EP2220346B1 - Dispositif de réglage variable de la distribution des soupapes de renouvellement des gaz d'un moteur à combustion interne - Google Patents

Dispositif de réglage variable de la distribution des soupapes de renouvellement des gaz d'un moteur à combustion interne Download PDF

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Publication number
EP2220346B1
EP2220346B1 EP08856902A EP08856902A EP2220346B1 EP 2220346 B1 EP2220346 B1 EP 2220346B1 EP 08856902 A EP08856902 A EP 08856902A EP 08856902 A EP08856902 A EP 08856902A EP 2220346 B1 EP2220346 B1 EP 2220346B1
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EP
European Patent Office
Prior art keywords
control
connection
working
valve housing
control piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP08856902A
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German (de)
English (en)
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EP2220346A2 (fr
Inventor
Jens Hoppe
Andreas Röhr
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of EP2220346A2 publication Critical patent/EP2220346A2/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
    • 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

Definitions

  • the invention relates to a device for variably setting the timing of gas exchange valves of an internal combustion engine with a drive element, an output element, a rotation angle limiting device and a control valve, wherein at least two mutually acting pressure chambers are provided, wherein by pressurizing one of the pressure chambers while emptying the other pressure chamber a phase adjustment between the output element and the drive element, wherein the rotation angle limiting device prevents a change in the phase position in a locked state, wherein the rotation angle limiting device in a unlocked state allows a change in the phase position, wherein the rotation angle limiting device are transferred by the pressure medium from the locked to the unlocked state can, wherein the control valve has a valve housing and a control piston, wherein at The inlet housing with a pressure medium source, the outlet connection with a tank, the control connection with the rotation angle limiting device and the first and the second Working port is connected to each one of the pressure chambers and wherein the working ports are axially offset from one another and are not formed overlapping on the valve housing.
  • the device In modern internal combustion engines devices for variable adjustment of the timing of gas exchange valves are used to make the phase relation between the crankshaft and the camshaft in a defined angular range, between a maximum early and a maximum late position variable.
  • the device is 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.
  • the device comprises at least two rotors rotatable relative to one another, one rotor being in driving connection with the crankshaft and the other rotor being connected in a rotationally fixed manner to the camshaft.
  • the device comprises at least one pressure chamber, which is subdivided by means of a movable element into two counteracting pressure chambers.
  • the movable element is in operative connection with at least one of the rotors.
  • the pressure medium inflow to, or the pressure drain from the pressure chambers is controlled by means of a control unit, usually a hydraulic directional control valve (control valve).
  • the control unit is controlled by means of a regulator which, with the aid of sensors, determines the actual and desired position of the camshaft relative to the crankshaft (phase position) and compares them with one another. If a difference is detected between the two positions, a signal is sent to the control unit which adapts the pressure medium flows to the pressure chambers to this signal.
  • the pressure in the pressure medium circuit of the internal combustion engine must exceed a certain value.
  • the pressure medium is usually provided by the oil pump of the internal combustion engine and the pressure thus provided increases synchronously with the speed of the internal combustion engine, below a certain speed of the oil pressure is still too low to change the phase position of the rotors specifically or keep. This may for example be the case during the starting phase of the internal combustion engine or during idling phases.
  • the device would make uncontrolled oscillations, resulting in increased noise emissions, increased wear, choppy running, and increased raw engine emissions.
  • mechanical locking devices can be provided which, during the critical operating phases of the internal combustion engine, couple the two rotors in a torque-proof manner with one another, wherein this coupling can be canceled by pressurizing the locking device.
  • the locking position may be provided in one of the end positions (maximum early position and the maximum late position) or between the end positions.
  • Such a device is for example from the US 6,684,835 B2 known.
  • the device is designed in vane-type construction, wherein an outer rotor is rotatably mounted on an inner rotor designed as an impeller.
  • two rotational angle limiting devices are provided, wherein a first rotational angle limiting device in the locked state allows an adjustment of the inner rotor to the outer rotor in an interval between a maximum late position and a defined center position (locking position).
  • the second rotation angle limiting device allows in the locked state, a rotation of the inner rotor to the outer rotor in an interval between the center position and the maximum early position. If both rotational angle limits are in the locked state, the phase angle of the inner rotor to the outer rotor is limited to the middle position.
  • Each of the rotational angle limiting devices consists of a spring-loaded locking pin, which is arranged in a receptacle of the outer rotor. Each locking pin is moved by a spring in the direction of Inner rotor loaded with a force. On the inner rotor a gate is formed, which faces the locking pins in certain operating positions of the devices. In these operating positions, the pins can engage in the backdrop. In this case, the respective rotation angle limiting device moves from the ent to the locked state. Each of the rotation angle limiting devices can be transferred by pressurizing the gate from the locked to the unlocked state. In this case, the pressure medium urges the locking pins back into their receptacle, whereby the mechanical coupling of the inner rotor to the outer rotor is canceled.
  • the pressure medium is applied to the pressure chambers and the gate by means of a control valve, wherein on the control valve, inter alia, two working ports which communicate with the pressure chambers, and a control port, which communicates with the locking groove, are formed.
  • Other such control valves are from the US 6,779,500 B2 known.
  • These control valves consist essentially of a conventional 4/3-way proportional valve, which directs the pressure medium flows to and from the pressure chambers, and a 2/2-way valve, which regulates the pressure medium flows to and from the rotation angle limiting devices, wherein the part valves are arranged in series.
  • the two part valves on a common control piston and a common valve housing.
  • control valves are not suitable for use as a central valve, which is arranged in a central receptacle of the inner rotor.
  • control valves on two inlet connections which must be supplied via the inner rotor of the device pressure medium. This increases the complexity and the susceptibility of the device to errors.
  • the device is designed to be wide in the axial direction, so that all five ports of the valve from the receptacle of the inner rotor be covered. This leads to increased costs in the manufacture of the device. Furthermore, their space requirements and their weight is increased.
  • the invention has for its object a device for variable adjustment of the timing of gas exchange valves of an internal combustion engine with a control valve to represent, with as simple and thus cost-effective design of the control valve to be achieved. In addition, the space requirement of the control valve should be minimized.
  • the object is achieved in that on the outer lateral surface of the control piston, a first control chamber is formed, via the two of the working ports, which are arranged directly adjacent, depending on the position of the control piston within the valve housing, optionally connected to the inlet port or separated from it can be. Directly adjacent connections are connections between which no further connection is arranged.
  • a first control chamber is formed, via which both the working port and the control port, depending on the position of the control piston within the valve housing, optionally connected to the inlet port or can be separated from this.
  • control piston can assume positions relative to the valve housing, in which communicate the directly adjacent working ports simultaneously with the first control chamber.
  • control piston can assume positions relative to the valve housing, in which the working port and the control port communicate simultaneously with the first control chamber. Furthermore, on the outer lateral surface of the control piston, a second control chamber may be formed, via which the working port, which is not directly communicates with the first control chamber, depending on the position of the control piston within the valve housing, optionally connected to the inlet port or can be separated from this.
  • ports axially offset from one another and in the order inlet port, first working port, drain port, second working port, control port or inlet port, control port, drain port, second working port, first working port (A) are arranged.
  • control piston and / or the valve housing may be formed substantially rotationally symmetrical.
  • the working ports and the control port may be formed as radial openings in the valve housing.
  • control valve is arranged in a central receptacle of the output element, wherein the inlet connection is arranged in the axial direction outside the output element and the drive element.
  • control piston is hollow and communicates the interior of the control piston at least with the inlet port and the first control chamber.
  • a third control chamber is formed, which opens into the interior of the control piston and communicates in each position of the control piston relative to the valve housing with the inlet connection.
  • control chambers can be designed as an annular groove on the outer circumferential surface of the control piston.
  • a fourth control chamber is formed, via which one of the adjacent working ports (A, B, S), and the working port (A, B, S), which does not communicate with the first control chamber , depending on the position of the control piston within the valve housing, optionally connected to the drain port (T) or can be separated from this.
  • the device comprises an adjusting device, which is designed as a hydraulic actuator, and a hydraulic system, which supplies the adjusting device with pressure medium.
  • the adjusting device may be formed, for example, as in the prior art in vane type or in axial piston design. In the latter type, a pressure piston, the two pressure chambers separated from each other by pressure medium applied in the axial direction. The movement of the pressure piston over two pairs of helical gears causes a relative phase rotation between the output element and the drive element.
  • mechanical means rotation angle limiting device
  • the coupling may for example be such that the possible phase angles are limited to an angular range or that a rotationally fixed coupling between the output element and the drive element can be produced in a defined phase position.
  • the rotation angle limiting device (s) may assume a locked state (coupling established) and an unlocked state (no coupling). The transition from the locked to the unlocked state takes place by applying pressure medium to the rotation angle limiting device (s).
  • the hydraulic system has a control valve with a valve housing and a control piston.
  • the valve housing can be made substantially hollow cylindrical.
  • the connections may be formed as openings in the cylindrical lateral surface.
  • a control piston occupy several positions relative to this, thereby several control positions can be realized.
  • the actuator may be, for example, electromagnetic or hydraulic nature. In each control position results in a defined connection of different connections.
  • the connections formed as openings on the lateral surface of the valve housing are arranged offset to one another.
  • the control piston and the valve housing may be formed substantially rotationally symmetrical, whereby the production can be considerably simplified.
  • the control piston has a plurality of control structures.
  • a first control chamber is provided, which communicates on the one hand in each position of the control piston with the inlet connection and on the other hand with one of the working ports and the control port (or the other working port) is connectable.
  • positions of the control piston can be provided, in which the first control chamber communicates exclusively with the working connection or the control connection (or other working connection).
  • positions may be provided in which the first control room communicates with both terminals.
  • the reduction in the number of necessary controls brings a reduction of the axial space with it, so that a use as a central valve is conceivable.
  • the desired control logic of the control valve can be defined.
  • control chambers can be formed, for example, as an annular groove on the outer circumferential surface of the control piston. Equally conceivable would be the formation of Operaringnuten.
  • connection between the first control chamber and the inlet connection can take place via the interior of the hollow control piston.
  • Pressure medium which enters via the inlet connection, can pass through piston openings into the interior of the control piston.
  • further piston openings be provided, which connect the first and / or the second control chamber with the interior of the piston.
  • the control valve By arranging the connections in the sequence inlet connection, working connection (or control connection), drain connection, working connection, control connection (or working connection), the control valve can be provided for central valve applications. Due to the sequence of connections, the pressure medium supply of the control valve can be arranged outside of the adjusting device. In this case, the control valve protrudes in the axial direction out of the inner rotor, wherein the inlet connection is outside the inner rotor. Thus, the width of the inner rotor only has to correspond to the maximum distance between the working ports, the control port and the drain port. The inner rotor and thus the adjusting device can thus be made narrower.
  • control valve can assume a first control position, in which the first working connection communicates exclusively with the tank, the second working connection exclusively with the inflow connection and the control connection exclusively with the tank.
  • a second control position may be provided, in which the first working connection communicates exclusively with the tank and the second working connection and the control connection exclusively with the inflow connection.
  • a third control position may be provided, in which the control port only communicates with the inflow port, while the working ports do not communicate with either the inflow port or the one of the outflow ports.
  • a fourth control position may be provided, in which the second working connection communicates exclusively with the tank and the first working connection and the control connection exclusively with the inflow connection.
  • control port and thus the rotational angle limiting device (s) are connected to the tank during the start of the internal combustion engine, in which the control valve assumes the first control position.
  • the control valve assumes the first control position.
  • 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 connected to an intake camshaft 6 or an exhaust camshaft 7 via a traction mechanism drive 5, wherein a first and a second device 10 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 intake gas exchange valves 9a or one or more exhaust gas exchange valves 9b.
  • it may be provided to equip only one of the camshafts 6, 7 with a device 10, or to provide only one camshaft 6, 7, which is provided with a device 10.
  • FIGS. 2a and 2 B show an embodiment of a device 10 according to the invention in a plan view or in longitudinal section.
  • the device 10 has an adjusting device 11 and a hydraulic system 12.
  • the adjusting device 11 has a drive element (outer rotor 22), a drive element rotatably connected to the camshaft 6, 7 (inner rotor 23) and two side covers 24, 25.
  • the inner rotor 23 is designed in the form of an impeller and has a substantially cylindrically designed hub member 26, extend from the outer cylindrical surface in the illustrated embodiment, five wings 27 in the radial direction outwards. In this case, the wings 27 may be integrally formed with the hub member 26. Alternatively, the wings 27, as in FIG.
  • a plurality of projections 30 extend radially inwardly.
  • the projections 30 are formed integrally with the peripheral wall 29.
  • the outer rotor 22 is mounted by means of radially inner circumferential walls of the projections 30 relative to the inner rotor 23 rotatably mounted on this.
  • a sprocket 21 is formed, by means of which a torque can be transmitted from the crankshaft 2 to the outer rotor 22 via a chain drive, not shown.
  • the sprocket 21 may be formed as a separate component and rotatably connected to the inner rotor 23 or formed integrally therewith. Alternatively, a belt or gear drive can be provided.
  • each of the projections 30 an axial opening 31 is provided for this purpose, wherein each axial opening 31 is penetrated by a fastening element 32, for example a bolt or a screw, which serves for the rotationally fixed fixing of the side cover 24, 25 on the outer rotor 22.
  • a fastening element 32 for example a bolt or a screw
  • a pressure space 33 is formed, which in the circumferential direction of opposite, substantially radially extending boundary walls 34 adjacent projections 30, in the axial direction of the side covers 24, 25, radially inwardly of the hub member 26 and radially outwardly bounded by the peripheral wall 29.
  • a wing 27 In each of the pressure chambers 33 projects a wing 27, wherein the wings 27 are formed such that they abut both on the side walls 24, 25, and on the peripheral wall 29. Each wing 27 thus divides the respective pressure chamber 33 into two oppositely acting pressure chambers 35, 36.
  • the outer rotor 22 is rotatably arranged in a defined Winkelbreich to the inner rotor 23.
  • the angular range is limited in one direction of rotation of the inner rotor 23 in that each vane 27 comes into contact with a boundary wall 34 of the pressure space 33 designed as an early stop 34a (early control times).
  • the angular range in the other direction of rotation is limited by the fact that each vane 27 comes into contact with the other boundary wall 34 of the pressure chamber 33, which serves as a late stop 34b (late control times).
  • a rotation limiting device may be provided, which the rotation angle range of the outer rotor 22nd limited to the inner rotor 23.
  • the phase angle of the outer rotor 22 to the inner rotor 23 and thus the camshaft 6, 7, to the crankshaft 2 can be varied.
  • the phase position of the two rotors 22, 23 are kept constant to each other.
  • it can be provided to pressurize none of the pressure chambers 35, 36 during phases of constant phase position with pressure medium.
  • hydraulic pressure medium usually the lubricating oil of the internal combustion engine 1 is used.
  • a locking mechanism 41 is provided which establishes a mechanical connection between the two rotors 22, 23.
  • the locking position may lie in one of the end positions of the inner rotor 23 relative to the outer rotor 22.
  • a rotation angle limiting device 42 is provided, wherein arranged in one of the rotors 22, 23 a locking pin 44 and in the other rotor 22, 23, a link 45 is formed, which is adapted to the locking pin 44. If the inner rotor 23 is in the locking position, then the locking pin 44 can engage in the link 45 and thus produce a mechanical rotationally fixed connection between the two rotors 22, 23.
  • FIG. 2a Such a locking mechanism 41 is in FIG. 2a shown.
  • This consists of a first and a second rotational angle limiting device 42, 43.
  • each of the rotational angle limiting devices 42, 43 consists of an axially displaceable locking pin 44, wherein each of the locking pins 44 is received in a bore of the inner rotor 23.
  • 24 two scenes 45 are formed in the form of circumferentially extending grooves in the first side wall. These are in FIG. 2a indicated in the form of broken lines.
  • Each of the locking pins 44 is acted upon by means of a spring element 46 with a force in the direction of the first side cover 24. If the inner rotor 23 to the outer rotor 22 assumes a position in which a locking pin 44 faces in the axial direction of the associated link 45, this is forced into the link 45 and the respective rotational angle limiting device 42, 43 transferred from an unlocked to a locked state.
  • the link 45 of the first rotational angle limiting device 42 is designed such that the phase position of the inner rotor 23 is limited to the outer rotor 22, with locked first rotational angle limiting device 42, on a range between a maximum late and the locking position.
  • the locking pin 44 of the first rotation angle limiting device 42 bears against a stop formed in the circumferential direction by the link 45, thereby preventing any further adjustment in the direction of earlier control times.
  • the link 45 of the second rotational angle limiting device 43 is designed such that when locked second rotational angle limiting device 43, the phase angle of the inner rotor 23 is limited to the outer rotor 22 to a range between a maximum early position and the locking position.
  • a plurality of pressure medium lines 38a, b, control lines 48, a control valve 37, a pressure medium pump 47 and a tank 49 is provided.
  • first and second pressure medium lines 38a, 38b are provided inside the inner rotor 23 inside the inner rotor 23 inside the inner rotor 23.
  • the first pressure medium line 38a extending from the first pressure chambers 35 to a central receptacle 40 of the inner rotor 23.
  • the second pressure medium line 38b extending from the second pressure chambers 36 also to the central receptacle 40.
  • the pressure medium lines 38a, b are in FIG. 2a for reasons of clarity shown only for two pressure chambers 33.
  • control lines 48 are provided, which extend from a first annular groove 50 in the central receptacle 40 of the inner rotor 23 via the first side cover 24 to the scenes 45.
  • the first annular groove 50 communicates with the scenes 45 in every phase of the device 10.
  • a control valve 37 is arranged within the receptacle 40 of the inner rotor 23.
  • the control valve 37 is received in a hollow camshaft 6,7, which passes through the receptacle 40 of the inner rotor 23.
  • the inner rotor 23 for example by means of a non-positive or cohesive connection with the camshaft 6,7 rotatably connected.
  • the control valve 37 has a first and a second working port A, B, an inlet port P, a third working port (control port S) and drain ports T, T a .
  • the control valve 37 can be supplied with pressure medium from a pressure medium pump 47.
  • the first and second working ports A, B communicate with the first and second pressure medium lines 38a, b, respectively.
  • the control connection S communicates with the control lines 48. Via the outflow connections T, T a , pressure medium can be removed from the control valve 37 to a tank 49.
  • control valve 37 can be transferred into four control positions S1-S4 ( FIG. 2a ).
  • first control position S1 the second working port B communicates with the inflow port P, while both the first one Working port A and the control port S with the drain ports T, T a are connected.
  • This control position S1 is taken during the starting phase of the internal combustion engine 1. In this phase, the hydraulic clamping of the wings 27 is not guaranteed within the pressure chambers 33 due to low system pressure in general. Since the scenes 45 both rotational angle limiting devices 42, 43 via the control lines 48, and the control valve 37 are connected to the tank 49, both rotational angle limiting device 42, 43 take the locked state.
  • the inner rotor 23 is mechanically connected to the outer rotor 22, whereby the phase position is fixed in the locking position. Since in this position of the control valve 37, the rotation angle limiting devices 42, 43 are not connected to the pressure medium pump 47 but the tank 49, there is no risk of unwanted unlocking. Thereby, the starting ability of the internal combustion engine 1 is secured and at the same time the exhaust emissions are reduced.
  • the control positions S2-S4 of the control valve 37 represent the control positions of the device 10, in which an adjustment in the direction of later control times (second control position S2) or an adjustment in the direction of early control times (fourth control position S4) or the control times are kept constant (third Control position S3).
  • the scenes 45 of the rotation angle limiting devices 42, 43 are connected via the control lines 48 and the control valve 37 to the pressure medium pump 47.
  • system pressure is applied to the end face of the locking pins 44, as a result of which the rotational angle limiting devices 42, 43 assume the unlocked state and permit phase adjustment of the inner rotor 23 to the outer rotor 22.
  • both the second working port B and the control port S communicate with the inflow port P, while the first working port A is connected to the outflow port T.
  • 36 pressure medium from the pressure medium pump 47 is supplied via the control valve 37 and the second pressure medium lines 38b the second pressure chambers.
  • the wings 27 are moved within the pressure chambers 33 in the direction of the late stops 34b. This results in a relative change in the phase position of the camshaft 6, 7 to the crankshaft 2 in the direction of later timing.
  • both the first working port A and the control port S communicate with the inflow port P, while the second working port B is connected to the outflow port T.
  • pressure medium from the pressure medium pump 47 is supplied to the first pressure chambers 35 via the control valve 37 and the first pressure medium lines 38a.
  • the wings 27 are moved within the pressure chambers 33 in the direction of the early stops 34a. This results in a relative change in the phase angle of the camshaft 6, 7 to the crankshaft 2 in the direction of early timing.
  • the control valve 37 is in the FIGS. 3a-d shown. It consists of a not shown actuator and a hydraulic section 51.
  • the hydraulic section 51 consists of a substantially hollow cylindrical valve housing 52 and a control piston 54.
  • the valve housing 52 carries the terminals A, B, P, S, T, T a .
  • the connections A, B, P, S, T are designed as openings in the cylindrical wall of the valve housing 52, which open into annular grooves which are formed on the outer lateral surface of the valve housing 52.
  • the working ports A, B communicate via openings in the camshaft 6, 7 with the first and second pressure medium lines 38a, b.
  • the control connection S kom-resp. second pressure medium lines 38a, b.
  • the control port S communicates via openings in the camshaft 6, 7 with the first annular groove 50 of the inner rotor 23, in which the control lines 48 open.
  • the drain port T communicates via further openings in the camshaft 6, 7 with a second annular groove 53, which is formed in the receptacle 40 of the inner rotor 23.
  • the second annular groove 53 is connected via an axial bore 39 in connection with the exterior of the adjusting device 11
  • connections A, B, P, S, T are axially offset from one another and arranged in the sequence inlet connection P, first working connection A, discharge connection T, second working connection B, control connection S.
  • all connections are arranged within the receptacle 40 (FIG. FIG. 2b ).
  • the inlet connection P projects out of the adjusting device 11 in the axial direction.
  • the pressure medium outside the adjusting device 11 can be supplied to the control valve 37.
  • the architecture of the inner rotor 23 is considerably simplified.
  • the axial discharge port T a is formed as an axial opening of the valve housing 52.
  • the control piston 54 is designed substantially hollow cylindrical and disposed axially displaceable within the valve housing 52. In this case, the axial position of the control piston 54 can be adjusted continuously by means of the adjusting unit, not shown.
  • the actuator acts against the force of a spring 55 which moves the control piston 54 to an initial position when the actuator is inactive.
  • the spring 55 is supported on a spring plate 55a, which is fixed in the axial opening which forms the axial discharge port T a .
  • the actuator 50 may be formed, for example, as an electrical actuator.
  • the control piston 54 has four axially spaced control spaces 56a, b, c, d.
  • the control chambers 56a, b, c, d are formed in the illustrated embodiment as annular grooves in the outer circumferential surface of the control piston 54.
  • the control spaces 56a, b, c communicate with the interior of the control piston 54 via piston openings 57a, b, c.
  • the control spaces 56a-d are each bounded by two annular lands 58a-e.
  • the first annular web 58a limits the first control chamber 56a in the direction of the axial outlet port T a and the fifth annular web 58e the inlet port P in the direction of the actuating unit, not shown.
  • the second ring land 58b separates the first control space 56a from the fourth control space 56d.
  • the third ring land 58c separates the fourth control space 56d from the second control space 56b.
  • the fourth ring land 58d separates the second control space 56b from the third control space 56c.
  • control spaces 56a-d communicate with various ports A, B, P, S, T, T a .
  • the first control chamber 56a is arranged such that communication with the second working port B and the control port S can be established.
  • the second control chamber 56b is arranged such that communication with the first working port A can be established.
  • the third control chamber 56c communicates in each position of the control piston 54 with the inlet port P.
  • the fourth control chamber 56d is arranged such that communication with the second working port B or the first working port A can be established. In this case, the fourth control chamber 56d always communicates with the drain port T.
  • FIGS. 3a-d Based on FIGS. 3a-d the function of the control valve 37 will be explained.
  • the figures differ in the relative position of the control piston 54 relative to the valve housing 52 FIG. 3a the control valve 37 is shown in a state in which the actuator is inactive.
  • the spring 55 urges the control piston 54 in the starting position, in which this rests against a first stop 59.
  • the control piston 54 is offset relative to the valve housing 52 by an increasing distance against the force of the spring 55.
  • Pressure medium thus passes from the pressure medium pump 47 via the control valve 37 to the second pressure chambers 36, while pressure medium from the scenes 45 and the first pressure chambers 35 is discharged to the tank 49.
  • the rotation angle limiting devices 42, 43 are consequently in the locked state and thus prevent a phase adjustment of the inner rotor 23 relative to the outer rotor 22.
  • Pressure medium thus passes from the pressure medium pump 47 via the control valve 37 to the scenes 45, while the pressure chambers 35, 36 supplied neither pressure medium, nor discharged from these.
  • the adjusting device 11 is thus hydraulically clamped, i. there is no phase adjustment between the inner rotor 23 and the outer rotor 22.
  • control piston 54 is deflected relative to the valve housing 52 by the distance x 3 > x 2 against the force of the spring 55.
  • Pressure medium which is supplied to the control valve 37 via the inlet port P, passes via the interior of the control piston 54 to the first control chamber 56a and from there to the control port S.
  • the pressure medium passes through the interior of the control piston 54 and the second piston openings 57b in the second control chamber 56b and from there to the first working port A.
  • a connection between the inlet port P and the second working port B is blocked by the second annular web 58b.
  • a pressure medium flow from the first working port A to the drain port T is blocked by the third annular web 58 c.
  • the second working port B is connected to the drain port T by means of the fourth control chamber 56d.
  • the first ring land 58a further separates the control port S from the axial discharge port T a .
  • Pressure medium thus passes from the pressure medium pump 47 via the control valve 37 to the first pressure chambers 35 and the scenes 45, while pressure medium is discharged from the second pressure chambers 36 to the tank 49.
  • the rotation angle limiting devices 42, 43 are transferred to the unlocked state. At the same time takes place by the pressure medium flow to the first pressure chambers 35 and the pressure medium outflow from the second pressure chambers 36, a phase adjustment in the direction of later timing instead.
  • the control valve 37 shown serves, on the one hand, to regulate the phase position of the inner rotor 23 relative to the outer rotor 22. Furthermore, the locking states of the rotational angle limiting devices 42, 43 can be controlled via a separate control connection S. By the separation of the control terminal S from the working ports A, B, the risk of unwanted input or Entriegelns the rotational angle limiting devices 42, 43 is reduced. In addition, the control logic with respect to the control terminal S can be performed independently of those of the working ports A, B and thus tailored to the particular application. By the pressure medium supply to one of the working ports B and to the control port S via a common control chamber 56a, the structure of the control piston 54 is simplified.
  • control valve 37 has only four control chambers 56a-d with the same functionality. This leads to a significant simplification of the control piston 54. Furthermore, the number of costly to manufacture control edges (limitations of the control spaces 56a-d) is reduced to a minimum. Thus, the control piston 54 can be made cheaper and more reliable. Furthermore, the control piston 54 can be designed to be shorter in the axial direction, as a result of which the space requirement of the control valve 37, which is arranged in installation-critical areas of the internal combustion engine 1, is considerably reduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (12)

  1. Dispositif (10) pour l'ajustement variable des temps de commande de soupapes d'échange de gaz (9a, 9b) d'un moteur à combustion interne (1), comprenant :
    - un élément d'entraînement (22), un élément de sortie (23), un dispositif de limitation d'angle de rotation (42, 43) et une soupape de commande (37),
    - au moins deux chambres de pression (35, 36) agissant l'une par rapport à l'autre étant prévues,
    - un déphasage entre l'élément de sortie (23) et l'élément d'entraînement (22) pouvant être causé par sollicitation en fluide sous pression de l'une des chambres de pression (35, 36) au cours d'une vidange simultanée de l'autre chambre de pression (35, 36),
    - le dispositif de limitation de l'angle de rotation (42, 43) empêchant, dans un état verrouillé, une variation de la position de phase,
    - le dispositif de limitation de l'angle de rotation (42, 43) permettant, dans un état déverrouillé, une variation de la position de phase,
    - le dispositif de limitation de l'angle de rotation (42, 43) pouvant être transféré par sollicitation en fluide sous pression de l'état verrouillé dans l'état déverrouillé,
    - la soupape de commande (37) présentant un boîtier de soupape (52) et un piston de commande (54),
    - au moins à chaque fois un raccord d'alimentation (P), un raccord d'écoulement (T), un premier et un deuxième raccord de travail (A, B) et un troisième raccord de travail (raccord de commande (S)) étant réalisés au niveau du boîtier de soupape (52),
    - le raccord d'alimentation (P) étant connecté à une source de fluide sous pression (47), le raccord d'écoulement (T) étant connecté à un réservoir (49), le raccord de commande (S) étant connecté au dispositif de limitation de l'angle de rotation (42, 43) et le premier et le deuxième raccord de travail (A, B) étant connectés à chaque fois à l'une des chambres de pression (35, 36), et
    - les raccords de travail (A, B, S) étant décalés axialement l'un par rapport à l'autre et étant réalisés de manière à ne pas se chevaucher sur le boîtier de soupape (52), caractérisé en ce que
    - sur la surface d'enveloppe extérieure du piston de commande (54) est réalisé un premier espace de commande (56a), par le biais duquel deux des raccords de travail (A, B, S) qui sont disposés directement l'un à côté de l'autre, peuvent être connectés, en fonction de la position du piston de commande (54) à l'intérieur du boîtier de soupape (52), de manière sélective au raccord d'alimentation (P) ou être séparés de celui-ci.
  2. Dispositif (10) selon la revendication 1, caractérisé en ce que le piston de commande (54) peut adopter des positions par rapport au boîtier de soupape (52), dans lesquelles les raccords de travail (A, B, S) directement adjacents communiquent simultanément avec le premier espace de commande (56a).
  3. Dispositif (10) selon la revendication 1, caractérisé en ce qu'un deuxième espace de commande (56b) est réalisé sur la surface d'enveloppe extérieure du piston de commande (54), par le biais duquel le raccord de travail (A, B, S) qui ne communique pas directement avec le premier espace de commande (56a), peut être connecté, en fonction de la position du piston de commande (54) à l'intérieur du boîtier de soupape (52), de manière sélective au raccord d'alimentation (P), ou être séparé de celui-ci.
  4. Dispositif (10) selon la revendication 1, caractérisé en ce que le piston de commande (54) est réalisé essentiellement avec une symétrie de révolution.
  5. Dispositif (10) selon la revendication 1, caractérisé en ce que le boîtier de soupape (52) est réalisé essentiellement avec une symétrie de révolution.
  6. Dispositif (10) selon la revendication 1, caractérisé en ce que les raccords de travail (A, B) et le raccord de commande (S) sont réalisés sous forme d'ouvertures radiales dans le boîtier de soupape.
  7. Dispositif (10) selon la revendication 3, caractérisé en ce que les raccords (A, B, P, S, T) sont décalés axialement les uns par rapport aux autres et disposés dans l'ordre suivant : raccord d'alimentation (P), premier raccord de travail (A), raccord d'écoulement (T), deuxième raccord de travail (B), raccord de commande (S) ou raccord d'alimentation (P), raccord de commande (S), raccord d'écoulement (T), deuxième raccord de travail (B), premier raccord de travail (A).
  8. Dispositif (10) selon la revendication 1, caractérisé en ce que la soupape de commande (37) est disposée dans un logement central (40) de l'élément de sortie (23), le raccord d'alimentation (P) étant disposé dans la direction axiale en dehors de l'élément de sortie (23) et de l'élément d'entraînement (22).
  9. Dispositif (10) selon la revendication 1, caractérisé en ce que le piston de commande (54) est réalisé sous forme creuse et l'intérieur du piston de commande (54) communique au moins avec le raccord d'alimentation (P) et le premier espace de commande (56a).
  10. Dispositif (10) selon la revendication 9, caractérisé en ce qu'un troisième espace de commande (56c) est réalisé sur la surface d'enveloppe extérieure du piston de commande (54), lequel débouche à l'intérieur du piston de commande (54) et communique dans chaque position du piston de commande (54) par rapport au boîtier de soupape (52) avec le raccord d'alimentation (P).
  11. Dispositif (10) selon la revendication 1, caractérisé en ce qu'un quatrième espace de commande (56d) est réalisé sur la surface d'enveloppe extérieure du piston de commande (54), par le biais duquel l'un des raccords de travail adjacents (A, B, S) et le raccord de travail (A, B, S) qui ne communique pas directement avec le premier espace de commande (56a), peuvent être connectés, en fonction de la position du piston de commande (54) à l'intérieur du boîtier de soupape (52), de manière sélective au raccord d'écoulement (T) ou être séparés de celui-ci.
  12. Dispositif (10) selon l'une quelconque des revendications 1, 3, 10 ou 11, caractérisé en ce que les espaces de commande (56a-d) sont réalisés sous forme de rainure annulaire sur la surface d'enveloppe extérieure du piston de commande (54).
EP08856902A 2007-12-05 2008-11-24 Dispositif de réglage variable de la distribution des soupapes de renouvellement des gaz d'un moteur à combustion interne Not-in-force EP2220346B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007058490A DE102007058490A1 (de) 2007-12-05 2007-12-05 Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
PCT/EP2008/066069 WO2009071458A2 (fr) 2007-12-05 2008-11-24 Dispositif de réglage variable de la distribution des soupapes de renouvellement des gaz d'un moteur à combustion interne

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EP2220346A2 EP2220346A2 (fr) 2010-08-25
EP2220346B1 true EP2220346B1 (fr) 2011-06-22

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US (1) US8297244B2 (fr)
EP (1) EP2220346B1 (fr)
KR (1) KR101530738B1 (fr)
CN (1) CN101883915B (fr)
AT (1) ATE513983T1 (fr)
DE (1) DE102007058490A1 (fr)
WO (1) WO2009071458A2 (fr)

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DE102009039384A1 (de) 2009-08-29 2011-03-03 Schaeffler Technologies Gmbh & Co. Kg Steuerventil
US8662039B2 (en) * 2011-03-16 2014-03-04 Delphi Technologies, Inc. Camshaft phaser with coaxial control valves
JP5722743B2 (ja) * 2011-10-14 2015-05-27 日立オートモティブシステムズ株式会社 内燃機関のバルブタイミング制御装置
GB201200493D0 (en) * 2012-01-12 2012-02-22 Jaguar Cars Vehicle test and diagnostics arrangement and method (switch pack actuation)
JP5873339B2 (ja) * 2012-01-17 2016-03-01 日立オートモティブシステムズ株式会社 内燃機関のバルブタイミング制御装置
DE102012201573A1 (de) * 2012-02-02 2013-08-08 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102014207989A1 (de) * 2014-04-29 2015-10-29 Schaeffler Technologies AG & Co. KG Hydraulischer Phasensteller einer Nockenwelle
US11459220B2 (en) * 2017-11-30 2022-10-04 Danfoss Power Solution II Technology A/S Hydraulic system with load sense and methods thereof

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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
JP4147435B2 (ja) 1998-01-30 2008-09-10 アイシン精機株式会社 弁開閉時期制御装置
JP4487449B2 (ja) * 2001-06-28 2010-06-23 アイシン精機株式会社 弁開閉時期制御装置
JP3867897B2 (ja) 2001-12-05 2007-01-17 アイシン精機株式会社 弁開閉時期制御装置
JP4000522B2 (ja) * 2003-02-26 2007-10-31 アイシン精機株式会社 弁開閉時期制御装置
JP2006170026A (ja) * 2004-12-14 2006-06-29 Aisin Seiki Co Ltd 内燃機関の弁開閉時期制御装置
DE102006020320A1 (de) * 2006-05-03 2007-11-08 Schaeffler Kg Ventil für einen Nockenwellenversteller

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Publication number Publication date
WO2009071458A2 (fr) 2009-06-11
US20110005482A1 (en) 2011-01-13
KR101530738B1 (ko) 2015-06-22
CN101883915A (zh) 2010-11-10
WO2009071458A3 (fr) 2009-08-13
ATE513983T1 (de) 2011-07-15
EP2220346A2 (fr) 2010-08-25
CN101883915B (zh) 2012-08-01
US8297244B2 (en) 2012-10-30
KR20100098618A (ko) 2010-09-08
DE102007058490A1 (de) 2009-06-10

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