EP2414644A1 - Cam shaft adjuster and method for adjusting the angle-of-rotation position of a cam shaft relative to a crankshaft - Google Patents

Cam shaft adjuster and method for adjusting the angle-of-rotation position of a cam shaft relative to a crankshaft

Info

Publication number
EP2414644A1
EP2414644A1 EP10709492A EP10709492A EP2414644A1 EP 2414644 A1 EP2414644 A1 EP 2414644A1 EP 10709492 A EP10709492 A EP 10709492A EP 10709492 A EP10709492 A EP 10709492A EP 2414644 A1 EP2414644 A1 EP 2414644A1
Authority
EP
European Patent Office
Prior art keywords
pressure oil
camshaft adjuster
pressure
chamber
chambers
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP10709492A
Other languages
German (de)
French (fr)
Other versions
EP2414644B1 (en
Inventor
Dirk Heintzen
Matthias Friedrichs
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP2414644A1 publication Critical patent/EP2414644A1/en
Application granted granted Critical
Publication of EP2414644B1 publication Critical patent/EP2414644B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34483—Phaser return springs

Definitions

  • the invention relates to a camshaft adjuster according to the preamble of claim 1. Furthermore, the invention relates to a method for adjusting the rotational angle position of a camshaft relative to a crankshaft for an internal combustion engine, in particular according to the preamble of claim 12.
  • DE 100 84 408 B4 discloses a vane-type camshaft adjuster, the drive element of which is driven by a crankshaft in the form of a drive gear via a traction means such as a chain or a belt.
  • a traction means such as a chain or a belt.
  • Rotationally connected to the drive wheel is a "stator" in which a rotor is rotatably arranged to generate a control angle.
  • the rotor is rotatably connected to a camshaft.
  • a relative angular position between the camshaft and the drive wheel and thus the crankshaft can be influenced, which is accompanied by a change in the control times.
  • the rotor has vanes which are slidable in the circumferential direction to generate a set angle in accordance with a hydraulic pressure in control chambers of the stator.
  • the stator On the side facing away from the camshaft, the stator is formed with a disc which limits the control chambers in the axial direction.
  • the force relationships between the rotor and stator are influenced by a torsion spring whose bases are supported on the one hand on the stator and on the other hand on the rotor.
  • the torsion spring is on the side of the disk facing away from the rotor. Be arranged with several turns around the longitudinal axis.
  • the radially outer foot is supported relative to the stator via screws, which serve at the same time a mounting of the disc in the stator.
  • the radially inner base of the torsion spring is bent in a U-shape and engages positively a rectangular partial cross section of a support element.
  • the support member further includes a cylindrical extension for extending therethrough through a central bore of the disc while permitting relative rotation therethrough. The extension is rotatably connected in the stator with the camshaft, in particular via an end face of the rotor.
  • a designated in the document as a locking pin pin is slidably guided parallel to the longitudinal axis of the camshaft adjuster in a bore of the rotor, wherein the axial position of the pin can be influenced by the force relationships of a compression spring and / or the hydraulic conditions in the region of the end surfaces of the pin.
  • the disc of the stator has a corresponding, oriented in the axial direction blind hole-shaped recess. For an activated position of the pin, in particular a start, intermediate, middle, early or late position, the pin exits with an end portion of the rotor and into the recess of the disc of the stator, so that the rotation free level between rotor and stator is limited.
  • the present invention has for its object to provide a camshaft adjuster, which has a particularly low oil requirement. Another object of the invention is to specify a corresponding method for adjusting the rotational angle position of a camshaft relative to a crankshaft.
  • the object directed to a camshaft adjuster is achieved by specifying a camshaft adjuster for adjusting the rotational angle position of a camshaft relative to a crankshaft, with at least two working chambers, to which pressure oil can be fed to change the rotational angle position, wherein at least one of the working chambers is dependent on an operating parameter by shutting off the pressure oil supply can be switched off.
  • the invention is based on the recognition that the pressure transmission, which is based on the torque mediated by the pressure oil for rotating the camshaft, is largely determined by conditions at a low pressure.
  • the pressure ratio of a camshaft adjuster is chosen so that even at a low engine oil pressure still a safe adjustment is possible.
  • the pressure ratio results from the size and number of working chambers and the size of the acting surfaces of the adjusting elements, so in a diegelzellenversteller the wing surfaces.
  • the actuating torque exceeds a value that would actually be sufficient for safe and sufficiently fast adjustment.
  • resources are given away at higher oil pressure.
  • the camshaft adjuster is designed in vane-type construction, wherein each working chamber is divided by a respective wing in two sub-chambers and wherein the pressure oil is supplied depending on the desired direction of change in the angular position of one of the two chambers so that this sub-chamber increases and the second sub-chamber is reduced , Due to the fact that, in the case of a vane-cell adjuster, a division into a plurality of working chambers is provided anyway, this design is particularly suitable for adapting it to an operating state by the possibility of switching off a working chamber.
  • the pressure oil supply can be shut off by a control element whose position is determined by the pressure of the pressure oil.
  • the actuating body has a return spring, the spring force of the adjusting action of the pressure oil is directed opposite.
  • This configuration results in a particularly simple mechanism for switching off the working chamber.
  • the rising pressure of the pressure oil acts directly on the adjusting body so that it prevents the supply of pressure oil in the working chamber from a certain pressure.
  • To set the Abschaltutes for the pressure is the restoring force of a spring.
  • a short-circuiting pressure oil connection between the two subchambers of this working chamber is preferably produced at the same time. This will ensure that the shut-off working chamber is not inadmissible due to the oil still in it. Delay the adjustment process causes.
  • the short-circuiting pressurized oil connection allows movement of the actuator, driven by the still active other working chambers, within the shut-off working chamber. The actuator displaces over the short circuit oil between the two sub-chambers of the working chamber without being unduly slowed down. More preferably, the shutdown of the working chamber and the Druckölkurz gleich is effected simultaneously by a control body.
  • At least two working chambers can be switched off, wherein the first working chamber can be switched off at a second value of the operating parameter and the second working chamber can be switched off at a second value of the operating parameter that is greater than the first value.
  • the shut-off mechanism as described above with actuator and return spring, this stage adjustment can be realized in a simple manner that a separate shut-off mechanism is provided with each different strong return spring for each working chamber.
  • Preferred dimensions of the actuator is double-acting executed so that, depending on the direction of change in the angular position, the working chamber can be switched off either by shutting off the pressure oil supply to the first or the second sub-chamber. There is thus provided a mechanism by which both the first and the second sub-chamber can be switched off. Thus, a shutdown of the working chamber can be achieved for both possible adjustment directions with a single shut-off.
  • a locking mechanism is provided, by which an adjustment of the rotational angle position can be blocked, wherein by the Verhegelungs- mechanism and the shut-off of the pressure oil supply is adjustable. More preferably, the locking mechanism unlocks at a first oil pressure against the force of a first spring and locks at a second, higher oil pressure against the force of a second spring, the pressure oil supply.
  • the locking mechanism unlocks at a first oil pressure against the force of a first spring and locks at a second, higher oil pressure against the force of a second spring, the pressure oil supply.
  • the object directed to a method is achieved by specifying a method for adjusting the rotational angle position of a Nockenwel- Ie relative to a crankshaft, in which a camshaft adjuster with at least two working chambers for changing the rotational angle position pressure oil is fed into the working chambers, wherein the pressure oil supply to at least one of the working chambers is locked when a predetermined pressure of the pressure oil is exceeded, while the pressure oil supply to at least one of the remaining working chambers remains open.
  • FIG. 1 shows a camshaft adjuster in a semi-longitudinal section in a three-dimensional representation
  • FIG. 2 shows a rotor of a camshaft adjuster
  • Figure 3 shows a cross section through a rotor of a camshaft adjuster in a three-dimensional representation
  • 4 shows a longitudinal section through a rotor of a camshaft adjuster
  • 5 shows a cross section through a rotor of a camshaft adjuster with a shut-off mechanism
  • FIG. 6A shows a cut-off mechanism with a short-circuit effect for the subchambers
  • Figure 6B is a cross-section of Figure 6A
  • FIG. 7B is a cross-section of FIG. 7A corresponding to FIG. 7C;
  • FIG. 7A shows a double-acting shut-off mechanism with a short-circuit effect for the subchambers
  • FIG. 7B shows a schematic illustration for switching off a working chamber by means of the shutdown device according to FIG. 8A in FIG
  • FIG. 7C shows a schematic illustration for switching off a working chamber by means of the shutdown device according to FIG. 8A in working position;
  • Figure 8 is a shut-off mechanism which is simultaneously formed as a locking mechanism
  • FIG. 1 shows a camshaft adjuster 1.
  • the camshaft adjuster 1 is, for example, a vane-type camshaft adjuster, although in principle any other type of camshaft adjuster can also be used in which the adjustment takes place via the pressure medium supply into a plurality of working chambers.
  • the camshaft adjuster 1 has a drive wheel 2, via which it is in drive connection with a crankshaft.
  • the drive wheel 2 is rotatably connected to a stator 3, which is connected to a pot-like housing 4 and a Housing cover 5 is formed.
  • a stator 3 which is connected to a pot-like housing 4 and a Housing cover 5 is formed.
  • an annular disc 6, which is oriented transversely to a longitudinal axis 7-7 of the camshaft adjuster 1 the limited of the housing 4 and the housing cover 5 interior is divided into two axially adjacent subspaces.
  • the camshaft facing subspace takes in a manner not shown to form control chambers on the wing rotor having 8, which is connected or clamped using a central screw, not shown, with an end-side threaded bore of the camshaft.
  • a torsion spring 16 is interposed, which extends with multiple windings about the longitudinal axis 7-7.
  • the arranged on the side facing away from the camshaft 6 disc space forms an annular, around the longitudinal axis 7-7 encircling annular space 10.
  • the annular space 10 is sealed in the contact area between the housing 4 of the stator 3 and housing cover 5 by interposing a sealing plate 11, which tightening fastening screws 12 between housing 4 and housing cover 5 can be tightened.
  • FIG. 2 shows the rotor 8 of a camshaft adjuster 1.
  • the rotor 8 has five wings 21 on its outer circumference. Each of these blades 21 is arranged in a working chamber 41, not shown here, which are formed by the stator 2, not shown, and the rotor 8.
  • a wing 21 divides its respective working chamber into two sub-chambers 41 A, 41 B. The working and sub-chambers are shown schematically later in FIG.
  • Each sub-chamber 41 A, 41 B is fed through an oil channel 29, 31 oil or it can be emptied through this oil passage 29, 31.
  • FIG 3 we see in cross-section through the rotor of Figure 2, as a shut-off mechanism is advantageously removed.
  • a control element 35 is pressed by means of a spring 33 which is seated on a spring carrier 26 in a basic position and releases the oil passage 29 for a supply of oil into a sub-chamber 41 A by means of an annular groove 36 arranged in the surface of the actuating body. From the oil channel 29 branches off a bypass 37, which opens into a recess 39. When supply of pressure oil through the oil passage 29, a force is thus exerted on the actuating body 35, which is directed against the spring force of the spring 33 against this recess 39.
  • the adjusting body 35 is displaced against the spring force and closes gradually the oil channel 29 by the displacement of the opening annular groove 36, until finally the oil supply is cut off and the working chamber 41 is thus switched off.
  • the value for the oil pressure at which the shutdown is done by the choice of the spring constant of the spring 33 easily adjustable. According to the embodiment in FIG. 2, two working chambers can be switched off in this way. In this case, the spring constant of the first shut-off mechanism 25 is selected smaller than the spring constant of the otherwise identical second shut-off mechanism 27.
  • each one shut-off mechanism 25 is arranged in each case a sub-chamber 41 a, 41 B according to the respective adjustment direction once on a front side and once on the back of the rotor 8.
  • FIG. 6A shows in a cross section a further embodiment of the shut-off mechanism, whereby here, as shown schematically in FIG. 6B, only a single shut-off mechanism is provided for both sub-chambers 41A, 41B.
  • the adjusting body 35 has an annular groove 67 so that upon displacement of the actuating body 35 by increasing oil pressure, the oil supply from an oil passage 51 cut and at the same time a short-circuit line 65 is opened, which connects the two sub-chambers 41 A, 41 B fluidly with each other.
  • the working chamber 41 is switched off, but at the same time, despite a lack of outflow of oil from the working chamber, prevents the wing 21 from being hydraulically clamped.
  • An adjustment via the action of the other working chambers 41 is still possible, since the oil in the disconnected working chamber 41 via the short-circuit connection 65 from a sub-chamber 41 A, 41 B in the other sub-chamber 41 A, 41 B can be displaced.
  • the shutdown mechanism of Figure 6A is advantageously carried out double-acting so that a shutdown is possible for both adjustment directions.
  • This is shown in FIG.
  • the actuating body is now arranged between two springs 33 and has a plurality of grooves 67 A, 67 B so that in both directions of displacement blocking the oil supply once to the sub-chamber 41 A and the other times to the sub-chamber 41 B takes place, in both cases with the blocking of the oil supply and thus the shutdown of the working chamber 41, a short-circuit connection 65 between the sub-chambers 41 A, 41 B is set.
  • the switching state “working chamber in operation” is shown in FIG. 7C and the switching state “working chamber switched off” is shown schematically in FIG. 7B.
  • FIG. 8 shows a further embodiment of a shut-off mechanism 25, wherein only the part of the spring 33 and the spring carrier 26 are shown.
  • a locking pin 73 which is against the spring force of a locking spring 71 at a first oil pressure from a arranged in a side cover 77 locking link 75th unlocked and thus releases the camshaft adjuster for adjustment.
  • the shut-off mechanism 25 is therefore structurally connected in a simple manner to a locking mechanism.

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

Abstract

The invention relates to a cam shaft adjuster (1) for adjusting the angle-of-rotation positions of a cam shaft relative to a crankshaft, having at least two operating chambers (41) to which pressure oil can be supplied to change the angle-of-rotation position, wherein at least one of the operating chambers (41) can be deactivated depending on an operating parameter by blocking the pressure oil supply.

Description

Bezeichnung der Erfindung Name of the invention
Nockenwellenversteller und Verfahren zur Verstellung der Drehwinkellage einerCamshaft adjuster and method for adjusting the angular position of a
Nockenwelle relativ zu einer KurbelwelleCamshaft relative to a crankshaft
Beschreibungdescription
Gebiet der ErfindungField of the invention
Die Erfindung betrifft einen Nockenwellenversteller gemäß dem Oberbegriff des Anspruchs 1. Weiterhin betrifft die Erfindung ein Verfahren zur Verstellung der Drehwinkellage einer Nockenwelle relativ zu einer Kurbelwelle für eine Brennkraftmaschine, insbesondere gemäß dem Oberbegriff des Anspruchs 12.The invention relates to a camshaft adjuster according to the preamble of claim 1. Furthermore, the invention relates to a method for adjusting the rotational angle position of a camshaft relative to a crankshaft for an internal combustion engine, in particular according to the preamble of claim 12.
Hintergrund der ErfindungBackground of the invention
Aus DE 100 84 408 B4 ist ein Nockenwellenversteller in Flügelzellenbauweise bekannt, dessen Antriebselement in Form eines Antriebszahnrads über ein Zugmittel wie eine Kette oder einen Riemen von einer Kurbelwelle angetrieben wird. Drehfest mit dem Antriebsrad verbunden ist ein "Stator", in dem ein Rotor verdrehbar zur Erzeugung eines Stellwinkels angeordnet ist. Der Rotor ist drehfest mit einer Nockenwelle verbunden. Nach Maßgabe des Stellwinkels kann eine relative Winkellage zwischen Nockenwelle und Antriebsrad und damit Kurbelwelle beeinflusst werden, was mit einer Veränderung der Steuerzei- ten einhergeht. Für eine Ausbildung in Flügelzellenbauweise besitzt der Rotor Flügel, die nach Maßgabe eines Hydraulikdrucks in Steuerkammern des Stators in Umfangsrichtung zur Erzeugung eines Stellwinkels verschieblich sind. Auf der der Nockenwelle abgewandten Seite ist der Stator mit einer Scheibe ausgebildet, die die Steuerkammern in axialer Richtung begrenzt. Die Kraftver- hältnisse zwischen Rotor und Stator können zusätzlich zu den Hydraulikverhältnissen im Bereich der Flügel beeinflusst durch eine Torsionsfeder, deren Fußpunkte sich einerseits an dem Stator und andererseits an dem Rotor abstützen. Die Torsionsfeder ist auf der dem Rotor abgewandten Seite der Schei- be angeordnet mit mehreren Windungen um die Längsachse. Der radial außenliegende Fußpunkt ist gegenüber dem Stator über Schrauben abgestützt, die gleichzeitig einer Befestigung der Scheibe in dem Stator dienen. Der radial innenliegende Fußpunkt der Torsionsfeder ist U-förmig gebogen und umgreift formschlüssig einen rechteckigen Teilquerschnitt eines Abstützelements. Das Abstützelement weist weiterhin einen zylinderförmigen Fortsatz auf, mit dem sich dieses durch eine zentrale Bohrung der Scheibe unter Ermöglichung einer relativen Verdrehung hindurch erstreckt. Der Fortsatz ist in dem Stator drehfest mit der Nockenwelle, insbesondere über eine Stirnseite des Rotors, verbunden.DE 100 84 408 B4 discloses a vane-type camshaft adjuster, the drive element of which is driven by a crankshaft in the form of a drive gear via a traction means such as a chain or a belt. Rotationally connected to the drive wheel is a "stator" in which a rotor is rotatably arranged to generate a control angle. The rotor is rotatably connected to a camshaft. Depending on the setting angle, a relative angular position between the camshaft and the drive wheel and thus the crankshaft can be influenced, which is accompanied by a change in the control times. For a vane-type construction, the rotor has vanes which are slidable in the circumferential direction to generate a set angle in accordance with a hydraulic pressure in control chambers of the stator. On the side facing away from the camshaft, the stator is formed with a disc which limits the control chambers in the axial direction. In addition to the hydraulic conditions in the area of the vanes, the force relationships between the rotor and stator are influenced by a torsion spring whose bases are supported on the one hand on the stator and on the other hand on the rotor. The torsion spring is on the side of the disk facing away from the rotor. Be arranged with several turns around the longitudinal axis. The radially outer foot is supported relative to the stator via screws, which serve at the same time a mounting of the disc in the stator. The radially inner base of the torsion spring is bent in a U-shape and engages positively a rectangular partial cross section of a support element. The support member further includes a cylindrical extension for extending therethrough through a central bore of the disc while permitting relative rotation therethrough. The extension is rotatably connected in the stator with the camshaft, in particular via an end face of the rotor.
Ein in der Druckschrift als Verriegelungspin bezeichneter Pin ist in einer Bohrung des Rotors parallel zu der Längsachse des Nockenwellenverstellers verschieblich geführt, wobei die axiale Position des Pins durch die Kraftverhältnisse einer Druckfeder und/oder die Hydraulikverhältnisse im Bereich von Stirn- flächen des Pins beeinflussbar ist. Die Scheibe des Stators besitzt eine korrespondierende, in axialer Richtung orientierte sacklochförmige Ausnehmung. Für eine aktivierte Stellung des Pins, insbesondere eine Start-, Zwischen-, Mitten-, Früh- oder Spät-Position, tritt der Pin mit einem Endbereich aus dem Rotor aus und in die Ausnehmung der Scheibe des Stators ein, so dass der Drehfrei- heitsgrad zwischen Rotor und Stator begrenzt ist. A designated in the document as a locking pin pin is slidably guided parallel to the longitudinal axis of the camshaft adjuster in a bore of the rotor, wherein the axial position of the pin can be influenced by the force relationships of a compression spring and / or the hydraulic conditions in the region of the end surfaces of the pin. The disc of the stator has a corresponding, oriented in the axial direction blind hole-shaped recess. For an activated position of the pin, in particular a start, intermediate, middle, early or late position, the pin exits with an end portion of the rotor and into the recess of the disc of the stator, so that the rotation free level between rotor and stator is limited.
Aufgabe der ErfindungObject of the invention
Der vorliegenden Erfindung liegt die Aufgabe zugrunde, einen Nockenwellen- versteller anzugeben, der einen besonders niedrigen Ölbedarf aufweist. Weite- re Aufgabe der Erfindung ist die Angabe eines entsprechenden Verfahrens zur Verstellung der Drehwinkellage einer Nockenwelle gegenüber einer Kurbelwelle.The present invention has for its object to provide a camshaft adjuster, which has a particularly low oil requirement. Another object of the invention is to specify a corresponding method for adjusting the rotational angle position of a camshaft relative to a crankshaft.
Zusammenfassung der ErfindungSummary of the invention
Erfindungsgemäß wird die einen Nockenwellenversteller gerichtete Aufgabe gelöst durch Angabe eines Nockenwellenverstellers zur Verstellung der Drehwinkellage einer Nockenwelle relativ zu einer Kurbelwelle, mit mindestens zwei Arbeitskammern, denen zur Änderung der Drehwinkellage Drucköl zuführbar ist, wobei mindestens eine der Arbeitskammern abhängig von einem Betriebsparameter durch Absperren der Druckölzufuhr abschaltbar ist.According to the invention, the object directed to a camshaft adjuster is achieved by specifying a camshaft adjuster for adjusting the rotational angle position of a camshaft relative to a crankshaft, with at least two working chambers, to which pressure oil can be fed to change the rotational angle position, wherein at least one of the working chambers is dependent on an operating parameter by shutting off the pressure oil supply can be switched off.
Die Erfindung geht von der Erkenntnis aus, dass das die Druckübersetzung, die der durch das Drucköl vermittelte Drehmoment zur Verdrehung der No- ckenwelle zugrunde liegt, maßgeblich durch Verhältnisse bei einem niederigen Druck bestimmt wird. Die Druckübersetzung eines Nockenwellenverstellers wird so gewählt, dass auch bei einem niedrigen Motoröldruck noch eine sichere Verstellung möglich ist. Die Druckübersetzung ergibt sich dabei aus Größe und Anzahl der Arbeitskammern sowie der Größe der wirkenden Flächen der Stellelemente, also bei einem Flügelzellenversteller die Flügelflächen. Bei steigendem Motoröldruck kommt es somit zu einem höheren Stellmoment. Dabei übersteigt das Stellmoment einen Wert, der eigentlich zur sicheren und ausreichend schnellen Verstellung ausreichend wäre. Somit werden durch Festlegung des Bedarfs bei niedrigem Öldruck Ressourcen bei höherem Öldruck verschenkt. Insbesondere ist man bestrebt, die Ölpumpe eines Verbrennungsmotors so klein wie möglich auszulegen, was durch den Bedarf der Ölverbraucher begrenzt wird. Ein niedrigerer Ölbedarf bei der Nockenwellenverstellung wäre somit vorteilhaft. Dies erreicht die Erfindung nunmehr dadurch, dass mindestens eine der Arbeitskammern des Nockenwellenverstellers abschaltbar gestaltet wird. Abhängig von einem Betriebsparameter, insbesondere dem Öldruck, wird also die Ölzufuhr zu einer der Arbeitskammern unterbunden und dadurch der Ölbedarf reduziert. In einem Betriebszustand, in dem das bereitgestellte Drehmoment zur Verstellung der Nockenwelle auch ohne diese Arbeitskammer ausreicht, führt die Reduktion der Ölmenge zu keiner Beeinträchtigung des Betriebs.The invention is based on the recognition that the pressure transmission, which is based on the torque mediated by the pressure oil for rotating the camshaft, is largely determined by conditions at a low pressure. The pressure ratio of a camshaft adjuster is chosen so that even at a low engine oil pressure still a safe adjustment is possible. The pressure ratio results from the size and number of working chambers and the size of the acting surfaces of the adjusting elements, so in a Flügelzellenversteller the wing surfaces. As the engine oil pressure rises, a higher actuating torque thus occurs. The actuating torque exceeds a value that would actually be sufficient for safe and sufficiently fast adjustment. Thus, by setting the demand at low oil pressure, resources are given away at higher oil pressure. In particular, it is endeavored to design the oil pump of an internal combustion engine as small as possible, which is limited by the need of the oil consumers. A lower oil requirement in the camshaft adjustment would thus be advantageous. This is achieved by the invention now characterized in that at least one of the working chambers of the camshaft adjuster is designed to be switched off. Depending on an operating parameter, in particular the oil pressure, so the oil supply to one of the working chambers is suppressed and thereby reduces the oil demand. In an operating state in which the torque provided for adjusting the camshaft is sufficient even without this working chamber, the reduction of the oil amount does not affect the operation.
Vorteilhafterweise ist der Nockenwellenversteller in Flügelzellenbauweise ausgeführt, wobei jede Arbeitskammer durch jeweils einen Flügel in zwei Teilkammern aufgeteilt ist und wobei das Drucköl je nach gewünschter Richtung der Änderung der Drehwinkellage einer der beiden Kammern so zugeführt wird, dass diese Teilkammer vergrößert und die zweite Teilkammer verkleinert wird. Dadurch, dass bei einem Flügelzellenversteller ohnehin eine Aufteilung in mehrere Arbeitskammern vorgesehen ist, ist diese Bauweise besonders geeignet, sie durch die Möglichkeit eines Abschaltens einer Arbeitskammer auf einen Betriebszustand anzupassen.Advantageously, the camshaft adjuster is designed in vane-type construction, wherein each working chamber is divided by a respective wing in two sub-chambers and wherein the pressure oil is supplied depending on the desired direction of change in the angular position of one of the two chambers so that this sub-chamber increases and the second sub-chamber is reduced , Due to the fact that, in the case of a vane-cell adjuster, a division into a plurality of working chambers is provided anyway, this design is particularly suitable for adapting it to an operating state by the possibility of switching off a working chamber.
Vorzugsweise ist die Druckölzufuhr durch einen Stellkörper absperrbar, dessen Stellposition durch den Druck des Drucköls bestimmt wird. Weiter bevorzugt weist der Stellkörper eine Rückstellfeder auf, deren Federkraft der Stellwirkung des Drucköls entgegengerichtet ist. Durch diese Ausgestaltung ergibt sich ein besonders einfacher Mechanismus zum Abschalten der Arbeitskammer. Hier wirkt der steigende Druck des Drucköls unmittelbar auf den Stellkörper so, dass dieser ab einem bestimmten Druck die Zufuhr von Drucköl in die Arbeitskammer unterbindet. Zur Einstellung des Abschaltwertes für den Druck dient die Rückstell kraft einer Feder.Preferably, the pressure oil supply can be shut off by a control element whose position is determined by the pressure of the pressure oil. More preferably, the actuating body has a return spring, the spring force of the adjusting action of the pressure oil is directed opposite. This configuration results in a particularly simple mechanism for switching off the working chamber. Here, the rising pressure of the pressure oil acts directly on the adjusting body so that it prevents the supply of pressure oil in the working chamber from a certain pressure. To set the Abschaltwertes for the pressure is the restoring force of a spring.
Bevorzugt wird bei einem Abschalten der Arbeitskammer gleichzeitig eine kurzschließende Druckölverbindung zwischen den beiden Teilkammern dieser Arbeitskammer hergestellt. Hierdurch wird sichergestellt, dass die abgeschaltete Arbeitskammer durch das weiterhin in ihr befindliche Öl keine unzulässige Ver- zögerung des Verstellvorgangs bewirkt. Die kurzschließende Druckölverbin- dung ermöglicht die Bewegung des Stellelementes, getrieben durch die weiterhin aktiven anderen Arbeitskammern, innerhalb der abgeschalteten Arbeits- kammer. Das Stellelement verschiebt dabei über den Kurzschluss Öl zwischen den beiden Teilkammern der Arbeitskammer ohne hierdurch unzulässig stark abgebremst zu werden. Weiter bevorzugt wird die Abschaltung der Arbeitskammer und der Druckölkurzschluss gleichzeitig durch einen Stellkörper bewirkt.At a shutdown of the working chamber, a short-circuiting pressure oil connection between the two subchambers of this working chamber is preferably produced at the same time. This will ensure that the shut-off working chamber is not inadmissible due to the oil still in it. Delay the adjustment process causes. The short-circuiting pressurized oil connection allows movement of the actuator, driven by the still active other working chambers, within the shut-off working chamber. The actuator displaces over the short circuit oil between the two sub-chambers of the working chamber without being unduly slowed down. More preferably, the shutdown of the working chamber and the Druckölkurzschluss is effected simultaneously by a control body.
Vorzugsweise sind mindestens zwei Arbeitskammern abschaltbar, wobei die erste Arbeitskammer bei einem ersten Wert des Betriebsparameters und die zweite Arbeitskammer bei einem zweiten, gegenüber dem ersten Wert größeren Wert des Betriebsparameters abschaltbar ist. Durch diese Ausgestaltung ist es möglich, eine noch feinere Anpassung des benötigten Ölbedarfs an den jeweiligen Betriebszustand vorzunehmen. Mit steigendem Druck und damit auch steigendem verfügbaren Drehmoment für den Verstellvorgang kann zunächst eine erste Arbeitskammer und dann eine zweite oder sogar weitere Kammern abgeschaltet werden. Bei einer Ausgestaltung des Abschaltmechanismus wie oben beschrieben mit Stellkörper und Rückstellfeder kann diese stufige Anpassung in einfacher Weise dadurch realisiert werden, dass für jede Arbeitskammer ein eigener Abschaltmechanismus mit jeweils unterschiedlich starker Rückstellfeder vorgesehen ist.Preferably, at least two working chambers can be switched off, wherein the first working chamber can be switched off at a second value of the operating parameter and the second working chamber can be switched off at a second value of the operating parameter that is greater than the first value. With this configuration, it is possible to make an even finer adjustment of the required oil consumption to the respective operating state. With increasing pressure and thus also increasing available torque for the adjustment operation, first a first working chamber and then a second or even further chambers can be switched off. In one embodiment of the shut-off mechanism as described above with actuator and return spring, this stage adjustment can be realized in a simple manner that a separate shut-off mechanism is provided with each different strong return spring for each working chamber.
Bevorzugtermaßen ist der Stell körper doppelwirkend so ausgeführt ist, dass je nach Richtung der Änderung der Drehwinkellage die Arbeitskammer entweder durch Absperren der Druckölzufuhr zur ersten oder zur zweiten Teilkammer abschaltbar ist. Es wird somit ein Mechanismus bereitgestellt, durch den sowohl die erste als auch die zweite Teilkammer abschaltbar sind. Damit kann für beide möglichen Stellrichtungen mit einem einzigen Abschaltmechanismus ein Abschalten der Arbeitskammer erreicht werden.Preferred dimensions of the actuator is double-acting executed so that, depending on the direction of change in the angular position, the working chamber can be switched off either by shutting off the pressure oil supply to the first or the second sub-chamber. There is thus provided a mechanism by which both the first and the second sub-chamber can be switched off. Thus, a shutdown of the working chamber can be achieved for both possible adjustment directions with a single shut-off.
Vorzugsweise ist ein Verriegelungsmechanismus vorgesehen, durch den eine Verstellung der Drehwinkellage sperrbar ist, wobei durch den Verhegelungs- mechanismus auch die Absperrung der Druckölzufuhr einstellbar ist. Weiter bevorzugt entriegelt der Verriegelungsmechanismus bei einem ersten Öldruck gegen die Kraft einer ersten Feder und sperrt bei einem zweiten, höheren Öldruck gegen die Kraft einer zweiten Feder die Druckölzufuhr. Somit wird durch einen einzigen Mechanismus sowohl eine Verriegelung des Versteller als auch die Abschaltung der Arbeitskammer bewirkt.Preferably, a locking mechanism is provided, by which an adjustment of the rotational angle position can be blocked, wherein by the Verhegelungs- mechanism and the shut-off of the pressure oil supply is adjustable. More preferably, the locking mechanism unlocks at a first oil pressure against the force of a first spring and locks at a second, higher oil pressure against the force of a second spring, the pressure oil supply. Thus, both a locking of the stage and the shutdown of the working chamber is effected by a single mechanism.
Erfindungsgemäß wird die auf ein Verfahren gerichtete Aufgabe gelöst durch Angabe eines Verfahrens zur Verstellung der Drehwinkellage einer Nockenwel- Ie relativ zu einer Kurbelwelle, bei dem einem Nockenwellenversteller mit mindestens zwei Arbeitskammern zur Änderung der Drehwinkellage Drucköl in die Arbeitskammern zuführbar ist, wobei die Druckölzufuhr zu mindestens einer der Arbeitskammern bei Überschreiten eines vorgegebenen Druckes des Drucköls gesperrt wird, während die Druckölzufuhr zu mindestens einer der verbleiben- den Arbeitskammern offen bleibt.According to the invention, the object directed to a method is achieved by specifying a method for adjusting the rotational angle position of a Nockenwel- Ie relative to a crankshaft, in which a camshaft adjuster with at least two working chambers for changing the rotational angle position pressure oil is fed into the working chambers, wherein the pressure oil supply to at least one of the working chambers is locked when a predetermined pressure of the pressure oil is exceeded, while the pressure oil supply to at least one of the remaining working chambers remains open.
Die Vorteile eines solchen Verfahrens entsprechen den Vorteilen des oben beschriebenen Nockenwellenverstellers.The advantages of such a method correspond to the advantages of the camshaft adjuster described above.
Ausführliche Beschreibung der ErfindungDetailed description of the invention
Die Erfindung wird beispielhaft anhand der Zeichnung näher erläutert. Es zeigen:The invention will be explained in more detail by way of example with reference to the drawing. Show it:
Figur 1 einen Nockenwellenversteller in einem Halblängsschnitt in räumlicher Darstellung;1 shows a camshaft adjuster in a semi-longitudinal section in a three-dimensional representation;
Figur 2 einen Rotor eines Nockenwellenverstellers;FIG. 2 shows a rotor of a camshaft adjuster;
Figur 3 einen Querschnitt durch einen Rotor eines Nockenwellenverstellers in räumlicher Darstellung;Figure 3 shows a cross section through a rotor of a camshaft adjuster in a three-dimensional representation;
Figur 4 einen Längsschnitt durch einen Rotor eines Nockenwellenverstellers; Figur 5 einen Querschnitt durch einen Rotor eines Nockenwellenverstellers mit einem Abschaltmechanismus;4 shows a longitudinal section through a rotor of a camshaft adjuster; 5 shows a cross section through a rotor of a camshaft adjuster with a shut-off mechanism;
Figur 6A einen Abschaltmechanismus mit Kurzschlusswirkung für die Teilkammern;FIG. 6A shows a cut-off mechanism with a short-circuit effect for the subchambers;
Figur 6B ein Querschnitt von 6A; Figur 7B: ein Querschnitt von 7A entsprechend Figur 7C;Figure 6B is a cross-section of Figure 6A; FIG. 7B is a cross-section of FIG. 7A corresponding to FIG. 7C;
Figur 7A einen doppelt wirkenden Abschaltmechanismus mit Kurzschlusswirkung für die Teilkammern;FIG. 7A shows a double-acting shut-off mechanism with a short-circuit effect for the subchambers;
Figur 7B eine schematische Darstellung zum Abschalten einer Arbeits- kammer mittels der Abschaltvorrichtung gemäß der Figur 8A inFIG. 7B shows a schematic illustration for switching off a working chamber by means of the shutdown device according to FIG. 8A in FIG
Abschaltstellung;off position;
Figur 7C eine schematische Darstellung zum Abschalten einer Arbeitskammer mittels der Abschaltvorrichtung gemäß der Figur 8A in Arbeitsstellung;FIG. 7C shows a schematic illustration for switching off a working chamber by means of the shutdown device according to FIG. 8A in working position;
Figur 8 ein Abschaltmechanismus der gleichzeitig als Verriegelungsmechanismus ausgebildet ist;Figure 8 is a shut-off mechanism which is simultaneously formed as a locking mechanism;
Figur 1 zeigt einen Nockenwellenversteller 1. Bei dem Nockenwellenversteller 1 handelt es sich beispielhaft um einen Nockenwellenversteller in Flügelzellenbauweise, obwohl grundsätzlich auch jeder andere Typ eines Nockenwellenverstellers einsetzbar ist, bei dem die Verstellung über die Druckmittelzufuhr in mehrere Arbeitskammern erfolgt.FIG. 1 shows a camshaft adjuster 1. The camshaft adjuster 1 is, for example, a vane-type camshaft adjuster, although in principle any other type of camshaft adjuster can also be used in which the adjustment takes place via the pressure medium supply into a plurality of working chambers.
Der Nockenwellenversteller 1 besitzt ein Antriebsrad 2, über das dieser in Antriebsverbindung mit einer Kurbelwelle steht. Das Antriebsrad 2 ist drehfest an einen Stator 3 angebunden, der mit einem topfartigen Gehäuse 4 und einem Gehäusedeckel 5 gebildet ist. Über eine kreisringförmige Scheibe 6, die quer zu einer Längsachse 7-7 des Nockenwellenverstellers 1 orientiert ist, ist der von Gehäuse 4 und Gehäusedeckel 5 begrenzte Innenraum aufgeteilt in zwei axial nebeneinander liegende Teilräume. Der der Nockenwelle zugewandte Teilraum nimmt in nicht dargestellter Weise unter Ausbildung von Steuerkammern den Flügel aufweisenden Rotor 8 auf, der unter Verwendung einer nicht dargestellten Zentralschraube mit einer stirnseitigen Gewindebohrung der Nockenwelle verbunden oder verspannt ist. Zwischen Stator 3 und Rotor 8 ist eine Torsionsfeder 16 zwischengeschaltet, die sich mit mehrfachen Windungen um die Längsachse 7-7 erstreckt. Der auf der der Nockenwelle abgewandten Seite der Scheibe 6 angeordnete Teilraum bildet einen ringförmigen, um die Längsachse 7-7 umlaufenden Ringraum 10. Der Ringraum 10 ist im Kontaktbereich zwischen Gehäuse 4 des Stators 3 und Gehäusedeckel 5 abgedichtet durch Zwischenschaltung eines Dichtblechs 11 , welches über ein Anziehen von Be- festigungsschrauben 12 zwischen Gehäuse 4 und Gehäusedeckel 5 verspannt werden kann.The camshaft adjuster 1 has a drive wheel 2, via which it is in drive connection with a crankshaft. The drive wheel 2 is rotatably connected to a stator 3, which is connected to a pot-like housing 4 and a Housing cover 5 is formed. About an annular disc 6, which is oriented transversely to a longitudinal axis 7-7 of the camshaft adjuster 1, the limited of the housing 4 and the housing cover 5 interior is divided into two axially adjacent subspaces. The camshaft facing subspace takes in a manner not shown to form control chambers on the wing rotor having 8, which is connected or clamped using a central screw, not shown, with an end-side threaded bore of the camshaft. Between stator 3 and rotor 8, a torsion spring 16 is interposed, which extends with multiple windings about the longitudinal axis 7-7. The arranged on the side facing away from the camshaft 6 disc space forms an annular, around the longitudinal axis 7-7 encircling annular space 10. The annular space 10 is sealed in the contact area between the housing 4 of the stator 3 and housing cover 5 by interposing a sealing plate 11, which tightening fastening screws 12 between housing 4 and housing cover 5 can be tightened.
Figur 2 zeigt den Rotor 8 eines Nockenwellenverstellers 1. Der Rotor 8 weist an seinem Außenumfang fünf Flügel 21 auf. Jeder dieser Flügel 21 ist in einer hier nicht näher dargestellten Arbeitskammer 41 angeordnet, die durch den nicht dargestellten Stator 2 und den Rotor 8 gebildet werden. Ein Flügel 21 unterteilt seine jeweilige Arbeiterkammer in zwei Teilkammern 41 A, 41 B. Die Arbeits- und Teilkammern sind später in Figur 4 schematisch dargestellt. Jeder Teilkammer 41 A, 41 B ist durch einen Ölkanal 29, 31 Öl zuführbar oder sie ist über diesen Ölkanal 29, 31 entleerbar. Zur Verstellung der Nockenwelle in einer ersten Stellrichtung wird dazu Öl z.B. jeder Teilkammer 41A links von einem Flügel 21 zugeführt, während die jeweils andere Teilkammer 41 B zum Tank hin geöffnet und entleert wird. Bei der umgekehrten, zweiten Stellrichtung erfolgt die umgekehrte Ölzu- bzw. -abfuhr. Das Öl wird dabei aus der Nocken- welle über die Nabe des Rotors zu- bzw. abgeführt. In der Ansicht der Figur 2 sind ein erster Abschaltmechanismus 25 und ein zweiter Abschaltmechanismus 27 sichtbar. Diese Abschaltmechanismen 25, 27 sind jeweils vor den Ölkanal 29, 31 einer Teilkammer 41 A, 41 B geschaltet. Auf der nicht sichtbaren, gege- nüberliegenden Seite des Rotors sind entsprechende Abschaltmechanismen vorgesehen, die für die andere Stellrichtung wirken. Die Funktion der Abschaltmechanismen 25, 27 wird näher anhand der Figur 3 beschrieben.FIG. 2 shows the rotor 8 of a camshaft adjuster 1. The rotor 8 has five wings 21 on its outer circumference. Each of these blades 21 is arranged in a working chamber 41, not shown here, which are formed by the stator 2, not shown, and the rotor 8. A wing 21 divides its respective working chamber into two sub-chambers 41 A, 41 B. The working and sub-chambers are shown schematically later in FIG. Each sub-chamber 41 A, 41 B is fed through an oil channel 29, 31 oil or it can be emptied through this oil passage 29, 31. To adjust the camshaft in a first setting direction, oil is supplied to each sub-chamber 41A to the left of a wing 21, while the other sub-chamber 41 B is opened and emptied to the tank. In the reverse, second direction of adjustment, the reverse Ölzu- or removal takes place. The oil is supplied or removed from the camshaft via the hub of the rotor. In the view of Figure 2, a first shut-off mechanism 25 and a second shut-off mechanism 27 are visible. These shut-off mechanisms 25, 27 are each connected in front of the oil passage 29, 31 of a sub-chamber 41 A, 41 B. On the invisible, gege opposite side of the rotor corresponding cut-off mechanisms are provided, which act for the other direction of adjustment. The function of the shutdown mechanisms 25, 27 will be described in greater detail with reference to FIG.
In Figur 3 wir im Querschnitt durch den Rotor der Figur 2 deutlich, wie ein Abschaltmechanismus vorteilhafterweise ausgebaut ist. Ein Stellkörper 35 wird mittels einer Feder 33, die auf einem Federträger 26 aufsitzt, in eine Grundstellung gedrückt und gibt dabei mittels einer in der Oberfläche des Stellkörpers angeordneten Ringnut 36 den Ölkanal 29 für eine Zufuhr von Öl in eine Teilkammer 41 A frei. Vom Ölkanal 29 zweigt dabei ein Bypass 37 ab, der in eine Ausnehmung 39 mündet. An diese Ausnehmung 39 grenzt der Stellkörper 35. Bei Zufuhr von Drucköl über den Ölkanal 29 wird somit auch eine Kraft auf den Stellkörper 35 ausgeübt, die der Federkraft der Feder 33 entgegen gerichtet ist. Bei steigendem Druck wird der Stellkörper 35 gegen die Federkraft ver- schoben und verschließt dabei durch die Verschiebung der öffnenden Ringnut 36 nach und nach den Ölkanal 29, bis schließlich die Ölzufuhr abgeschnitten und die Arbeitskammer 41 somit abgeschaltet ist. Der Wert für den Öldruck, bei dem das Abschalten erfolgt ist durch die Wahl der Federkonstanten der Feder 33 einfach einstellbar. Gemäß der Ausgestaltung in Figur 2 sind auf diese Weise zwei Arbeitskammern abschaltbar. Dabei wird die Federkonstante des ersten Abschaltmechanismus 25 kleiner gewählt, als die Federkonstante des sonst baugleichen zweiten Abschaltmechanismus 27. Hierdurch kommt es zu einem gestuften Abschalten der beiden Arbeitskammern: Bei einem ersten, niedrigeren Öldruck schaltet die erste Arbeitskammer 41 ab, während bei ei- nem zweiten, höheren Öldruck zusätzlich die zweite Arbeitskammer 41 abgeschaltet wird, auf diese Weise kann angepasst an den Betriebszustand der Ölbedarf eingestellt werden.In Figure 3, we see in cross-section through the rotor of Figure 2, as a shut-off mechanism is advantageously removed. A control element 35 is pressed by means of a spring 33 which is seated on a spring carrier 26 in a basic position and releases the oil passage 29 for a supply of oil into a sub-chamber 41 A by means of an annular groove 36 arranged in the surface of the actuating body. From the oil channel 29 branches off a bypass 37, which opens into a recess 39. When supply of pressure oil through the oil passage 29, a force is thus exerted on the actuating body 35, which is directed against the spring force of the spring 33 against this recess 39. As the pressure increases, the adjusting body 35 is displaced against the spring force and closes gradually the oil channel 29 by the displacement of the opening annular groove 36, until finally the oil supply is cut off and the working chamber 41 is thus switched off. The value for the oil pressure at which the shutdown is done by the choice of the spring constant of the spring 33 easily adjustable. According to the embodiment in FIG. 2, two working chambers can be switched off in this way. In this case, the spring constant of the first shut-off mechanism 25 is selected smaller than the spring constant of the otherwise identical second shut-off mechanism 27. This results in a stepped shutdown of the two working chambers: At a first, lower oil pressure, the first working chamber 41 turns off while at a nem second, higher oil pressure in addition the second working chamber 41 is turned off, in this way can be adjusted adjusted to the operating condition of the oil demand.
In Figur 4 ist erkennbar wie jeweils ein Abschaltmechanismus 25 für jeweils eine Teilkammer 41 a, 41 B entsprechend der jeweiligen Stellrichtung einmal auf einer Vorderseite und einmal auf der Rückseite des Rotors 8 angeordnet ist. In einem Querschnitt ist in Figur 5 noch einmal die Anordnung des Abschaltmechanismus wie oben beschrieben dargestellt. Figur 6A zeigt in einem Querschnitt eine weitere Ausgestaltung des Abschalt- mechanismus, wobei hier, wie in Figur 6B schematisch dargestellt, lediglich ein einziger Abschaltmechanismus für beide Teilkammern 41 A, 41 B vorgesehen ist. Dabei weist der Stellkörper 35 eine Ringnut 67 so auf, dass bei einem Verschieben des Stellkörpers 35 durch steigenden Öldruck die Ölzufuhr aus einem Ölkanal 51 abgeschnitten und gleichzeitig eine Kurzschlussleitung 65 geöffnet wird, die die beiden Teilkammern 41 A, 41 B miteinander strömungstechnisch verbindet. Hierdurch wird einerseits die Arbeitskammer 41 abgeschaltet, gleich- zeitig aber trotz eines fehlenden Abflusses von Öl aus der Arbeitskammer verhindert, dass der Flügel 21 hydraulisch eingespannt wird. Eine Verstellung über die Wirkung der anderen Arbeitskammern 41 ist weiterhin möglich, da das Öl in der abgeschalteten Arbeitskammer 41 über die Kurzschlussverbindung 65 von einer Teilkammer 41 A, 41 B in die andere Teilkammer 41 A, 41 B verdrängt werden kann.In Figure 4 it can be seen how each one shut-off mechanism 25 is arranged in each case a sub-chamber 41 a, 41 B according to the respective adjustment direction once on a front side and once on the back of the rotor 8. In a cross-section, the arrangement of the shut-off mechanism is again shown in Figure 5 as described above. FIG. 6A shows in a cross section a further embodiment of the shut-off mechanism, whereby here, as shown schematically in FIG. 6B, only a single shut-off mechanism is provided for both sub-chambers 41A, 41B. In this case, the adjusting body 35 has an annular groove 67 so that upon displacement of the actuating body 35 by increasing oil pressure, the oil supply from an oil passage 51 cut and at the same time a short-circuit line 65 is opened, which connects the two sub-chambers 41 A, 41 B fluidly with each other. As a result, on the one hand, the working chamber 41 is switched off, but at the same time, despite a lack of outflow of oil from the working chamber, prevents the wing 21 from being hydraulically clamped. An adjustment via the action of the other working chambers 41 is still possible, since the oil in the disconnected working chamber 41 via the short-circuit connection 65 from a sub-chamber 41 A, 41 B in the other sub-chamber 41 A, 41 B can be displaced.
Der Abschaltmechanismus der Figur 6A wird vorteilhafterweise doppelwirkend so ausgeführt, dass für beide Stellrichtungen ein Abschalten möglich ist. Dies ist in Figur 7 dargestellt. Der Stellkörper ist nunmehr zwischen zwei Federn 33 angeordnet und weist mehrere Nuten 67A, 67B so auf, dass in beiden Verschiebungsrichtungen ein Sperren der Ölzufuhr einmal zur Teilkammer 41A und das andere mal zur Teilkammer 41 B erfolgt, wobei in beiden Fällen mit der Sperrung der Ölzufuhr und damit dem Abschalten der Arbeitskammer 41 eine Kurzschlussverbindung 65 zwischen den Teilkammern 41 A, 41 B eingestellt wird. Die Schaltzustand „Arbeitskammer in Betrieb" ist in Figur 7C und der Schaltzustand „Arbeitskammer abgeschaltet" ist in Figur 7B schematisch gezeigt.The shutdown mechanism of Figure 6A is advantageously carried out double-acting so that a shutdown is possible for both adjustment directions. This is shown in FIG. The actuating body is now arranged between two springs 33 and has a plurality of grooves 67 A, 67 B so that in both directions of displacement blocking the oil supply once to the sub-chamber 41 A and the other times to the sub-chamber 41 B takes place, in both cases with the blocking of the oil supply and thus the shutdown of the working chamber 41, a short-circuit connection 65 between the sub-chambers 41 A, 41 B is set. The switching state "working chamber in operation" is shown in FIG. 7C and the switching state "working chamber switched off" is shown schematically in FIG. 7B.
Schließlich zeigt Figur 8 eine weitere Ausgestaltung eines Abschaltmechanis- mus 25, wobei nur der Teil der Feder 33 und des Federträgers 26 gezeigt sind. Mit dem Federträger 26 im Eingriff befindet sich ein Verriegelungspin 73, der gegen die Federkraft einer Verriegelungsfeder 71 bei einem ersten Öldruck aus einer in einem Seitendeckel 77 angeordneten Verriegelungskulisse 75 heraus entriegelt und somit den Nockenwellenversteller für ein Verstellen freigibt. Bei weiter steigendem Öldruck ergibt sich wie in oben beschriebener Weise das Abschalten einer Arbeitskammer 41. der Abschaltmechanismus 25 ist somit in einfacher Weise konstruktiv mit einem Verriegelungsmechanismus verbunden. Finally, FIG. 8 shows a further embodiment of a shut-off mechanism 25, wherein only the part of the spring 33 and the spring carrier 26 are shown. With the spring carrier 26 is engaged a locking pin 73 which is against the spring force of a locking spring 71 at a first oil pressure from a arranged in a side cover 77 locking link 75th unlocked and thus releases the camshaft adjuster for adjustment. As the oil pressure continues to increase, the switching off of a working chamber 41 results, as in the manner described above. The shut-off mechanism 25 is therefore structurally connected in a simple manner to a locking mechanism.
BezugszeichenlisteLIST OF REFERENCE NUMBERS
1 Nockenwellenversteller 73 Verriegelungspin1 Camshaft adjuster 73 Locking pin
2 Antriebsrad 75 Verriegelungskulisse2 drive wheel 75 locking link
3 Stator 77 Seitendeckel3 Stator 77 side cover
4 Gehäuse4 housing
5 Gehäusedeckel5 housing cover
6 Scheibe6 disc
7 Längsachse7 longitudinal axis
8 Rotor8 rotor
10 Ringraum10 annulus
11 Dichtblech11 sealing sheet
12 Befestigungsschraube12 fixing screw
21 Flügel21 wings
25 Abschaltmechanismus25 shut-off mechanism
26 Federträger26 spring carrier
27 Abschaltmechanismus27 shut-off mechanism
29 Ölkanal29 oil channel
31 Ölkanal31 oil channel
33 Feder33 spring
35 Stell körper35 Stell body
37 Bypasskanal37 bypass channel
39 Ausnehmung39 recess
41 Arbeitskammer41 working chamber
41A Teilkammer41A compartment
41 B Teilkammer41 B partial chamber
51 ,53 Zu- /Ablauf51, 53 inlet / outlet
61 ,63 Kammerzu- /-ablauf61, 63 Chamber inlet / outlet
67 Ringnut67 ring groove
67A Ringnut67A ring groove
67B Ringnut67B ring groove
65 Kurzschlusskanal65 short-circuit channel
71 Verriegelungsfeder 71 locking spring

Claims

Patentansprüche claims
1. Nockenwellenversteller (1 ) zur Verstellung der Drehwinkellage einer Nockenwelle relativ zu einer Kurbelwelle, mit mindestens zwei Arbeitskam- mern (41 ), denen zur Änderung der Drehwinkellage Drucköl zuführbar ist, dadurch gekennzeichnet, dass mindestens eine der Arbeitskammern (41 ) abhängig von einem Betriebsparameter durch Absperren der Druckölzufuhr abschaltbar ist.1. camshaft adjuster (1) for adjusting the rotational angle position of a camshaft relative to a crankshaft, with at least two working chambers (41) to which the rotational angle position pressure oil can be supplied, characterized in that at least one of the working chambers (41) depending on a Operating parameters can be switched off by blocking the pressure oil supply.
2. Nockenwellenversteller (1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass er in Flügelzellenbauweise ausgeführt ist, wobei jede Arbeitskammer (41 ) durch jeweils einen Flügel in zwei Teilkammern (41 A, 41 B) aufgeteilt ist und wobei das Drucköl je nach gewünschter Richtung der Änderung der Drehwinkellage einer der beiden Teilkammern (41A) so zugeführt wird, dass diese Teilkammer (41A) vergrößert und die zweite Teilkammer (41 B) verkleinert wird.2. camshaft adjuster (1) according to claim 1, characterized in that it is designed in vane-like construction, each working chamber (41) is divided by a respective wing in two sub-chambers (41 A, 41 B) and wherein the pressure oil depending on the desired direction the change in the angular position of one of the two sub-chambers (41A) is supplied so that this sub-chamber (41A) increases and the second sub-chamber (41 B) is reduced.
3. Nockenwellenversteller (1 ) nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Betriebsparameter der Druck des Drucköls ist.3. camshaft adjuster (1) according to claim 1 or 2, characterized in that the operating parameter is the pressure of the pressure oil.
4. Nockenwellenversteller (1 ) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Druckölzufuhr durch einen Stellkörper (35) absperrbar ist, dessen Stellposition durch den Druck des Drucköls bestimmt wird.4. camshaft adjuster (1) according to one of the preceding claims, characterized in that the pressure oil supply by a control body (35) can be shut off, the control position is determined by the pressure of the pressure oil.
5. Nockenwellenversteller (1 ) nach Anspruch 4, dadurch gekennzeichnet, dass der Stellkörper eine Rückstellfeder (33) aufweist, deren Federkraft der Stellwirkung des Drucköls entgegengerichtet ist.5. camshaft adjuster (1) according to claim 4, characterized in that the actuating body has a return spring (33), whose spring force of the actuating action of the pressure oil is directed opposite.
6. Nockenwellenversteller (1 ) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass bei einem Abschalten der Arbeitskammer (41 ) gleichzeitig eine kurzschließende Druckölverbindung (65) zwischen den beiden Teilkammern (41 A, 41 B) dieser Arbeitskammer hergestellt wird. 6. Camshaft adjuster (1) according to one of the preceding claims, characterized in that at a shutdown of the working chamber (41) at the same time a short-circuiting pressure oil connection (65) between the two sub-chambers (41 A, 41 B) of this working chamber is produced.
7. Nockenwellenversteller (1 ) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass mindestens zwei Arbeitskammern (41 ) abschaltbar sind, wobei die erste Arbeitskammer (41 ) bei einem ersten Wert des Betriebsparameters und die zweite Arbeitskammer (41 ) bei einem zweiten, gegenüber dem ersten Wert größeren Wert des Betriebsparameters abschaltbar ist.7. camshaft adjuster (1) according to one of the preceding claims, characterized in that at least two working chambers (41) are switched off, wherein the first working chamber (41) at a first value of the operating parameter and the second working chamber (41) at a second, opposite the first value larger value of the operating parameter can be switched off.
8. Nockenwellenversteller (1 ) nach Anspruch 4 und Anspruch 6, dadurch gekennzeichnet, dass durch den Stellkörper (35) gleichzeitig die Abschaltung der Arbeitskammer (41 ) und der Druckölkurzschluss einstellbar sind.8. camshaft adjuster (1) according to claim 4 and claim 6, characterized in that by the actuating body (35) at the same time the shutdown of the working chamber (41) and the Druckölkurzschluss are adjustable.
9. Nockenwellenversteller nach Anspruch 4, dadurch gekennzeichnet, dass der Stellkörper (35) doppelwirkend so ausgeführt ist, dass je nach Richtung der Änderung der Drehwinkellage die Arbeitskammer entweder durch Absperren der Druckölzufuhr zur ersten Teilkammer (41A) oder zur zweiten Teilkammer (41 B) abschaltbar ist.9. camshaft adjuster according to claim 4, characterized in that the adjusting body (35) is designed double-acting so that depending on the direction of change of the angular position the working chamber either by shutting off the pressure oil supply to the first sub-chamber (41 A) or the second sub-chamber (41 B) can be switched off.
10. Nockenwellenversteller (1 ) nach einem der vorhergehenden Ansprüche, bei dem ein Verriegelungsmechanismus (73) vorgesehen ist, durch den eine Verstellung der Drehwinkellage sperrbar ist, dadurch gekennzeichnet, dass durch den Verriegelungsmechanismus (73) auch die Absperrung der Druckölzufuhr einstellbar ist.10. camshaft adjuster (1) according to any one of the preceding claims, wherein a locking mechanism (73) is provided, through which an adjustment of the rotational angular position can be blocked, characterized in that by the locking mechanism (73) and the shut-off of the pressure oil supply is adjustable.
11. Nockenwellenversteller (1 ) nach Anspruch 10, dadurch gekennzeichnet, dass der Verriegelungsmechanismus (73) bei einem ersten Öldruck gegen die Kraft einer ersten Feder (71 ) entriegelt und bei einem zweiten, höheren Öldruck gegen die Kraft einer zweiten Feder(33) die Druckölzufuhr sperrt.11. camshaft adjuster (1) according to claim 10, characterized in that the locking mechanism (73) at a first oil pressure against the force of a first spring (71) unlocked and at a second, higher oil pressure against the force of a second spring (33) Pressure oil supply locks.
12. Verfahren zur Verstellung der Drehwinkellage einer Nockenwelle relativ zu einer Kurbelwelle, bei dem einem Nockenwellenversteller (1 ) mit mindestens zwei Arbeitskammern (41 ) zur Änderung der Drehwinkellage Drucköl in die Arbeitskammern (41 ) zuführbar ist, dadurch gekennzeichnet, dass die Druckölzufuhr zu mindestens einer der Arbeitskammern (41 ) bei Überschreiten eines vorgegebenen Druckes des Drucköls gesperrt wird, während die Druckölzufuhr zu mindestens einer der verbleibenden Arbeitskammern (41 ) offen bleibt. 12. A method for adjusting the rotational angle position of a camshaft relative to a crankshaft, wherein a camshaft adjuster (1) having at least two working chambers (41) for changing the rotational angle position pressure oil in the working chambers (41) can be fed, characterized in that the pressure oil supply to at least one of the working chambers (41) is blocked when a predetermined pressure of the pressure oil is exceeded, while the pressure oil supply to at least one of the remaining working chambers (41) remains open.
EP20100709492 2009-04-01 2010-03-16 Cam shaft adjuster and method for adjusting the angle-of-rotation position of a cam shaft relative to a crankshaft Not-in-force EP2414644B1 (en)

Applications Claiming Priority (2)

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DE200910015882 DE102009015882A1 (en) 2009-04-01 2009-04-01 Camshaft adjuster and method for adjusting the angular position of a camshaft relative to a crankshaft
PCT/EP2010/053343 WO2010112329A1 (en) 2009-04-01 2010-03-16 Cam shaft adjuster and method for adjusting the angle-of-rotation position of a cam shaft relative to a crankshaft

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EP2414644B1 EP2414644B1 (en) 2015-05-13

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DE102011081971A1 (en) * 2011-09-01 2013-03-07 Schaeffler Technologies AG & Co. KG Phaser
DE102012212857A1 (en) 2012-07-23 2014-01-23 Schaeffler Technologies AG & Co. KG Hydraulic camshaft adjusting device for e.g. motor car, has first pressure chambers and second pressure chambers provided with hydraulic fluid distribution system that is interrupted through speed-dependent actuable control valve
DE102013217519A1 (en) 2013-09-03 2015-03-05 Schaeffler Technologies Gmbh & Co. Kg Camshaft adjuster with a stator-fixed central magnet
DE102015200147B4 (en) 2015-01-08 2021-07-15 Schaeffler Technologies AG & Co. KG Camshaft adjuster with centrifugal force-controlled switching element between working chambers of a pressure chamber
DE102021101306A1 (en) 2021-01-22 2022-07-28 Schaeffler Technologies AG & Co. KG Camshaft adjuster with locking mechanism

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DE10007200A1 (en) 2000-02-17 2001-08-23 Schaeffler Waelzlager Ohg Device for changing the control times of gas exchange valves of an internal combustion engine
JP4605473B2 (en) 2005-12-27 2011-01-05 アイシン精機株式会社 Valve timing control device
US7318401B2 (en) * 2006-03-15 2008-01-15 Borgwarner Inc. Variable chamber volume phaser
JP4484843B2 (en) * 2006-04-28 2010-06-16 日立オートモティブシステムズ株式会社 Valve timing control device for internal combustion engine
JP2008175128A (en) * 2007-01-18 2008-07-31 Denso Corp Valve timing adjusting device

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* Cited by examiner, † Cited by third party
Title
See references of WO2010112329A1 *

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US20120085304A1 (en) 2012-04-12

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