EP1963629A1 - Nockenwellenversteller - Google Patents
NockenwellenverstellerInfo
- Publication number
- EP1963629A1 EP1963629A1 EP06830088A EP06830088A EP1963629A1 EP 1963629 A1 EP1963629 A1 EP 1963629A1 EP 06830088 A EP06830088 A EP 06830088A EP 06830088 A EP06830088 A EP 06830088A EP 1963629 A1 EP1963629 A1 EP 1963629A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- lubricant
- camshaft
- camshaft adjuster
- channel
- flow
- 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.)
- Granted
Links
- 239000000314 lubricant Substances 0.000 claims abstract description 149
- 230000005540 biological transmission Effects 0.000 claims description 29
- 238000005461 lubrication Methods 0.000 claims description 22
- 238000002485 combustion reaction Methods 0.000 claims description 4
- 238000002347 injection Methods 0.000 claims description 2
- 239000007924 injection Substances 0.000 claims description 2
- 125000004122 cyclic group Chemical group 0.000 abstract description 3
- 239000002245 particle Substances 0.000 description 11
- 238000013461 design Methods 0.000 description 10
- 239000003921 oil Substances 0.000 description 9
- 238000007789 sealing Methods 0.000 description 9
- RDYMFSUJUZBWLH-UHFFFAOYSA-N endosulfan Chemical compound C12COS(=O)OCC2C2(Cl)C(Cl)=C(Cl)C1(Cl)C2(Cl)Cl RDYMFSUJUZBWLH-UHFFFAOYSA-N 0.000 description 7
- 239000003595 mist Substances 0.000 description 7
- 230000000694 effects Effects 0.000 description 6
- 230000007704 transition Effects 0.000 description 6
- 230000010349 pulsation Effects 0.000 description 5
- 230000009471 action Effects 0.000 description 4
- 230000008021 deposition Effects 0.000 description 4
- 238000012546 transfer Methods 0.000 description 4
- 238000005096 rolling process Methods 0.000 description 3
- 239000000243 solution Substances 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000010705 motor oil Substances 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 238000003860 storage Methods 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 229910001018 Cast iron Inorganic materials 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000011109 contamination Methods 0.000 description 1
- 230000001186 cumulative effect Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 229920001971 elastomer Polymers 0.000 description 1
- 239000000806 elastomer Substances 0.000 description 1
- 238000011010 flushing procedure Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000002156 mixing Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000012549 training Methods 0.000 description 1
- 238000009736 wetting Methods 0.000 description 1
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.
- Camshaft adjusters can be roughly classified as follows:
- phase adjuster with an actuator, so a functional unit which engages in the mass flow or energy flow, which is for example formed hydraulically, electrically or mechanically, and rotates with gear elements of the camshaft adjuster.
- phase adjuster with a separate actuator, ie a functional unit in which from the controller output variable required for the control of the actuator control variable is formed, and a separate actuator
- Phase adjuster with a co-rotating actuator and a co-rotating actuator such as a high-ratio gearbox whose adjusting shaft can be advanced by a co-rotating hydraulic motor or centrifugal motor and can be reset by means of a spring.
- Phase adjuster with a co-rotating actuator and a stationary motor-fixed actuator such as an electric motor or an electric or mechanical brake, see DE 100 38 354 A1, DE 102 05 034 A1, EP 1 043 482 B1.
- Phase adjuster with a directional combination of the solutions according to a. and b. For example, a motor-mounted brake, in which a part of the braking power is used, for example, for adjusting to early to tension a spring, which allows the return adjustment after switching off the brake, s. a. DE 102 24 446 A1, WO 03-098010, US 2003 0226534, DE 103 17 607 A1.
- 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 cam phaser 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 present invention is based on the object
- the object is achieved by the features of claim 1. Further embodiments of the solutions according to the invention will become apparent according to the dependent claims 2 to 5.
- 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 increasing over time can be formed, which drops back to zero after reaching a maximum (flushing holes), whereby the time signal of the excess volume flow can be predetermined. Possibly.
- 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.
- 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 for an open crossover cross section with increasing speed.
- Figure 1 is a schematic representation of a camshaft adjuster
- Figure 2 is a schematic representation of a camshaft adjuster with a swash plate transmission
- FIG. 3 shows a camshaft adjuster in a schematic representation with a lubricant circuit
- Figure 4 shows a camshaft adjuster in a schematic representation with a lubricant circuit, in which a filter element is integrated;
- Figure 5 shows a camshaft adjuster in the half-longitudinal section with a Dead space for the deposition of dirt particles
- Figure 6 shows a camshaft adjuster in a schematic representation with a lubricant circuit which is equipped both on the input side and on the output side with a throttle and a diaphragm;
- Figure 7 shows a camshaft adjuster in longitudinal section with the leadership of
- Figure 8 shows a camshaft adjuster in longitudinal section, in which in a
- Figure 9 shows a phaser in longitudinal section with a patch on a central screw flow element which forms an aperture with an inner circumferential surface of the camshaft
- FIG. 10 shows a longitudinal section of a camshaft adjuster with a diaphragm formed between a hollow shaft and a central screw;
- FIG. 11 shows a camshaft adjuster in longitudinal section with the supply of a lubricant via a crossover cross section from an outlet opening of the cylinder head to an inlet cross section of the camshaft;
- Figure 12 shows a further embodiment of a supply of a lubricant to a camshaft and a phaser in a longitudinal section
- FIG. 13 shows a further embodiment of a supply of a lubricant to a camshaft and to a camshaft adjuster in a longitudinal section
- FIG. 14 shows a further embodiment of a supply of a lubricant to a camshaft and to a camshaft adjuster in a longitudinal section
- Figure 15 further embodiment of a supply of a lubricant to a camshaft and a phaser in a longitudinal section;
- FIG. 16 shows a longitudinal section of a camshaft adjuster with different examples of an arrangement of orifices or throttles for influencing the flow of a lubricant
- FIG. 17 is a perspective view of a camshaft adjuster with openings of a housing of the transmission for passage of the lubricant in the form of drops, lubricant mist or sprayed lubricant;
- FIG. 18 shows a further spatial view of the camshaft adjuster according to FIG. 17 with further possibilities for openings
- FIG. 20 shows a camshaft adjuster in the installed state in side view with a drip plate, on which drops of an oil mist are deposited and drop in the direction of the interior of the camshaft adjuster.
- FIG. 1 shows a schematic representation of a camshaft adjuster 1 in which the movement of two input elements, here a drive wheel 3 and an adjusting shaft 4 (also called a wobble shaft) to an output movement of an output element, in this case a rotationally fixed manner to a camshaft, is connected in a gearbox 2 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 surroundings, for example the cylinder head 8 or another part fixed to the engine.
- FIG. 2 shows an exemplary embodiment of a camshaft adjuster 1 with a gearbox 2 in a swash plate design.
- 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 relative to the cylinder head 8 with a sealing element 1 1.
- 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 Abbybsgelgel 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 on circumferentially offset portions with one another with the drive bevel gear 20 and on the other hand with the output bevel gear 18 meshes, between Abtsbsgelrad and Abtriebskegelrad an over - or reduction is given.
- the driven bevel gear 18 is rotatably connected to the camshaft 6.
- the hollow shaft 16 is screwed with Abtriebskegelrad 18 via a central screw 22 which extends through the hollow shaft 16, frontally with the camshaft 6.
- Lubrication with a lubricant, in particular oil, is required in the area of lubrication points 23, 24, which are, for example, at
- a continuous, cyclic, pulsating or intermittent supply and / or forwarding of a lubricant via lubricant channels takes place.
- the lubricant Via a Zunaturalaus Principleung 25 of the cylinder head 8, the lubricant is fed to a flow channel 26 of the camshaft 6, which communicates with a flow channel 27, which is hollow cylindrical between an inner circumferential surface 28 of the hollow shaft 16 and an outer circumferential surface 29 of the central screw 22 is formed.
- a radial bores 30 of the hollow shaft 16 the lubricant from the flow channel 27 can pass radially outward and are supplied to the lubrication points.
- FIG. 3 shows a schematic lubricant circuit.
- the lubricant is supplied 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 feed recess 25 and the flow pump. mungskanal 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 schematic lubricant circuit according to FIG. 4 has an additional filter element 35.
- the filter element 35 is preferably assigned to the camshaft adjuster 1 and arranged, for example, after a branch of the lubricant circuit to further components to be lubricated and exclusively associated 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 can serve to keep machining residues in flow channels, which are arranged upstream of the filter element 35, away from flow channels 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, for example.
- the filter element 35 may, for example, as
- a sieve a sieve, a ring filter, a plug-in filter, a cap filter, Filter plates, filter net or sintered filter
- 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 almost 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 in the circumferential direction relative to the housing 9 can move , 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 net and in the area of the camshaft, which can be achieved so 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.
- a dirt separation takes place in that the lubricant is guided in a flow channel labyrinth-like 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.
- the schematic lubricant circuit has an input-side diaphragm 41 and an input-side throttle 42 and an output-side diaphragm 43 and an output-side throttle 44.
- the diaphragms 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 orifices 41, 43 and throttles 42, 44 can be used to throttle the volume flow to the camshaft adjuster.
- An additional throttling can result from the use of the filter element 35.
- the filter element 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 continuously variable or in stages variable flow element can be used. It is possible to use a flow element, its flow effect
- 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.
- 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 recess 48 introduced with rectangular in the longitudinal section shown geometry.
- a portion of the lubricant supplied to the recess 48 via the receiving channel 45 and bore 46 passes via an axial bore 49 of the camshaft
- the other part of the groove 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 circular cross-section to at least one radial bore 52 to a lubrication point, for example, the bearing 17 or 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 a type of aperture can be created for a partial overlap of the bores with a small transitional cross section or aperture cross section, although the bores 49, 50 can be made in themselves with relatively large diameters and thus coarse tools ,
- the extension of the hollow shaft 16 in the longitudinal direction is extended in the longitudinal direction for the exemplary embodiment shown in FIG. 8 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 defining the transverse surface 55, and an edge 56, of the outer circumferential surface 57 of the hollow shaft 16 and a ner 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 according to FIG. 9 does not have a recess 48.
- the bores 49, 50 and the transitional area 53 are not provided, so that the lubricant completely flows out of the bore 46 the flow channel 51 is supplied.
- 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, 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 face this leg forms an annular gap 60 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 gradual 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 to the rotating camshaft 6 is generally carried out by means of a known rotary transformer.
- This is usually an annular groove 64 of the outer lateral surface of the camshaft 6.
- the annular groove 64 is enclosed by a corresponding cylindrical lateral surface 65 of the cylinder head 8, to which an axial groove 64 aligned to the groove 64 or feed channel 66 leads from the lubricant gallery.
- the feed channel 66 can radially penetrate the lateral surface 65, as shown in FIG. 11, or break it through, 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 circumferential surface of the camshaft 6 may have a groove running over part of its circumference in the transition region between the supply channel 66 and the receiving channel 69, so that passage from the supply channel 66 to the receiving channel 69 is possible how 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 better mixing and wetting of the lubrication points with the lubricant.
- the risk of blockages for example, of diaphragms or chokes, be reduced.
- Figure 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 bores 71 of the camshaft and the bores 72 of the housing 9, a circumferential annular groove 73 is provided, whereby the holes 71, 72 do not have to be aligned coaxially with each other during assembly.
- FIG. 13 shows an exemplary embodiment which substantially corresponds to the exemplary embodiment according to FIG. 9, although no flow element 59 is provided.
- FIG. 14 shows an exemplary embodiment in which the annular groove 64 is connected directly to the annular channel 73 via a bore or receiving channel 74 inclined relative to the longitudinal axis 21 - 21 and the transverse axis.
- an annular channel between 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.
- Figure 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 arrangement of the openings 77, 78 of the transmission 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. E- it is also conceivable that a point or an area outside 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 outside of the transmission, 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 lubrication points such as plain bearings and / or gears, be equipped with emergency running properties.
- emergency running properties can, for example
- 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.
Abstract
Description
Claims
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 true EP1963629A1 (de) | 2008-09-03 |
EP1963629B1 EP1963629B1 (de) | 2009-06-24 |
Family
ID=37913599
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06830088A Expired - Fee Related EP1963629B1 (de) | 2005-12-15 | 2006-11-23 | Nockenwellenversteller |
Country Status (6)
Country | Link |
---|---|
US (1) | US7934478B2 (de) |
EP (1) | EP1963629B1 (de) |
JP (1) | JP4982503B2 (de) |
CN (1) | CN101331298B (de) |
DE (2) | DE102005059840A1 (de) |
WO (1) | WO2007071518A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105370334A (zh) * | 2015-11-23 | 2016-03-02 | 重庆祥吉机械制造有限公司 | 一种新型凸轮轴结构 |
Families Citing this family (7)
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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 |
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JPS6090508U (ja) * | 1983-11-28 | 1985-06-21 | 富士重工業株式会社 | カムシヤフトの潤滑油供給装置 |
JPS6170510U (de) * | 1984-10-15 | 1986-05-14 | ||
JPS6197508U (de) * | 1984-11-30 | 1986-06-23 | ||
JPH04232321A (ja) * | 1990-12-28 | 1992-08-20 | Mazda Motor Corp | エンジンの動弁装置 |
JPH1037722A (ja) | 1996-07-25 | 1998-02-10 | Toyota Motor Corp | 内燃機関におけるオイルの供給構造 |
JP3834890B2 (ja) * | 1996-10-15 | 2006-10-18 | トヨタ自動車株式会社 | 内燃機関のバルブ特性制御装置 |
JP3786511B2 (ja) * | 1997-11-20 | 2006-06-14 | 株式会社日本自動車部品総合研究所 | 内燃機関の潤滑油回路における油量制御装置 |
US6328006B1 (en) | 1999-03-23 | 2001-12-11 | Tcg Unitech Aktiengesellschaft | Device for adjusting the phase angle of a camshaft of an internal combustion engine |
JP3798924B2 (ja) * | 1999-07-27 | 2006-07-19 | 株式会社日立製作所 | 内燃機関のバルブタイミング制御装置 |
JP2001107709A (ja) * | 1999-10-06 | 2001-04-17 | Unisia Jecs Corp | 内燃機関のバルブタイミング制御装置 |
DE10038354C2 (de) * | 2000-08-05 | 2003-03-20 | Atlas Fahrzeugtechnik Gmbh | Steuereinrichtung zum Verstellen des Drehwinkels einer Nockenwelle |
DE10205034A1 (de) | 2002-02-07 | 2003-08-21 | Daimler Chrysler Ag | Vorrichtung zum geregelten Verstellen der relativen Drehlage zwischen einer Kurbelwelle und einer Nockenwelle |
JP3937164B2 (ja) | 2002-04-19 | 2007-06-27 | 株式会社デンソー | バルブタイミング調整装置 |
DE10222475A1 (de) | 2002-05-22 | 2003-12-04 | Atlas Fahrzeugtechnik Gmbh | Getriebe mit zwei ineinander angeordneten Drehscheiben, die durch eine Taumelscheibe miteinander verbunden sind |
DE10224446A1 (de) | 2002-06-01 | 2003-12-11 | Daimler Chrysler Ag | Vorrichtung zur relativen Winkelverstellung zwischen zwei rotierenden Elementen |
JP3986371B2 (ja) * | 2002-06-07 | 2007-10-03 | 株式会社日立製作所 | 内燃機関のバルブタイミング制御装置 |
US6935297B2 (en) * | 2002-07-24 | 2005-08-30 | Honda Giken Kogyo Kabushiki Kaisha | Lubricating system for 4-cycle engine |
DE10248355A1 (de) * | 2002-10-17 | 2004-04-29 | Ina-Schaeffler Kg | Nockenwellenversteller mit elektrischem Antrieb |
JP4166631B2 (ja) * | 2003-06-05 | 2008-10-15 | 三菱電機株式会社 | バルブタイミング調整装置 |
DE102004038681B4 (de) * | 2004-08-10 | 2017-06-01 | Schaeffler Technologies AG & Co. KG | Elektromotorischer Nockenwellenversteller |
DE102004062067B4 (de) * | 2004-12-23 | 2017-06-08 | Schaeffler Technologies AG & Co. KG | Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine |
-
2005
- 2005-12-15 DE DE102005059840A patent/DE102005059840A1/de not_active Withdrawn
-
2006
- 2006-11-23 JP JP2008544927A patent/JP4982503B2/ja not_active Expired - Fee Related
- 2006-11-23 EP EP06830088A patent/EP1963629B1/de not_active Expired - Fee Related
- 2006-11-23 CN CN2006800471164A patent/CN101331298B/zh not_active Expired - Fee Related
- 2006-11-23 WO PCT/EP2006/068804 patent/WO2007071518A1/de active Application Filing
- 2006-11-23 DE DE502006004091T patent/DE502006004091D1/de active Active
- 2006-11-23 US US12/097,603 patent/US7934478B2/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105370334A (zh) * | 2015-11-23 | 2016-03-02 | 重庆祥吉机械制造有限公司 | 一种新型凸轮轴结构 |
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 |
Also Published As
Publication number | Publication date |
---|---|
US7934478B2 (en) | 2011-05-03 |
CN101331298B (zh) | 2010-12-15 |
JP2010510420A (ja) | 2010-04-02 |
DE102005059840A1 (de) | 2007-06-28 |
EP1963629B1 (de) | 2009-06-24 |
CN101331298A (zh) | 2008-12-24 |
DE502006004091D1 (de) | 2009-08-06 |
US20080308054A1 (en) | 2008-12-18 |
JP4982503B2 (ja) | 2012-07-25 |
WO2007071518A1 (de) | 2007-06-28 |
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