EP2331797B1 - Dispositif de réglage variable des temps de commande des soupapes d échange de gaz d un moteur à combustion interne - Google Patents

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

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Publication number
EP2331797B1
EP2331797B1 EP09782804.0A EP09782804A EP2331797B1 EP 2331797 B1 EP2331797 B1 EP 2331797B1 EP 09782804 A EP09782804 A EP 09782804A EP 2331797 B1 EP2331797 B1 EP 2331797B1
Authority
EP
European Patent Office
Prior art keywords
piston
camshaft
cavity
housing
pressure
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
EP09782804.0A
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German (de)
English (en)
Other versions
EP2331797A1 (fr
Inventor
Andreas Strauss
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 EP2331797A1 publication Critical patent/EP2331797A1/fr
Application granted granted Critical
Publication of EP2331797B1 publication Critical patent/EP2331797B1/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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • F01L2001/34446—Fluid accumulators for the feeding circuit

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 accumulator, 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 and wherein the interior of the camshaft has a cavity.
  • the device usually consists of a camshaft and 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 removal.
  • 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 DE 195 29 277 A1 known.
  • the device comprises a phase adjusting device and a camshaft.
  • 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 output element and the drive element define a pressure chamber, which is divided by means of an axially displaceable piston into two counteracting pressure chambers.
  • the piston By supplying pressure medium to or removing pressure medium from the pressure chambers, the piston is displaced within the pressure chamber.
  • the piston has a helical toothing, which meshes with a helical toothing of the camshaft.
  • the device further comprises a pressure accumulator, which is arranged in a crankcase or a cylinder head of the internal combustion engine.
  • a pressure accumulator which is arranged in a crankcase or a cylinder head of the internal combustion engine.
  • the pressure accumulator of a pressure medium pump of the internal combustion engine with pressure medium, usually the engine oil, filled. If the system pressure delivered by the pressure medium pump drops below a value which is required for the functionally reliable operation of the device, the pressure accumulator empties into the pressure medium circuit of the internal combustion engine. Thus, short-term minimum pressure drops can be intercepted within the pressure fluid system or the flow rate can be increased.
  • the high space requirement of the pressure accumulator within the crankcase and the cylinder head is arranged in a crankcase or a cylinder head of the internal combustion engine.
  • the DE 102 28 354 A1 1 shows a camshaft with a camshaft adjusting device.
  • an accumulator and a pressure generating device is arranged within the camshaft.
  • the pressure generating device can be operated with a nitrogen tablet.
  • the pressurized fluid under pressure in the accumulator (oil) can be fed to the camshaft adjusting device.
  • the US 2003/0188705 A1 shows a hydraulic circuit with a pressure accumulator 114, a pump 102, a proportional valve 68, various hydraulic fluid lines and a camshaft 73, on the front side a camshaft adjuster 83 is attached.
  • 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 space requirement of the device to be reduced.
  • the object is achieved in that the pressure accumulator is arranged in the cavity and communicates with the phase adjusting device.
  • the device has at least one hydraulic phase adjusting device on a camshaft and a pressure accumulator.
  • 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 has a cavity.
  • the camshaft consists of a tube on the outer lateral surface of cam force, are positively or materially secured.
  • solidly executed camshafts in which a cavity, for example in the form of a blind hole, is provided.
  • the pressure accumulator can be connected, for example, positive, non-positive or cohesive, stationary with the camshaft.
  • the interior of the camshaft can be supplied for example via a camshaft bearing pressure medium.
  • the pressure medium passes on the one hand to the hydraulic phase adjusting device, on the other hand to the pressure accumulator, which is filled with pressure medium during normal operation of the internal combustion engine.
  • the pressure accumulator has a longitudinally displaceable piston. Furthermore, the pressure accumulator may have a spring element, which acts on the piston against the force of the pressure medium with a force. Alternatively, for example, gas cushions can be provided as energy storage.
  • the pressure accumulator can be designed, for example, as a piston accumulator, in particular as a piston spring accumulator. This is a very robust solution.
  • the pressure accumulator has a housing which is arranged in the cavity and in which the piston is guided longitudinally displaceable.
  • the running surface of the piston is represented by an inner circumferential surface of the housing.
  • the housing can be realized, for example, as a cylindrical or cup-shaped sheet metal part which can be produced, for example, by a non-cutting shaping process, for example by a deep drawing process. As a result, the weight and the manufacturing cost of the housing are kept low.
  • the deep-drawing process automatically produces the running surface of the piston with the required accuracy. Elaborate post-processing steps are not necessary
  • the pressure accumulator is arranged by means of a frictional connection between the housing and a wall of the cavity in this stationary.
  • fabric or positive connections such as adhesive, solder or welded joints can be provided.
  • the housing has a guide portion and the piston has an outer circumferential surface which is adapted to an inner circumferential surface of the guide portion.
  • the piston is guided axially movably on a guide surface of the guide section.
  • the length of the guide section corresponds to the stroke of the piston within the pressure accumulator.
  • the guide portion may extend over the entire length of the piston, for example.
  • the frictional connection between the housing and the wall of the cavity along the entire length of the guide portion is formed, whereby the connection receives a high stability.
  • the outer circumferential surface of the wall of the cavity is adapted.
  • the housing has an enlarged diameter at both axial ends of the guide portion, the outer circumferential surfaces of the wall of the cavity are adapted.
  • the housing has, at least in one direction of displacement of the piston, advantageously in both, at least one stop for limiting the travel of the piston.
  • the camshaft is tubular.
  • 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, wherein a first and a second device 11 for a relative rotation between 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.
  • the Figures 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 accumulator 15.
  • the phase adjusting device 12 comprises a drive element 14, an output element 16 and two side covers 17, 18, which are arranged on the axial side surfaces of the drive element 14.
  • 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 circumferential wall 21 of the drive element 14, five projections 22 extend radially inwards. 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 element 14.
  • the output member 16 is rotatably connected to the camshaft 6,7.
  • a central screw 13 passes through a central opening 16a of the output element 16 and engages in a threaded portion 25 of the camshaft 6, 7 a.
  • a shoulder of the central screw 13 is located on the camshaft 6, 7 facing away from the side surface of the output element 16 at.
  • 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 is formed in the opening of the first side cover 17.
  • 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.
  • the camshaft 6, 7 has a plurality of openings 35, via which pressure medium conveyed by a pressure medium pump 48 passes into its interior.
  • a pressure medium path 36 is formed, which communicates on the one hand with the openings 35 and on the other hand with the control valve 34.
  • a control valve 34 is arranged in the interior of the central screw 13. By means of the control valve 34 pressure medium can be selectively directed to the first or second pressure chambers 30, 31 and discharged from the respective other pressure chambers 30, 31.
  • a pressure medium channel 37 is provided which communicates on the one hand with the pressure medium path 36 and on the other hand with a cavity 38 of the hollow camshaft 6, 7.
  • the pressure medium channel 37 is formed as an axial bore, which passes through the threaded portion of the central screw 13.
  • the pressure accumulator 15 is arranged.
  • the pressure accumulator 15 comprises a housing 40, a piston 41 and a force accumulator, in the illustrated embodiment, a spring element 42.
  • the housing 40 is disposed within the cavity 38 and fixedly connected to a wall 43 of the cavity 38.
  • the outer surface of the housing 40 of the wall 43 is adapted and non-positively connected thereto. Also conceivable are embodiments in which the housing 40 is connected to the wall 43 in a material or form-fitting manner. In addition, the housing 40 can be fixed by means of a securing ring 24. In the interior of the housing 40, the piston 41 is arranged axially displaceable, wherein this is cup-shaped in the illustrated embodiment.
  • the entire housing 40 serves as a guide portion 44, wherein an inner circumferential surface of the guide portion 44 is formed as a guide surface 45 for a cylindrical portion of the piston 41.
  • the cylindrical portion of the piston 41 completely or partially abut the guide surface 45.
  • the outer circumferential surface of the piston 41 is adapted to the guide surface 45 such that it separates the housing 40 pressure medium-tight in two areas axially in front of and behind the bottom of the piston 41.
  • the piston 41 is acted upon by means of the spring element 42, which is arranged in the region of the cylindrical portion with a force.
  • the spring element 42 is supported, on the one hand, on a stop 46, which is formed on the end of the housing 40 facing away from the phase adjusting device 12, and on the other hand on the bottom of the piston 41.
  • the spring element 42 acts on the piston 41 with a force in the direction of the pressure medium channel 37.
  • the displacement of the piston 41 is limited in the direction of the pressure medium channel 37 by a stop 46 which is formed on the phase adjusting device 12 facing the end.
  • the housing 40 and the piston 41 are formed as sheet metal parts, which are made for example by a non-cutting manufacturing process, such as a deep drawing process. This has the advantage that the guide surface 45 and the cylindrical portion of the piston 41 can be produced so precisely by this shaping process that they do not have to be reworked.
  • the use of the housing 40 also eliminates costly post-processing steps of the wall 43 of the cavity 38.
  • FIG. 6 a second embodiment of a pressure accumulator 15 is shown.
  • This has the difference from the first embodiment in that the guide portion 44 does not extend over the entire axial length of the housing 41 and does not abut the wall 43 of the cavity 38.
  • the guide section 44 is adjoined in the axial direction by an enlarged area 47.
  • the outer circumferential surfaces of the enlarged diameter portions 47 of the wall 43 are adapted.
  • the non-positive connection between the housing 40 and wall 43 is only in Area of the diameter-enlarged areas 47 before.
  • deformation of the guide surface 45 during the press-fitting operation of the housing 40 into the cavity 38 is avoided.
  • pressure medium is passed from the pressure medium pump 48 via the openings 35, the pressure medium path 36 and the control valve 34 to the phase adjusting device 12. Furthermore, pressure medium is conducted via the openings 35, the pressure medium path 36, the pressure medium channel 37 and a housing opening 50 in the housing 40.
  • the pressure medium acts on the piston 41 with a force, whereby it is axially displaced against the force of the spring element 42.
  • the accumulator 15 is filled ( FIG. 4 ). If the system pressure delivered by the pressure medium pump 48 drops, the force of the pressure medium on the piston 41 drops, as a result of which it is displaced by the spring element 42 in the direction of the pressure medium channel 37 and thus supplies pressure medium to the system. Due to a check valve 49, the pressure medium is prevented from flowing back into the pressure medium system and thus is completely available to the phase adjusting device 12, whereby its responsiveness and the adjustment speed are maintained at a high level.

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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 (7)

  1. Ensemble (11) servant à établir de manière variable les instants de commutation de soupapes (9, 10) de remplacement des gaz d'un moteur (1) à combustion interne, l'ensemble présentant
    un dispositif hydraulique (12) de réglage de phase, un arbre (6, 7) à cames et un réservoir sous pression (15),
    le dispositif hydraulique (12) de réglage de phase pouvant être amené à être relié à entraînement à un arbre (2) de vilebrequin et étant relié à rotation solidaire à l'arbre (6, 7) à cames,
    la position de la phase de l'arbre (6, 7) à cames par rapport à l'arbre (2) de vilebrequin pouvant être établie de manière variable au moyen du dispositif hydraulique (12) de réglage de phase,
    l'intérieur de l'arbre (6, 7) à cames présentant une cavité (38),
    le réservoir sous pression (15) étant disposé dans la cavité (38) et communiquant avec le dispositif hydraulique (12) de réglage de phase,
    le réservoir sous pression (15) présentant un piston (41) coulissant longitudinalement,
    caractérisé en ce que
    le réservoir sous pression (15) présente un boîtier (40) disposé dans la cavité (38) et dans lequel le piston (41) est guidé à coulissement longitudinal.
  2. Ensemble (11) selon la revendication 1, caractérisé en ce que le réservoir sous pression (13) présente un élément élastique (42) qui applique sur le piston (41) une force opposée à la force du moyen de poussée.
  3. Ensemble (11) selon la revendication 1, caractérisé en ce que le boîtier (40) présente au moins dans une direction de coulissement du piston (41) au moins une butée (46) qui limite la course du piston (41).
  4. Ensemble (11) selon la revendication 1, caractérisé en ce que le réservoir sous pression (15) est immobilisé dans la cavité (38) au moyen d'une liaison en correspondance mécanique entre le boîtier (40) et une paroi (43) de cette cavité.
  5. Ensemble (11) selon la revendication 1, caractérisé en ce que le boîtier (40) présente une partie de guidage (44) et le piston (41) une surface d'enveloppe extérieure adaptée à la surface d'enveloppe intérieure de la partie de guidage (44).
  6. Ensemble (11) selon la revendication 5, caractérisé en ce que la partie de guidage (44) s'étend sur toute la longueur du piston (41).
  7. Ensemble (11) selon la revendication 5, caractérisé en ce que le boîtier (40) présente aux deux extrémités axiales de la partie de guidage (44) une partie (47) de plus grand diamètre dont les surface extérieures sont adaptées à la paroi de la cavité (38).
EP09782804.0A 2008-10-07 2009-09-09 Dispositif de réglage variable des temps de commande des soupapes d échange de gaz d un moteur à combustion interne Not-in-force EP2331797B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008050672 2008-10-07
PCT/EP2009/061674 WO2010040617A1 (fr) 2008-10-07 2009-09-09 Dispositif de réglage variable des temps de commande des soupapes d’échange de gaz d’un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP2331797A1 EP2331797A1 (fr) 2011-06-15
EP2331797B1 true EP2331797B1 (fr) 2018-05-09

Family

ID=41319702

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09782804.0A Not-in-force EP2331797B1 (fr) 2008-10-07 2009-09-09 Dispositif de réglage variable des temps de commande des soupapes d échange de gaz d un moteur à combustion interne

Country Status (7)

Country Link
US (1) US8622038B2 (fr)
EP (1) EP2331797B1 (fr)
JP (1) JP2012505335A (fr)
KR (1) KR101600123B1 (fr)
CN (1) CN102177317B (fr)
DE (1) DE102009034011B4 (fr)
WO (1) WO2010040617A1 (fr)

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DE102010061337B4 (de) 2010-12-20 2015-07-09 Hilite Germany Gmbh Hydraulikventil für einen Schwenkmotorversteller
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DE102013219075B4 (de) * 2013-09-23 2020-11-26 Schaeffler Technologies AG & Co. KG Multiverriegelung eines Nockenwellenverstellers
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DE102009034011A1 (de) 2010-04-08
KR101600123B1 (ko) 2016-03-04
DE102009034011B4 (de) 2018-04-05
EP2331797A1 (fr) 2011-06-15
CN102177317B (zh) 2014-07-02
WO2010040617A1 (fr) 2010-04-15
US20110239966A1 (en) 2011-10-06
KR20110082555A (ko) 2011-07-19
JP2012505335A (ja) 2012-03-01
US8622038B2 (en) 2014-01-07
CN102177317A (zh) 2011-09-07

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