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EP1888895B1 - Dispositif de reglage variable des temps de commande de soupapes d'echange des gaz d'un moteur a combustion interne - Google Patents

Dispositif de reglage variable des temps de commande de soupapes d'echange des gaz d'un moteur a combustion interne Download PDF

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Publication number
EP1888895B1
EP1888895B1 EP06791509A EP06791509A EP1888895B1 EP 1888895 B1 EP1888895 B1 EP 1888895B1 EP 06791509 A EP06791509 A EP 06791509A EP 06791509 A EP06791509 A EP 06791509A EP 1888895 B1 EP1888895 B1 EP 1888895B1
Authority
EP
European Patent Office
Prior art keywords
pressure medium
pressure
angle limiting
output element
supply
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
EP06791509A
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German (de)
English (en)
Other versions
EP1888895A1 (fr
Inventor
Lars PFÜTZENREUTER
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 Engineering GmbH
Original Assignee
AFT Atlas Fahrzeugtechnik GmbH
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Publication of EP1888895A1 publication Critical patent/EP1888895A1/fr
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Publication of EP1888895B1 publication Critical patent/EP1888895B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • 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
    • 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
    • F01L1/34—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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34476—Restrict range locking means

Definitions

  • the invention relates to a device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine according to the preambles of claims 1 and 2.
  • camshafts are used to actuate the gas exchange valves.
  • Camshafts are mounted in the internal combustion engine such that cams attached to them abut cam followers, for example cup tappets, drag levers or rocker arms. If a camshaft is rotated, the cams roll on the cam followers, which in turn actuate the gas exchange valves. Due to the position and the shape of the cams thus both the opening duration and the opening amplitude but also the opening and closing times of the gas exchange valves are set.
  • valve lift and valve opening duration should be variable, up to the complete shutdown of individual cylinders.
  • concepts such as switchable cam followers or electrohydraulic or electric valve actuations are provided.
  • it has been found to be advantageous to be able to influence the opening and closing times of the gas exchange valves during operation of the internal combustion engine.
  • it is particularly desirable to be able to influence the opening or closing times of the inlet or outlet valves separately, in order, for example, to adjust a defined valve overlap in a targeted manner.
  • the attitude the opening and closing times of the gas exchange valves in dependence on the current map range of the engine for example, the current speed or the current load
  • the specific fuel consumption can be lowered, the exhaust behavior positively influenced, the engine efficiency, the maximum torque and the maximum power can be increased.
  • the described variability of the valve timing is achieved by a relative change in the phase angle of the camshaft to the crankshaft.
  • the camshaft is usually via a chain, belt, gear drive or equivalent drive concepts in drive connection with the crankshaft.
  • a device for changing the timing of an internal combustion engine hereinafter also called camshaft adjuster, mounted, which transmits the torque from the crankshaft to the camshaft.
  • this device is designed such that during operation of the internal combustion engine, the phase angle between the crankshaft and camshaft securely held and, if desired, the camshaft can be rotated in a certain angular range relative to the crankshaft.
  • each with a camshaft for the intake and the exhaust valves these can each be equipped with a camshaft adjuster.
  • the opening and closing times of the intake and exhaust valves can be shifted in time relative to one another and the valve overlaps can be adjusted in a targeted manner.
  • the seat of modern camshaft adjuster is usually located at the drive end of the camshaft.
  • the camshaft adjuster can also be arranged on an intermediate shaft, a non-rotating component or the crankshaft. It consists of a driven by the crankshaft, a fixed phase relation to this holding drive wheel, a driving connection with the camshaft standing output part and a torque transmitting from the drive wheel to the output part adjusting mechanism.
  • the drive wheel may be designed as a chain, belt or gear in the case of a not arranged on the crankshaft camshaft adjuster and is driven by means of a chain, a belt or a gear drive from the crankshaft.
  • the adjustment mechanism can be operated electrically (by means of a driven three-shaft transmission), hydraulically or pneumatically.
  • hydraulically adjustable camshaft adjusters Two preferred embodiments of hydraulically adjustable camshaft adjusters are the so-called Axialkolbenversteller and Rotationskolbenversteller.
  • the drive wheel is connected to a piston and this with the output part via helical gears in combination.
  • the piston separates a cavity formed by the driven part and the drive wheel into two pressure chambers arranged axially relative to one another. If now one pressure chamber is acted upon by pressure medium while the other pressure chamber is connected to a tank, the piston shifts in the axial direction. The axial displacement of the piston is translated by the helical gears in a relative rotation of the drive wheel to the output part and thus the camshaft to the crankshaft.
  • a second embodiment of hydraulic phaser are the so-called Rotationskolbenversteller.
  • the drive wheel is rotatably connected to a stator.
  • the stator and a rotor are arranged concentrically to each other, wherein the rotor force, form or materially connected, for example by means of a press fit, a screw or weld connection with a camshaft, an extension of the camshaft or an intermediate shaft.
  • a plurality of circumferentially spaced cavities are formed which extend radially outward from the rotor.
  • the cavities are limited pressure-tight in the axial direction by side cover.
  • a wing connected to the rotor extends, dividing each cavity into two pressure chambers.
  • camshaft adjuster sensors detect the characteristics of the engine, such as the load condition and the speed. These data are supplied to an electronic control unit, which controls the supply and the outflow of pressure medium to the various pressure chambers after comparing the data with a characteristic field of the internal combustion engine.
  • one of the two counteracting pressure chambers of one cavity is connected in hydraulic camshaft adjusters with a pressure medium pump and the other with the tank.
  • the inlet of pressure medium to a chamber in conjunction with the flow of pressure medium from the other chamber moves the pressure chambers separating piston in the axial direction, whereby in Axialkolbenverstellern on the helical gears, the camshaft is rotated relative to the crankshaft.
  • Rotationskolbenverstellern is caused by the pressurization of a chamber and the pressure relief of the other chamber, a displacement of the wing and thus directly a rotation of the camshaft to the crankshaft.
  • both pressure chambers are either connected to the pressure medium pump or separated from both the pressure medium pump and the tank.
  • the control of the pressure medium flows to and from the pressure chambers by means of a control valve, usually a 4/3-proportional valve.
  • a valve housing is provided with one connection each for the pressure chambers (working connection), a connection to the pressure medium pump and at least one connection to a tank.
  • an axially displaceable control piston is arranged within the substantially hollow cylindrical valve housing.
  • the control piston can be brought by means of an electromagnetic actuator against the spring force of a spring element axially in any position between two defined end positions.
  • the control piston is further provided with annular grooves and control edges, whereby the individual pressure chambers can be optionally connected to the pressure medium pump or the tank.
  • a position of the control piston may be provided, in which the pressure medium chambers are separated from both the pressure medium pump and the pressure medium tank.
  • camshaft adjuster need a certain period of time until the phase position can be kept safe.
  • this is due to the fact that during the stoppage of the engine pressure medium exits the pressure chambers and thus the hydraulic clamping of the piston or the wing is not guaranteed at start of the internal combustion engine.
  • the oil pump driven by the crankshaft of the internal combustion engine supplies the camshaft adjuster sufficiently with pressure medium, the phase angle of the camshaft to the crankshaft is not fixed. This results in worse starting and running properties of the internal combustion engine.
  • the piston or wings within the pressure chambers due to the reaction moments of the camshaft are adjusted unrestrained, whereby they beat against limitations in the device, causing noise and wear is caused.
  • rotational angle limiting devices are provided which mechanically couple the output element to the drive element and thus prevent a rotation of both components relative to each other.
  • Such rotation angle limiting devices are realized by a locking piston, which is arranged in a formed on the output member or the drive member recording.
  • a spring is provided which urges the locking piston in the direction of the other component.
  • a link is provided on the other component, in which the Verrieglungskolben is urged when the predetermined Verrieglungsphase is reached. It may be advantageous to lock the output element to the drive element in one of the two extreme phase positions or in an intermediate phase position.
  • one or more locking devices provided, wherein the scenes can be formed in the second case as a blind hole or as circumferentially extending groove.
  • a drive element which is in drive connection with the camshaft, is rotatably mounted on a driven element rotatably connected to a camshaft.
  • the drive element is formed with recesses open to the output element.
  • side covers are provided, which limit the device.
  • the recesses are pressure-sealed by the drive element, the output element and the side cover and thus form pressure chambers.
  • axial grooves are introduced, in which wings are arranged which extend into the recesses. The wings are designed such that they divide the pressure chambers into two oppositely acting pressure chambers.
  • a locking piston is arranged, which is acted upon by means of a spring means with a force in the direction of the output element.
  • a blind hole is formed on an outer lateral surface output element, which faces the locking piston.
  • the blind hole is arranged and designed such that in a defined phase position of the output element to the drive element of the locking piston engages in the blind hole when it is not acted upon by pressure medium.
  • the rotor is thus locked relative to the stator whereby a relative rotation is prevented.
  • Via a control line pressure medium is passed to the blind hole, whereby an end face of the locking piston is subjected to pressure medium.
  • the piston is pressed into the receptacle and allows an adjustment of the rotor relative to the stator in one direction.
  • the control line is designed separately from a device for supplying pressure medium, which pressurizes the pressure chambers with the pressure chambers. Furthermore, a switching valve is provided which controls the supply and removal of pressure medium to the control line. This switching valve is adjusted via a microprocessor and an electromagnetic actuator from a state in which pressure fluid is discharged from the blind hole in a state in which the blind hole is subjected to pressure medium.
  • the disadvantage here is the high cost, which arises because the separate control line is actuated by means of an electromagnetic actuator. In order to release the locking of the output element to the drive element only when the device is sufficiently filled with pressure medium, this state must be detected, or wait a certain period of time after the start of the internal combustion engine until the switching valve is actuated.
  • sensors In the first case, sensors must be provided which must be monitored by the ECU of the internal combustion engine, which leads to increased costs and increased control effort.
  • the lock can be released before the desired filling state of the device is reached, whereby disadvantages mentioned above occur.
  • the invention is therefore based on the object to avoid these disadvantages and thus to propose a device for variable adjustment of the timing of gas exchange valves of an internal combustion engine, in which the locking of the output element to the drive element process reliable only after reaching a desired filling state of the device, this without costly additional Components, such as electromagnetic actuators, and should be done with the least possible control effort.
  • a device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine with a camshaft driving output element, driven by a crankshaft drive element a hydraulic actuator with at least two mutually acting pressure chambers and a device for supplying pressure medium for supplying and discharging pressure medium to or from the pressure chambers
  • the drive element is rotatably arranged to the output element and a phase angle between the two components by supplying and discharging pressure medium to or from the At least one rotational angle limiting device, which does not limit the phase position of the output element to the drive element in an unlocked state and limited in a locked state to a defined angular range or a defined angle, wherein the rotational angle limiting device by supplying pressure medium from the locked is transferred to the unlocked state
  • a control line for supplying and discharging pressure medium to or from the or the rotation angle limiting devices wherein the control line does not communicate with the means for supplying pressure medium niziert and a switching valve, which allows in an
  • On fault-prone power supply to the switching valve can also be dispensed with, as well as additional necessary control software in the engine control unit (ECU). Furthermore, the actuation of the switching valve process reliable means of pressure only at a time, since the device is already sufficiently pressurized with pressure medium. Furthermore, no electrical energy is needed to actuate and maintain the switching position of the switching valve.
  • Another advantage results from the fact that the rotation angle limiting device is automatically transferred to a locked state when the system pressure supplied by a pressure medium pump falls below a value at which the device is no longer sufficiently pressurized with pressure medium and therefore the phase position of the output element to the drive element not can be kept more reliable. This can occur, for example, when the internal combustion engine is operated at idle and thus the driven by the crankshaft pressure medium pump can not build up sufficient pressure.
  • the means for supplying pressure medium comprises a control valve, a first and a second pressure medium line, wherein the control valve communicates with a pressure medium pump, the pressure medium lines to the control valve and one of the pressure chambers and the hydraulic actuating mechanism with one of the pressure medium lines.
  • a device for variably setting the timing of gas exchange valves of an internal combustion engine with a drive element driving a camshaft, driven by a crankshaft drive element wherein the two components are rotatably mounted to each other and define at least one pressure chamber, wherein in each pressure chamber a on one of the components arranged wings which divides the pressure chamber into two oppositely acting pressure chambers, two Pressure medium lines, each pressure medium line communicates with a pressure chamber or a group of pressure chambers and wherein a phase position of the output element to the drive element can be selectively held or adjusted by supplying and discharging pressure medium to or from the pressure chambers, at least one rotation angle limiting device, the phase angle of the Output element to the drive element in an unlocked state is not limited and limited in a locked state to a defined angular range or a defined angle, wherein the rotation angle limiting device is transferred and maintained by supplying pressure medium in the unlocked state, a control line and a switching valve, wherein the control line with the switching valve
  • the switching valve has a working connection, an inlet connection and a drain connection, wherein the working connection communicates with the control line and the hydraulic actuating mechanism of the switching valve, the inlet connection with a pressure medium pump and the outlet connection with a tank. This ensures that the rotation angle limiting device is held in the unlocked state, even when the pressure chambers are acted upon by the pressure medium not communicating with the actuating mechanism pressure medium line.
  • the rotational angle limiting device is formed with an output element or on the drive element formed in the first receptacle, a first piston and a first spring, wherein the first spring urging the first piston in the direction of the component on which the first link is formed.
  • the first link is designed as a blind hole or step slot with blind hole, wherein the opening of the blind hole is adapted to the dimensions of the locking piston.
  • a second rotation angle limiting device may be provided which is formed with a formed on the output element or on the drive element second receptacle and formed on the other component second gate, wherein in the second receptacle, a second piston and a second spring is received, wherein the second spring the second piston in the direction of the component urges on which the second link is formed.
  • the first link may be formed as a groove extending in the circumferential direction and the second link as a blind hole, the opening of which is adapted to the dimensions of the locking piston.
  • the first and the second link are each formed as a groove extending in the circumferential direction.
  • FIGS. 1 and 2 show a first embodiment of a device 1 for the variable adjustment of the timing of gas exchange valves of an internal combustion engine.
  • An adjusting device 1a essentially consists of a drive element 2 and an output element 3 arranged concentrically therewith.
  • a drive wheel 4 is non-rotatably connected to the drive element 2 and, in the illustrated embodiment, designed as a sprocket. Also conceivable are embodiments of the drive wheel 4 as a belt or gear.
  • the drive element 2 is rotatably mounted on the driven element 3, wherein on the inner circumferential surface of the drive element 2 in the illustrated Embodiment five circumferentially spaced recesses 5 are provided.
  • the recesses 5 are bounded in the radial direction by the drive element 2 and the driven element 3, in the circumferential direction by two side walls 6 of the drive element 2 and in the axial direction by a first and a second side cover 7, 8. Each of the recesses 5 is sealed pressure-tight manner in this way.
  • the first and the second side cover 7, 8 are rotatably connected to the drive element 2 by means of connecting elements 9, for example screws.
  • each vane groove 10 On the outer circumferential surface of the output element 3 axially extending vane grooves 10 are formed, wherein in each vane groove 10, a radially extending wing 11 is arranged. In each recess 5, a wing 11 extends, wherein the wings 11 in the radial direction on the drive element 2 and in the axial direction of the side covers 7, 8 abut. Each wing 11 divides a recess 5 in two oppositely acting pressure chambers 12, 13. In order to ensure a pressure-tight abutment of the wings 11 on the drive element 2, 11 leaf spring elements 15 are mounted between the groove bases 14 of the wing grooves 10 and the wings, which the wing 11 in Apply a force to the radial direction.
  • first and second pressure medium lines 16, 17, the first and second pressure chambers 12, 13 are connected via a control valve, not shown, with a likewise not shown pressure medium pump or a tank, also not shown.
  • an actuator 18 is formed, which allows a relative rotation of the drive element 2 with respect to the output element 3. It is provided that either all the first pressure chambers 12 are connected to the pressure medium pump and all second pressure chambers 13 to the tank or the exact opposite configuration. If the first pressure chambers 12 are connected to the pressure medium pump and the second pressure chambers 13 are connected to the tank, then the first pressure chambers 12 expand at the expense of the second pressure chambers 13. This results in a displacement of the wings 11 in the circumferential direction, in the direction indicated by the first arrow 21.
  • both pressure medium lines 16, 17 are separated from the tank and from the pressure medium pump. As a result, the current phase position is maintained.
  • a defined supply of pressure medium to both pressure chambers 12, 13 are allowed to compensate for leakage losses occurring.
  • the drive element 2 is driven by the crankshaft by means of a chain drive (not shown) acting on its drive wheel 4. Also conceivable is the drive of the drive element 2 by means of a belt or gear drive.
  • the output element 3 is non-positively, positively or materially, for example by means of press fit or by a screw connection by means of a central screw, connected to a camshaft, not shown. From the relative rotation of the output element 3 relative to the drive element 2, as a result of the supply and discharge of pressure medium to and from the pressure chambers 12, 13, resulting in a phase shift between the camshaft and crankshaft. By selective introduction and discharge of pressure medium into the pressure chambers 12, 13, the control times of the gas exchange valves of the internal combustion engine can thus be selectively varied.
  • Each of the pressure medium lines 16, 17 communicates via a, in a central bore 22 of the driven element 3, not shown, the pressure medium distributor, each having a pressure medium channel 16a, 17a, each of the pressure medium channels 16a, 17a in one of the pressure chambers 12, 13 opens.
  • Another possibility is to arrange a central valve within the central bore 22, via which the pressure medium channels 16a, 17a and thus the pressure chambers 12, 13 can be selectively connected to a pressure medium pump or a tank.
  • the substantially radially extending side walls 6 of the recesses 5 are provided with formations 23 which extend in the circumferential direction in the recesses 5.
  • the formations 23 serve as a stop for the wings 11 and ensure that the pressure chambers 12, 13 with pressure medium can be supplied, even if the output element 3 occupies one of its two extreme positions relative to the drive element 2, in which the wings 11 abut against one of the side walls 6.
  • the output element 3 is due to the alternating and drag moments, which exerts the camshaft on this uncontrolled relative to the drive element 2 moves.
  • the drag torques of the camshaft urge the driven element 3 relative to the drive element 2 in a circumferential direction, which is opposite to the direction of rotation of the drive element 2, until they abut against the side walls 6.
  • the alternating torques exerted by the camshaft on the output element 3 to a swinging oscillation of the driven element 3 and thus the wing 11 in the recesses 5, until at least one of the pressure chambers 12, 13 is completely filled with pressure medium.
  • Each rotation angle limiting device 24 consists of a cup-shaped piston 26, which is arranged in a receptacle 25 of the output element 3.
  • the piston 26 is acted upon by a spring 27 in the axial direction with a force.
  • the spring 27 is supported in the axial direction on the one side on a venting element 28 and is disposed with its axial end facing away from inside the pot-shaped executed piston 26.
  • a link 29 is formed per rotational angle limiting device 24 such that the output element 3 can be locked relative to the drive element 2 in a position corresponding to an optimum position for starting and / or idling the internal combustion engine.
  • the piston 26 are urged in insufficient supply of pressure medium of the device 1 by means of the springs 27 in the scenes 29.
  • means are provided to the piston 26 at sufficient Supply the device 1 with pressure medium in the receptacles 25 push back and thus cancel the lock.
  • it is provided to act on the scenes 29 via pressure medium channels and recesses 30, not shown, with pressure medium.
  • pressure medium urges the piston 26 against the force of the springs 27 in the receptacles 25, whereby the fixed phase relationship between the output element 3 and drive element 2 is repealed.
  • the pressure medium is passed through a control line 19 and not shown pressure medium channels in the scenes 29.
  • FIG. 2a shows an alternative embodiment of a device 1. This is substantially identical to that in FIG. 2 shown device 1 which is why the same components have been provided with the same reference numerals. Unlike the in FIG. 2 illustrated embodiment, this is provided with only one rotational angle limiting device 24.
  • FIGS. 3 to 5 show schematic representations of a device 1 with differently designed rotation angle limiting devices 24.
  • Each of the devices 1 consists of a drive element 2, on which a pressure chamber 31 is formed. Furthermore, one or more scenes 29 are formed on the drive element 2.
  • a wing 11 of the output element extends 3.
  • 3 receptacles 25 are formed on the driven element, in each of which a piston 26 is arranged, which is urged by means of a respective spring 27 in the direction of the drive element 2.
  • a device for pressure medium supply 32 is provided, via which selectively pressure medium to the pressure chambers 12, 13 can be added or discharged.
  • the device for pressure medium supply 32 consists of a control valve 33, first and second pressure medium lines 16, 17 and pressure medium channels 16a, 17a.
  • the control valve 33 is designed as a 4/3-way valve, which can be transferred via an actuator 34 in three control positions.
  • the control valve 33 is formed with two working ports A, B, an inlet port P and a drain port T.
  • the inlet connection P communicates with a pressure medium pump 35, the outlet connection T with a tank 36, the working port A via the first pressure medium line 16 and the first pressure medium channel 16a with the first pressure chamber 12 and the second working port B via the second pressure medium line 17 and the second pressure medium channel 17a with the second pressure chamber 13.
  • FIG. 3 a first embodiment of a device 1 is shown, in which only one rotational angle limiting device 24 is provided.
  • the phase position between the output element 3 and the drive element 2 can be fixed in one of the extreme positions or a middle position.
  • the gate 29 is designed as a blind hole 20, wherein the opening cross section of the blind hole 20 is adapted to the cross section of the piston 26.
  • the rotation angle limiting device 24 In order to allow a change in the phase position between the output element 3 and the drive element 2, the rotation angle limiting device 24 must be transferred to an unlocked state in which the piston 26 is pushed back as far into the receptacle 25 against the force of the spring 27, that he no longer in the Gate 29 engages.
  • the control line 19 is provided, via which the slide 29 pressure medium can be supplied.
  • a switching valve 38 is provided, which is arranged between the pressure medium pump 35 and the control line 19.
  • the switching valve 38 controls the flow of pressure medium from the pressure medium pump 35 to the control line 19 or from the control line 19 to the tank 36.
  • the switching valve 38 is formed in the illustrated embodiment as a 3/2-way valve.
  • a working port A1 an inlet port P1 and a discharge port T1 are formed on the switching valve 38.
  • the working port A1 communicates with the control line 19, the drain port T1 with the tank 36, and the inflow port P1 with the pressure medium pump 35.
  • a first control position of the switching valve 38 In a first control position of the switching valve 38, the in FIG. 3 is taken, the working port A1 is connected to the drain port T1. In this position, the gate 29 is kept pressure-free, whereby the piston 26 is held in the gate 29. The rotation angle limiting device 24 is in a locked state.
  • the working port A1 In a second control position of the switching valve 38, the working port A1 is connected to the inlet port P1, whereby the gate 29 pressure medium supplied and thus the piston 26 is urged out of the gate 29. In this case, the rotation angle limiting device 24 changes from the locked to the unlocked state, and the phase angle of the device 1 can be changed.
  • a check valve 37 is disposed between the pressure medium pump 35 and the control valve 33, which prevents pressure spikes, which arise within the device 1 by the reaction moments of the camshaft, to the pressure medium pump 35 propagate.
  • the inlet port P1 of the switching valve 38 is fed via a pressure medium line from the pressure medium pump 35, wherein this branch is upstream relative to the check valve 37. Unlocking the rotation angle limiting device 24 thus takes place by means of system pressure. That is, the hydraulic system for unlocking the rotation angle limiting device 24 does not communicate with the means for pressure medium supply 32 of the device 1. This has the advantage that the pressure peaks are not fed into the system for unlocking the rotation angle limiting device 24.
  • the switching valve 38 is provided with a hydraulic actuating mechanism 39, via which the switching valve 38 can be adjusted between the two control positions.
  • the actuating mechanism 39 communicates with one of the pressure medium lines 16, 17 such that the switching valve 38 is transferred to the second control position, when in this pressure medium line 16, 17, the pressure exceeds a certain value.
  • the actuating mechanism 39 communicates with the first pressure medium line 16, which in turn communicates with the working port A of the control valve 33.
  • the control valve 33 is in the position shown.
  • the pressure medium pump 35 is connected via the second pressure medium line 17 to the second pressure chamber 13. This has the consequence that the second pressure chamber 13 is filled with pressure medium.
  • control valve 33 switches to the third control position, whereby pressure medium via the first pressure medium line 16 of the first pressure chamber 12 is supplied.
  • hydraulic actuating mechanism 39 is acted upon with pressure medium, whereby the switching valve 38 is transferred to the second control position.
  • pressure fluid passes from the pressure medium pump 35 to the gate 29, with the result that the rotation angle limiting device 24 is transferred to the unlocked state.
  • both pressure chambers 12, 13 are filled with pressure medium, the device 1 is in a defined Condition and an uncontrolled oscillation of the output element 3 to the drive element 2 is prevented.
  • the working port A1 of the switching valve 38 is also connected to the operating mechanism 39. If the actuating mechanism 39 is activated for the first time via the first pressure medium line 16, both the slide 29 and the actuating mechanism 39 are supplied with pressure medium via the switching valve 38. This ensures that the switching valve 38 is kept until the breakdown of the pressure built up by the pressure medium pump 35 or until the system pressure drops below a certain value in the second control position. This is therefore a self-holding mechanism of the switching valve 38. If the second pressure medium line 17 is now connected via the control valve 33 with the pressure medium pump 35 and thus the first pressure medium line 16 to the tank 36, the switching valve 38 by this self-holding mechanism in the second control position held and thus continues to apply the gate 29 with pressure medium. This reliably prevents unintentional adjustment of the rotation angle limiting device 24.
  • the output element 3 is held relative to the drive element 2 in an optimum phase position for this operating state. If the system pressure again rises above the predetermined value, then the rotational angle limiting device 24 is automatically unlocked again and the phase position between the output element 3 and the drive element 2 can be set variably in accordance with a stored characteristic map.
  • FIGS. 4 and 5 show two further devices 1, which differ from the in FIG. 3 distinguished device 1 characterized in that two rotational angle limiting devices 24 are provided. These embodiments are particularly suitable for locking the output element 3 to the drive element 2 in a phase position between the two possible extreme positions.
  • Both scenes 29 of the rotation angle limiting devices 24 are designed as grooves.
  • the grooves are formed and arranged such that a rotational angle limiting device 24 limits the phase position between a maximum retardation of the driven element 3 to the drive element 2 and a center position, while the second rotational angle limiting device 24, the phase angle of the output element 3 to the drive element 2 between the center position and a maximum advance limited.
  • both rotational angle limiting devices 24 in the locked Condition the output member 3 is held relative to the drive member 2 in the center position.
  • one of the scenes 29 is designed as a blind hole 20 and the second link 29 as a groove.
  • the rotational angle limiting device 24 with the groove 29 designed as a guide 29 limits the phase angle of the driven element 3 to the drive element 2 to an angular range extending between a center position and either a maximum early position or a maximum late position.
  • the blind hole 20 is arranged such that this rotational angle limiting device 24 can be transferred only in the middle position in the locked state.
  • the pistons 26 may be arranged in the drive element 2 and the scenes 29 in the output element 3.
  • a radial locking direction is conceivable.
  • the in FIG. 3 illustrated embodiment with a rotation angle limiting device 24 is in a locked state, when the wing 11 abuts against one of the side walls 6 or when it assumes a defined position between the side walls 6.
  • various embodiments of the control valve 33 are conceivable.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

Dispositif de réglage variable des temps de commande de soupapes d'échange des gaz d'un moteur à combustion interne, qui comporte un mécanisme de commande hydraulique (18) pourvu de deux chambres (12, 13) à fluide sous pression à action contraire et d'un dispositif d'alimentation (32) en fluide sous pression destiné à introduire du fluide sous pression dans les chambres (12, 13) et à évacuer du fluide sous pression desdites chambres. Ledit dispositif (1) comporte en outre au moins un dispositif de limitation de l'ange de rotation (24) qui ne limite pas la position de phase de l'élément de sortie (3) par rapport à l'élément d'entrée (2) dans un état de non verrouillage et qui limite ladite position de phase dans un état de verrouillage à une zone angulaire définie ou à un angle défini, le dispositif de limitation de l'angle de rotation (24) passant de l'état verrouillé à l'état non verrouillé par l'apport de fluide sous pression. Une conduite de commande (19) est destinée à l'introduction de fluide sous pression dans le(s) dispositifs de limitation d'angle de rotation (24) et à l'évacuation de fluide sous pression dudit (desdits) dispositif(s), ladite conduite de commande (19) ne communiquant pas avec le dispositif d'alimentation (32) en fluide sous pression. Une soupape de commande (38) régule l'introduction de fluide sous pression dans la conduite de commande (19) et l'évacuation de fluide sous pression de ladite conduite (19). La soupape de commande (38) possède un mécanisme d'actionnement hydraulique (39) qui est soumis à l'action de fluide sous pression par le dispositif d'alimentation (32) en fluide sous pression.

Claims (9)

  1. Dispositif (1) de réglage variable des temps de commande de soupapes d'échange de gaz d'un moteur à combustion interne, comprenant
    - un élément de sortie (3) entraînant un arbre à cames,
    - un élément d'entraînement (2) entraîné par un vilebrequin,
    - un entraînement de commande hydraulique (18) avec au moins deux chambres de pression (12, 13) interagissant l'une avec l'autre et
    - un système d'alimentation en fluide sous pression (32) pour acheminer et évacuer du fluide sous pression à et depuis les chambres de pression (12, 13),
    - l'élément d'entraînement (2) étant disposé de manière à pouvoir tourner par rapport à l'élément de sortie (3), et une position de phase entre les deux composants pouvant être maintenue ou réglée au choix en acheminant ou en évacuant du fluide sous pression vers ou depuis les chambres de pression (12, 13),
    - au moins un dispositif de limitation de l'angle de rotation (24), qui ne limite pas la position de phase de l'élément de sortie (3) par rapport à l'élément d'entraînement (2) dans un état déverrouillé et qui la limite à une plage angulaire définie ou à un angle défini dans un état verrouillé,
    - le dispositif de limitation de l'angle de rotation (24) étant transféré de l'état verrouillé dans l'état déverrouillé par alimentation en fluide sous pression,
    - une conduite de commande (19) pour acheminer et évacuer du fluide sous pression à ou depuis le ou les dispositifs de limitation de l'angle de rotation (24), la conduite de commande (19) ne communiquant pas avec le système d'alimentation en fluide sous pression (32), et
    - une soupape de commutation (38), qui permet, dans un état actionné, l'alimentation en fluide sous pression vers la conduite de commande (19), et dans un état non actionné, l'évacuation du fluide sous pression depuis la conduite de commande (19), caractérisé en ce que
    - la soupape de commutation (38) présente un mécanisme d'actionnement hydraulique (39),
    - qui est sollicité en fluide sous pression par le système d'alimentation en fluide sous pression (32).
  2. Dispositif (1) de réglage variable des temps de commande de soupapes d'échange de gaz d'un moteur à combustion interne, comprenant
    - un élément de sortie (3) entraînant un arbre à cames,
    - un élément d'entraînement (2) entraîné par un vilebrequin,
    - les deux composants étant montés de manière à pouvoir tourner l'un par rapport à l'autre, et
    - définissant au moins une chambre de pression (31), une ailette (11) disposée sur l'un des composants s'étendant dans chaque chambre de pression, et divisant la chambre de pression (31) en deux chambres de pression (12, 13) interagissant l'une avec l'autre,
    - deux conduites de fluide sous pression (16, 17), chaque conduite de fluide sous pression (16, 17) communiquant avec une chambre de pression (12, 13) ou un groupe de chambres de pression (12, 13), et une position de phase de l'élément de sortie (3) par rapport à l'élément d'entraînement (2) pouvant être maintenue ou réglée au choix en acheminant ou en évacuant du fluide sous pression vers ou depuis les chambres de pression (12, 13),
    - au moins un dispositif de limitation de l'angle de rotation (24), qui ne limite pas la position de phase de l'élément de sortie (3) par rapport à l'élément d'entraînement (2) dans un état déverrouillé et qui la limite à une plage angulaire définie ou à un angle défini dans un état verrouillé, le dispositif de limitation de l'angle de rotation (24) étant transféré dans l'état déverrouillé et y étant maintenu par apport de fluide sous pression,
    - une conduite de commande (19) et une soupape de commutation (38),
    - la conduite de commande (19) communiquant avec la soupape de commutation (38) et le ou les dispositifs de limitation de l'angle de rotation (24) et
    - la soupape de commutation (38) permettant, dans un état actionné, l'alimentation en fluide sous pression vers la conduite de commande (19) et dans un état non actionné, l'évacuation du fluide sous pression depuis la conduite de commande (19), caractérisé en ce que
    - la soupape de commutation (38) présente un mécanisme d'actionnement hydraulique (39) et
    - le mécanisme d'actionnement hydraulique (39) communique avec au moins l'une des conduites de fluide sous pression (16, 17).
  3. Dispositif (1) selon la revendication 1, caractérisé en ce que le système d'alimentation en fluide sous pression (32) présente une soupape de commande (33), une première et une deuxième conduite de fluide sous pression (16, 17), la soupape de commande (33) communiquant avec une pompe de fluide sous pression (35), les conduites de fluide sous pression (16, 17) communiquant avec la soupape de commande (33) et à chaque fois avec l'une des chambres de pression (12, 13) et le mécanisme d'actionnement hydraulique (38) communiquant avec l'une des conduites de fluide sous pression (16, 17).
  4. Dispositif (1) selon l'une quelconque des revendications 1 ou 2, caractérisé en ce que la soupape de commutation (38) présente un raccord de travail (A1), un raccord d'entrée (P1) et un raccord de sortie (T1), le raccord de travail (A1) communiquant avec la conduite de commande (19) et le mécanisme d'actionnement hydraulique (39) de la soupape de commutation (38), le raccord d'entrée (P1) communiquant avec une pompe de fluide sous pression (35) et le raccord de sortie (T1) communiquant avec un réservoir (36).
  5. Dispositif (1) selon l'une quelconque des revendications 1 ou 2, caractérisé en ce que le dispositif de limitation de l'angle de rotation (24) est réalisé avec un premier logement (25) réalisé sur l'élément de sortie (3) ou sur l'élément d'entraînement (2) et avec une première coulisse (29) réalisée sur l'autre composant, un premier piston (26) et un premier ressort (27) étant reçus dans le premier logement (25), le premier ressort (27) poussant le premier piston (26) dans la direction du composant sur lequel est réalisée la première coulisse (29).
  6. Dispositif (1) selon la revendication 5,
    caractérisé en ce qu'il est prévu un deuxième dispositif de limitation de l'angle de rotation (24), qui est réalisé avec un deuxième logement (25) réalisé sur l'élément de sortie (3) ou sur l'élément d'entraînement (2) et avec une deuxième coulisse (29) réalisée sur l'autre composant, un deuxième piston (26) et un deuxième ressort (27) étant reçus dans le deuxième logement (25), le deuxième ressort (27) poussant le deuxième piston (26) dans la direction du composant sur lequel est réalisée la deuxième coulisse (29).
  7. Dispositif (1) selon la revendication 7, caractérisé en ce que la première coulisse (29) est réalisée sous forme de trou borgne (20), dont l'ouverture est adaptée aux dimensions du piston (26).
  8. Dispositif (1) selon la revendication 8, caractérisé en ce que la première coulisse (29) est réalisée sous la forme d'une rainure s'étendant dans la direction périphérique et la deuxième coulisse (29) est réalisée sous la forme d'un trou borgne (20), dont l'ouverture est adaptée aux dimensions du piston (26).
  9. Dispositif (1) selon la revendication 8, caractérisé en ce que la première et la deuxième coulisse (29) sont réalisées chacune sous forme de rainure s'étendant dans la direction périphérique.
EP06791509A 2005-05-20 2006-05-10 Dispositif de reglage variable des temps de commande de soupapes d'echange des gaz d'un moteur a combustion interne Active EP1888895B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005023204A DE102005023204A1 (de) 2005-05-20 2005-05-20 Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
PCT/EP2006/004381 WO2006136239A1 (fr) 2005-05-20 2006-05-10 Dispositif de reglage variable des temps de commande de soupapes d'echange des gaz d'un moteur a combustion interne

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EP1888895A1 EP1888895A1 (fr) 2008-02-20
EP1888895B1 true EP1888895B1 (fr) 2008-10-29

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US (1) US7578275B2 (fr)
EP (1) EP1888895B1 (fr)
KR (1) KR101242882B1 (fr)
DE (2) DE102005023204A1 (fr)
WO (1) WO2006136239A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102007004197A1 (de) * 2007-01-27 2008-07-31 Schaeffler Kg System zur Verstellung des Stellwinkels eines Nockenwellenverstellers
DE102007007072A1 (de) * 2007-02-13 2008-08-14 Schaeffler Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102007007073B4 (de) * 2007-02-13 2020-10-01 Schaeffler Technologies AG & Co. KG Vorrichtung und Verfahren zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102012024955A1 (de) 2012-12-20 2014-06-26 Volkswagen Aktiengesellschaft Rotor-Stator-Einheit, Welle-in-Welle-System mit einer solchen Rotor-Stator-Einheit sowie Verfahren zur Montage einer Rotor-Stator-Einheit auf einem Welle-in-Welle-System
DE102013204928A1 (de) * 2013-03-20 2014-09-25 Schaeffler Technologies Gmbh & Co. Kg Hydraulischer Nockenwellenversteller mit zum Hydraulikmittelsteuern vorgesehenem Verriegelungspin zur Mittenverriegelung
CN112334637B (zh) * 2018-08-09 2022-09-09 舍弗勒技术股份两合公司 凸轮轴相位器用定子组件及凸轮轴相位器

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JP4202440B2 (ja) * 1997-02-06 2008-12-24 アイシン精機株式会社 弁開閉時期制御装置
JP3918971B2 (ja) 1998-04-27 2007-05-23 アイシン精機株式会社 弁開閉時期制御装置
JP2002122009A (ja) * 2000-08-09 2002-04-26 Mitsubishi Electric Corp バルブタイミング調整装置
US6766777B2 (en) 2002-06-14 2004-07-27 Borgwarner, Inc. Method to ensure robust operation of a pin lock in a vane style cam phaser
US6668778B1 (en) * 2002-09-13 2003-12-30 Borgwarner Inc. Using differential pressure control system for VCT lock
US6814038B2 (en) * 2002-09-19 2004-11-09 Borgwarner, Inc. Spool valve controlled VCT locking pin release mechanism
US6966288B2 (en) 2003-11-17 2005-11-22 Borgwarner Inc. Lock pin with centrifugally operated release valve

Also Published As

Publication number Publication date
EP1888895A1 (fr) 2008-02-20
KR20080016568A (ko) 2008-02-21
DE502006001948D1 (de) 2008-12-11
US20080184949A1 (en) 2008-08-07
KR101242882B1 (ko) 2013-03-12
US7578275B2 (en) 2009-08-25
DE102005023204A1 (de) 2006-11-30
WO2006136239A1 (fr) 2006-12-28

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