EP1844215A1 - Arbre a cames pourvu de cames pouvant tourner en sens contraire, en particulier pour des vehicules a moteur - Google Patents

Arbre a cames pourvu de cames pouvant tourner en sens contraire, en particulier pour des vehicules a moteur

Info

Publication number
EP1844215A1
EP1844215A1 EP06705777A EP06705777A EP1844215A1 EP 1844215 A1 EP1844215 A1 EP 1844215A1 EP 06705777 A EP06705777 A EP 06705777A EP 06705777 A EP06705777 A EP 06705777A EP 1844215 A1 EP1844215 A1 EP 1844215A1
Authority
EP
European Patent Office
Prior art keywords
camshaft
outer shaft
shaft
features
axial
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
Application number
EP06705777A
Other languages
German (de)
English (en)
Other versions
EP1844215B1 (fr
Inventor
Markus Lettmann
Roland Schacherer
Falk Schneider
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.)
Mahle International GmbH
Original Assignee
Mahle International GmbH
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 Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP1844215A1 publication Critical patent/EP1844215A1/fr
Application granted granted Critical
Publication of EP1844215B1 publication Critical patent/EP1844215B1/fr
Ceased legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • 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
    • 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
    • F01L2001/3444—Oil filters
    • 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
    • F01L2303/00—Manufacturing of components used in valve arrangements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49229—Prime mover or fluid pump making
    • Y10T29/49293—Camshaft making
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2102—Adjustable

Definitions

  • the invention relates to a camshaft with mutually rotatable cams for motor vehicles in particular, according to the features a to c, in particular a to e of the preamble of patent claim 1.
  • the invention is concerned with the problem to add the mutually movable elements de camshaft so and store that a possible frictionless movement of the parts with each other fert tion and operationally safely ensured.
  • the invention proposes a number of measures, each of which contributes to solving the problem of the invention, whereby a partial or complete combination of all of these features will in each case improve the achievable result, up to an optimum result a combination of all proposed individual measures.
  • the advantage of the solution measure according to claim 1 is there in, from the drive of the camshaft outgoing support transverse forces acting radially to the camshaft axis, abwei chend of previously known versions do not attack on the inner shaft, but on the overall more resistant outer shaft.
  • the measure according to claim 2 has various advantages.
  • Egg first advantage is that a simp che and secure axial fixation between the outer and inner shaft can be achieved on the there vorl gene pinning between inner and outer shaft. It is of particular advantage that the fixation only at one end of the cam. wave, so that different expansions Währe: the camshaft operation between inner and outer shaft a "the axial fixation can exert no influence, which could lead to an increase in friction with a movement between the two waves.
  • a further advantage is that a force transmission element which can be easily connected between the camshaft drive and the shaft which is to be connected to this force transmission element via the pin firmly connected to the respective shaft.
  • Simply connectable means that the connecting elements can easily be produced with the lowest tolerances with respect to the connection.
  • the embodiments according to claims 3 to 6 represent further advantages, which will be explained in more detail below in the context of abuts ⁇ example.
  • the measure according to claim 7 relates to a camshaft design, in which the drive connection means comprise a camshaft operation under no load at high lubricating oil pressure, which is directly adjacent to the inner shaft. This results in an axial load on the inner shaft, with the result that adjusts a frictional force by this axial load at a rotation of the inner shaft. To avoid this consequence, is relieved of pressure by the measure according to claim of the angren in the manner described above to the inner shaft Zende space.
  • a particularly advantageous embodiment is the subject of claim 8.
  • the inner shaft is suspended in the cams practically via the connecting means connecting them with the cams.
  • the measure according to claim 9 relates to the following problem.
  • the annular gap between the inner and outer shaft is basically lubricated with pressure oil.
  • the pressure oil is introduced via located on the outer shaft bearing rings by provided in this, radial holes, which in turn are aligned with radial holes in the outer shaft, in the annular gap. Dam the pressure oil can not escape axially from the annular gap, so far, the axial end portions of the outer shaft into which the annular gap opens, sealed axially outside. This results between the seals and the inner shaft clearances that are filled by pressure oil. If such a seal Ii diglich provided at one end of the inner shaft with axial distance zi of the end face of this inner shaft, the result is a friction-inducing pressurization of the inner shaft in the axial direction. This problem is solved by the measure "according to claim 10 simply and safely.
  • the embodiment according to claim 10 represents a simplification that reduces manufacturing costs.
  • the I. nenwelle relative to the outer shaft lengthwise according to claim 13 shorten.
  • the inner shaft can be shortened so far that they are just below the last adjustable cam at this end to lie korru which leads to a weight saving of the overall wave.
  • This manufacturing process is based on the following consideration.
  • the inner shaft is in each case by a direct mounted radial system within the outer shaft, wherein di can be done by ger over the length of the camshaft axially spaced La.
  • the rotatably mounted on the outer shaft cam are usually pinned to the inner shaft, wherein the respective pins are guided irriwelle through a recess of the Au.
  • the recess has in the circumferential direction of the camshaft a size that specifies the angle of rotation of the relevant, associated with the inner shaft cam.
  • D bores within the cams and the inner shaft can be in practice, however, often not so tolerant free manufacture that the pins used in the supercooled state can be pushed force-free in particular the inner shaft. If insertion under force, so kan this can lead to bending of the inner shaft, which in turn can lead to jamming of the inner shaft in the statedwe Ie. If the camshaft is then still functional at all, twisting the inner shaft against the outer shaft causes undesirably high friction and such high friction is not permissible because of an often associated, for the operation nich acceptable reaction time magnification with an adjustment of the cam against each other during of camshaft operation In a production of a generic camshaft na claim 14, the above-described problems v not occur at all in advance.
  • the inner shaft Before pinning the inner shaft with the cams rotatably supported on the outer shaft, the inner shaft is pushed into the outer shaft in a state in which it is inserted by a thin mounting sleeve of incompressible material such as steel. During this state, in which the inner shaft is almost free of play within the outer shaft in a kind of sliding seat, the pegs can be pinned to the inner shaft. In order to make this pinning before, the pins must be passed through the mounting sleeve. In addition, after the pinning, the mounting sleeve of the inner shaft must be able to be pulled completely a. For this purpose, the mounting sleeve to the end of the sleeve has open, axial grooves.
  • FIG. 1 shows a schematic representation of the connection means of a camshaft to a rotary drive
  • FIG. 2 shows a section through a camshaft drawn in length
  • Fig. 3 is a plan view of the camshaft of FIG. . ' 4 shows a section through the camshaft along the line IV-IV in FIG. 2,
  • Fig. 5 is a perspective view of a camshaft according to FIGS. 2, 3.
  • Fig. ⁇ a, b is a view (a) of a section of the camshaft and a longitudinal section (b) through this section,
  • Fig. 7 shows a detail of the right-hand end region of a camshaft according to FIG. 2 in a modified embodiment
  • Fig. 8 shows a section of the right-hand end region of a camshaft according to FIG. 2 in a further modi fixed embodiment with an axial ⁇ lzurine channel within the outer shaft and a FiI ter in this feed,
  • FIG. 9 is a camshaft of Figure 2 in a further modified embodiment with an axial ⁇ lz guide channel within the outer shaft and in this channel axially conveying ⁇ lleinspritzei direction,
  • Fig. 10 is a section of the right end portion of a camshaft of FIG. 2 in a turn modi ficated embodiment with an axial ⁇ lzurine channel within the outer shaft and an axially communicating with this channel oil supply spatial,
  • Fig. 11 shows a section of the left end region of a camshaft according to FIG. 2 with a modified.
  • Twist device, Fig. 12a, b show a detail of a middle region e of a camshaft according to FIG. 2 with a different axial fixation between inner and outer shaft.
  • Fig. 13a, b show a detail of a left end region e of a camshaft similar to FIG. 2 with an axially shortened drive connection means in a longitudinal section (a) and in a plan view (b)
  • Fig. 14a, b show a section of a left end region e of a camshaft similar to FIG. 2 with an axially shortened drive connection means in an alternative embodiment to FIG. 13 in a longitudinal section (a), in a plan view (b) and in a section (c) according to line XIIV c - XIV c in part (a)
  • An adjustable camshaft comprises an outer shaft 1 mi in this superimposed inner shaft 2.
  • the inner shaft 2 i pinned with rotatably mounted on the outer shaft 1 ers th cam 3 in the form of double cams.
  • the pinning is in each case given by equally pressed into the cam 3 un in the inner shaft 2 pins 4.
  • the pins 4 are preferably subcooled in the corresponding holes of the j e election cam 3 and the inner shaft 2 is inserted.
  • the wife; Press seats adjust to a sufficient height at temperature compensation.
  • an introduction of the pins at Jardintemperat ⁇ is possible.
  • Cams 3 are firmly connected to the outer shaft 1 second cam 5 and also firmly connected to the outer shaft 1 bearing rings. 6
  • a camshaft having the above-described components is in its, a 'camshaft drive zugwandten end portion in FIG. 1 shown schematically.
  • a stationary bearing of the camshaft is due to the location
  • a belt operation via which the camshaft is driven by the crankshaft of an automobile engine is designated by 9.
  • this belt drive 9 can also be a chain drive or a drive b of any kind.
  • connection means 10 of the Nockenwe Ie acts on a drive connection means 10 of the Nockenwe Ie.
  • This connection means 10 is supported with respect to a transverse force stress with respect to the axis of the cam shaft via bearing elements 11 on the outer shaft 1 from.
  • the drive to connection means 10 also has Drehmomentübertra supply means 12, with the aid of which the camshaft on the one hand driven in terms of speed and with which on the other hand, the g gen worne rotatability between inner and outer shaft 2 1 relative to the connection means 10 can be generated.
  • De type devices are known in the art, we do not go further here on details of these known A drive and adjustment is received. Due to the schematic representation in FIG.
  • a mounting sleeve 13 is pushed with a push fit. Together with the mounting sleeve 13, the inner shaft 2 is then inserted into the outer shaft 1.
  • the mounting sleeve 13 is made of incompressible material, in particular a thin steel sheet.
  • the thickness of the mounting sleeves 13 wall determines the radial clearance between the inner and outer shaft 2, 1. This means in other words, the radial clearance between the inner and outer shaft 2, 1 is to be interpreted as that the inner shaft 2 can be inserted with mounted mounting sleeve 13 in the outer shaft 1.
  • the pinning between the inner shaft 2 and the first cam 3 associated therewith takes place in a state in which the mounting sleeve 13 is located between the inner and outer shaft 2.
  • radial recesses in the outer shaft 1 un in the mounting sleeve 13 must be connected.
  • the recesses in the outer shaft 1 are formed as in the circumferential direction of the outer shaft extending slots whose length limits the displacement between the outer and inner shaft 1, 2.
  • the mounting sleeve 13 are located at one of their ends diametrically opposite, axial grooves 14, the ax open axially from the mounting sleeve 13.
  • the pins 4 j can be mounted in each case.
  • the assembly of the pins 4 is effected by a force-fitting pressing into holes of the first cam 3 in each case and the inner shaft 2. In this way, a press-fit connection between the first cam 3 and the inner shaft 2 is achieved.
  • the pins 4 are undercooled i introduced the respective holes of the first cam 3 and réellewe Ie 2. In this case, in particular radial egg pressing forces occur when the holes into which the Stif 4 are to be introduced, are not exactly aligned by manufacturing tolerance deviations.
  • the inner shaft 1 undergoes radial engagement with the egg Pressing forces virtually do not bend along its axis, it is prevented by the form fit in the annular gap between the inner and outer shaft 2, 1 mounting sleeve 13 thereto. This can only take place a shift of the inner shaft 2 to the small sliding seat clearance of the mounting sleeve 1 within the annular gap between the inner and outer shaft 2 1. Such a shift would, even if it occurred, not critical, since after removing the mounting sleeve 13 remains unopposed by such a displacement wheel aspiel.
  • the pinning of the individual first cam 3 always starts at one end of the camshaft and then proceeds over the length of the camshaft with a stepwise withdrawal of the mounting sleeve 13 out of the outer shaft 1. Such pulling out of the mounting sleeve 13 is necessary in order to be able to insert the pins 4 in each case through the axial grooves 14.
  • the mounting sleeve 13 is completely separated from the camshaft. The state in which this volli separation takes place is shown in Fig. 2 and 3 at the right end of the camshaft.
  • the mounting sleeve 13 can then be used for the assembly of further corresponding camshafts.
  • the first cams 3 are designed as double cams.
  • Herg> is such a double cam as per se known g built camshafts by individual cam 3 ', 3''passgena 1 shrunk onto a base tube 3'''.
  • the pin 4 only engages in the base tube 3 '. in and in a region which lies axially between the two cams 3 '''and3''.
  • a Schrumpfverbind ⁇ are alternatively or additionally still connections by Kl ben, welding, expansion of the base tube 3 ''', any ges form-fitting method or the like possible.
  • the assembly of the individual cams 3 ', 3''and a base tube 3' ' '', with which they are firmly connected, can additionally contain additional functional elements of the camshaft.
  • Fig. 6 for example, one with the Ba sisrohr 3 '''firmly connected, on its circumference positioning sections having rotary encoder (26) as a func onselement.
  • a spring through which in an inactive Verstel drive the camshaft a predeterminable Drehwinkelzuor tion between inner and outer shaft 2, 1 is automatically turned is.
  • the spring_ is to be connected for this purpose to the inner u outer shaft 2, 1.
  • This spring is not shown in the drawing.
  • the annular gap 15 between the inner and outer shaft 2, 1 supplied with supplied under pressure lubricating oil is supplied with supplied under pressure lubricating oil.
  • the bearing rings 6 as shown in FIG. 4 four feed bores gene 16 provided. From this annular channel 17 lead from only two Radialbohrun conditions 18 in the annular gap 15.
  • a special feature is that fewer radial bores 18 a Zu Industriesbohrept 16 are provided. This peculiarity is made possible by the fact that the supply bores 16 are not supplied ra dial externally of a ring-shaped upcoming lubricating oil source, but in each case sections by alignment with radially oriented, corresponding, not shown in de drawing supply channels.
  • annular gap 15 In order to prevent pressurized lubricating oil can escape from the annular gap 15 at the ends of the inner shaft 2, there are provided in each case the annular gap 15 sealing Ringdid lines 19.
  • Camshaft drive connection means 10 received in more detail and in the first place with reference to FIGS. 2 and 3.
  • connection flange 7 which is part of the drive connection means 10.
  • connection flange 7 are rad: ale recesses 20 provided through which a Anschlußsti 21 engages.
  • the connecting pin 23 frictionally passes through a corresponding bore within the inner shaft 2.
  • the radial recesses 20 have a length in the circumferential direction which determines the adjustment angle between the inner and outer shafts 2, 1.
  • the connecting pin 21 represents a first force transmission element.
  • the drive connection means 10 a second power transmission element - not shown - positively and positively connected.
  • the connection is made in a simple way de by that the second power transmission element has an axially aligned, the first power transmission element 21 associated axial groove, whereby the second Kraftübertre transmission element can be accurately pushed pa ⁇ to the first force transmission element 21.
  • pin 21 Another function of the pin 21 is dari the inner shaft 2 relative to the outer shaft 1 axially to Fixie ren. In this way, an extremely simple, axial fi xation of the inner shaft 2 within the outer shaft 1 is erreic only at one end of the camshaft. Hierdurc remain different expansions between the outer shaft and inner shaft 2, if such should occur without j egl Chen influence on the axial fixation between inner and outer shaft 2, 1.
  • this rr is in each case diametrically opposed planar Anschlußfläcfr in the one circumferential direction of the camshaft and on the other hand in Axial direction of the camshaft equipped.
  • only four of these four flat surfaces are designated by way of example as 22.
  • the Eckbere surface between the four flat surfaces are formed on a Kreisu catch lying.
  • the connecting pin 21 is securely and accurately fixed within the inner shaft 2.
  • connection connection means device 10 is located within the connection flange 7 a fixedly mounted cone 23 for a pressure oil supply.
  • a pressure oil supply is an annular gap 24 between this cone 23 and the connection flange I 1 of the inner shaft 2 zug applied end is sealed by a ring seal 25. In this way, no hydraulic pressure is exerted on the end of the inner shaft 2 from there, which could lead to a Reibungser increase in a rotation of the inner shaft 2 relative to the outer shaft 1.
  • a camshaft of FIG. 2 can at the right in the drawing end, which is shown in Fig. 7, in the not filled by the inner shaft 2 cavity of the A .welle 1 lubricating oil accumulate, for example, from a oil-lubricated bearing ring 6 at the end of the outer shaft 1 can penetrate into the sen space within the outer shaft 1. Sowei this penetrating oil is supplied under pressure, in a completely filled space within the Au .welle 1 an axial pressure on the adjacent to this space inner shaft 2 build. This in turn would lead to an additional friction during a relative movement between the inner and outer shafts 2, 1.
  • ra dial outwardly leading openings r 28 may be arranged in the outer shell 1 in the area in question.
  • FIGS. 8 to 10 is a ⁇ lver supply of the camshaft from the inside by an axial feed channel 29 in the outer shaft 1 at the drive side opposite end provided.
  • This oil supply is an alternative to that in the embodiment of FIGS. 2 to 4 oil supply by in the outer shaft 1 before seen radial openings 18 which are supplied by radial bores 16 of a bearing ring 6 with supplied under pressure lubrication.
  • this supply channel 29 must be able to communicate with the annular gap 15 between the inner and outer shaft 2, 1 in a seal-free manner.
  • lubricating oil introduced into the supply channel 29 under pressure through the annular gap 15 between inner outer shaft 2, 1 can flow up to the drive end d of the camshaft.
  • this lubricating oil by the in the embodiment of the camshaft of FIG. 2 provided rad ale recess 20 flow to the outside.
  • the axial Zu rawkana 29 is supplied from the provided at this end of the camshaft bearing 6 from, wherein the relevant end of the camshaft beauf by the lubrication of the bearing ring 6 beat transitional space 30 is provided, from which Bearing ring ⁇ under pressure supplied lubricating oil can flow into the interior of the outer shaft 1.
  • lubricating oil can also be introduced into the feed channel 29 through an oil spray nozzle 2 that conveys axially into the feed channel 29 in accordance with the method shown in FIG. 9 illustrated embodiment are introduced.
  • an oil injection nozzle can be used as oil supply device 32, as used for injection-cooling of a reciprocating piston of a combustion engine in a generally known manner.
  • FIG. 8 shows a camshaft with a feed channel 29, in which a filter 27 is inserted into the feed channel 29.
  • This filter 27 may be formed as a disc-shaped particle screen.
  • This particle sieve can be bell-shaped or funnel-shaped, each with a 29ic senen upstream end.
  • Such a bell-shaped design has the advantage / that from the lubricating oil abg different dirt particles due to the outgoing of the rotating camshaft centrifugal force can detach radially from the screen and attach to the inside of the tube.
  • the central filter area remains in this way auc for dirt-free operation at long operating times of the camshaft.
  • FIG. 2 takes place an axial Fixieru between inner and outer shaft 2, 1 via a radial con nection pin 21, which penetrates both shafts 1, 2.
  • An alternative to such an axial fixation between inner and outer shaft 2, 1 is shown in FIG. 12 in two different variants according to the parts a and b of this F gur.
  • the second cam 5 are provided with the axial width extending stops, u can fix the first cam 3 axially accurate fit between two neigh th, correspondingly formed second cam 5.
  • FIG. 11 in the drive connection means 10 according to the embodiment in FIG. 2 another type of oil supply provided there a hydraulic oil drive.
  • the relevant drive connection means 10 is shown in FIG. 11 denoted by 10 '.
  • This drive connection means 10 ' is provided mi ⁇ l arrangementkanälen 31.
  • These oil guide channels 31 each lead radially outward one end in a ⁇ lverso generating device 32 and the other end in a hydraulic drive 33.
  • the components 32 and 33 are indicated in the drawing only dash-dotted lines.
  • ⁇ llaysein device 32 As ⁇ lchucksein device 32 is used in the example shown, a bearing device of the camshaft, wherein the drive connecting means 10 as a fixed verbun with the outer shaft 1: dener inner bearing ring is formed while the ⁇ lvei supply by supply channels 34 within a statior ren, the inner bearing ring leading outer bearing ring are provided.
  • Such an oil supply of a hydraulically operating camshaft adjusting device is extremely advantageous since it can be realized with a few components.
  • such an oil supply device has an axially short drive-side, so that axial space can be saved.
  • the erfindunc proper camshaft may be completely or at least largely dispensed with an oil lubrication, if the mating partner on the one hand wear-coated and on the other hand provided with a hardened surface sine provided with a hardened surface insbesonde be the outer shaft and double cams.
  • the number of radial bores 39 is specified for a particular Hy raulik drive 33 with a total of 4.
  • the function of one of these four dial bores is integrated into a portion of the drive connection means 10 "which serves for other purposes. Dab is that area of the drive connection means 10 '', in which the pin 21 b is found, by the operation of the inner and outer shaft 1 can be rotated against each other.
  • the connecting pin 21 engages in the drive connection means 10 '' a ra Diale opening 20. This opening 20 fills the Anschlußstif 1 21 in ümfangsraum not because this recess 20 must allow a rotational adjustment of the pin 21 in this direction.
  • the recess 20 can fulfill the same radio tion 1 as the radial bores 39 are required zusharm 1 Liehe seals in the form of, for example Ringdichtu] gen 41 and 42nd
  • the ring seal 41 seals the space of the recess 20 with respect to the annular gap between outer and outer rings. O-ring and inner shaft 1, 2.
  • the ring seal 42 provides for a seal outward within the hydraulic drive 33rd
  • FIG. 14 shows a further alternative embodiment of the drive connection means 10 in a basic version of this drive connection means according to the embodiment in FIG. 2.
  • E axial shortening with respect to the camshaft is in c embodiment of FIG. 14 achieved by a displacement of the connecting pin 21 in the axial interior of the adjacent bearing rings, said bearing ring is an integral part of the connecting flange 7.
  • the connecting flange 7 in this example consists of a central core area as well as a bearing bearing 36 mounted on it.
  • Fig. - 14 is designed as a power transmission element through which the torque required to rotate the pin 21 is transmitted from the hydraulic drive 33 in the form of a connecting fork 38.
  • this connection is made via a positive connection in Drehric tion and that for example by a rotation 3 in the form of a tongue and groove.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)
  • Gears, Cams (AREA)
  • Lubrication Details And Ventilation Of Internal Combustion Engines (AREA)

Abstract

Arbre à cames pourvu de cames pouvant tourner en sens contraire, dans lequel la première came (3) au moins est montée rotative sur un arbre externe (1) et est reliée de manière fixe à l'arbre interne (2) à travers au moins une ouverture radiale ménagée dans l'arbre externe (1). Des moyens (10) situés à l'une des extrémités axiales de l'arbre à cames servent à la connexion avec un entraînement rotatif d'arbre à cames, et cet entraînement rotatif (9) exerçant des forces d'appui sur l'arbre à cames est en prise avec les moyens de connexion. L'objet de la présente invention est de garantir de manière sûre une ajustabilité à faible friction entre les arbres interne et externe et de permettre une fabrication à faible coût dudit arbre à cames.
EP06705777A 2005-02-03 2006-01-13 Arbre a cames pourvu de cames pouvant tourner en sens contraire, en particulier pour des vehicules a moteur Ceased EP1844215B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005005212 2005-02-03
DE102005014680A DE102005014680A1 (de) 2005-02-03 2005-03-29 Nockenwelle mit gegeneinander verdrehbaren Nocken für insbesondere Kraftfahrzeuge
PCT/DE2006/000038 WO2006081788A1 (fr) 2005-02-03 2006-01-13 Arbre a cames pourvu de cames pouvant tourner en sens contraire, en particulier pour des vehicules a moteur

Publications (2)

Publication Number Publication Date
EP1844215A1 true EP1844215A1 (fr) 2007-10-17
EP1844215B1 EP1844215B1 (fr) 2011-03-23

Family

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EP06705777A Ceased EP1844215B1 (fr) 2005-02-03 2006-01-13 Arbre a cames pourvu de cames pouvant tourner en sens contraire, en particulier pour des vehicules a moteur

Country Status (5)

Country Link
US (1) US7610890B2 (fr)
EP (1) EP1844215B1 (fr)
JP (1) JP5038908B2 (fr)
DE (3) DE202005021715U1 (fr)
WO (1) WO2006081788A1 (fr)

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Also Published As

Publication number Publication date
US20080257290A1 (en) 2008-10-23
DE502006009155D1 (de) 2011-05-05
WO2006081788A9 (fr) 2007-08-23
JP2008530412A (ja) 2008-08-07
US7610890B2 (en) 2009-11-03
DE102005014680A1 (de) 2006-08-10
JP5038908B2 (ja) 2012-10-03
EP1844215B1 (fr) 2011-03-23
DE202005021715U1 (de) 2009-07-02
WO2006081788A1 (fr) 2006-08-10

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