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EP2321501B1 - Dispositif de réglage variable des temps de commande de soupapes d'échange des gaz d'un moteur à combustion interne - Google Patents

Dispositif de réglage variable des temps de commande de soupapes d'échange des gaz d'un moteur à combustion interne Download PDF

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Publication number
EP2321501B1
EP2321501B1 EP09781129A EP09781129A EP2321501B1 EP 2321501 B1 EP2321501 B1 EP 2321501B1 EP 09781129 A EP09781129 A EP 09781129A EP 09781129 A EP09781129 A EP 09781129A EP 2321501 B1 EP2321501 B1 EP 2321501B1
Authority
EP
European Patent Office
Prior art keywords
camshaft
pressurizing means
pressure medium
distributor
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.)
Not-in-force
Application number
EP09781129A
Other languages
German (de)
English (en)
Other versions
EP2321501A1 (fr
Inventor
Boris PÜTZ
Ali Bayrakdar
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP2321501A1 publication Critical patent/EP2321501A1/fr
Application granted granted Critical
Publication of EP2321501B1 publication Critical patent/EP2321501B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—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
    • 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
    • F01L2001/0475—Hollow camshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • 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
    • F01L2001/34426—Oil control valves
    • 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
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—Location oil control valves

Definitions

  • the invention relates to a device for variably setting the timing of gas exchange valves of an internal combustion engine with a hydraulic phase adjusting device, a camshaft and a pressure medium distributor, wherein the phase adjusting device can be brought into drive connection with a crankshaft and rotatably connected to the camshaft, wherein a phase angle of the camshaft relative to Crankshaft is variably adjustable by means of the phase adjusting device, wherein the interior of the camshaft has a cavity which communicates with one or more camshaft bearings, which are formed separately from a pressure medium rotary transformer, wherein the pressure medium distributor is arranged in a receiving area of the camshaft, wherein the camshaft in the area of the pressure medium distributor has an opening which communicates on the one hand with the interior of the camshaft and on the other hand with the pressure medium rotary transformer, wherein within the camshaft a Druc kstoffpfad is formed, which communicates on the one hand with the opening and on the other hand with the hydraulic phase adjusting device.
  • the device usually consists of a camshaft, a hydraulic phase adjusting device, by means of which a phase relation between the crankshaft and the camshaft can be selectively changed by pressure medium supply or discharge, and a pressure medium distributor, by means of which the phase adjusting means pressure medium can be supplied or discharged from this.
  • the phase adjusting device is integrated in a drive train, via which torque is transmitted from the crankshaft to the camshaft.
  • This drive train can be realized for example as a belt, chain or gear drive.
  • Such a device is for example from the US Pat. No. 6,799,544 B1 known.
  • the device comprises a phase adjusting device, a central screw and a camshaft which is mounted in the cylinder head of the internal combustion engine by means of a plurality of camshaft bearings.
  • the phase adjusting device has an output element, which is arranged rotatably to a drive element.
  • the drive element is in drive connection with the crankshaft.
  • the device In the axial direction, the device is limited by a respective side cover.
  • the output element, the drive element and the two side covers define a plurality of pressure chambers, wherein each of the pressure chambers is divided by a wing into two counteracting pressure chambers.
  • the phase adjusting device is rotatably connected by means of the central screw with the camshaft.
  • the central screw passes through a central opening of the output element and is supported on its side facing away from the camshaft side surface on the driven element.
  • a control valve is arranged in the region of the central opening, to which pressure medium is supplied via a camshaft bearing. By means of the control valve, the pressure medium flows to or from the pressure chambers and thus the phase relation between the crankshaft and camshaft are controlled.
  • a disadvantage of this embodiment is that per camshaft bearing complex lubricant supply lines must be formed within the cylinder head to supply the camshaft bearings lubricant. This considerably increases the complexity and the manufacturing cost of the cylinder head.
  • the invention has for its object to provide a device for variable adjustment of the timing of gas exchange valves of an internal combustion engine, the lubricant supply of the camshaft bearing should be simplified.
  • a second pressure medium channel is provided which communicates on the one hand with the opening and on the other hand with the cavity, wherein the second pressure medium channel is at least partially formed by the pressure medium distributor.
  • the pressure medium distributor is provided with a threaded portion, by means of which the phase adjusting device can be fastened to the camshaft.
  • the pressure medium distributor has a control valve, by means of which the phase adjusting device can be supplied with pressure medium.
  • the pressure medium distributor can pass through a central opening of the phase adjusting device.
  • the second pressure medium channel can be formed, for example, within the pressure medium distributor. Alternatively it can be provided to form the second pressure medium channel at an interface between the cavity and the pressure medium distributor. It can be provided, for example, that the second pressure medium channel as a longitudinal groove on an outer circumferential surface of the pressure medium distributor or is formed on an inner circumferential surface of the camshaft in the region of the pressure medium distributor.
  • the pressure medium rotary transformer may be formed, for example, as a camshaft bearing.
  • the pressure medium path is at least partially formed by the pressure medium distributor.
  • the device has at least one hydraulic phase adjusting device on a camshaft and a pressure medium distributor.
  • the phase adjusting device comprises at least one drive element and an output element.
  • the drive element is in the assembled state of the device via a traction drive, such as a belt or chain drive, or a gear drive, with the crankshaft in drive connection.
  • the output member is pivotally mounted in an angular range relative to the drive element and rotatably secured to the camshaft.
  • At least one pressure chamber is provided, by the pressurization of which the output element relative to the drive element and thus the camshaft can be pivoted relative to the crankshaft.
  • one or more pairs of mutually acting pressure chambers are provided.
  • the camshaft is designed as a hollow shaft with a cavity. This can be realized, for example, by the fact that the camshaft consists of a tube, whose one end is closed and on the cam force, are fixed or cohesively. But also conceivable are solidly executed camshafts, which have an axial channel, in the form of a blind hole, which opens into a receptacle in which the pressure medium distributor is arranged.
  • the camshaft is supported in a plurality of camshaft bearings, the cavity communicating with at least one of the camshaft bearings via radial openings in the camshaft.
  • the pressure medium distributor is received in a receptacle of the camshaft, said receptacle communicating with the cavity.
  • the receptacle may be part of the cavity, for example.
  • the camshaft has an opening in the region of the receptacle in which the pressure medium distributor is arranged.
  • a pressure medium rotary transformer is arranged. This can surround the camshaft, for example, completely in the circumferential direction.
  • the pressure medium rotary transformer can be designed as a camshaft bearing or as a separate component.
  • About the pressure medium rotary transformer and the opening is supplied to the interior of the camshaft during operation of the internal combustion engine permanently or at intervals pressure medium.
  • the pressure medium distributor separates a pressure medium path which is provided for supplying the phase adjusting device by a second pressure medium channel, which opens into the cavity of the camshaft and over which the camshaft bearing separate from the pressure medium rotary transformer are supplied with lubricant.
  • the pressure medium distributor closes the cavity, apart from the second pressure medium channel, pressure-tight to the outside.
  • a filter element can be integrated in the second pressure medium channel, which keeps foreign bodies in the lubricant or pressure medium away from the camshaft bearings and thus reduces the wear of the bearing points. Since all camshaft bearings are supplied with lubricant / pressure medium via the second pressure medium channel, only a single filter element is required in this embodiment.
  • the pressure medium rotary transformer can fulfill other functions in addition to the leadership of the lubricant / pressure medium flows.
  • a threaded portion may be formed on this, by means of which the phase adjusting device, such as the output member, rotatably connected to the camshaft can be connected.
  • the pressure medium distributor has a control valve, via which the pressure medium flows can be controlled to and from the pressure chambers of the phase adjusting device.
  • the second pressure medium channel which communicates on the one hand with the opening and thus with the pressure medium rotary transformer and on the other hand with the cavity of the camshaft is at least partially formed by the pressure medium distributor.
  • a pressure medium distributor in the interior of a Bore is provided, which branches off from the pressure medium path, which supplies the phase adjusting device with pressure medium.
  • the second pressure medium channel is formed solely by the pressure medium distributor.
  • the second pressure medium channel is formed at an interface between the pressure medium distributor and the camshaft, for example an inner lateral surface of the camshaft and an outer lateral surface of the pressure medium distributor. This can be realized for example by a longitudinal groove which is formed on the outer circumferential surface of the pressure medium distributor or the inner circumferential surface of the camshaft.
  • a minimum flow area of the second pressure medium channel is made smaller than a minimum flow area of the pressure medium path between the opening and the phase adjusting device.
  • the second pressure medium channel may have a throttle point.
  • the throttle point may for example be realized by means of a separate component, which is arranged in the second pressure medium channel.
  • FIG. 1 an internal combustion engine 1 is sketched, wherein a seated on a crankshaft 2 piston 3 is indicated in a cylinder 4.
  • the crankshaft 2 is in the illustrated embodiment via a respective traction drive 5 with an intake camshaft 6 and exhaust camshaft 7 in combination, with a first and a second device 11 for a relative rotation between the crankshaft 2 and the camshafts 6, 7 can provide.
  • Cams 8 of the camshafts 6, 7 actuate one or more inlet gas exchange valves 9 or one or more Auslassgas scaffoldventile 10.
  • it may be provided only one of the camshafts 6, 7 with a device 11, or provide only a camshaft 6, 7, which with a Device 11 is provided.
  • FIGS. 2 and 3 show a first embodiment of a device 11 according to the invention in longitudinal or in cross section.
  • the device 11 has a phase adjusting device 12, a camshaft 6, 7 and a pressure medium distributor 13.
  • the phase adjusting device 12 comprises a drive element 14 and an output element 16.
  • the drive element 14 has a housing 15 and two side covers 17, 18, which are arranged on the axial side surfaces of the housing 15.
  • the output element 16 is designed in the form of an impeller and has a substantially cylindrical hub member 19, extend from the outer cylindrical surface in the illustrated embodiment, five wings 20 in the radial direction outwardly. Starting from an outer peripheral wall 21 of the housing 15, five projections 22 extend radially inwardly. In the illustrated embodiment, the projections 22 and the wings 20 are integrally formed with the peripheral wall 21 and the hub member 19, respectively.
  • the drive element 14 is arranged by means of radially inner circumferential walls of the projections 22 relative to the output member 16 rotatable thereto.
  • a sprocket 23 is formed, via which by means of a chain drive, not shown, torque can be transmitted from the crankshaft 2 to the drive member 14.
  • the output member 16 is rotatably connected to the camshaft 6,7.
  • the pressure medium distributor 13 is provided with a threaded portion 24 which engages in a threaded portion 25 of the camshaft 6, 7.
  • the pressure medium distributor 13 passes through a central opening 16a of the output element 16. A shoulder of the pressure medium distributor 13 rests against the side surface of the output element 16 facing away from the camshaft 6, 7.
  • a screw 27 passes through an opening of the second side cover 18, an axial opening 26 and an opening of the first side cover 17. In this case engages a threaded portion of the screw 27 in a threaded portion which in the Opening of the first side cover 17 is formed.
  • a pressure space 28 is formed between each two circumferentially adjacent projections 22.
  • Each of the pressure chambers 28 is circumferentially bounded by opposing, substantially radially extending boundary walls 29 of adjacent projections 22, in the axial direction of the side covers 17, 18, radially inwardly of the hub member 19 and radially outwardly of the peripheral wall 21.
  • a wing 20 In each of the pressure chambers 28 projects a wing 20, wherein the wings 20 are formed such that they rest against both the side covers 17, 18, and on the peripheral wall 21. Each wing 20 thus divides the respective pressure chamber 28 into two counteracting pressure chambers 30, 31.
  • the output element 16 is arranged rotatably in a defined Winkelbreich to the drive element 14.
  • the angular range is limited in one direction of rotation of the driven element 16 in that the wings 20 come into contact with a corresponding boundary wall 29 (early stop 32) of the pressure chambers 28.
  • the angular range in the other direction of rotation is limited by the fact that the wings 20 come to rest on the other boundary walls 29 of the pressure chambers 28, which serve as a late stop 33.
  • phase position of the drive element 14 to the output element 16 can be varied.
  • phase position can be kept constant.
  • the pressure medium distributor 13 is provided with a control valve 34.
  • the control valve 34 comprises a substantially hollow cylindrical valve housing 35 and a control piston 36 which disposed axially displaceable within the valve housing 35 is.
  • the valve housing 35 is provided with an inlet port P, a drain port T, and two working ports A, B.
  • the pressure medium distributor 13 passes through the central opening 16a of the output element 16, wherein the camshaft-facing portion in a receptacle 37 of the hollow camshaft 6, 7 is arranged.
  • the camshaft 6, 7 has in the region of the receptacle 37 a plurality of openings 38, on the one hand with a pressure medium rotary transformer 39, which at least partially surrounds the camshaft 6, 7, and on the other hand with the interior of the camshaft 6, 7 communicate.
  • the pressure medium rotary transformer 39 is simultaneously formed as a camshaft bearing 50.
  • About the pressure medium rotary transformer 39 and the openings 38 is supplied to the interior of the camshaft 6, 7 during operation of the internal combustion engine 1 pressure medium from the lubricant circuit.
  • the pressure medium rotary transformer 39 is designed separately from the camshaft bearings 50 and only the pressure medium transfer between the cylinder head fixed components and the camshaft 6, 7 allows.
  • the pressure medium distributor 13 is designed and arranged such that a pressure medium path 40 is formed, which communicates on the one hand with the openings 38 and on the other hand with the inlet port P.
  • the pressure medium path 40 consists of a first pressure medium channel 41 between the outer lateral surface of the pressure medium distributor 13 and the inner lateral surface of the camshaft 6, 7, which communicates with radial openings 42, which in turn communicate with the interior of the pressure medium distributor 13. From there, the pressure medium passes through a check valve 43 and an axial channel 44 to the inlet port P.
  • the pressure medium reaches either the first or second working port A, B and from there via radial pressure medium lines 45, 46 to the first and second pressure chambers 30, 31.
  • the pressure medium from the other pressure chambers 30, 31 via the pressure medium lines 45, 46 returned to the control valve 34 and ⁇ -ejected via the drain port.
  • the axial position of the control piston 36 relative to the valve housing 35 is selectively adjustable by means of an electromagnetic actuator 47.
  • a second pressure medium channel 48 is provided, which communicates on the one hand via the radial openings 42 and the first pressure medium channel 41 with the openings 38 and on the other hand with a cavity 49 of the hollow camshaft 6, 7.
  • the second pressure medium channel 48 is in the in the Figures 2 and 4 illustrated embodiments designed as an axial bore, which passes through the threaded portion 24.
  • the cavity 49 extends as in FIG FIG. 4 represented over the entire length of the camshaft 6, 7, wherein the phase adjusting device 12 facing away from the side formed closed and limited by the pressure medium distributor 13 in the other direction.
  • the pressure medium distributor 13 seals the cavity 49, apart from the second pressure medium channel 48, to the outside.
  • the camshaft 6, 7 is rotatably mounted in the cylinder head of the internal combustion engine 1 by means of one or more camshaft bearings 50.
  • at least one, advantageously a plurality, radial openings 51 are provided which communicate on the one hand with the cavity 49 and on the other hand with the bearing surface of the camshaft bearing 50.
  • the camshaft bearing 50 is supplied via the pressure medium rotary transformer 39, the openings 38, the first pressure medium channel 41, the radial openings 42, the second pressure medium channel 48, the cavity 49 and the radial openings 51 lubricant.
  • a filter element 54 is provided, which frees the pressure fluid / lubricant flow to the camshaft bearings and the phase adjusting device 12 of impurities.
  • the filter element 54 is formed as a ring filter.
  • a throttle 52 is provided within the second pressure medium channel 48, which limits the flow of pressure medium from the pressure medium rotary transformer 39 to the bearing surfaces of the camshaft bearings 50, without hindering the pressure medium flow to the phase adjusting device 12.
  • the throttle 52 is formed separately from the pressure medium manifold 13 and fixed in the second pressure medium channel 48, for example by a positive, material or non-positive connection attached.
  • the diameter of the second pressure medium channel 48 is designed in such a way that it causes the throttling function ( FIG. 2 ) or in which the throttle 52 is formed on the pressure medium distributor 13.
  • the minimum flow area of the second pressure medium channel 48 is smaller than the minimum flow area between the pressure medium rotary transformer 39 and the pressure chambers 30, 31.
  • FIG. 5 shows a further embodiment according to the invention of the device 11, which is formed substantially identical to the first two embodiments.
  • the second pressure medium channel 48 is formed at the interface between the inner circumferential surface of the camshaft 6, 7 and the outer circumferential surface of the pressure medium distributor 13.
  • a longitudinal groove 53 is provided, which communicates on the one hand with the cavity 49 and on the other hand with the first pressure medium channel 41.
  • the longitudinal groove 53 may be formed, for example, on the inner circumferential surface of the camshaft 6, 7 or the outer circumferential surface of the pressure medium distributor 13. In any case, therefore, the second pressure medium channel 48 is partially limited by the pressure medium distributor 13.
  • the longitudinal groove 53 may have a constant small cross section or a local throttle point.
  • one or more of the pressure medium rotary transformer 39 separate camshaft bearing 50 can be supplied with lubricant.
  • the usual in the cylinder head structures for supplying lubricant to each individual camshaft bearing 50 can be omitted, whereby the complexity and the cost of the cylinder head can be reduced.
  • the pressure medium supply of all camshaft bearing 50 via the cavity 49 of the camshaft 6, 7 only a pressure medium supply to the camshaft 6, 7 is necessary, via which the phase adjusting device 12 is supplied simultaneously.
  • the formation of the second pressure medium channel 48 through the pressure medium distributor 13 significantly reduces the costs and complexity of the device 11.
  • the supply of the phase adjusting device 12 and the camshaft bearings 50 can be realized by means of a single component, whereby the assembly cost drops considerably.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Claims (14)

  1. Dispositif (11) pour l'ajustement variable des temps de commande de soupapes d'échange de gaz (9, 10) d'un moteur à combustion interne (1), comprenant :
    - un déphaseur hydraulique (12), un arbre à came (6, 7) et un distributeur de fluide sous pression (13) ,
    - le déphaseur (12) pouvant être amené en liaison d'entraînement avec un vilebrequin (2) et étant connecté de manière solidaire en rotation à l'arbre à came (6, 7),
    - une position de phase de l'arbre à came (6, 7) par rapport au vilebrequin (2) pouvant être ajustée de manière variable au moyen du déphaseur (12),
    - l'intérieur de l'arbre à came (6, 7) présentant une cavité (49), qui communique avec un ou plusieurs paliers d'arbre à came (50) qui sont réalisés de manière séparée d'un dispositif de transfert de rotation à fluide sous pression (39),
    - le dispositif de fluide sous pression (13) étant disposé dans une région de réception (37) de l'arbre à came (6, 7),
    - l'arbre à came (6, 7) présentant, dans la région du dispositif de fluide sous pression (13), une ouverture (38) qui communique d'une part avec l'intérieur de l'arbre à came (6, 7) et d'autre part avec le dispositif de transfert de rotation à fluide sous pression (39),
    - à l'intérieur de l'arbre à came (6, 7) étant réalisé un chemin de fluide sous pression (40), qui communique d'une part avec l'ouverture (38) et d'autre part avec le déphaseur hydraulique (12),
    - caractérisé en ce qu'un deuxième canal de fluide sous pression (48) est prévu, lequel communique d'une part avec l'ouverture (38) et d'autre part avec la cavité (49),
    - le deuxième canal de fluide sous pression (48) étant réalisé au moins en partie par le distributeur de fluide sous pression (13).
  2. Dispositif (11) selon la revendication 1, caractérisé en ce que le dispositif de fluide sous pression (13) est pourvu d'une portion filetée (24) au moyen de laquelle le déphaseur (12) peut être fixé à l'arbre à came (6, 7).
  3. Dispositif (11) selon la revendication 1, caractérisé en ce que le distributeur de fluide sous pression (13) présente une soupape de commande (34) au moyen de laquelle le déphaseur (12) peut être alimenté en fluide sous pression.
  4. Dispositif (11) selon la revendication 1, caractérisé en ce que le distributeur de fluide sous pression (13) s'engage à travers une ouverture centrale (16a) du déphaseur (12).
  5. Dispositif (11) selon la revendication 1, caractérisé en ce qu'une surface de passage d'écoulement minimale du deuxième canal de fluide sous pression (48) est réalisée de manière plus petite qu'une surface de passage d'écoulement minimale du chemin de fluide sous pression (40) entre l'ouverture (38) et le déphaseur (12).
  6. Dispositif (11) selon la revendication 1, caractérisé en ce que le deuxième canal de fluide sous pression (48) est réalisé à l'intérieur du distributeur de fluide sous pression (13).
  7. Dispositif (11) selon la revendication 1, caractérisé en ce que le deuxième canal de fluide sous pression (48) est réalisé sur une surface limite entre la cavité (49) et le distributeur de fluide sous pression (13).
  8. Dispositif (11) selon la revendication 7, caractérisé en ce que le deuxième canal de fluide sous pression (48) est réalisé sous forme de rainure longitudinale (53) sur une surface d'enveloppe intérieure du distributeur de fluide sous pression (13).
  9. Dispositif (11) selon la revendication 7, caractérisé en ce que le deuxième canal de fluide sous pression (48) est réalisé sous forme de rainure longitudinale (53) sur une surface d'enveloppe intérieure de l'arbre à came (6, 7) dans la région du distributeur de fluide sous pression (13).
  10. Dispositif (11) selon la revendication 1, caractérisé en ce que le deuxième canal de fluide sous pression (48) présente un étranglement (52).
  11. Dispositif (10) selon la revendication 10, caractérisé en ce que l'étranglement (52) est réalisé au moyen d'un composant séparé, qui est disposé dans le deuxième canal de fluide sous pression (48).
  12. Dispositif (11) selon la revendication 1, caractérisé en ce que le dispositif de transfert de rotation à fluide sous pression (39) est réalisé sous forme de palier d'arbre à came (50).
  13. Dispositif (11) selon la revendication 1, caractérisé en ce que le chemin de fluide sous pression (40) est réalisé au moins en partie par le distributeur de fluide sous pression (13).
  14. Dispositif (11) selon la revendication 1, caractérisé en ce qu'un élément de filtre (54) est disposé dans le deuxième canal de fluide sous pression (48).
EP09781129A 2008-08-02 2009-07-27 Dispositif de réglage variable des temps de commande de soupapes d'échange des gaz d'un moteur à combustion interne Not-in-force EP2321501B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008036182A DE102008036182A1 (de) 2008-08-02 2008-08-02 Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
PCT/EP2009/059668 WO2010015541A1 (fr) 2008-08-02 2009-07-27 Dispositif de réglage variable des temps de commande de soupapes d’échange des gaz d’un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP2321501A1 EP2321501A1 (fr) 2011-05-18
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DE102012201573A1 (de) 2012-02-02 2013-08-08 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102012204617A1 (de) 2012-03-22 2013-09-26 Schaeffler Technologies AG & Co. KG Steuerventil eines Nockenwellenverstellers
DE102012210178B4 (de) 2012-06-18 2016-05-19 Schaeffler Technologies AG & Co. KG Steuerventil eines Nockenwellenverstellers
DE102012218802B4 (de) 2012-10-16 2018-05-17 Schaeffler Technologies AG & Co. KG Steuerventil für ein Nockenwellenverstellersystem
DE102012221876B4 (de) * 2012-11-29 2021-01-07 Schaeffler Technologies AG & Co. KG Nockenwellenverstellvorrichtung
DE102013104573B4 (de) * 2013-05-03 2018-05-17 Hilite Germany Gmbh Hydraulikventil und Schwenkmotorversteller
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DE102014102617A1 (de) 2014-02-27 2015-08-27 Hilite Germany Gmbh Hydraulikventil für einen Schwenkmotorversteller einer Nockenwelle
DE102014204566B4 (de) * 2014-03-12 2021-05-12 Schaeffler Technologies AG & Co. KG Zentralventil für einen Nockenwellenversteller mit Mittenverriegelung
DE102014115903B4 (de) * 2014-10-31 2020-07-30 Hilite Germany Gmbh Hydraulikventil und Schwenkmotorversteller
DE102016214501B4 (de) 2015-10-28 2021-07-29 Schaeffler Technologies AG & Co. KG Nockenwellenverstellvorrichtung
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ATE542984T1 (de) 2012-02-15
CN102112707B (zh) 2013-09-18
EP2321501A1 (fr) 2011-05-18
DE102008036182A1 (de) 2010-02-04
WO2010015541A1 (fr) 2010-02-11
CN102112707A (zh) 2011-06-29
US20110132303A1 (en) 2011-06-09

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