EP2267282A1 - Régulateur de phase d'arbres à came doté d'un couvercle de boîtier multifonctionnel - Google Patents

Régulateur de phase d'arbres à came doté d'un couvercle de boîtier multifonctionnel Download PDF

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Publication number
EP2267282A1
EP2267282A1 EP09174480A EP09174480A EP2267282A1 EP 2267282 A1 EP2267282 A1 EP 2267282A1 EP 09174480 A EP09174480 A EP 09174480A EP 09174480 A EP09174480 A EP 09174480A EP 2267282 A1 EP2267282 A1 EP 2267282A1
Authority
EP
European Patent Office
Prior art keywords
housing
cover
pressure chamber
fluid
channel
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.)
Granted
Application number
EP09174480A
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German (de)
English (en)
Other versions
EP2267282B1 (fr
Inventor
Jürgen Bohner
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.)
Schwaebische Huettenwerke Automotive GmbH
Original Assignee
Schwaebische Huettenwerke Automotive GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication of EP2267282A1 publication Critical patent/EP2267282A1/fr
Application granted granted Critical
Publication of EP2267282B1 publication Critical patent/EP2267282B1/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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L2001/028—Pre-assembled timing arrangement, e.g. located in a cassette
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—Location oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34436—Features or method for avoiding malfunction due to foreign matters in oil
    • F01L2001/3444—Oil filters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit
    • 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
    • F01L2303/00—Manufacturing of components used in valve arrangements

Definitions

  • the invention relates to a hydraulic camshaft phaser for an internal combustion engine, which preferably has a pressure accumulator in order to ensure a control pressure required for high actuating speeds.
  • camshaft phaser for varying the intake and exhaust timing. Due to the high reliability, but also in terms of a favorable cost-benefit ratio have hydraulic, operated by the lubricating oil for the internal combustion engine phaser proven by the principle of hydraulic swing motor. Stricter fuel consumption and pollutant requirements require high speeds.
  • phaser is mounted in an attachable housing mountable on the cylinder head housing.
  • the attachment housing forms a peripheral wall and an end wall of a pressure chamber of the pressure accumulator.
  • a lid closes the pressure chamber at the opposite end.
  • fluid channels such as a feed channel for the oil are also closed with lids or plugs.
  • the subject of the invention is a hydraulic camshaft phaser having an adjusting device which can be acted upon by a hydraulic pressure fluid for adjusting the phase position of a camshaft of an internal combustion engine.
  • the adjusting device may in particular comprise a first rotor rotationally driven by a crankshaft of the internal combustion engine and a second rotor rotationally driven by the first rotor, whose rotational angular position is adjustable relative to the first rotor by means of the pressurized fluid.
  • the second rotor drives the camshaft whose phase position is thus adjustable relative to the drive shaft.
  • the phaser is preferably formed as a hydraulic swing motor.
  • the adjusting device is acted upon by means of a control valve with the pressurized fluid so that the second rotor is adjusted relative to the first rotor and thus the camshaft to be controlled relative to the crankshaft in a favorable angle of rotation for the respective operating situation.
  • the phase adjuster comprises in a preferred embodiment a pressure accumulator with a volume-variable pressure chamber for the pressurized fluid.
  • the volume of the pressure chamber is preferably elastically changeable, so that a supply pressure for the actuating device adjusts in the pressure chamber as a function of an elastic restoring force acting in the direction of a reduction in volume.
  • the pressure accumulator has a pressure chamber and a pressure chamber limiting wall structure, which is movable against a resiliency elastic force.
  • the movable wall structure may be an elastically flexible, but fluid-tight wall structure, or preferably a reciprocating piston in the pressure chamber. In the first case, the wall structure may be attached to the chamber wall. It can itself form a spring member that generates the restoring elasticity force.
  • the accumulator would be in such embodiments, a diaphragm accumulator with an elastic membrane or possibly a flexible, non-elastic membrane, which is stretched by an additional spring member.
  • the pressure accumulator can also be formed as an elastic bellows.
  • a piston pressure accumulator is particularly preferred.
  • a piston is supported on a Spring member off.
  • the spring member for the piston or the only flexible wall structure may be formed by a gas pressure chamber, but is preferably a mechanical spring, for example a coil spring, which is tensioned with an increase in the pressure in the chamber, preferably on pressure.
  • the pressure accumulator can be arranged in the supply circuit of the phaser so that the pressure fluid can flow only through the pressure chamber to the actuator.
  • the supply circuit may branch upstream of the pressure accumulator into a first flow path, on which pressure fluid passes bypassing the pressure accumulator to the actuating device, and a second flow path, through which the pressure accumulator flows and the pressure fluid passes from the pressure accumulator to the actuating device.
  • the accumulator is connected via the branch with the adjusting device, for which the above-mentioned EP 1 985 813 A2 is referred to.
  • the phase adjuster further comprises a cover attached to the housing. Housing and cover may together form the pressure chamber of the accumulator, if the phaser as preferred has the pressure accumulator. In embodiments with pressure accumulator, but especially in versions without pressure accumulator, the housing and the lid together form a receiving space for the actuator or the control valve.
  • the word “or” is here as well as otherwise understood by the invention in the usual logical sense as “inclusive or”, so includes both the meaning of "either ... or” as well as the meaning of "and”, as far as from the each concrete context can not exclusively give only one of these two meanings.
  • the at least one Fluid channel may extend upstream of the adjusting device or in particular of the control valve, so that pressurized fluid of the actuating device or the control valve can be supplied via it.
  • the at least one fluid channel may also be a discharge channel or discharge channel which extends in the housing downstream from the control valve or in particular the adjusting device, so that the fluid can flow out through such a fluid channel into a reservoir.
  • the at least one fluid channel can also be a fluid channel which connects the pressure accumulator, if present, with the control valve or the adjusting device.
  • the lid is fixed to the housing so as to face the mouth of the at least one fluid channel extending through the housing and to encapsulate, as it were, to cover the fluid channel.
  • the fluid channel ends at or in the lid or is closed by the lid in at least one direction of flow, preferably the outflow.
  • the lid thus fulfills at least two different functions according to the invention. In first function, it forms together with the housing the pressure chamber of the optional pressure accumulator or a receiving space for the actuator or the control valve, and in secondary function that of Abdeckelns or capsules of at least one lid opposite the fluid opening of the housing opening. For the fluid channel no additional lid or plug is required.
  • the cover has a joining surface, which faces in a mounting direction of the lid of a joint counter-surface of the housing and is tensioned in the mounting direction directly or preferably via a seal on the joint counter-surface, preferably by means of screw.
  • the joining surface of the cover facing the housing and the joining mating surface of the housing are sufficiently large or long in their extent about an assembly axis parallel to the mounting direction, so that the cover can simultaneously fulfill the at least two or preferably even more different cover functions.
  • Cover and housing may instead of a single, contiguous joining and joining mating surface also form separate pairs of joining and joining mating surfaces to cover with the same cover a plurality of fluid channels and separate from each other, for example, a supply channel for the pressurized fluid and a discharge channel.
  • the cover not only encapsulates a single fluid channel, but also at least one further fluid channel in the for the at least one fluid channel said way.
  • the at least two fluid channels may be a supply channel extending upstream of the control valve and a discharge channel located downstream of the control valve. If the phaser as preferred has a pressure accumulator, in particular by means of the lid a connecting the pressure accumulator to the control valve connecting portion of a housing in the control valve or the adjusting device continuing supply channel to be encapsulated.
  • the encapsulation of the at least one fluid channel can be designed such that the cover simply closes the fluid channel. When covering a plurality of fluid channels by the same cover this can be realized for each of the fluid channels. If, as preferred, the pressure accumulator is present, the fluid channel or a plurality of fluid channels can flow into the pressure chamber enclosed by a common joining and joining counter surface.
  • the cover has a fluid channel, which is connected to the at least one fluid channel of the housing via the interface of the cover and the housing, sealingly surrounded by the joining and joining mating surface. For example, a supply channel for the pressurized fluid can extend through the cover.
  • a check valve advantageously be formed by the housing and the cover together by the cover form a valve seat and the housing support for a valve body in the valve seat exciting spring member.
  • the lid may already have a corresponding check valve in its lid supply channel alone, but more preferably such a check valve is formed by the housing and cover together.
  • the fluid channel encapsulated by the cover is the said discharge channel, in particular such a fluid channel can be closed off by the lid, for example in the manner of a stopper or simply by a flat closure.
  • the cover can in particular form a pot-like part of the pressure chamber, that is to say the peripheral wall and an end wall of the pressure chamber.
  • the discharge channel can be continued into the cover up to a rear side of a piston arranged in the pressure chamber in order to discharge leaking fluid from there can. The removal can be done for example via the lid.
  • the lid preferably encapsulates the discharge channel, which in such embodiments is led out of the housing at another location.
  • the phase adjuster is integrated in the lubricating oil supply of the internal combustion engine, so that the lubricating oil simultaneously forms the pressurized fluid for the phaser.
  • the accumulator is preferably a piston accumulator.
  • the pressure chamber is cylindrical in such embodiments and takes a piston back and forth movable.
  • the piston is elastically stretched in one direction of its mobility and counteracts this elastic restoring force against the pressure fluid. If the fluid pressure is sufficiently high, the pressure chamber is filled against the elastic restoring force. Decreases the fluid pressure, the piston displaces the pressure fluid from the pressure chamber in the direction of the adjusting device of the phaser according to the elastic restoring force, so that the supply of pressurized fluid is ensured.
  • a spring expediently a mechanical spring, acts on the piston.
  • the piston is sealed by means of a piston sealing ring against the liner of the pressure chamber. In simple, preferred embodiments, however, is dispensed with such an additional seal between the piston and peripheral wall of the pressure chamber. As a result, the cost of the pressure accumulator can be reduced and the breakaway force at the onset of piston movement can also be reduced.
  • the adjusting device is controlled by means of a control valve in order to advantageously set the phase position of the camshaft for the respective operating phase of the internal combustion engine.
  • the control valve is arranged in preferred first embodiments coaxially to the axis of rotation of the camshaft. In particular, it can be arranged axially reciprocatingly in a central cavity of the camshaft. If the control valve is arranged in a cavity of the camshaft, this advantageously forms a valve cylinder with control openings to the pressure chambers of the adjusting device. In such embodiments, the camshaft in one piece forms the valve cylinder of the control valve.
  • the camshaft can also be designed as a built-up camshaft, in the sense that the valve cylinder is manufactured separately from the camshaft and firmly connected to the camshaft at its axial end.
  • the adjusting device when the adjusting device is designed as a swivel motor, its rotors are arranged concentrically with the control valve.
  • the valve cylinder can also form a rotatably connected to the camshaft connected rotor of the adjusting device.
  • control valve is not coaxial with the camshaft, but arranged next to the axis of rotation of the camshaft, preferably at a small distance next to the actuating device.
  • An example of such an arrangement discloses the EP 1985 813 A2 which is also referred to in this regard.
  • the control valve may, in particular, be a proportional valve with a valve piston, an electromagnetic device for acting on the piston with a positioning force and a spring counteracting the actuating force.
  • a proportional valve with a valve piston
  • an electromagnetic device for acting on the piston with a positioning force and a spring counteracting the actuating force.
  • other types of control valves can be used.
  • the structure of the control valve can in particular be such that the pressure fluid passes through the valve piston or over the circumference of the valve piston of the axial position of the valve piston correspondingly via control bores of the valve cylinder in pressure chambers of the actuating device.
  • the housing is preferably formed in one piece, but in principle can also be assembled from separately molded housing parts, so even be already a built housing and not only with the mounted lid.
  • it is an attachment housing that is attached to a machine housing of the internal combustion engine or provided for cultivation.
  • Housing and cover are mounted in preferred first versions in the assembled state, as a unit, on the machine housing.
  • the housing can also be mounted without a lid in a first step and the lid can be mounted on the attached housing in a second step.
  • a cylinder head housing of the machine housing or a valve cover assumes a housing function for the phaser.
  • Such a housing part can in particular form an end wall of the pressure chamber of the pressure accumulator.
  • It may be a supply channel for Pressure chamber or extending from the pressure chamber supply channel to the control valve or the adjusting device in such a housing part.
  • the lid may be mounted directly on the machine housing or a valve cover to encapsulate the feed channel or the secondary feed channel.
  • the cover can also form the pressure chamber with the machine housing or a valve cover.
  • An enclosed under the inclusion of the machine housing, preferably a cylinder head housing of the machine housing, or a valve cover formed phaser housing comprises in an appropriate embodiment an additional, attached to the machine housing housing part, which surrounds the actuating device or the control valve and thereby for the actuator or the control valve, a cover and forms the said recording room in this sense.
  • FIG. 1 shows a phaser S, which is arranged in a cylinder headspace of an internal combustion engine.
  • the internal combustion engine has two juxtaposed camshafts on, of which in the illustrated section only a first camshaft 1 can be seen.
  • One of the camshafts serves to control intake valves and the other to control exhaust valves of the internal combustion engine.
  • the camshafts may also each control one or more inlet valve (s) and one or more outlet valve (s), ie at least one inlet valve may be arranged next to an outlet valve per combustion chamber in the axial direction of the camshaft.
  • a phase adjuster is sufficient for only one of the camshafts.
  • phaser can also be provided for each of the camshafts in such embodiments.
  • the camshafts are rotatably arranged in a cylinder head housing 3 about the respective axis of rotation, the camshaft 1 about its axis of rotation R 1 ,
  • the camshafts are rotationally driven by a crankshaft of the internal combustion engine.
  • the phase adjuster S has a drive wheel 6 which is arranged coaxially with the camshaft 1 and is driven by the crankshaft via a circulating traction means, preferably a traction-driving traction means such as a chain or a toothed belt.
  • Drive altematives for the camshafts are used in the EP 1 985 813 A2 disclosed in this regard.
  • the phaser S comprises an adjusting device 7, which is arranged in the torque train between the drive wheel 6 and the camshaft 1.
  • the adjusting device 7 comprises a first rotor 8, which is connected to the drive wheel 6 so as to be secured against rotation, and a second rotor 9, which is connected secured against rotation with the camshaft 1.
  • the rotor 9 is rotatable relative to the rotor 8 within a predetermined Drehwinkelverstell Schemes.
  • the phaser S is hydraulically adjustable. For the adjustment, it is supplied together with the internal combustion engine with a pressure oil, which serves the internal combustion engine as a lubricating oil and the phase adjuster S as pressurized fluid for the adjustment of the phase position of the second rotor 9 relative to the first rotor 8.
  • the pressurized fluid, or lubricating oil is supplied to the adjusting device 7 via a control valve 10, which centrally on the axis of rotation R 1 of Camshaft 1 is arranged.
  • the camshaft 1 has at the axial end, on which the phaser S is arranged, a central cavity in which a valve piston 11 of the control valve 10 is axially reciprocally accommodated.
  • the camshaft 1 forms for the valve piston 11 a valve cylinder with control openings through which the pressure fluid passes according to the axial position of the valve piston 11 in pressure chambers of the adjusting device 7, which are limited in the circumferential direction of the rotors 8 and 9.
  • a clamping means 2 for example a clamping nut
  • the control valve 10 is a proportional valve. It comprises, via the valve piston 11 and the valve cylinder formed by the camshaft 1 addition, an electromagnetic coil 12 with a central, axially movable armature, which acts on the valve piston 11 in an axial direction with an electromotive force, and a force acting counteracting the mechanical spring 13, by way of example a helical compression spring.
  • the coil 12 is adjusted to the respective operating phase of the internal combustion engine, so that its armature pushes the valve piston 11 against the restoring force of the spring 13 in an axial control position in which the actuator 7 of this axial control position is acted upon accordingly by the pressurized fluid.
  • a fixed to the cylinder head housing 3 housing part 4 forms with the cylinder head housing 3 a receiving space for the adjusting device 7 and the control valve 10 by covering these components radially outward and by means of a coil housing of the coil inserted 12 also on the side facing away from the camshaft 1 end face.
  • the pressurized fluid is supplied to the adjusting device 7 via the camshaft 1, which has a rotating pressure fluid supply 14 for this purpose.
  • This rotary feeder 14 is formed by a thrust bearing, a thrust bearing of the camshaft 1.
  • the rotary feeder 14 is supplied as a pressurized fluid lubricating oil from the oil gallery of the cylinder head housing 3.
  • the camshaft 1 is provided within the thrust bearing with a circumferential groove from which one or more radial channels open into the cavity of the camshaft 1 to the pressurized fluid to pass through the valve piston 11 and the respective control bore of the valve cylinder formed by the camshaft 1 to the adjusting device 7.
  • the phaser S has an accumulator.
  • the accumulator is disposed in the pressurized fluid circuit upstream of the control valve 10 and also upstream of the rotary oil supply 14.
  • the accumulator is designed as a piston accumulator.
  • a piston 22 is reciprocally received in a pressure chamber 21 of the accumulator.
  • the piston 22 is acted upon on one side with the pressurized fluid.
  • the piston 22 is acted upon by the pressure of the pressure fluid against a spring force of a mechanical spring 23, for example a helical compression spring.
  • the accumulator is connected via a gallery channel 16 to the lubricating oil gallery of the cylinder head 3.
  • the lubricating oil passes as the pressurized fluid through the gallery channel 16 and one of them branching feed channel 17 into the pressure chamber 21.
  • a check valve 18 and a filter element 19 are arranged in the feed channel 17.
  • the check valve 18 closes the feed channel 17 when the pressure of the pressure fluid in the upstream channel 16 falls below the pressure prevailing in the pressure chamber 21 pressure.
  • a cup-shaped cover 20 forms a peripheral wall 26 and the end wall 24 opposite another end wall of the pressure chamber 21.
  • the lid 20 is fluid-tight by means of a circumferential around the central longitudinal axis of the pressure chamber 21 seal 25 connected to the end wall 24.
  • the spring 23 is supported on one side on the cover 20 and on the lid 20 axially opposite side of the pot-shaped piston 22 and thus biases it axially in the direction of the end wall 24.
  • the cover 20 is in a mounting direction M on the cylinder head housing. 3 attached to its end wall 24, so that a joining surface 20a of the lid 20 and a joining counter surface 3a of the cylinder head housing 3 face each other over the seal 25 in and facing the mounting direction M and against the seal 25 and thus are stretched towards each other.
  • the sealed by the seal 25 joint gap between the joining surface 20 a and the Füge literally simulation 3a surrounds the pressure chamber 21 in a closed circuit around the mounting direction M parallel to the longitudinal axis of the pressure chamber 21, along which the piston 22 is reciprocally guided by the cover 20.
  • the cylinder head housing 3 forms the end wall 24 and the feed channel 17, the upstream gallery channel 16 leading to it, and in particular also a further feed channel 15, which connects the pressure chamber 21 with the rotary feeder 14.
  • the supply channel 15 is straight and connects the pressure chamber 21 directly to the rotary feeder 14.
  • the pressure chamber 21 is thus connected to the adjusting device 7 in a direct, advantageously short path.
  • the feed channel 15 extends in the mounting direction M orthogonal to the axis of rotation R 1 of the camshaft 1 in the rotary feeder 14.
  • the feed channel 15 would advantageously remain in an exclusively straight but oblique extension to the camshaft.
  • the feed channel 15 and the further feed channel 17 lead to the same end wall 24 in the pressure chamber 21.
  • the channels 15 and 17 are parallel to each other. Due to this arrangement and orientation, the channels 15 and 17 can be inexpensively formed in the cylinder head housing 3, preferably by drilling in the same machining direction.
  • the gallery channel 16 is preferably also drilled in the material of the cylinder head housing 3.
  • the pressure chamber 21 connects the channels 15 and 17, and the lid 20 encapsulates or covers the channels 15 and 17 from.
  • a discharge channel 28 is further formed, through which leaking from the back of the piston 22 leakage fluid from the pressure chamber 21 into the cylinder head space.
  • a short downstream channel portion 29 is formed, in which the discharge channel 28 of the lid 20 opens.
  • the channel portion 29 is also advantageously parallel to the channels 15 and 17, so that the channels 15, 17, and 29 can be inexpensively produced by drilling in the same machining direction.
  • the channels 15, 16, 17 and 29 are arranged in the same sectional plane. In general, it will be advantageous not to arrange all of these channels in the same sectional plane, but to provide an offset around the longitudinal axis of the pressure chamber 21 in the circumferential direction while maintaining the parallelism.
  • the cylinder head housing 3 and the attached housing part 4 including the housing of the coil 12 used in the context of the invention, a housing for the adjusting device 7 and the control valve 10 and together with the cover 20, the pressure chamber 21.
  • the end wall 24 with the fluid channels 15, 17 and 29 molded in one piece on the housing part 4 or mounted on this and be grown together with this as a unit on the correspondingly simplified cylinder head housing.
  • the cover 20 would be mounted in the modification to the housing part 4 and part of a unit assembly of the housing part 4 and cover 20 mounted attachment housing.
  • the pressure chamber 21 is closed by a lid 20 manufactured as an additional part. If the camshafts covered in a further modification of a valve cover, such as a valve cover made of plastic, this can form the lid 20, so that by mounting such a valve cover on the cylinder head housing 3 at the same time the pressure chamber 21 and thereby also the channels 15, 17 and 29 closed.
  • a valve cover such as a valve cover made of plastic
  • FIG. 2 shows a phaser with a mounting housing consisting of a housing 5 and a cover 5 attached to the housing 5.
  • the phaser is completely mounted as a phaser add-on module to the camshaft and a machine housing by the rotary feeder 14 coaxial to be adjusted in its rotational position
  • Camshaft and the housing 5 are attached to the cylinder head housing of the internal combustion engine.
  • About the rotary feeder 14 is a section of the FIG. 2 unrecognizable adjusting device 7, which may correspond to the adjusting device 7 of the first embodiment, the pressure fluid supplied.
  • the rotary feeder 14 is rotatably connected in the mounted state of the module accordingly about the axis of rotation R 1 of the camshaft and secured against rotation with one of the two rotors of the adjusting device 7.
  • the adjusting device 7 and the rotary feeder 14 are accommodated together in a receiving space of the housing 5.
  • the control valve 10 is not coaxial with the adjusting device 7 and rotary feeder 14, but in a separate receiving space of the housing 5, added next to the adjusting device 7 and the rotary feeder 14, unlike in the first embodiment.
  • the control valve 10 is inserted into this further receiving space as a unit and embedded in the inserted state in the fluid system of the attachment housing 5, 30.
  • EP 1 985 813 A2 referenced.
  • the control valve 10 has a valve cylinder and a valve piston 11 reciprocating in the valve piston, so that as in the first embodiment according to the switching position of the valve piston 11, the adjusting device 7 is acted upon in one or the other of the two directions of rotation in the one the two rotors is adjustable relative to the other.
  • the application of the corresponding pressure chamber (s) takes place in accordance with the switching position of the valve piston 11 either via a first control channel 11a in the one direction of rotation or via another control channel 11b in the other direction of rotation.
  • the control valve 10 is actuated electromagnetically again, so that the valve piston 11 either the in FIG. 2 shown neutral position or one of the two addressed switching positions for a relative left or right rotation occupies.
  • the control valve 10 controls the pressure fluid as in the first embodiment via either the control channel 11a or the control channel 11b or closes as shown in the neutral position both control channels 11a and 11b, so that the adjusting device 7 is blocked in its currently occupied angular position of their rotors.
  • the pressurized fluid is guided to the control valve 10 via a cover feed channel 37 extending through the cover 30 and a housing feed channel 35 which adjoins the cover feed channel 37 in a straight line.
  • a check valve with a valve body 18 and a valve seat 37 'and a spring member is arranged, which presses the valve body 18 against the direction indicated by a direction arrow feed direction into the valve seat 37'.
  • the valve seat 37 ' provides the cover 30, in whose feed channel 37 a valve seat 37' directly forming insert element is inserted.
  • the insert element also serves to hold a filter element 19, which is likewise arranged in the cover feed channel 37.
  • the spring member is supported on a support 5 formed by the housing. In the spring member it may in particular be a helical compression spring.
  • the support is formed by a diameter jump, a diameter reduction, in the housing feed channel 35. Due to the straight in the attachment housing 5, 30 to the control valve 10 straight course of the composed of the supply channels 35 and 37 pressure fluid supply can be reduced to a small degree, the flow resistance.
  • the cover 30 forms a cup-shaped part of a pressure chamber 31 which is arranged in the fluid system parallel to the cover supply channel 37, so that the pressure fluid supply composed of the two supply channels 35 and 37 is located in the branch immediately downstream of the valve seat 37 '. to the housing supply channel 35 and branched via a formed in the housing 5 connecting portion 36 into the pressure chamber 31 of the pressure accumulator.
  • the connecting portion 36 is formed on the joining side of the housing 5 facing the lid 30 as a pocket-like recess open to the lid 30 and extends on the joining side of the housing 5 to a side transverse to the mounting direction M until completely overlapping with the housing supply passage 37 and to the other side into the overlap with the pressure chamber 31, the lid feed channel 37 and the pressure chamber 31 are arranged directly adjacent to each other in a confined space and both open into the pocket-shaped connecting portion 36, which on the one hand to a compact design and on the other hand at most low flow losses also between the pressure chamber 31 and housing supply channel 35 leads.
  • the housing 5 forms again as in the first embodiment, an end wall 34 of the pressure chamber 31.
  • the cover 30 forms again the opposite end wall and the peripheral wall of the pressure chamber 31.
  • the pressure chamber is the end wall 34 opposite the reciprocating piston 32 limited, at its rear counteracted by the spring 33 against the pressure of the pressure fluid in the pressure chamber 31 with an elastic restoring force.
  • the spring 33 is received as in the first embodiment in a spring chamber formed by the lid 30 at the back of the piston 32; By way of example, it is again a helical compression spring, which is supported on the end wall of the lid 30 and acts in the direction of the end wall 34 on the piston 32.
  • the cover 30 encapsulates the housing discharge channel 39, in that the discharge channel 39 in the cover 30, namely in the spring chamber, terminates at the rear side of the piston 32.
  • the cover 30 also encapsulates the housing supply channel 35, namely by means of the non-return valve arranged in the transition region of the supply channels 35 and 37 with the valve body 18.
  • FIG. 3 shows the view AA on the joining surface 30a of the lid 30th
  • FIG. 4 shows the view BB on the mating counter surface 5a of the housing fifth
  • FIG. 4 shows the mounting housing 5, 30 in the mounted state, of the internal combustion engine, only the camshaft 1 is shown.
  • joining surface 30a and joining counter surface 5a face each other in the assembly direction M and seal the pressure chamber 31 and the feed composed of the channels 35 and 37 and of the channels 38 by means of a seal arranged between the surfaces 5a and 30a, for example a metal flat gasket , 38 'and 39 composite discharge to the outside from the environment. Furthermore, they seal the pressure chamber 31 and the feed 35, 37 together against the discharge 38, 38 'and 39 from.
  • FIG. 3 shows the view AA on the joining surface 30a of the lid 30th
  • FIG. 4 shows the view BB on the mating counter surface 5a of the housing fifth
  • FIG. 4 shows the mounting housing 5, 30 in the mounted state, of the internal combustion engine, only the camshaft 1 is shown
  • FIG. 3 is also the pocket-shaped in the joining surface 30a as a recess shaped, transversely to the mounting direction M extending connecting portion 38 'recognizable, which connects the staggered discharge channels 38 and 39 together.
  • FIG. 4 is in the direction of the lid 30 open, in the joining counter surface 5a pocket-like shaped recess recognizable, which forms the connecting portion 36.
  • housing supply channel 35 and housing discharge channel 39 is still nachzutragen that these two channels structurally very simple in the mounting direction M ( FIG. 2 ), orthogonal to the joint counter surface 5a extend and in particular can be incorporated as a simple, straight holes from the joint counter surface 5a ago.
  • the comparatively flat, open at the joining counter surface 5a pocket-shaped connecting portion 36 can be very easily formed, preferably in a primary molding by casting or only after the initial forming by machining.
  • the pocket-shaped connecting portion 36 is advantageously wide, for example, it is in the overlap with the feed channel 35 in a diameter of the Feed channel 35 corresponding width formed so that it opposes the flow of pressure between the pressure chamber 31 and the supply channel 35 as little flow resistance, a throttle effect is accordingly negligible.
  • the connecting portion 36 is widened to its diameter and shaped adapted to the cross-sectional shape of the pressure chamber 31. This also contributes to a low-resistance cross-connection between the pressure chamber 31 and feed channel 35.
  • FIG. 5 shows a phaser of a third embodiment.
  • the adjusting device 7 with the rotary feeder 14 and the control valve 10 are arranged as in the second embodiment, each in its own receiving space of a housing 50 and coupled together as in the second embodiment via control channels 11a and 11b. Differences exist in comparison with the second embodiment only in relation to the division of functions between the housing 50 and a cover 40.
  • the cover 40 is fixed as in the other two embodiments in the mounting direction M on a joining side of the housing 50.
  • the housing 50 forms with the preassembled cover 40 as in the second embodiment, a mounting housing for the phase adjuster formed as a mounting module.
  • the lid 40 is simplified relative to the lid 30 of the second embodiment by the housing 50 forms a cup-shaped space in which a piston 42 is axially reciprocally movable in and against the mounting direction M as in the other embodiments.
  • the housing 50 accordingly forms the peripheral wall and one of the two end walls of the pressure chamber 41 of the pressure accumulator jointly formed with the cover 40.
  • the cover 40 forms only the missing for encapsulation of the pressure chamber 41 1 end wall.
  • He also serves only as a closure for the housing 50 extending discharge channel 49, via which is discharged from the back of the piston 42, from the space of the arranged there spring 43, leakage fluid to the reservoir, wherein as in the second embodiment of the discharge channel 49 not only the leak fluid of the pressure accumulator, but) also dissipates the fluid from the adjusting device 7 and any leakage fluid from the control valve 10.
  • the cover 40 also fulfills the function of supplying the pressurized fluid to the control valve 10.
  • the cover 40 extends, as in the second exemplary embodiment, a cover feed channel 47, which extends on the side of the housing 40 into a further Housing supply channel 45 continues.
  • a check valve with a valve body 18 and a spring member is formed in the transition region between the cover 40 and the housing 50, which biases the valve body 18 elastically against a valve seat 47 ', which forms the housing 50 facing the end of the lid feed channel 47.
  • the valve seat 47 ' is directly on the lid 40, so shaped without insert element.
  • valve seat 47 'could also be formed with an insert element as in the second exemplary embodiment.
  • a filter element may be arranged in the feed channel 47.
  • the supply 45, 47 extends from a connection formed by the cover 40 to the control valve 10 in a straight line over a short path.
  • FIG. 6 shows the view AA on the joining surface 40a of the lid 40th
  • FIG. 7 shows the view BB on the mating counter-surface 50a of the housing 50.
  • the feed channel 45 and the pressure chamber 41 extend in the housing 50 of its mating counter-surface 50a in the mounting direction M ( Fig. 5 ) orthogonal to the joining surface 50a.
  • a connecting portion 46 which is pocket-shaped in the joining counterface 50a and opens toward the cover 40 connects the housing feed channel 45 to the pressure chamber 41.
  • the feed channel 45 and the pressure chamber 41 respectively open against the mounting direction M (FIG. FIG. 5 ) In the pocket-shaped connecting portion 46.
  • the connecting portion 46 surrounds in view of the mating counter-surface 50a and the mouth of Ab technologicalkanals 49, which also extends from joint surface 50a as in mounting direction M straight bore orthogonal to the joining surface 50a.
  • the mouth of the discharge channel 49 is completely surrounded circumferentially by a sealing web of the housing 50. This web forms around the mouth of the Ab technologicalkanals 49 encapsulated by the lid 40, namely sealed sealing joint surface and is accordingly also designated 50a.
  • the web protrudes inside the connecting portion 46.
  • a seal for sealing is between the joining surface 40 a and the joint mating surface 50a arranged a seal, expediently a metal flat gasket, a soft gasket, an elastomer profile gasket, a metal elastomer seal or the like, as may also be the case in the other embodiments.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP09174480.5A 2009-06-10 2009-10-29 Régulateur de phase d'arbres à came doté d'un couvercle de boîtier multifonctionnel Not-in-force EP2267282B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009024482A DE102009024482A1 (de) 2009-06-10 2009-06-10 Nockenwellen-Phasensteller mit Druckspeicher

Publications (2)

Publication Number Publication Date
EP2267282A1 true EP2267282A1 (fr) 2010-12-29
EP2267282B1 EP2267282B1 (fr) 2015-09-30

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Country Link
EP (1) EP2267282B1 (fr)
CN (1) CN101922322B (fr)
DE (1) DE102009024482A1 (fr)
HU (1) HUE027187T2 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011117016A1 (fr) * 2010-03-24 2011-09-29 Schaeffler Technologies Gmbh & Co. Kg Dispositif pour la modification de la position angulaire relative d'un arbre à came par rapport à un vilebrequin d'un moteur à combustion interne
WO2012000786A1 (fr) * 2010-07-02 2012-01-05 Schaeffler Technologies Gmbh & Co. Kg Dispositif permettant de modifier la position angulaire relative d'un arbre à cames par rapport à un vilebrequin d'un moteur à combustion interne
DE102011007745A1 (de) * 2011-04-20 2012-10-25 Mahle International Gmbh Dichtungsanordnung
WO2012167958A1 (fr) * 2011-06-07 2012-12-13 Schaeffler Technologies AG & Co. KG Cloche de boîtier possédant un accumulateur de pression intégré qui comporte un couvercle bordé
EP2487339A3 (fr) * 2011-02-11 2013-01-23 Schaeffler Technologies AG & Co. KG Dispositif de réglage d'arbres à came à l'aide d'un accumulateur de pression

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Publication number Priority date Publication date Assignee Title
DE102009050490B4 (de) 2009-10-23 2015-05-13 Schwäbische Hüttenwerke Automotive GmbH Anbaumodul mit Dichtung
DE102010034014B4 (de) 2010-08-11 2015-06-25 Schwäbische Hüttenwerke Automotive GmbH Sinterverbund und Verfahren zu seiner Herstellung
DE102011076652B4 (de) * 2011-05-27 2017-06-01 Schwäbische Hüttenwerke Automotive GmbH Vorrichtung zur Verstellung der relativen Drehwinkelposition geschachtelter Nockenwellen
DE102012209859A1 (de) 2012-06-13 2013-12-19 Schaeffler Technologies AG & Co. KG Ventileinheit mit axialem Druckmittelzufluss
DE102013219075B4 (de) * 2013-09-23 2020-11-26 Schaeffler Technologies AG & Co. KG Multiverriegelung eines Nockenwellenverstellers

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EP1201884A2 (fr) * 2000-10-25 2002-05-02 Honda Giken Kogyo Kabushiki Kaisha Commande de soupapes pour moteur à combustion interne
EP1985813A2 (fr) 2007-04-27 2008-10-29 Schwäbische Hüttenwerke Automotive GmbH & Co. KG Déphaseur d'arbres à cames et pompe à vide pour un moteur à combustion interne
US20090314235A1 (en) * 2008-06-18 2009-12-24 Gm Global Technology Operations, Inc. Hydraulic Control System for Engine Cam Phasing

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JPH08100611A (ja) * 1994-09-30 1996-04-16 Yamaha Motor Co Ltd エンジンにおけるカム位相角度可変装置の取付構造
JP2008002324A (ja) * 2006-06-21 2008-01-10 Hitachi Ltd 位相角検出装置及び該位相角検出装置を用いた内燃機関のバルブタイミング制御装置
CN100514020C (zh) * 2007-04-26 2009-07-15 天津大学 一种内燃机连续可变正时相位器检测装置及检测方法

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Publication number Priority date Publication date Assignee Title
US5718196A (en) * 1994-09-30 1998-02-17 Yamaha Hatsudoki Kabushiki Kaisha Lubrication and camshaft control system for engine
EP1201884A2 (fr) * 2000-10-25 2002-05-02 Honda Giken Kogyo Kabushiki Kaisha Commande de soupapes pour moteur à combustion interne
EP1985813A2 (fr) 2007-04-27 2008-10-29 Schwäbische Hüttenwerke Automotive GmbH & Co. KG Déphaseur d'arbres à cames et pompe à vide pour un moteur à combustion interne
US20090314235A1 (en) * 2008-06-18 2009-12-24 Gm Global Technology Operations, Inc. Hydraulic Control System for Engine Cam Phasing

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011117016A1 (fr) * 2010-03-24 2011-09-29 Schaeffler Technologies Gmbh & Co. Kg Dispositif pour la modification de la position angulaire relative d'un arbre à came par rapport à un vilebrequin d'un moteur à combustion interne
US9587524B2 (en) 2010-03-24 2017-03-07 Volkswagen Ag Device for changing the relative angular position of a camshaft with respect to a crankshaft of an internal combustion engine
US9759100B2 (en) 2010-03-24 2017-09-12 Volkswagen Ag Device for changing the relative angular position of a camshaft with respect to a crankshaft of an internal combustion engine
WO2012000786A1 (fr) * 2010-07-02 2012-01-05 Schaeffler Technologies Gmbh & Co. Kg Dispositif permettant de modifier la position angulaire relative d'un arbre à cames par rapport à un vilebrequin d'un moteur à combustion interne
EP2487339A3 (fr) * 2011-02-11 2013-01-23 Schaeffler Technologies AG & Co. KG Dispositif de réglage d'arbres à came à l'aide d'un accumulateur de pression
US8534248B2 (en) 2011-02-11 2013-09-17 Schaeffler Technologies AG & Co. KG Camshaft adjuster having a pressure accumulator
DE102011007745A1 (de) * 2011-04-20 2012-10-25 Mahle International Gmbh Dichtungsanordnung
WO2012167958A1 (fr) * 2011-06-07 2012-12-13 Schaeffler Technologies AG & Co. KG Cloche de boîtier possédant un accumulateur de pression intégré qui comporte un couvercle bordé
US9309790B2 (en) 2011-06-07 2016-04-12 Schaeffler Technologies AG & Co. KG Housing bell with integrated pressure accumulator having a flanged cover

Also Published As

Publication number Publication date
DE102009024482A1 (de) 2010-12-16
CN101922322B (zh) 2013-08-21
EP2267282B1 (fr) 2015-09-30
HUE027187T2 (en) 2016-10-28
CN101922322A (zh) 2010-12-22

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