EP1550793B1 - Actionneur variable d'arbres à came avec une alimentation en huile sous pression intérrompue partiellement - Google Patents

Actionneur variable d'arbres à came avec une alimentation en huile sous pression intérrompue partiellement Download PDF

Info

Publication number
EP1550793B1
EP1550793B1 EP20040100003 EP04100003A EP1550793B1 EP 1550793 B1 EP1550793 B1 EP 1550793B1 EP 20040100003 EP20040100003 EP 20040100003 EP 04100003 A EP04100003 A EP 04100003A EP 1550793 B1 EP1550793 B1 EP 1550793B1
Authority
EP
European Patent Office
Prior art keywords
camshaft
bearing
annular groove
receptacle
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
EP20040100003
Other languages
German (de)
English (en)
Other versions
EP1550793A1 (fr
Inventor
Ulrich Kramer
Guido Bingen
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.)
Ford Global Technologies LLC
Original Assignee
Ford Global Technologies LLC
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 Ford Global Technologies LLC filed Critical Ford Global Technologies LLC
Priority to EP20040100003 priority Critical patent/EP1550793B1/fr
Priority to DE200450009304 priority patent/DE502004009304D1/de
Publication of EP1550793A1 publication Critical patent/EP1550793A1/fr
Application granted granted Critical
Publication of EP1550793B1 publication Critical patent/EP1550793B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

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
    • 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
    • F01L1/053—Camshafts overhead type
    • F01L1/0532—Camshafts overhead type the cams being directly in contact with the driven valve
    • 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
    • F01L1/024—Belt drive
    • 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
    • F01L1/34403—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft
    • F01L1/34406—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft the helically teethed sleeve being located in the camshaft driving pulley
    • 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
    • F01L1/34409—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 by torque-responsive means
    • 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
    • F01L2001/0476—Camshaft bearings
    • 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
    • F01L1/053—Camshafts overhead type
    • F01L2001/0537—Double overhead camshafts [DOHC]

Definitions

  • the invention relates to a system comprising a camshaft having at least one cam and camshaft receiving for supplying a device for camshaft adjustment of an internal combustion engine with pressurized oil, in which the camshaft is designed hollow in the manner that an inner camshaft passage is formed and on the one hand this inner camshaft passage with the adjustment in On the other hand, at least one camshaft connecting passage leads from the inner camshaft passage to the outer circumferential surface of the camshaft, wherein the camshaft receiving has at least one supply line leading to the inner circumferential surface of the camshaft receptacle and connectable via the camshaft connecting passage and the inner camshaft passage with the adjusting device and the supply the adjusting device with hydraulic oil is used.
  • Such systems are required to make a camshaft adjustment, with which the control times of the control elements of a valve train can be influenced.
  • the variation of the timing is a solution to reduce fuel consumption.
  • the problem is the fuel consumption and thus the efficiency, especially in gasoline engines.
  • the reason for this lies in the basic working method of the gasoline engine.
  • the Otto engine works with a homogeneous fuel-air mixture, that - if there is no direct injection - is prepared by external mixture formation by fuel is introduced into the intake air in the intake tract.
  • the desired power is adjusted by changing the filling of the combustion chamber, so that the operating method of the gasoline engine - unlike the diesel engine - is based on a quantity control.
  • This load control is usually carried out by means of a throttle valve provided in the intake tract.
  • a throttle valve provided in the intake tract.
  • the pressure of the intake air behind the throttle valve can be reduced more or less.
  • the air mass i. E. the quantity will be set.
  • the quantity control by means of throttle valve has thermodynamic disadvantages due to the pressure reduction and the associated throttle losses.
  • variable valvetrain In contrast to conventional valve trains, where both the stroke of the valves and the timing, d. H. the opening and closing times of the intake and exhaust valves, due to the non-flexible, since non-adjustable mechanism of the valve train are given as immutable variables, these parameters can be varied more or less by means of variable valve trains influencing the combustion process and thus the fuel consumption.
  • the ideal solution would be a fully variable valve control, which allows for specially tuned values for the stroke and the timing for any operating point of the gasoline engine.
  • One way to vary the timing of the valves is to use a camshaft phaser with which the camshaft can be rotated relative to the crankshaft by a certain angle so that the timing is shifted early or late.
  • Such adjusting devices are usually hydraulically actuated or controlled, wherein one or more pressure chambers are selectively acted upon with hydraulic oil or relieved.
  • Such adjusting device 100 is in the German Offenlegungsschrift DE 198 50 947 A1 described and is in FIG. 1 played.
  • a pulley 110 with a housing cover 112 and a first intermediate member 114 is rotatably connected.
  • the intermediate element 114 has radially inwardly a toothing 116, which meshes with a counter-toothing 120 arranged on an axially displaceably mounted piston device 118.
  • the piston device 118 has a second toothing 122, which engages in a second counter toothing 126 arranged on a second intermediate element 124.
  • At least one pair of gears 116, 120 and 122, 126 is helically toothed.
  • the second intermediate element 124 is non-rotatably connected to the camshaft 128, so that upon axial displacement of the piston device 118, the camshaft 128 is rotated relative to the belt wheel 110 and thus relative to the crankshaft.
  • two adjustment chambers 132, 134 are provided, wherein the piston device 118 separates the two adjustment chambers 132, 134 from one another.
  • These chambers 132, 134 are pressurized with oil through conduits 136, 138 for axial displacement, i. controlled.
  • a pressure oil supply In order to pressurize an adjusting device of the type described specifically with pressure oil, a pressure oil supply must be provided.
  • a system of the generic type as is the subject of the present invention. Such a system is in the German Offenlegungsschrift DE 197 47 244 A1 disclosed and described.
  • camshaft is a dynamically loaded component by the interaction of their cams with the valve trains of the internal combustion engine.
  • the camshaft is loaded via their cams with an additional torque when these cams accumulate on plunger of a valve train and compresses a provided in the valve train return spring. This torque counteracts the actual camshaft rotation.
  • the energy stored in the return spring is returned to the cams during the expansion phase of the spring.
  • the cams are loaded with a torque that supports the actual camshaft rotation, ie the camshaft and the torque exerted on it by the valve train torque are rectified in the closing phase of the valve.
  • the equipped with a hydraulic adjusting camshaft is supported indirectly via the oil in the adjusting device, which is why the force exerted by the valve train on the camshaft, dynamic torque leads to pressure fluctuations of the hydraulic oil in the adjustment and the leads.
  • valve in the pressure oil supply In the simplest case, this can be a non-return valve which closes automatically when there is a return flow.
  • this check valve is in principle only activated when a return flow occurs, i. the camshaft rotation has already come to a standstill.
  • the leaktightness i. significantly reduce the impermeability of the valve.
  • the valve may also be a controllable valve which is selectively closed during the phase in which the cam is running.
  • Valves with a sufficiently fast response which can be controlled without delay and with sufficient accuracy, are not available in a wide range and very expensive.
  • a system comprising a camshaft having at least one cam and camshaft receptacle for supplying a device for adjusting the camshaft of an internal combustion engine with pressurized oil, with the features according to claim 1.
  • the system according to the invention has a forced control, which, without additional costly components must be provided for effective interruption of the connection between the supply line and the adjusting device, when the cam runs on the plunger of the valve train and a provided in the valve train return spring is compressed.
  • connection does not coincide exactly with the emergence phase of the cam.
  • connection can already be interrupted before the cam rests on the tappet and, on the other hand, does not necessarily have to be restored once the maximum valve stroke has been reached.
  • the system according to the invention offers sufficient free space for any controls of the hydraulic oil supply.
  • the casserole phase of the cam - measured in degrees camshaft rotation angle - depending on the cam contour for different shaped cams can be different lengths, also the angular range in which the adjusting device is preferably to be separated from the pressure oil supply line, different in size.
  • This circumstance can be taken into account by appropriate design of the at least one annular groove, on the one hand by the expansion of the annular groove in the circumferential direction and on the other hand by the arrangement of the at least one annular groove relative to the cam or the camshaft connecting channel can be taken specifically influence on the timing, too where the connection between the supply line and the adjusting device is disconnected and restored.
  • the control of the adjusting device or the oil supply is implemented in the camshaft bearing, wherein the required for this at least one annular groove is arranged either in the outer circumferential surface of the camshaft or in the inner circumferential surface of the camshaft receiving.
  • the oil supply line which is provided for supplying the camshaft bearing with oil, simultaneously used as a supply line for the adjusting device.
  • the camshaft in the camshaft receiving camshaft or the camshaft rotation is used as such for controlling the oil supply.
  • the system according to the invention fulfills all the subtasks of a conventional pressurized oil supply system, as described in US Pat DE 197 47 244 A1 is described, namely the bearing of the camshaft and the pressure oil supply to the adjusting device.
  • the system according to the invention by the arrangement of at least one annular groove includes a control slot or a control with which the adjustment of the pressure oil supply in the emergence phase of the cam can be separated. This means that when using the system according to the invention, it is not necessary to arrange a valve in the supply line or to provide another control unit or to equip the adjusting device with such a control.
  • a control By complementing or equipping a conventional camshaft bearing with an additional design feature - namely the at least one annular groove - a control is realized, which is characterized over conventional devices in that it is much less complex and thus less prone to failure and less expensive.
  • the inventive control by means of annular groove ensures exact timing, thus has the required accuracy and also has an excellent tightness and impermeability.
  • the object underlying the invention is achieved, namely to provide an optimized spinning oil supply for a camshaft adjusting, with the known disadvantages of the prior art are overcome and with the particular adverse effects of pressure fluctuations in the oil supply to the adjustment and Verstellgenautechnik lessen Advantageous embodiments of the system in which the camshaft receiving is divided into two and a bearing arranged in the cylinder head bearing saddle and - in the assembled state - arranged on this bearing saddle bearing cap.
  • a bearing of the camshaft in a one-piece camshaft mount is in principle possible.
  • this requires either a built-up camshaft, if the camshaft does not allow its insertion into the annular camshaft receiving their free end due to their cams, or a so-called tunnel camshaft, which can be easily inserted into the one-piece camshaft.
  • camshaft is mounted in the two-piece camshaft holder.
  • the camshaft is inserted in a first assembly step in the bearing saddles, which are integrally formed with the cylinder head. They are already part of the cast cylinder head blank and get their final shape as part of a post-processing.
  • the camshaft receiving is completed by a bearing cap, wherein the bearing cap is arranged opposite the bearing saddle and braced with this.
  • the sliding bearing comprises two plain bearing half shells.
  • a plain bearing half shell is arranged in the bearing saddle and in the bearing cap.
  • the annular groove can already be taken into account in the manufacture of the slide bearing in a simple manner by the fact that the board from which the slide bearing is formed, for example, is provided as part of a punching process with a window, wherein the window forms the annular groove in the assembled state of the system according to the invention.
  • Embodiments of the system in which the bearing saddle and / or the bearing cap of the camshaft receptacle have or have an annular channel extending over the entire circumference are advantageous, wherein the annular channel - in the mounted state - is in communication with the at least one segment-like annular groove in the plain bearing ,
  • the over the entire circumference extending annular channel allows for embodiments which have more than one annular groove, the supply of the annular grooves via a common feed line.
  • the hydraulic oil passes through the supply line into the annular channel, which distributes the oil to the individual annular grooves. Without ring channel a single feed line must be provided in the camshaft holder for each annular groove.
  • the casserole phase of the cam on the ram comprises between 40 ° and 75 ° camshaft rotation angle (NWW). Consequently, in short casserole phases, the annular groove extending in the circumferential direction over a larger angle ⁇ ⁇ 320 °, wherein on the one hand, the connection between the supply line and the adjusting device is interrupted during the entire compression phase of the valve spring element and on the other hand the largest possible camshaft angle window for the pressure oil supply and -beaufschlagung the adjustment is provided.
  • the annular groove is formed in the circumferential direction longer or shorter.
  • the angle data refer to an embodiment with a cam and an annular groove, i. to the camshaft of a single-cylinder internal combustion engine with an intake valve and / or an exhaust valve.
  • a four-cam type camshaft is used, for example, in a four-cylinder in-line engine in which each cylinder has an intake valve and / or an exhaust valve.
  • Embodiments of the system in which each annular groove in the circumferential direction covers an angle ⁇ ⁇ 40 ° or an angle ⁇ ⁇ 25 ° are advantageous.
  • FIG. 1 has already been explained in connection with the description of the prior art.
  • FIGS. 2a and 2 B show a first embodiment of the system 1 in cross section.
  • the system 1 has a camshaft receptacle 2 which is divided into two and comprises a bearing cap 3 and a bearing saddle 4.
  • the camshaft 9 is arranged and mounted, wherein the camshaft 9 has a cam 10 in the illustrated embodiment.
  • FIG. 2a Shown is the system 1 in FIG. 2a at the beginning of the start-up phase of the cam 10 on a plunger 26 of a - not shown - valvetrain, whereas FIG. 2b the system 1 after the start-up phase ie after exceeding the maximum valve lift shows. It is therefore at FIG. 2a a snapshot, the system 1 at the beginning of the compression phase of a valve spring 27, on which the plunger 26 is supported, shows. at FIG. 2b on the other hand, it is a snapshot showing the system 1 in the expansion phase of the valve spring 27.
  • the camshaft 9 In the compression phase of the valve spring 27, the camshaft 9 is loaded via the cam 10 with a dynamic torque, which is opposite to the actual rotational movement of the camshaft 9. To avoid adverse effects of this dynamic torque on the pressure oil supply or a - not shown - adjustment, the connection between pressure oil supply and adjustment in the compression phase of the valve spring 27 that is in the casserole phase of the cam 10 - FIG. 2a shown - separated.
  • the system 1 has a segment-like annular groove 21, which is provided in the inner circumferential surface 20 of the camshaft receptacle 2 in the region of the feed line 5 and extends in the circumferential direction. If the cam 10 is not in the run-up phase, the pressure oil supply is in communication with the adjusting device. It will - like FIG. 2b can be seen - the adjusting device via the supply line 5, the annular groove 21, the camshaft connecting passage 15 and the inner camshaft passage 14, which leads to the adjusting supplied with pressurized oil.
  • the pressure oil passes through this camshaft connecting passage 15 in the interior of the camshaft 9 d. H. in the inner camshaft passage 14 and from there to the adjusting device.
  • the annular groove 21 is designed and arranged in such a way that the connection between the supply line 5 and the adjusting device in the compression phase of the valve spring 27 d. H. is separated in the emergence phase of the cam 10.
  • the pressure oil supply is suppressed over a camshaft rotation angle of about 65 °. The separation takes place in that the connection between the annular groove 21 and the camshaft connecting channel 15 is released.
  • the camshaft connecting channel 15 is closed at its lying on the outer circumferential surface 19 of the camshaft 9 end by the inner circumferential surface 20 of the camshaft receiver 2.
  • FIGS. 3a and 3b show a second embodiment of the system 1 in cross section. Shown is the system 1 in FIG. 3a at the beginning of the casserole phase of the cam 10 on the plunger 26, whereas FIG. 3b the system 1 after Exceeding the maximum valve lift shows. It is therefore at FIG. 3a by a snapshot that shows the system 1 at the beginning of the compression phase of the valve spring 27, whereas it is at FIG. 2b is a snapshot that shows the system 1 in the expansion phase of the valve spring 27.
  • the segment-like annular groove 22 is arranged in the second embodiment in the outer circumferential surface 19 of the camshaft 9 in the region of the camshaft connection channel 15. Otherwise, reference is made to the FIGS. 2a and 2 B and the statements made in connection with these figures. The same reference numerals have been used for the same components.
  • FIG. 4 shows a snapshot of a third embodiment of the system in cross section. Shown is the system 1 at the beginning of the compression phase of the valve spring 27th
  • the third embodiment is characterized in that on the one hand, the camshaft 9 has four camshaft connecting channels 15,16,17,18 and four each offset by 90 ° on its circumference cams 10,11,12,13 and on the other hand, the camshaft receiving with four leads 5,6,7,8 and four annular grooves 21,22,23,24 is provided.
  • the four segment-like annular grooves 21,22,23,24 are arranged in the inner circumferential surface 20 of the camshaft receptacle 2, wherein the annular grooves 21,22,23,24 each cover an angle ⁇ ⁇ 30 ° and are regularly spaced in the circumferential direction.
  • annular grooves 21,22,23,24 arranged in a sliding bearing, these annular grooves 21,22,23,24 could be supplied via a common feed line by an annular channel is formed in the camshaft receiver 2, which with the common supply line and the annular grooves 21,22,23,24 in the plain bearing is in communication.
  • FIGS. 2a . 2 B . 3a and 3b are identical to the same reference numerals.
  • the same reference numerals have been used for the same components.
  • FIG. 5 shows a fourth embodiment of the system 1 in a perspective view.
  • This embodiment is characterized in that a bearing cap 3a for an intake camshaft and an adjacent bearing cap 3b for an exhaust camshaft are formed integrally in the form of a bearing bridge 25. This reduces the number of components and increases the rigidity of the entire system.
  • the bearing bridge 25 forms, together with two bearing saddles 4, two camshaft receptacles 2, in whose inner lateral surfaces 20 segment-like annular grooves 21 are provided, which are supplied with feed oil via supply lines 5.

Claims (13)

  1. Système (1) constitué d'un arbre à came (9) comprenant au moins une came (10, 11, 12, 13) et un logement d'arbre à came (2) pour l'alimentation d'un dispositif (100) de réglage d'arbre à came d'un moteur à combustion interne avec de l'huile sous pression, dans lequel l'arbre à came (9) est réalisé sous forme creuse, de telle sorte qu'un canal interne d'arbre à came (14) soit réalisé et que d'une part ce canal interne d'arbre à came (14) soit en liaison avec le dispositif de réglage (100) et que d'autre part au moins un canal de connexion d'arbre à came (15, 16, 17, 18) conduise depuis le canal interne d'arbre à came (14) vers la surface d'enveloppe extérieure (19) de l'arbre à came (9), le logement d'arbre à came (2) disposant d'au moins une conduite d'amenée (5, 6, 7, 8) qui conduit vers la surface d'enveloppe interne (20) du logement d'arbre à came (2) et qui peut être connectée par le biais du canal de connexion d'arbre à came (15, 16, 17, 18) et du canal interne d'arbre à came (14) au dispositif de réglage (100), et qui sert à l'alimentation en huile hydraulique du dispositif de réglage (100),
    caractérisé en ce que
    le logement d'arbre à came (2) est divisé en deux et comprend un siège de palier (4) disposé dans une culasse et un couvercle de palier (3) disposé sur ce siège de palier (4), dans l'état monté, et soit dans la surface d'enveloppe extérieure (19) de l'arbre à came (9) dans la région du canal de connexion d'arbre à came (15, 16, 17, 18) soit dans la surface d'enveloppe intérieure (20) du logement d'arbre à came (2) dans la région de l'au moins une conduite d'amenée (5, 6, 7, 8), au moins une rainure annulaire réalisée sous forme segmentée (21, 22, 23, 24) est prévue, l'au moins une rainure annulaire réalisée sous forme segmentée (21, 22, 23, 24) étant réalisée et disposée de telle sorte que :
    - la connexion entre la conduite d'amenée (5, 6, 7, 8) et le dispositif de réglage (100) soit interrompue dans la phase de compression d'un élément de ressort de soupape (27) d'un mécanisme de soupape actionné par le biais de l'arbre à came (9), qui est comprimé par l'au moins une came (10, 11, 12, 13) de l'arbre à came (9),
    - pendant la phase d'amenée de l'au moins une came (10, 11, 12, 13), le canal de connexion d'arbre à came (15, 16, 17, 18) est fermé à son extrémité située sur la surface d'enveloppe extérieure (19) de l'arbre à came (9), par la surface d'enveloppe intérieure (20) du logement d'arbre à came (2).
  2. Système (1) selon la revendication 1,
    caractérisé en ce
    qu'un couvercle de palier (3) pour l'arbre à came d'entrée et un couvercle de palier adjacent (3) pour un arbre à came de sortie, sont réalisés d'une seule pièce sous forme de pont de palier (25).
  3. Système (1) selon la revendication 1 ou 2,
    caractérisé en ce que
    le logement d'arbre à came (2) présente un palier lisse pour le support de l'arbre à came (9), lequel est reçu par le siège de palier (4) ou le couvercle de palier (3).
  4. Système (1) selon la revendication 3,
    caractérisé en ce que
    le palier lisse est une douille de palier lisse réalisée d'une seule pièce dans l'état monté.
  5. Système (1) selon la revendication 3,
    caractérisé en ce que
    le palier lisse comprend deux demi-coques de palier lisse.
  6. Système (1) selon l'une quelconque des revendications 3 à 5,
    caractérisé en ce que
    l'au moins une rainure annulaire réalisée sous forme segmentée (21, 22, 23, 24) est prévue dans le palier lisse.
  7. Système (1) selon la revendication 6,
    caractérisé en ce que
    le siège de palier (4) et/ou le couvercle de palier (3) du logement d'arbre à came (2) présente(nt) un canal annulaire qui s'étend sur toute la périphérie, le canal annulaire - dans l'état monté - étant en liaison avec l'au moins une rainure annulaire réalisée sous forme segmentée (21, 22, 23, 24) dans le palier lisse.
  8. Système (1) selon la revendication 7,
    caractérisé en ce que
    l'arbre à came (9) présente une came (10) et une rainure annulaire (21) réalisée sous forme segmentée, la rainure annulaire (21) s'étendant sur un angle α < 320° dans la direction périphérique.
  9. Système (1) selon la revendication 8,
    caractérisé en ce que
    la rainure annulaire (21) s'étend sur un angle α < 285° dans la direction périphérique.
  10. Système (1) selon la revendication 8 ou 9,
    caractérisé en ce que
    la rainure annulaire (21) s'étend sur un angle α < 270° dans la direction périphérique.
  11. Système (1) selon l'une quelconque des revendications 1 à 7,
    caractérisé en ce que
    l'arbre à came (9) présente quatre canaux de connexion d'arbre à came (15, 16, 17, 18) et quatre, respectivement huit, cames (10, 11, 12, 13) disposées par paires les unes derrière les autres, décalées à chaque fois de 90° sur la circonférence dudit arbre à came, et en ce que quatre rainures annulaires (21, 22, 23, 24) réalisées sous forme segmentée sont prévues, les rainures annulaires (21, 22, 23, 24) s'étendent à chaque fois sur un angle α < 50° dans la direction périphérique, sont espacées régulièrement dans la surface d'enveloppe extérieure (19) de l'arbre à came (9) ou sont disposées dans la surface d'enveloppe interne (20) du logement d'arbre à came (2).
  12. Système (1) selon la revendication 11,
    caractérisé en ce que
    les rainures annulaires (21, 22, 23, 24) s'étendent sur un angle α < 40 ° dans la direction périphérique.
  13. Système (1) selon la revendication 11 ou 12,
    caractérisé en ce que
    les rainures annulaires (21, 22, 23, 24) s'étendent sur un angle α < 25° dans la direction périphérique.
EP20040100003 2004-01-05 2004-01-05 Actionneur variable d'arbres à came avec une alimentation en huile sous pression intérrompue partiellement Expired - Fee Related EP1550793B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20040100003 EP1550793B1 (fr) 2004-01-05 2004-01-05 Actionneur variable d'arbres à came avec une alimentation en huile sous pression intérrompue partiellement
DE200450009304 DE502004009304D1 (de) 2004-01-05 2004-01-05 Nockenwellenversteller mit teilweise unterbrochener Druckölzufuhr

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20040100003 EP1550793B1 (fr) 2004-01-05 2004-01-05 Actionneur variable d'arbres à came avec une alimentation en huile sous pression intérrompue partiellement

Publications (2)

Publication Number Publication Date
EP1550793A1 EP1550793A1 (fr) 2005-07-06
EP1550793B1 true EP1550793B1 (fr) 2009-04-08

Family

ID=34560269

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20040100003 Expired - Fee Related EP1550793B1 (fr) 2004-01-05 2004-01-05 Actionneur variable d'arbres à came avec une alimentation en huile sous pression intérrompue partiellement

Country Status (2)

Country Link
EP (1) EP1550793B1 (fr)
DE (1) DE502004009304D1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018206901A1 (de) * 2018-05-04 2019-11-07 Volkswagen Aktiengesellschaft Zylinderkopfhaube mit Öffnung zur Durchführung und Lagerung einer Nockenwelle einer Brennkraftmaschine sowie Anordnung einer Nockenwelle an einer solchen Zylinderkopfhaube

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0547309U (ja) * 1991-11-28 1993-06-22 株式会社ユニシアジェックス 内燃機関のバルブタイミング制御装置
DE19850947A1 (de) * 1998-11-05 2000-05-11 Schaeffler Waelzlager Ohg Vorrichtung zur Steuerung der Öffnungs- und Schließzeiten von Gaswechselventilen einer Brennkraftmaschine
US6247434B1 (en) * 1999-12-28 2001-06-19 Borgwarner Inc. Multi-position variable camshaft timing system actuated by engine oil

Also Published As

Publication number Publication date
DE502004009304D1 (de) 2009-05-20
EP1550793A1 (fr) 2005-07-06

Similar Documents

Publication Publication Date Title
EP2463486B1 (fr) Dispositif de réglage de la position de l&#39;angle de rotation d&#39;un arbre à came
DE69907989T2 (de) Variable Ventilzeitsteuervorrichtung
EP2321501B1 (fr) Dispositif de réglage variable des temps de commande de soupapes d&#39;échange des gaz d&#39;un moteur à combustion interne
DE102004036096A1 (de) Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE102004038252A1 (de) Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE102006022402A1 (de) Steuerventil für einen Nockenwellenversteller
WO2015000476A1 (fr) Système de vanne centrale pour transmission par courroie à sec
DE102007019307B4 (de) Ventiltaktungssteuerungseinrichtung
EP0469334B1 (fr) Procédé pour changer la position angulaire des arbres d&#39;un moteur à combustion interne
DE112015000171T5 (de) Motorölzufuhrvorrichtung
EP2470757B1 (fr) Vanne de commande
DE102010008001A1 (de) Vorrichtung zur variablen Einstellung von Ventilerhebungskurven von Gaswechselventilen einer Brennkraftmaschine
WO2015074649A1 (fr) Dispositif pour faire varier le taux de compression d&#39;une unité de cylindre d&#39;un moteur à combustion interne à piston alternatif
WO2016177368A1 (fr) Système de déphasage d&#39;arbre à cames
DE102016201414B4 (de) Brennkraftmaschine mit Ölkreislauf
DE2926327A1 (de) Mechanisch-hydraulische ventilsteuerung
WO2010006855A1 (fr) Dispositif de réglage variable de la périodicité de soupapes d&#39;échange de gaz d&#39;un moteur à combustion interne
DE102006005333A1 (de) Ventiltrieb für eine Brennkraftmaschine
WO2006074732A1 (fr) Dispositif de modification des temps de commande d&#39;un moteur a combustion interne
DE102012203383B3 (de) Filteranordnung eines Steuerventils für einen Nockenwellenversteller
DE102005023204A1 (de) Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102010026393B4 (de) Kraftstoffpumpen-Antriebssystem
DE102008010225B4 (de) Variables Ventilsteuerzeitventilhubsystem
EP1550793B1 (fr) Actionneur variable d&#39;arbres à came avec une alimentation en huile sous pression intérrompue partiellement
DE102016200487A1 (de) Brennkraftmaschine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK

RIN1 Information on inventor provided before grant (corrected)

Inventor name: BINGEN, GUIDO

Inventor name: KRAMER, ULRICH

17P Request for examination filed

Effective date: 20060109

AKX Designation fees paid

Designated state(s): DE FR GB

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: FORD GLOBAL TECHNOLOGIES, LLC, A SUBSIDARY OF FORD

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 502004009304

Country of ref document: DE

Date of ref document: 20090520

Kind code of ref document: P

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20100111

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20141230

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20141226

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20150126

Year of fee payment: 12

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502004009304

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20160105

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20160930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160802

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160105

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160201