are moved relative to each other in the course of rotation of the camshaft and / or the camshaft adjuster.
  • a plurality of feed channels and / or receiving channels may be evenly or non-uniformly distributed over the circumference.
  • At least one check valve can be arranged in the lubricant circuit, in particular in the region of the camshaft adjuster, the camshaft, the camshaft bearing, the cylinder head.
  • the pulsations of the lubricant are utilized in that downstream of the receiving channel a lubricant injection nozzle is arranged, from which the lubricant can emerge with increasing pressure with increasing pressure for open crossover cross section.
  • FIG. 1 shows a schematic representation of a camshaft adjuster 1, in which in a transmission 2, the movement of two input elements, here a drive wheel 3 and an adjustment 4 (also called wobble) to an output movement of an output element, here a rotatably connected to a cam shaft output shaft 5 or directly the camshaft 6, is superimposed.
  • the drive wheel 3 is in driving connection with a crankshaft of the internal combustion engine, for example via a traction means such as a chain or a belt or a suitable toothing, wherein the drive wheel 3 may be formed as a chain or pulley.
  • the adjusting shaft 4 is driven by an electric motor 7 or is in operative connection with a brake.
  • the electric motor 7 is supported relative to the environment, for example the cylinder head 8 or another motor-fixed part.
  • FIG. 2 shows an exemplary embodiment of a camshaft adjuster 1 with a gear 2 swash plate type.
  • a housing 9 is rotatably connected to the drive wheel 3 and sealed in an axial end region via a sealing element 10 relative to the adjusting shaft 4. In the opposite axial end region, the housing 9 is sealed with respect to the cylinder head 8 with a sealing element 11.
  • interior 36 protrudes an end portion of the camshaft 6 in.
  • a coupling 12 with the adjusting shaft 4 eccentric shaft 13, a via a bearing element 14, for example, a roller bearing, mounted swash plate 15 and a hollow shaft 16, via a bearing element 17, for example, a roller bearing, inside in a central Recess of the eccentric shaft 13 is supported and a Abtriebskegelrad 18 carries arranged.
  • the driven bevel gear 18 is supported via a bearing 19 relative to the housing 9. Inside, the housing 9 forms a drive bevel wheel 20.
  • the swash plate 15 has on opposite end faces suitable teeth.
  • the eccentric shaft 13 with Bearing element 14 and swash plate rotates about a relative to a longitudinal axis 21-21 inclined axis, so that the swash plate intermeshing circumferentially offset portions on the one hand with the drive bevel gear 20 and the other with the Abreteskegelrad 18, wherein between the drive bevel gear and Abreteskegelrad given an over- or reduction is.
  • the driven bevel gear 18 is rotatably connected to the camshaft 6.
  • FIG. 3 shows a schematic lubricant circuit.
  • the lubricant is from a reservoir 31, for example an oil pan or an oil tank, via a pump 32, for example an engine oil pump, through a filter 33, in particular an engine oil filter, to the Zulanderaus Principleung 25 and the flow channel 26 of the camshaft 6 promoted.
  • the lubricant leaves the camshaft adjuster 1 or the housing 9 thereof via an outlet opening 34 and is returned to the reservoir 31 again.
  • the filter element 35 is preferably assigned to the camshaft adjuster 1 and, for example, arranged according to a branch of the lubricant circuit to further components to be lubricated and associated exclusively with the branch of the lubricant circuit, which serves to lubricate the camshaft adjuster.
  • the filter 35 is arranged as close as possible to the installation location of the camshaft adjuster 1 or in the camshaft adjuster itself.
  • the filter element 35 may serve to keep machining residues in flow channels upstream upstream of the filter element 35 from flow passages of the cylinder head and the camshaft.
  • a diaphragm characteristic or a throttle effect of the filter element 35 can be used selectively in order to influence the flow conditions, in particular the pressure, the volume flow and the speed of the lubricant.
  • the filter element 35 is preferably to be implemented in such a way that it can not clog or become clogged due to the flow conditions in the maximum assumed contamination with particles and dirt during the life of the camshaft adjuster.
  • the arrangement in a riser and / or as a bypass filter is advantageous.
  • lubricant is conveyed into an interior 36 of the housing 9, for example according to the embodiments described above, wherein in the interior 36, the lubricant comes into contact with the lubrication points.
  • the inner space 36 is in lubricant communication with a dead space 37, which is arranged at a radially farthest point of the inner space 36.
  • a connection of the dead space 37 to the interior 36 can be formed over a large area over crossing cross sections or via separate channels, via which an access of lubricant and an outlet of lubricant to and from the dead space 37 is possible.
  • the dead space 37 is formed as a circumferential annular channel.
  • a dead space 37 is, in particular, a space in which the lubricant moves or rests at low speeds, so that the dead space 37 is not arranged in an immediate, maximum flow zone of the lubricant.
  • the lubricant is subjected to a centrifugal force due to the rotation of the housing 9, whereby heavy components and suspended particles are pressed in the lubricant to the outside and can deposit on a radially outer wall 38 and are not performed back to a lubrication point.
  • annular dead space 37 is separated in the circumferential direction by intermediate walls, so that a plurality of individual chambers are formed in the circumferential direction, is avoided by the fact that in the dead space 37, the lubricant can move relative to the housing 9 in the circumferential direction.
  • a deposition of dirt is thus analogous to a rotating centrifuge.
  • Dead spaces according to dead space 37 can be arranged at any point in the transmission be as well as in the area of the camshaft, which can be achieved that important functional surfaces, for example, in the immediate vicinity of the dead space, not "silted” by centrifuged dirt in the transmission.
  • the centrifugal action is enhanced by increasing the distance of the dead spaces from the longitudinal axis 21-21.
  • the dead space has no additional outflow, so that centrifuged dirt particles are permanently deposited in the dead space 37.
  • the dead space has at least one additional outlet opening 39, 40, wherein the outlet opening 39 is axially oriented and the outlet opening 40 is radially oriented.
  • the lubricant with deposited dirt particles in the radial direction moves out of the outlet opening 40, wherein the promotion of the dirt particles is supported by the centrifugal action. Notwithstanding this, there is a promotion through the outlet opening 39 only by the pressure difference in the dead space 37 on the one hand and in the vicinity of the camshaft adjuster 1 on the other.
  • a dirt separation takes place in that the lubricant is guided in a flow channel labyrinthine or zigzag.
  • Dirt deposition by such a labyrinthine dirt separator is due to the different inertia of the lubricant and interfering particles in the lubricant.
  • a strong deflection of the lubricant flow can cause the particles are not deflected, but deposit at the boundaries of the labyrinth.
  • deposition in the labyrinth on radially outer surfaces due to the centrifugal action described above can take place in such channels as well as also in axial channels.
  • An alternative or cumulative separation effect may arise when the lubricant is decelerated and accelerated, with the easier to accelerate lighter lubricants while leaving particles of dirt behind.
  • the centrifugal effect can be at least partially generated by the fact that the lubricant flow channels are circular or spirally oriented, so that solely by the movement of the lubricant through the curved flow channels can form a deposit on outer boundaries of the flow channels.
  • FIG. 6 illustrated schematic lubricant circuit an input-side aperture 41 and an input-side throttle 42 and an output-side aperture 43 and an output-side throttle 44.
  • the aperture 41, 43 and throttles 42, 44 form flow elements for influencing the flow conditions in the lubricant circuit.
  • the aforementioned flow elements are associated with a parallel lubricant path, which acts exclusively on the camshaft adjuster 1.
  • the flow elements are arranged close to or at least partially in the camshaft adjuster 1, the camshaft or a cylinder head in the region of a bearing for the camshaft.
  • the filter element 35 is arranged in the flow direction upstream of the flow elements, so that the flow elements are not clogged by particles or added over time.
  • a change of the flow element takes place, for example, such that the volume flow of the lubricant is kept at a constant value, regardless of a temperature of the lubricant. It is also possible that the volume flow is increased or decreased by influencing the flow element in operating areas in which a higher lubricant or cooling demand or a lower such need exists.
  • a supply of lubricant via a plurality of bores or receiving channels 45 of the camshaft 6, wherein the receiving channels 45 are inclined relative to the longitudinal axis 21-21 and the radial orientation.
  • the camshaft 6 has an end blind bore 46, which merges with a conical chamfer 47 into a thread for receiving the central screw 22.
  • the receiving channels 45 open into the chamfer 47.
  • the receiving channels 45 are fed by a supply groove of the cylinder head 8 with the lubricant.
  • Approximately in the center of the receiving channel 45 is a radial circumferential groove 48 introduced in the illustrated longitudinal section rectangular geometry.
  • a portion of the supplied via the receiving channel 45 and bore 46 to the recess 48 lubricant passes through an axial bore 49 of the camshaft 6, which opens into the recess 48, and one with a certain overlap, but radially offset axial bore 50 of the housing 9 in the Interior of the transmission 2 to the lubrication points, for example to the bearing element 17, the bearing element 14, the rolling tooth connections of the swash plate 15 and / or the storage 19th
  • the other part of the recess 48 supplied lubricant passes through a formed between the inner surface of the hollow shaft 16 and the outer surface of the central screw 22 flow channel 51 with annular cross section to at least one radial bore 52 to a lubrication point, for example, the bearing 17 or in the interior of the transmission 2.
  • the recess 48 is formed with a radial extent, which extends beyond the bore 49, so that radially outwardly a circumferential annular dead space 37 is formed.
  • Between the bores 49, 50 may be formed a transition region 53 in the form of a recess, a radial groove o. ⁇ ., To allow the passage between the radially offset holes 49, 50.
  • non-aligned bores 49, 50 can be created for a partial overlap of the holes a kind of aperture with a small transition cross-section or aperture cross-section, although the holes 49, 50 can be made with relatively large diameters and thus coarse tools.
  • FIG. 7 corresponding embodiment is for the in FIG. 8 illustrated embodiment, the extension of the hollow shaft 16 in the longitudinal direction extended such that the hollow shaft protrudes into the recess 48.
  • a circumferential edge 54 which is formed by the inner circumferential surface of the bore 46 and a recess bounding the transverse surface 55, and an edge 56 of the outer circumferential surface 57 of the hollow shaft 16 and a End face 58 of the hollow shaft 16 is formed, a diaphragm is formed for a passage of the lubricant from the bore 46 to the recess 48th
  • the camshaft 6 has according FIG. 9 no puncture 48.
  • the holes 49, 50 and the transition region 53 are for the embodiment according to FIG. 9 not provided, so that the lubricant from the bore 46 is completely supplied to the flow channel 51.
  • a flow element 59 is arranged, which is at a striped over the central screw 22 ring, for example, plastic or an elastomer can act.
  • the flow element 59 has an approximately T-shaped half longitudinal section, wherein the transverse leg of the T under elastic contact radially inwardly abuts the lateral surface of the central screw 22, while the vertical leg of the T extends radially outwardly and the end of this leg an annular gap 60th formed with the bore 46, whereby a diaphragm is created.
  • the flow element 59 may, for example, be clamped radially outward against the bore 46, in which case an annular gap 60 is formed between the inner surface of the flow element and the central screw. Also, a positive reception of the flow element 59, for example in a suitable groove of the camshaft or the central screw, is conceivable. Any configuration of the contour of the flow element 59 in the region of the annular gap 60 for influencing the flow conditions is possible, for example with stepwise transitions or continuous transitions.
  • the hollow shaft 16 in the region of the flow channel 51 has a radial, circumferential recess 61, the is limited on the chamfer 47 side facing by a radially inwardly facing, circumferential radial projection 62.
  • an annular gap 63 is formed, which constitutes a diaphragm.
  • the recess 61 forms a dead space 37 radially on the outside, since both the annular gap 63 and the flow channel 51 open radially inward from the dead space 37 into the recess 61.
  • the camshaft 6 is supplied with lubricant from a lubricant gallery of the cylinder head 8.
  • the transmission of the lubricant from the engine-fixed cylinder head 8 on the rotating camshaft 6 is usually carried out by means of known rotary transformer.
  • This is usually an annular groove 64 of the outer circumferential surface of the camshaft 6.
  • the annular groove 64 is surrounded by a corresponding cylindrical surface 65 of the cylinder head 8, to which an axially aligned with the annular groove 64 tap hole or feed channel 66 leads from the lubricant gallery.
  • the feed channel 66 may be the lateral surface 65, as in FIG. 11 represented, break through radially or break them, for example, tangentially.
  • a rotary transformer can be arranged in a radial bearing for the camshaft 6 or on a separate shoulder. In the latter, however, because of the usually larger radial gap often sealing rings 67, 68, for example, a steel, cast iron, plastic sealing ring required. In an arrangement of the rotary transformer in a radial bearing of the camshaft 6, it should be noted that the bearing width is reduced by the width of the annular groove.
  • annular grooves can be executed in the form of a cylinder head, for example in the bearing, the bearing bridge or an inserted bearing bush. In the camshaft then no annular grooves 64 are required.
  • the feed channel 66 and the annular groove 64 are arranged offset from one another in the axial direction, whereby a kind of throttle is created already when the lubricant from the supply channel 66 to the annular groove 64, the opening cross section is smaller, the greater the offset in the axial Direction between feed channel 66 and annular groove 64 is.
  • a throttle effect can be achieved here also for a relatively large diameter of the feed channel 66 and a large width of the annular groove 64, so that no dirt-sensitive and production-sensitive small holes or grooves must be created.
  • the lubricant is supplied via a cyclic lubricant supply.
  • a cyclic lubricant supply eliminates the annular groove 64, so that a lubricant connection between the feed channel 66 and the receiving channels 69 is given only for such rotational positions of the camshaft 6, for which the channels 66, 69 are aligned or have an overlap.
  • the cylinder head 8 or the lateral surface of the camshaft 6 may have a groove extending over part of its circumference in the transition region between supply channel 66 and receiving channel 69, so that passage from the supply channel 66 to the receiving channel 69 is possible as long as possible these channels 66, 69 are interconnected by the groove.
  • the transfer of the lubricant can be made variable via the design of the width profile of the groove.
  • a volume flow and mass flow of the lubricant can be specified constructively and cyclically.
  • a pulsating lubricant flow can be effected, which results in pressure fluctuations, which can be used for example for a better mixing and wetting of the lubrication points with the lubricant.
  • the risk of blockages for example, of diaphragms or chokes, be reduced.
  • FIG. 12 shows an embodiment in which the transmission 2 lubricant via a radial blind hole or a feed channel 70, an axial, opening into the feed channel 70 end blind hole 71 of the camshaft and a tap hole 72 of the housing 9 is supplied.
  • a simplification of the assembly results when in the transition region between the holes 71 of the camshaft and the bores 72 of the housing 9, a circumferential annular groove 73 is provided, whereby the holes 71, 72 need not be coaxially aligned with each other during assembly.
  • FIG. 13 shows an embodiment which essentially according to the embodiment according to FIG. 9 corresponds, but no flow element 59 is provided.
  • FIG. 14 shows an embodiment in which the annular groove 64 via a (e) relative to the longitudinal axis 21-21 and the transverse axis inclined (r) bore or receiving channel 74 is connected directly to the annular channel 73.
  • FIG. 16 has an annular channel between the hollow shaft 16 and central screw 22 has a ring width in the range of 0.2 to 1 mm.
  • the radial connection bores between this flow channel and the interior of the transmission preferably have a diameter between 0.5 and 3 mm. Further influencing or throttling or diaphragms can take place by specification of the axial and / or radial gaps 76, which can be predetermined in terms of design and form flow cross sections or diaphragms or throttles for the lubricant.
  • the outer circumferential surface of the housing 9 has recesses or windows 77, which may be distributed uniformly or non-uniformly in the circumferential direction, cf. FIG. 17 ,
  • FIG. 18 shows further possibilities for the arrangement of recesses or openings 78 in the region of an end face of the camshaft adjuster 1.
  • a transmission of the lubricant via the camshaft can be omitted if a lubricant through the openings 78, 77 is supplied to the transmission 2.
  • the lubricant can be conveyed through the openings 77, 78 via a lubricant syringe.
  • a lubricant syringe may be arranged on the cylinder head or on a chain case.
  • a lubricant syringe may simply be a lubricant bore from which a fine jet of lubricant exits and which impinges on a point outside the transmission or within the transmission, for example through the openings 77, 78.
  • a point may lie as close as possible to the axis of rotation in the interior of the transmission. Due to the centrifugal force acting on the lubricant in the rotating system, the lubricant is distributed outwards to the lubrication points, for example to a bearing and / or to the toothing.
  • the lubricant must be sprayed directly onto a toothing or other lubricant points. It is also conceivable that the spraying with lubricant is combined with the lubricant supply to other engine components, for example a chain or a tensioner. It is also conceivable that a point or an area outside of the transmission 2m is sprayed with the lubricant. Lubrication is then ensured by the rebounding or reflected lubricant or lubricating mist generated thereby.
  • a supply of lubricant can take place via the lubricant mist which is present in any case in a chain case and can penetrate through the openings 77, 78 into the camshaft adjuster.
  • a drip tray 80 is provided, on which the lubricant mist condenses and drips.
  • special drip lubricant nozzles can be provided, which are specifically aligned in the direction of the openings 77, 78.
  • the lubricant reservoirs are provided by microscopic or macroscopic small pockets of lubricant locations in which lubricants are for cold start or low Lubricant temperatures can be stored.
  • Better emergency running properties may preferably also be present if rolling bearings are provided at the bearing points as far as possible.
  • an oil dripping from an oil-lubricated traction means can furthermore be used which passes through an opening in the housing.
  • the traction means u.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP06830088A 2005-12-15 2006-11-23 Nockenwellenversteller Expired - Fee Related EP1963629B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005059840A DE102005059840A1 (de) 2005-12-15 2005-12-15 Nockenwellenversteller
PCT/EP2006/068804 WO2007071518A1 (de) 2005-12-15 2006-11-23 Nockenwellenversteller

Publications (2)

Publication Number Publication Date
EP1963629A1 EP1963629A1 (de) 2008-09-03
EP1963629B1 true EP1963629B1 (de) 2009-06-24

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EP06830088A Expired - Fee Related EP1963629B1 (de) 2005-12-15 2006-11-23 Nockenwellenversteller

Country Status (6)

Country Link
US (1) US7934478B2 (ja)
EP (1) EP1963629B1 (ja)
JP (1) JP4982503B2 (ja)
CN (1) CN101331298B (ja)
DE (2) DE102005059840A1 (ja)
WO (1) WO2007071518A1 (ja)

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JP4247644B2 (ja) 2007-06-29 2009-04-02 三菱自動車工業株式会社 内燃機関の可変動弁装置
JP5394157B2 (ja) * 2009-07-29 2014-01-22 株式会社ジェイテクト カムシャフト装置
DE102009054049B4 (de) * 2009-11-20 2020-08-27 Schaeffler Technologies AG & Co. KG Nockenwellenverstellanordnung
JP5315266B2 (ja) * 2010-03-01 2013-10-16 住友重機械工業株式会社 ホロー出力軸と被駆動軸との連結構造、及び減速機
JP5991274B2 (ja) * 2013-07-08 2016-09-14 株式会社デンソー バルブタイミング調整装置
DE102013216184B4 (de) * 2013-08-14 2020-11-26 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102013220220B4 (de) * 2013-10-08 2020-06-18 Schaeffler Technologies AG & Co. KG Nockenwellenverstellvorrichtung
CN105370334B (zh) * 2015-11-23 2018-01-16 重庆祥吉机械制造有限公司 一种凸轮轴结构

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DE102004062067B4 (de) * 2004-12-23 2017-06-08 Schaeffler Technologies AG & Co. KG Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine

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JP4982503B2 (ja) 2012-07-25
US7934478B2 (en) 2011-05-03
WO2007071518A1 (de) 2007-06-28
US20080308054A1 (en) 2008-12-18
EP1963629A1 (de) 2008-09-03
JP2010510420A (ja) 2010-04-02
CN101331298A (zh) 2008-12-24
DE502006004091D1 (de) 2009-08-06
CN101331298B (zh) 2010-12-15
DE102005059840A1 (de) 2007-06-28

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