EP2478189B1 - Dispositif de dephasage d'ouverture de soupapes pour moteur a combustion interne - Google Patents

Dispositif de dephasage d'ouverture de soupapes pour moteur a combustion interne Download PDF

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Publication number
EP2478189B1
EP2478189B1 EP10745609.7A EP10745609A EP2478189B1 EP 2478189 B1 EP2478189 B1 EP 2478189B1 EP 10745609 A EP10745609 A EP 10745609A EP 2478189 B1 EP2478189 B1 EP 2478189B1
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EP
European Patent Office
Prior art keywords
pressure medium
pressure
hand
volume
chambers
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.)
Active
Application number
EP10745609.7A
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German (de)
English (en)
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EP2478189A1 (fr
Inventor
Jürgen Plate
Jochen Auchter
Lutz Witthöft
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of EP2478189A1 publication Critical patent/EP2478189A1/fr
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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
    • 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
    • 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
    • F01L2001/0475—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
    • 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 and at least one volume memory, wherein the phase adjusting device can be brought into driving connection with a crankshaft and a camshaft and at least one Tecverstellhunt and at least one retardation has, which via pressure medium lines pressure medium supplied or can be discharged from these, wherein by pressure medium supply to the advance chamber at the same pressure medium discharge from the retard a phase angle of the camshaft relative to the crankshaft in the direction of early timing can be adjusted by pressure medium supply to the retardation with simultaneous pressure fluid discharge from the ceremoniestellhunt a phase the camshaft can be adjusted relative to the crankshaft in the direction of later timing, wherein the or Volume accumulators can be supplied during operation of the internal combustion engine pressure medium.
  • a hydraulic phase adjusting device the device integrated into 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.
  • Essential characteristics of such devices are the Phasenverstell für and the need for pressure medium. In order to be able to optimally adapt the phase position to the different driving situations, high phase adjustment speeds are desirable.
  • an ever lower pressure medium requirement is required to be able to design the pressure medium pump of the internal combustion engine smaller or to be able to reduce the delivery rate when using regulated pressure medium pumps.
  • Such a device is for example from the EP 0 806 550 A1 known.
  • the device comprises a vane-type phase-adjusting device with a drive element, which is in drive connection with the crankshaft, and an output element, which is non-rotatably connected to the camshaft.
  • a plurality of pressure chambers are formed, wherein each of the pressure chambers is divided by means of a wing into two counteracting pressure chambers.
  • the pressure medium required for the phase adjustment is provided by a pressure medium pump of the internal combustion engine and directed by means of a control valve selectively to the early or late adjustment.
  • the pressure medium flowing out of the phase adjusting device is directed into a pressure medium reservoir, the oil sump of the internal combustion engine. The phase adjustment thus takes place by means of the system pressure provided by the pressure medium pump of the internal combustion engine.
  • phase adjusting device is also formed in prisegelzellenbauart and several early or late adjustment provided.
  • the phase adjustment is not done by pressurizing the pressure chambers by a pressure medium pump, but it is exploited alternating torques acting on the camshaft.
  • the alternating moments are caused by the rolling of the cams on each biased with a valve spring gas exchange valves.
  • the rotational movement of the camshaft is braked during the opening of the gas exchange valves and accelerated during closing. These alternating moments are transmitted to the phase adjusting device, so that the wings are periodically applied in the direction of the late and early attack with a force.
  • pressure peaks are generated alternately in the advance chambers and the retard chambers. If the phase position is to be kept constant, then a flow of pressure medium from the pressure chambers is prevented. In the case of a phase adjustment in the direction of earlier control times, a drainage of pressure medium from the advance chambers is prevented, even at the times in which pressure peaks are generated in the advance chambers. Increases due to the alternating moments of the pressure in the retardation, so this pressure is used to direct pressure medium from the retardation under the pressure of the generated pressure peak in the advance chambers. Analog succeeds a phase adjustment in the direction of later timing.
  • the pressure chambers are connected to a pressure medium pump, but only to compensate for leaks from the phase adjusting device. The phase adjustment is thus carried out by diverting pressure medium from the pressure chambers to be emptied into the pressure chambers to be filled under the pressure of the generated pressure peak.
  • Another device is from the US 2009/0133652 A1 known.
  • a phase adjustment takes place at low alternating torques, analogous to the device of the EP 0 806 550 A1 .
  • a pressure medium pump By pressurizing the Tecverstellhuntn or captive cells by a pressure medium pump, at the same pressure medium discharge from the other pressure chambers to the oil sump of the internal combustion engine.
  • high alternating torques analogous to the device from the US 5,107,804 A , these used to direct the pressure medium under high pressure from the Vietnameseverstellhuntn (S Georgtverstellhuntn) in the phoneverstellhuntn (Schverstellhuntn).
  • the pressure medium ejected from the pressure chambers is returned to a control valve which controls the pressure medium supply to or the pressure medium discharge from the pressure chambers.
  • This pressure medium passes via check valves within the control valve to the inlet connection, which is connected to the pressure medium pump, wherein a portion of the pressure medium is ejected into the pressure medium reservoir of the internal combustion engine.
  • the document EP1607590 A1 discloses an internal combustion engine with a hydraulic device (1) for adjusting the rotational angle of a camshaft relative to a crankshaft with a rotor arranged thereon wings and a rotatably connected to a drive wheel stator.
  • the rotor and the stator form pressure chambers with one another, which can be filled with hydraulic fluid via a hydraulic fluid system, wherein a volume accumulator is arranged in the hydraulic fluid system. Therefore, this volume storage is based on the object to reduce pressure fluctuations as far as possible in a hydraulic fluid circuit provided with a device for adjusting the rotational angle and thus to eliminate in particular pressure peaks.
  • 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 Phasenverstell für to be increased.
  • the object is achieved in that in addition at least two pressure medium channels are provided, the first pressure fluid channel on the one hand into one of the volume memory and on the other hand communicates with the Aktverstellhunt, the second pressure fluid channel on the one hand into one of the volume memory and on the other hand communicates with the retardation and each of the pressure medium channels is associated with a check valve, which prevents a pressure medium flow from the respective pressure chamber to the volume memory and can allow a reverse pressure medium flow.
  • the device has a hydraulic phase adjusting device which has at least two mutually acting pressure chambers, at least one advance chamber and at least one retard adjustment chamber.
  • the invention is applicable to any type of hydraulic phase adjusting device, such as vane-type devices, such as in the EP 0 806 550 A1 disclosed as Axialkolbenversteller, such as in the DE 42 18 078 C1 discloses, or as Schwenkhebelversteller, such as in the US 4,903,650 A disclosed.
  • the phase adjusting device has at least one drive element and an output element, wherein the drive element is in drive connection with a crankshaft of the internal combustion engine, for example via a chain, belt or gear drive.
  • the output element is in drive connection with the camshaft.
  • pressure medium line is supplied to the pressure chambers and discharged from these.
  • the pressure medium can for example be provided by a pressure medium pump of the internal combustion engine and the pressure medium to be discharged from the pressure chambers can be passed into a pressure medium reservoir, for example the oil sump of the internal combustion engine.
  • the device also has one or more volume storage for receiving pressure medium.
  • the pressure medium can be stored without pressure or under pressure in the volume store (s). During operation of the internal combustion engine, the pressure medium is supplied to the volume accumulator (s).
  • At least two pressure medium channels are provided, which connect the one or more volume memory with the pressure chambers.
  • one end of each pressure medium channel opens into one of the volume accumulators, the other end of the first pressure medium channel communicating with the one or more advance chambers and the other end of the second pressure medium channel communicating with the retard chamber (s).
  • the first pressure medium channel communicates exclusively with the or the advance chambers and not with the late adjustment chambers.
  • the second pressure medium channel communicates exclusively with the retardation chambers or chambers and not with the advance chambers.
  • volume memory Conceivable, for example, embodiments with only one volume memory, which communicates via the pressure medium channels with all the pressure chambers.
  • a plurality of volume reservoirs are provided.
  • a part of the volume memory communicate exclusively with the advance chambers while another portion of the volume memory communicates exclusively with the retard chambers.
  • each volume memory two pressure chambers, for example, a Vietnameseverstellhunt and a boss are assigned, with which the respective volume memory communicates via the pressure medium channels.
  • first / second pressure medium channel communicates with all early / late adjustment
  • several pressure medium channels may be provided, for example, a pressure medium channel per pressure chamber.
  • a first (early) retardation chamber communicates via a pressure medium channel with a volume accumulator and the other (early) retard chambers pressure medium via the first (early) retard chamber is supplied from the volume memory.
  • Each of the pressure medium channels is associated with a check valve, wherein each of the check valves prevents a pressure medium flow from the associated pressure chamber to the volume memory and a reverse pressure medium flow, with a suitable pressure difference upstream and downstream of the check valve permits.
  • the check valves can be arranged, for example, within the pressure medium channel and designed, for example, as a ball or plate check valve. Likewise conceivable are embodiments in which a spring plate cooperates with an opening region of the associated pressure medium channel in the manner of a check valve.
  • the volume accumulator can communicate via one or more pressure medium lines with a pressure medium reservoir of the internal combustion engine or be connectable.
  • the phase angle of the camshaft relative to the crankshaft can be varied or held with this device on the one hand by the system pressure provided by the pressure medium pump of the internal combustion engine. To the Others can be used to change the moment acting on the camshaft to bring about a phase adjustment.
  • the proportion of the alternating torque acting against the adjustment direction is intercepted and the proportion acting in the adjustment direction is utilized in order to increase the phase adjustment speed.
  • the amount of the component of the alternating torque, which is to be used for phase adjustment increases continuously in dependence on the rotational position of the camshaft from 0 to a maximum value and falls back to zero.
  • the output element is rotated relative to the drive element in the direction of the desired phase position.
  • the pressure increases rapidly in the pressure chambers to be emptied, whereby the emptying of the pressure chambers is accelerated.
  • the pressure medium requirement of the pressure chambers to be filled increases to the same extent.
  • the pressure medium requirement of the pressure chambers to be filled can be supplied by the pressure medium pump.
  • the pressure fluid flowing out of the pressure chambers to be emptied fills the volume reservoir (s).
  • the pressure medium requirement of the pressure chambers to be filled increases, which can lead to the fact that the volume flow delivered by the pressure medium pump is insufficient to completely fill the pressure chambers to be filled.
  • the pressure medium stored in the volume memory (s) can be used in these phases to fill the pressure chambers by the pressure accumulator (s) and the pressure medium channels provided.
  • the phase adjustment speed can be increased considerably in comparison to devices which are operated exclusively by the system pressure provided by the pressure medium pump.
  • the pressure medium which is ejected from the pressure chambers to be emptied, passed directly and under high pressure to the pressure chambers to be filled.
  • the pressure medium is not passed under high alternating torques under the high pressure generated by these high pressure in the pressure chambers. Rather, the vacuum occurring in the pressure chambers to be filled is utilized to forward the pressure medium from the volume or the accumulators in the pressure chambers. Thus, no sudden phase changes occur, whereby the controllability of the device is maintained.
  • the volume memory is arranged within the phase adjusting device.
  • the stored pressure medium is in local proximity to the pressure chambers.
  • pressure medium losses between volume memory and pressure chambers are lowered and the response of the device improved.
  • the volume accumulator is connectable via one or more pressure medium lines with a pressure medium reservoir, wherein the mouth region of the pressure medium channels in the volume memory with larger Distance from the axis of rotation of the phase adjusting device is arranged as the mouth region of the pressure medium lines in the volume memory. This ensures that excess pressure medium can be removed from the volume accumulator to the pressure medium reservoir of the internal combustion engine.
  • the phase adjusting device rotates about its axis of rotation is ensured due to the centrifugal force that still pending at the mouth areas of the pressure medium channels in the volume or the pressure medium for further transport to the pressure chambers.
  • a check valve is assigned, which prevents a pressure medium flow from the pressure medium reservoir to the volume memory and allow a reverse pressure medium flow. If this check valve is dispensed with, the pressure in the pressure medium reservoir, as a rule atmospheric pressure, prevails in the volume reservoirs.
  • the volume or the accumulator pressure medium can be supplied directly from a pressure medium pump. In this case, for example, branch off a pressure medium line directly from the engine oil gallery and open, bypassing the pressure chambers in the volume memory.
  • the pressure medium via a control valve, which controls the pressure medium flow to and from the pressure chambers, reach the volume or the stores. This ensures that the volume accumulator is adequately supplied with pressure medium at all times.
  • pressure medium can be supplied to the volume accumulator from the pressure chambers. With each phase adjustment, one group of pressure chambers expands at the expense of the other pressure chambers.
  • the pressure fluid flowing out of the other pressure chambers can be supplied to the volume accumulator (s) and reused, as a result of which the delivery flow of the pressure medium pump can be lowered.
  • the pressure medium ejected from the pressure chambers can, for example, via a control valve, which controls the pressure medium flows from and to the pressure chambers, are directed to the or the volume memory.
  • the device has a control valve, by means of which the pressure medium supply can be controlled by a pressure medium pump to the pressure chambers and the pressure medium discharge from the pressure chambers.
  • the control valve has an inlet port, a first and a second working port and at least a first volume storage port, wherein a first pressure medium line is provided which communicates on the one hand with the first working port and on the other hand into the advance chamber, wherein a second pressure medium line is provided which communicates on the one hand with the second working port and on the other hand into the retardation, wherein a third pressure medium line is provided which communicates on the one hand with the inlet port and on the other hand with a pressure medium pump, wherein at least a fourth pressure medium line is provided, on the one hand with the Volumen Grandean gleich communicates and on the other hand opens into the volume memory and wherein by means of the control valve, a connection between the inlet port and the first and the second working port and e
  • the control valve has an inlet connection, a first and a second working connection, two volume storage connections and a discharge connection, wherein a first pressure medium line is provided which communicates with the first working connection on the one hand and opens into the advance chamber on the other hand second pressure medium line is provided which communicates on the one hand with the second working port and on the other hand into the retardation, wherein a third pressure medium line is provided which communicates on the one hand with the inlet port and on the other hand with a pressure medium pump, wherein two fourth pressure medium lines are provided, on the one hand in the volume memory and on the other hand with one each communicate the volume storage ports, with a fifth pressure medium line provided, which communicates on the one hand with the drain port and the other with a pressure medium reservoir, wherein by means of the control valve, a connection between the inlet port and the first and the second working port, a connection between one of the volume storage ports and the other working port and a connection between the other volume storage port and the drain port can be made.
  • the pressure fluid flows to be filled to the pressure chambers and the pressure fluid outflows are controlled by the pressure chambers to be emptied via a control valve which simultaneously controls the filling of the volume or the memory from the pressure chambers to be emptied.
  • the pressure medium flows are conducted via control edges within the control valve and can be influenced by the design of existing between the control edges flow areas.
  • the device can operate both in a mode in which the phase adjustment is effected by the system pressure generated by the pressure medium pump and in a mode in which the change moment is used for phase adjustment. In this case, the change from one to the other mode takes place automatically in that the delivery volume of the pressure medium pump no longer covers or recovers the pressure medium requirement of the pressure chambers to be filled.
  • the phase adjustment can be controlled by means of a sequence control, ie the adjustment speed is determined by the amount of pressure flowing from the pressure chambers and not by the amount of the pressure chambers to be filled pressure medium.
  • the adjustment speed is determined by the amount of pressure flowing from the pressure chambers and not by the amount of the pressure chambers to be filled pressure medium.
  • This can be realized in a simple manner in that a flow area of the pressure chambers to the volume or the accumulator or the pressure medium reservoir is always designed smaller than a flow area of the pressure medium pump to the pressure chambers. This prevents air from being sucked into the pressure chambers.
  • the pressure medium flow to and from the pressure chambers in response to a control parameter of the control valve does not increase abruptly, so that a simple and stable control of the device is ensured.
  • the pressure medium channels which connect the volume or the storage with the pressure chambers for example, open directly into the corresponding pressure chambers or in the pressure medium lines that connect the working ports of the control valve with the pressure chambers.
  • 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 variably setting the timing of gas exchange valves 9,10 an internal combustion engine 1 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.
  • FIG. 2 shows a first embodiment of a device 11 according to the invention in longitudinal section.
  • FIG. 3 shows a plan view of a phase adjusting device 12 of the device 11, wherein the arranged in the line of sight side cover 17 has been omitted.
  • the device 11 has a phase adjusting device 12 and a control valve 13.
  • the phase adjusting device 12 has a drive element 15 and an output element 16.
  • On the axial side surfaces of the drive element 15 each have a side cover 17 is rotatably attached.
  • the output element 16 is designed in the form of an impeller and has a substantially cylindrical hub member 18, extend from the outer cylindrical surface in the illustrated embodiment, two wings 19 in the radial direction outwards and are integrally formed with the hub member 18.
  • a central passage opening of the output element 16 is penetrated by a hollow camshaft 6, 7, wherein the output element 16 by means of a press fit with the Camshaft 6, 7 is rotatably connected.
  • projections 21 extend radially inwards.
  • the projections 21 are formed integrally with the peripheral wall 20.
  • the drive element 15 is mounted by means of radially inner circumferential walls of the projections 21 relative to the output member 16 rotatably mounted on this.
  • a pressure medium chamber 22 is formed between each two circumferentially adjacent projections 21.
  • Each of the pressure medium spaces 22 is circumferentially bounded by opposing, substantially radially extending boundary walls 23 of adjacent projections 21, in the axial direction of the side covers 17, radially inwardly of the hub member 18 and radially outwardly of the peripheral wall 20.
  • one wing 19 projects in two of the four pressure medium spaces 22, wherein the wings 19 are designed in such a way that they rest against both the side covers 17 and the peripheral wall 20.
  • Each wing 19 thus divides the respective pressure medium chamber 22 into two counteracting pressure chambers 24, 25, an advance chamber 24 and a retard 25.
  • Each of the pressure chambers 24, 25 communicates with one of the volume accumulators 31 via a pressure medium channel 32a, b formed in the projections 21.
  • a first pressure medium channel 32a connects a volume accumulator 31 with an advance chamber 24 and a respective second pressure medium channel 32b with a volume accumulator 31 a late adjustment 25.
  • Each fluid channel 32a, b is associated with a first check valve 33, which prevents a flow of pressure medium from the respective pressure chamber 24, 25 to the respective volume memory 31 and a pressure medium flow from the volume memory 31 to the respective pressure chamber 24, 25 permits, as soon as de Finished pressure difference between the pressure chamber 24, 25 and the volume memory 31 prevails.
  • the first check valves 33 can be arranged, for example, within the pressure medium channels 32a, b and as ball check valves be educated.
  • the output member 16 is received in the drive member 15 and rotatably supported within a defined Winkelbreichs to this.
  • the angular range is limited in one direction of rotation of the driven element 16 in that the wings 19 come into contact with a corresponding boundary wall 23 (early stop 23a) of the associated pressure medium spaces 22.
  • the angular range in the other direction of rotation is limited by the fact that the wings 19 come to rest on the other boundary walls 23 of the associated pressure medium spaces 22, which serve as a late stop 23b.
  • the phase angle of the output element 16 can be adjusted relative to the drive element 15 in the direction of earlier control times.
  • the output element 16 is rotated in the direction of rotation of the device 11, characterized by the arrow 29, relative to the drive element 15.
  • the phase position of the output element 16 can be adjusted relative to the drive element 15 in the direction of later control times.
  • the output element 16 is rotated counter to the direction of rotation 29 of the device 11 relative to the drive element 15.
  • the pressure medium supply to or pressure fluid removal from the pressure chambers 24, 25 via a hydraulic circuit, the in FIG. 4 is shown and controlled by means of the control valve 13.
  • the control valve 13 has an inlet connection P, a volume storage port V 1 and two working ports A, B on.
  • the hydraulic circuit has five pressure medium lines 26a, b, p, v, t.
  • the first pressure medium line 26a communicates on the one hand with the first working port A and on the other hand flows into the advance chambers 24.
  • the second pressure medium line 26b communicates on the one hand with the second working port B and on the other hand flows into the retardation chambers 25.
  • the third pressure medium line 26p connects a pressure medium pump 27 with the inlet port P.
  • a second check valve 34 prevents a pressure medium flow from the control valve 13 to the pressure medium pump 27 and can allow a reverse pressure medium flow.
  • the fifth pressure medium line 26v communicates on the one hand with the volume storage port V 1 and on the other hand flows into the volume accumulator 31.
  • the fifth pressure medium line 26t opens on the one hand in the volume accumulators 31 and on the other hand in a pressure medium reservoir 28, for example an oil sump of the internal combustion engine 1.
  • the fifth pressure medium line can directly Pressure medium reservoir 28 open (solid line in FIG. 4 ) or with the interposition of a third check valve 50 (dashed line in FIG. 4 ).
  • the control valve 13 can assume three control positions S1-S3.
  • the inlet connection P is connected to the first working connection A and the second working connection B is connected to the volume storage connection V 1 .
  • the second control position S2 there is no connection between the working ports A, B on the one side and the inlet port P and the volume storage port V 1 on the other side.
  • the third control position S3 the inlet connection P is connected to the second working connection B and the first working connection A is connected to the volume storage connection V 1 .
  • each gas exchange valve 9, 10 by means of a cam 8 periodically against the force of a valve spring 30 (FIG. FIG. 1 ) opened and closed again.
  • a braking torque which is the vector product of the force of the valve spring 30 with the Lever arm of the cam 8 corresponds.
  • the closing of the gas exchange valve 9, 10 acts on the camshaft 6, 7 an accelerating torque, which corresponds to the vector product of the force of the valve spring 30 with the lever arm of the cam 8.
  • the alternating moment causes the wings 19 to be urged counter to the direction of rotation 29 of the phase adjusting device 12 when the cam 8 runs up.
  • the pressure in the advance chambers 24 is increased and the pressure in the retard chambers 25 is lowered.
  • the wings 19 are urged in the direction of rotation 29 of the phase adjusting device 12, whereby the pressure in the Vietnameseverstellhuntn 24 decreases and the pressure in the retard 25 increases.
  • the control valve 13 assumes the first control position S1.
  • the pressure medium conveyed by the pressure medium pump 27 reaches via the third pressure medium line 26p, the inlet port P, the first working port A and the First pressure medium line 26a to the advance chambers 24.
  • the wings 19 are moved within the respective pressure medium spaces 22 in the direction of rotation 29 of the phase adjusting device 12.
  • pressure medium from the retardation chambers 25 via the second pressure medium line 26b, the second working port B, the volume storage port V 1 and the fourth pressure medium line 26v is forced into the volume memory 31.
  • the volume of the 31 crowded.
  • the volume of Aktverstellhuntn 24 increases at the expense of phoneverstellhuntn 25 and the wings 19 are moved in the direction of rotation 29 of the phase adjusting device 12.
  • the camshaft 6, 7 is rotated in the direction of earlier control times relative to the crankshaft 2.
  • the volume accumulators 31 are filled by the pressure medium flowing out of the retard chambers 25, excess pressure medium being expelled via the fifth pressure medium line 26t into the pressure medium reservoir 28 against atmospheric pressure or the third nonreturn valve 50.
  • a higher pressure level prevails both in the advance chambers 24 and in the retard adjustment chambers 25 than in the volume accumulators 31, whereby the first check valves 33 prevent a pressure medium flow from the volume accumulators 31 into the pressure chambers 24, 25.
  • Pressure medium is thus supplied to the volume accumulators 31 from the retard adjustment chambers 25 via the second pressure medium line 26b, the second working port B, the volume storage port V 1 and the fourth pressure medium line 26v.
  • the volume accumulators 31 prevails due to the opening into the pressure medium reservoir 28 fifth pressure medium line 26t atmospheric pressure, or in embodiments in which a third check valve 50 is provided in the fifth pressure medium line 26t, defined by the third check valve 50 higher pressure level, but which less than the pressure level within the retard chambers 25 is.
  • the first check valves 33 Due to the higher pressure levels in the retard chambers 25 block the first check valves 33, which connect the volume memory 31 with the retard 25, a pressure medium flow from the volume accumulators 31 in the retard 25 simultaneously arrives pressure medium from the pressure medium pump 27 via the inlet port P, the first When the pressure medium requirement of the pressure chambers 24 to be filled exceeds the volume flow delivered by the pressure medium pump 27, the pressure in the advance chambers 24 drops below the pressure prevailing in the volume accumulators 31. Thus, the first check valves 33 release a pressure medium flow through the first pressure medium channels 32 a from the volume stores 31 to the advance chambers 24.
  • the control valve 13 assumes the third control position S3.
  • the pressure medium conveyed by the pressure medium pump 27 reaches the third pressure medium line 26p, the inlet port P, the second working port B and the second pressure medium line 26b to the retarding 25.
  • the wings 19 are moved within the respective pressure medium spaces 22 against the direction of rotation 29 of the phase adjusting device 12.
  • pressure medium from the Appelverstellhuntn 24 via the first pressure medium line 26a, the first working port A, the volume storage port V 1 and the fourth pressure medium line 26v is forced into the volume memory 31.
  • the volume of the retard chambers 25 increases at the expense of the advance chambers 24 and the wings 19 are displaced counter to the direction of rotation 29 of the phase adjuster 12.
  • the camshaft 6, 7 is rotated in the direction of later control times relative to the crankshaft 2.
  • the volume memory 31 are filled by the running out of the advance chambers 24 pressure medium, wherein excess pressure medium via the fifth pressure medium line 26t in the pressure medium reservoir 28 against atmospheric pressure or the third check valve 50 is ejected.
  • a higher pressure level prevails both in the advance chambers 24 and in the retard adjustment chambers 25 than in the volume accumulators 31, whereby the first check valves 33 prevent a pressure medium flow from the volume accumulators 31 into the pressure chambers 24, 25.
  • Pressure medium is thus supplied from the advance chambers 24 via the first pressure medium line 26a, the first working port A, the volume storage port V 1 and the fourth pressure medium line 26v the volume accumulators 31.
  • the volume accumulators 31 prevails due to the opening into the pressure medium reservoir 28 fifth pressure medium line 26t atmospheric pressure or in embodiments in which a third check valve 50 is provided in the fifth pressure medium line 26t, defined by the third check valve 50 higher pressure level, but which lower as the pressure level within the retard chambers 25.
  • the first check valves 33 which connect the volume accumulators 31 to the advancing chambers 24, block a flow of pressure medium from the volume accumulators 31 into the advancing chambers 24.
  • pressure medium from the pressure medium pump 27 passes via the inlet connection P, the second working connection B and the second pressure medium line 26b to the retard chambers 25. If the pressure medium requirement of the pressure chambers 25 to be filled exceeds the volume flow delivered by the pressure medium pump 27, the pressure in the retard adjustment chambers 25 drops under the pressure prevailing in the volume accumulators 31 pressure. Thus, the first check valves 33 release a pressure medium flow through the second pressure medium channels 32 b from the volume stores 31 to the retard chambers 25.
  • the control valve 13 assumes the second control position S2. In this control position are the working connections Completed. Thus, the pressure medium conveyed from the pressure medium pump 27 to the inlet port P does not reach any of the working ports A, B. Likewise, no pressure fluid from the pressure chambers 24, 25 reaches the volume memory port V 1 . Upon the occurrence of pressure peaks in the pressure chambers 24, 25, which are caused by the acting on the camshaft 6, 7 alternating torque, an outlet of pressure medium from the pressure chambers 24, 25 prevented by the closed working ports A, B. The wings 19 are thus hydraulically clamped between the pressure chambers 24, 25, whereby the current phase position is maintained.
  • FIGS. 5 and 6 show the detail Z out FIG. 2 in an enlarged view, wherein the control valve 13 in the first ( FIG. 5 ) or third control position S3 ( FIG. 6 ) is shown.
  • the first and the second pressure medium line 26a, b are formed as axial staggered radial bores within the output element 16.
  • two fourth pressure medium lines 26v are provided, which are likewise designed as axially offset radial bores within the output element 16.
  • the first, the second and the fourth pressure medium lines 26a, b, v are arranged offset to one another in the circumferential direction of the output element 16 (see FIG. 3 ), in the FIGS. 5 and 6 but shown in a single level for better explanation.
  • the first, second and fourth pressure medium lines 26a, b, v open on the one hand into the advance chambers 24 and the retard chambers 25 and the volume reservoirs 31.
  • the other ends of the pressure medium lines 26a, b, v open into radial bores of the camshaft 6, 7, in turn communicate with the first working port A and the second working port B and two volume accumulator ports V 1 of the control valve 13, which are formed on a valve housing 36 of the control valve 13 as radial openings 37.
  • a control piston 38 is arranged, which by means of an actuating unit, not shown against the force of a spring 39 in the axial direction within the a spring 39 in the axial direction within the valve housing 36 can be moved. In this case, the control piston 38 in each position between the in FIG. 5 and the in FIG. 6 shifted position shown and held.
  • the pressure medium passes through a second control surface 43, which is defined by the overlap of the radial opening 37 of the second working port B with the first annular groove 42.
  • the second control surface 43 is made smaller than the first control surface 41 (flow control).
  • the first control position S1 can be realized by a plurality of positions of the control piston 38 relative to the valve housing 36.
  • control piston 38 must be in a position in which pressure medium from the inlet port P to the first working port A and pressure medium from the second working port B can reach the volume storage port V 1 .
  • first and second control surfaces 41, 43 and, analogously, the pressure medium flow to and from the pressure chambers 24, 25 are greater the further the control piston 38 in the FIG. 5 approaching position shown.
  • the pressure medium passes through a fourth control surface 46, which is defined by the overlap of the radial opening 37 of the first working port A with the second annular groove 45.
  • the fourth control surface 46 is made smaller than the third control surface 44 (process control).
  • the third control position S3 can be realized by a plurality of positions of the control piston 38 relative to the valve housing 36.
  • control piston 38 must be in a position in which pressure medium can pass from the inlet connection P to the second working connection B and pressure medium from the first working connection A to the volume storage connection V 1 .
  • FIGS. 7 and 8 show a second embodiment analogous to the illustrations of FIGS. 5 and 6 , This embodiment is largely identical to the first embodiment, so that in the following only the differences will be discussed.
  • a fourth pressure medium line is 26v provided which communicates on the one hand with the volume accumulators 31 and on the other hand with the single volume memory port V1.
  • the fourth pressure medium line 26v is arranged in the axial direction between the first and second pressure medium line 26a, b.
  • the control piston 38 has two piston openings 40, 47 and an annular groove 42 on its outer circumferential surface, wherein the piston openings 40, 47 and the annular groove 42 are arranged spaced from each other in the axial direction.
  • the annular groove 42 is arranged between the piston openings 40, 47.
  • pressure medium from the late adjustment chambers 25 reaches the second working connection B via the second pressure medium line 26b.
  • the latter communicates via the annular groove 42 with the volume storage connection V 1 .
  • the pressure medium passes through a second control surface 43, which is defined by the overlap of the radial opening 37 of the second working port B with the annular groove 42.
  • the second control surface 43 is made smaller than the first control surface 41 (flow control).
  • the pressure medium passes through a fourth control surface 46, which is defined by the overlap of the radial opening 37 of the first working port A with the annular groove 42.
  • the fourth control surface 46 is made smaller than the third control surface 44 (process control).
  • FIG. 9 shows a further embodiment of a device 11 according to the invention.
  • the third embodiment is designed in many parts identical to the first two embodiments, so that in the following only the deviations are explained.
  • the control valve 13 has two volume storage ports V 1 , V 2 and an additional drain port T. Both volume storage ports V 1 , V 2 are connected via a respective fourth pressure medium line 26 v to the volume reservoirs 31.
  • the outlet connection T is connected to the pressure medium reservoir 28 by means of the fifth pressure medium line 26t.
  • the control valve 13 can in turn assume three control positions S1-S3.
  • first control position S1 the inlet connection P to the first working port A, the second working port B to the second volume storage port V 2 and the first volume storage port V 1 to the drain port T is connected.
  • second control position S2 there is no connection between the working ports A, B on the one side and the inflow port P and the volume accumulator ports V 1 , V 2 on the other side.
  • the inlet connection P is connected to the second working connection B, the first working connection A to the first volume storage connection V 1 and the second volume storage connection V 2 to the discharge connection T.
  • FIGS. 10 and 11 show the control valve 13 of the third embodiment and the associated pressure medium lines 26a, b, v, t.
  • the first, the second and the two fourth pressure medium line 26a, b, v are in turn formed as axially offset from one another, radial bores within the output element 16.
  • the first and second pressure medium line 26a, b in turn open into the corresponding pressure chambers 24, 25 and are connected to the working ports A, B.
  • the fourth pressure medium lines 26v open into the volume memory 31 and are each connected to one of the volume storage ports V 1 , V 2 .
  • the fifth pressure medium line 26t is realized as a radial opening 37 in the camshaft 6, 7 and communicates with the discharge port T and the pressure medium reservoir 28.
  • the control piston 38 is provided with a radial piston opening 40, which is arranged between two annular grooves 42, 45 formed on the outer circumferential surface of the control piston 38.
  • pressure medium from the retardation chambers 25 reaches the second working connection B via the second pressure medium line 26b.
  • the latter is connected to the second volume storage connection V 2 via a second annular groove 45 Connection.
  • the pressure medium passes through a second control surface 43 which is defined by the overlap of the radial opening 37 of the second working port B with the second annular groove 45. If the volume accumulators 31 are completely filled, pressure medium from the volume accumulators 31 passes via the fourth pressure medium line 26v to the first volume accumulator connection V 1 , which is connected to the outlet connection T via the first annular groove 42. In this case, the pressure medium passes through a third control surface 44, which is defined by the overlap of the radial opening 37 of the first volume storage port V 1 with the first annular groove 42.
  • the third control surface 44 is smaller than the second control surface 43 and made smaller than the first control surface 41.
  • the outflow from the late adjustment chambers 25 is throttled with respect to the inflow to the advance chambers 24 and thus a flow control realized in this embodiment.
  • the feed to the volume accumulators 31 is throttled in comparison to the first two embodiments, whereby the pressure medium enters under higher pressure in this.
  • the pressure medium passes through a fifth control surface 48, which is defined by the overlap of the radial opening 37 of the first working port A with the first annular groove 42. If the volume accumulators 31 are completely filled, pressure medium from the volume accumulators 31 reaches the second volume accumulator connection V 2 via the fourth pressure medium line 26 v, which is connected to the outlet connection T via the second annular groove 42. In this case, the pressure medium passes through a sixth control surface 49, which is defined by the overlap of the radial opening 37 of the second volume storage port V 2 with the second annular groove 45. In the illustrated embodiment, the sixth control surface 49 is smaller than the fourth control surface 46 and smaller than the fifth control surface 48 executed.
  • the outflow from the Tecverstellhuntn 24 is throttled with respect to the inflow to the retardation 25 and thus realized in this embodiment, a flow control.
  • the feed to the volume accumulators 31 is throttled in comparison to the first two embodiments, whereby the pressure medium enters under higher pressure in this.
  • the operation of the third embodiment is analogous to the first two embodiments.
  • the presented devices 11 are characterized by significantly increased Phasenverstell füren. In addition, occur due to the realized flow control with small displacements of the control piston 38, no high changes in the pressure medium inflow to the pressure chambers to be filled 24, 25, whereby the control of the phase position is greatly facilitated.
  • a further advantage is that the positions of the control piston 38 to be adjusted relative to the valve housing 36 is independent of whether the volume flow delivered by the pressure medium pump 27 covers or does not cover the pressure medium requirement of the pressure chambers 24, 25 to be filled. Thus, only one control strategy is needed, which can be applied to both operating states of the internal combustion engine 1, whereby the control of the device 11 is further simplified.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (10)

  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) et au moins un accumulateur de volume (31),
    - le déphaseur (12) pouvant être amené en liaison d'entraînement avec un vilebrequin (2) et un arbre à cames (6, 7) et présentant au moins une chambre de réglage en avance (24) et au moins une chambre de réglage en retard (25), auxquelles du fluide sous pression peut être acheminé ou desquelles du fluide sous pression peut être évacué par le biais de conduites de fluide sous pression (26a, b, p, v),
    - une position de phase de l'arbre à cames (6, 7) par rapport au vilebrequin (2) pouvant être déplacée dans la direction de temps de commande en avance par apport de fluide sous pression à la chambre de réglage en avance (24) avec évacuation simultanée de fluide sous pression de la chambre de réglage en retard (25),
    - une position de phase de l'arbre à cames (6, 7) par rapport au vilebrequin (2) pouvant être déplacée dans la direction de temps de commande en retard par apport de fluide sous pression à la chambre de réglage en retard (25) avec évacuation simultanée de fluide sous pression de la chambre de réglage en avance (24),
    - du fluide sous pression pouvant être acheminé au ou aux accumulateurs de volume (31) pendant le fonctionnement du moteur à combustion interne (1),
    - caractérisé en ce qu'en outre au moins deux canaux de fluide sous pression (32a, b) sont prévus, le premier canal de fluide sous pression (32a) débouchant d'une part dans l'un des accumulateurs de volume (31) et d'autre part communiquant avec la chambre de réglage en avance (24), le deuxième canal de fluide sous pression (32b) débouchant d'une part dans l'un des accumulateurs de volume (31) et d'autre part communiquant avec la chambre de réglage en retard (25) et un clapet antiretour (33) étant associé à chacun des canaux de fluide sous pression (32a, b), lequel clapet antiretour interrompt un flux de fluide sous pression de la chambre de pression respective (24, 25) à l'accumulateur de volume (31) et peut autoriser un flux de fluide sous pression en sens inverse.
  2. Dispositif (11) selon la revendication 1, caractérisé en ce que l'accumulateur de volume (31) est disposé à l'intérieur du déphaseur (12).
  3. Dispositif (11) selon la revendication 1, caractérisé en ce que l'accumulateur de volume (31) communique avec ou peut être connecté à un réservoir de fluide sous pression (28) du moteur à combustion interne (1) par le biais d'une ou plusieurs conduites de fluide sous pression (26v, t).
  4. Dispositif (11) selon la revendication 2, caractérisé en ce que l'accumulateur de volume (31) peut être connecté à un réservoir de fluide sous pression (28) par le biais d'une ou plusieurs conduites de fluide sous pression (26v, t), la région d'embouchure des canaux de fluide sous pression (32a, b) dans l'accumulateur de volume (31) étant disposée à plus grande distance de l'axe de rotation du déphaseur (12) que la région d'embouchure des conduites de fluide sous pression (26v, t) dans l'accumulateur de volume (31).
  5. Dispositif (11) selon l'une quelconque des revendications 3 ou 4, caractérisé en ce qu'un clapet antiretour (50) est associé à la ou aux conduites de fluide sous pression (26v, t) qui relient l'accumulateur de volume (31) au réservoir de fluide sous pression, lequel clapet antiretour interrompt un flux de fluide sous pression du réservoir de fluide sous pression (28) à l'accumulateur de volume (31) et peut autoriser un flux de fluide sous pression dans le sens inversé.
  6. Dispositif (11) selon la revendication 1, caractérisé en ce que du fluide sous pression sortant des chambres de pression (24, 25) est acheminé à l'accumulateur de volume (31).
  7. Dispositif (11) selon la revendication 1, caractérisé en ce que du fluide sous pression est acheminé directement depuis la pompe de fluide sous pression (27) à l'accumulateur de volume (31).
  8. Dispositif (11) selon la revendication 1, caractérisé en ce que le dispositif (11) présente une soupape de commande (13) au moyen de laquelle l'apport de fluide sous pression depuis une pompe de fluide sous pression (27) jusqu'aux chambres de pression (24, 25) et l'évacuation de fluide sous pression hors des chambres de pression (24, 25) peuvent être commandés.
  9. Dispositif (11) selon la revendication 8, caractérisé en ce que la soupape de commande présente un raccord d'amenée (P), un premier et un deuxième raccord de travail (A, B), et au moins un premier raccord d'accumulateur de volume (V1),
    - une première conduite de fluide sous pression (26a) étant prévue, laquelle communique d'une part avec le premier raccord de travail (A) et débouche d'autre part dans la chambre de réglage en avance (24),
    - une deuxième conduite de fluide sous pression (26b) étant prévue, laquelle communique d'une part avec le deuxième raccord de travail (B) et débouche d'autre part dans la chambre de réglage en retard (25),
    - une troisième conduite de fluide sous pression (26p) étant prévue, laquelle communique d'une part avec le raccord d'amenée (P) et communique d'autre part avec une pompe de fluide sous pression (27),
    - au moins une quatrième conduite de fluide sous pression (26v) étant prévue, laquelle communique d'une part avec le raccord d'accumulateur de volume (V1) et débouche d'autre part dans l'accumulateur de volume (31) et
    - une connexion entre le raccord d'amenée (P) et le premier ou le deuxième raccord de travail (A, B), et une connexion entre le raccord d'accumulateur de volume (V1) et l'autre raccord de travail (A, B) pouvant être établies au moyen de la soupape de commande (13).
  10. Dispositif (11) selon la revendication 8, caractérisé en ce que
    - la soupape de commande présente un raccord d'amenée (P), un premier et un deuxième raccord de travail (A, B), deux raccords d'accumulateur de volume (V1, V2) et un raccord de sortie (T),
    - une première conduite de fluide sous pression (26a) étant prévue, laquelle communique d'une part avec le premier raccord de travail (A) et débouche d'autre part dans la chambre de réglage en avance (24),
    - une deuxième conduite de fluide sous pression (26b) étant prévue, laquelle communique d'une part avec le deuxième raccord de travail (B) et débouche d'autre part dans la chambre de réglage en retard (25),
    - une troisième conduite de fluide sous pression (26p) étant prévue, laquelle communique d'une part avec le raccord d'amenée (P) et communique d'autre part avec une pompe de fluide sous pression (27),
    - deux quatrièmes conduites de fluide sous pression (26v) étant prévues, lesquelles débouchent d'une part dans l'accumulateur de volume (31) et communiquent d'autre part avec l'un respectif des raccords d'accumulateur de volume (V1, V2),
    - une cinquième conduite de fluide sous pression (26t) étant prévue, laquelle communique d'une part avec le raccord de sortie (T) et d'autre part avec un réservoir de fluide sous pression (28).
    - une connexion entre le raccord d'amenée (P) et le premier ou le deuxième raccord de travail (A, B), et une connexion entre l'un des raccords d'accumulateur de volume (V1, V2) et l'autre raccord de travail (A, B) et une connexion entre l'autre raccord d'accumulateur de volume (V1, V2) et le raccord de sortie (T) pouvant être établies au moyen de la soupape de commande (13) .
EP10745609.7A 2009-09-18 2010-08-23 Dispositif de dephasage d'ouverture de soupapes pour moteur a combustion interne Active EP2478189B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009042202A DE102009042202A1 (de) 2009-09-18 2009-09-18 Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
PCT/EP2010/062212 WO2011032805A1 (fr) 2009-09-18 2010-08-23 Dispositif pour le réglage variable des temps de commande de soupapes d'échange de gaz d'un moteur à combustion interne

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EP2478189A1 EP2478189A1 (fr) 2012-07-25
EP2478189B1 true EP2478189B1 (fr) 2013-11-06

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US (1) US8763574B2 (fr)
EP (1) EP2478189B1 (fr)
JP (1) JP5579271B2 (fr)
KR (1) KR101632097B1 (fr)
CN (1) CN102549241B (fr)
BR (1) BR112012005958A2 (fr)
DE (1) DE102009042202A1 (fr)
IN (1) IN2012DN00553A (fr)
RU (1) RU2012115466A (fr)
WO (1) WO2011032805A1 (fr)

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DE102017102810A1 (de) 2017-02-13 2018-08-16 Schaeffler Technologies AG & Co. KG Hydraulischer Nockenwellenversteller

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DE102012025791B3 (de) * 2012-02-02 2021-03-25 Schaeffler Technologies AG & Co. KG Anordnung eines Volumenspeichers im Nockenwellenversteller
DE102012201558B4 (de) 2012-02-02 2017-09-07 Schaeffler Technologies AG & Co. KG Gestaltung eines Tankanschlusses in einem Nockenwellenversteller mit Volumenspeicher
DE102012201550B4 (de) * 2012-02-02 2015-05-21 Schaeffler Technologies AG & Co. KG Nockenwellenversteller mit einem Rückschlagventil
DE102012201560B4 (de) 2012-02-02 2019-02-21 Schaeffler Technologies AG & Co. KG Volumenspeicherausführung in einer Nockenwellenverstellvorrichtung
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US20120111295A1 (en) 2012-05-10
DE102009042202A1 (de) 2011-04-14
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KR101632097B1 (ko) 2016-06-20
JP5579271B2 (ja) 2014-08-27
RU2012115466A (ru) 2013-10-27
IN2012DN00553A (fr) 2015-06-12
US8763574B2 (en) 2014-07-01
WO2011032805A1 (fr) 2011-03-24
CN102549241B (zh) 2014-06-11
JP2013505388A (ja) 2013-02-14
BR112012005958A2 (pt) 2020-01-14
EP2478189A1 (fr) 2012-07-25

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