EP2487339A2 - Camshaft adjuster with a pressure storage unit - Google Patents

Camshaft adjuster with a pressure storage unit Download PDF

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Publication number
EP2487339A2
EP2487339A2 EP11191381A EP11191381A EP2487339A2 EP 2487339 A2 EP2487339 A2 EP 2487339A2 EP 11191381 A EP11191381 A EP 11191381A EP 11191381 A EP11191381 A EP 11191381A EP 2487339 A2 EP2487339 A2 EP 2487339A2
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EP
European Patent Office
Prior art keywords
pressure accumulator
rotor
pressure
camshaft adjuster
wing
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
EP11191381A
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German (de)
French (fr)
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EP2487339B1 (en
EP2487339A3 (en
Inventor
Jürgen Weber
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of EP2487339A2 publication Critical patent/EP2487339A2/en
Publication of EP2487339A3 publication Critical patent/EP2487339A3/en
Application granted granted Critical
Publication of EP2487339B1 publication Critical patent/EP2487339B1/en
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    • 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

Definitions

  • the invention relates to a camshaft adjuster with a pressure accumulator.
  • Camshaft adjusters are used in internal combustion engines for varying the timing of the combustion chamber valves. Adjusting the timing to the current load lowers fuel consumption and emissions.
  • the camshaft adjuster is usually fixed against rotation on a camshaft of the internal combustion engine and is in driving connection with a crankshaft. This drive connection can be realized for example as a belt, chain or gear drive.
  • a hydraulic phase adjusting device of the camshaft adjuster By means of a hydraulic phase adjusting device of the camshaft adjuster, a phase relation between the crankshaft and the camshaft can be selectively changed by pressure medium supply or removal.
  • Vane adjusters include a stator, a rotor and a drive wheel.
  • the rotor is usually non-rotatably connected to the camshaft.
  • the stator and the drive wheel are also interconnected with the rotor coaxial with the stator and within the stator.
  • the vane cell adjusters have various sealing lids.
  • the composite of stator, drive wheel and sealing cover is formed by a plurality of screw connections.
  • a camshaft adjuster is for example from the DE 195 29 277 A1 known.
  • the camshaft adjuster has an output element, which is arranged rotatably to a drive element.
  • the drive element is in drive connection with the crankshaft, the output element is non-rotatably connected to the camshaft.
  • the output element and the drive element define a pressure chamber, which is divided by means of an axially displaceable piston into two counteracting pressure chambers.
  • By supplying pressure medium to or removing pressure medium from the pressure chambers the piston is displaced within the pressure chamber.
  • the piston has a helical toothing, which meshes with a helical toothing of the camshaft.
  • an accumulator is provided, which is arranged in a crankcase or a cylinder head of the internal combustion engine.
  • the pressure accumulator of a pressure medium pump of the internal combustion engine with pressure medium, usually engine oil, filled. If the system pressure delivered by the pressure medium pump drops below a value which is required for the functionally reliable operation of the camshaft adjuster, then the pressure accumulator can be emptied into the pressure medium circuit of the internal combustion engine. Thus, short-term minimum pressure drops can be intercepted within the pressure fluid system or the volume flow can be increased.
  • camshaft adjuster is out of the EP 0 806 550 A1 known.
  • This camshaft adjuster is designed in the form of an impeller, wherein the pressure medium distributor is also supported by a pressure accumulator.
  • the pressure accumulator after switching off the internal combustion engine to urge the camshaft adjuster in a phase position in which the internal combustion engine can be safely restarted.
  • a collapse of the adjustment speed during the adjustment can be prevented.
  • At the beginning of a phase adjustment of the pressure fluid system of the internal combustion engine is removed a certain amount of pressure medium. As a result, the system pressure drops to a lower level.
  • the existing system pressure prior to adjustment is not fully available for phase adjustment.
  • the adjustment speed of the phase adjustment and thus the performance of the entire internal combustion engine decreases. This pressure drop is intercepted when filled pressure accumulator through this, the adjustment speed is maintained at a high level.
  • the object of the invention is to provide a camshaft adjuster with an advantageously arranged pressure accumulator.
  • the pressure accumulator includes a pressure accumulator housing, a pressure accumulator spring, an accumulator piston and one or more control vanes.
  • the accumulator housing is designed as a U-shaped component in cross-section. In it is axially movable pressure accumulator piston in the form of an annular disc.
  • the accumulator piston can be mounted coaxially through the remaining, open side.
  • the pressure accumulator piston on the inner and outer circumference has a groove for receiving sealing means, such as sealing rings.
  • the pressure accumulator housing is divided by the pressure accumulator piston in two mutually tight chambers, the spring chamber and the pressure chamber.
  • the pressure accumulator spring is arranged, which acts against the accumulator piston against a hydraulic medium pressure in the pressure chamber.
  • hydraulic fluid is introduced through arranged on the pressure accumulator housing pressure accumulator openings, whereby the Pressure accumulator spring is biased.
  • the pressure storage openings are closed. At the desired operating point of the camshaft adjuster, the stored pressure can be returned via the pressure accumulator openings back into the camshaft adjuster, in particular into the working chambers, thus supporting the operation of the camshaft adjuster in the event of a lack of hydraulic fluid.
  • the pressure storage openings are arranged mutually to the control wings.
  • the control wings are in turn bounded by the wall of the wing in the rotor. Due to the relative movement of the control blade to the rotor blade, the pressure storage opening are brought into or out of overlap with the hub of the rotor.
  • About the hub, or its inner diameter of the pressure accumulator or accumulator housing is received with its outer diameter and arranged concentrically thereto.
  • the concentricity is advantageous here, since the control vanes must work sealingly with their radial ends with the rotor blade during their relative movement.
  • the accumulator spring constructed as a compression spring is thus likewise positioned largely concentrically with respect to the arrangement.
  • the control wing controls the overlap of the pressure storage openings with the hub of the rotor.
  • the hub can also be replaced by another sleeve component, which can rotate relative to the pressure accumulator housing.
  • the control wing In the case of the charged accumulator, or in the absence of external hydraulic fluid pressure, the control wing must close the pressure accumulator openings without influence of the external hydraulic fluid pressure.
  • control spring means which move the control wing in a rest position, which closes the pressure storage openings.
  • this position is in the symmetry center of the wing, wherein the control wing is located.
  • This control spring means can be arranged directly between a control wing and a rotor blade, wherein an arrangement on each control wing / rotor blade pair is conceivable. For example, this can be done by leaf springs will be realized.
  • a centrally arranged to camshaft adjuster torsion spring bring the control wing and thus the entire pressure accumulator in a rest position. In this case, no impairment of the pressurization would occur on the control wing and space to be optimized.
  • a lock can be used to secure the control wing in one position.
  • control spring means is identical to the pressure storage spring.
  • the accumulator spring can work both axially and circumferentially.
  • a slot is provided on the pressure accumulator housing for a spring end, which is arranged on the pressure piston side, which allows axial movement of the spring end and allows a rotational movement of the pressure accumulator housing and thus also the control vane.
  • the control wings must have a pressure surface acting in the circumferential direction for reliable operation.
  • the control wings are arranged with the wing largely hydraulic medium tight, so that no excessive leakage affects the functionality.
  • sprung and / or flexible sealing elements can be used, which maintain the required tightness during operation. These may be formed integrally or separately with the control wing or the wing.
  • the shape of the pressure surface of the control wing can be optimized for the hydraulic fluid flow.
  • the formation of the surface may be curved, turbine blade-like, radially straight or skewed to the radial and axial directions
  • the rotor is designed as a sheet-metal part, whereby the recording of the pressure accumulator with its control wings is particularly simplified.
  • the corresponding leads and openings can be easily and inexpensively manufactured by punching operations.
  • the use of sheet metal material can be applied to the manufacture of control wings, as well as to the production of the pressure accumulator housing and the Expand accumulator piston.
  • the control wings can be plugged as a separately manufactured sheet metal tab on corresponding receptacles of the accumulator housing.
  • a one-piece design is advantageous if leaks at the joint between the control wing and pressure accumulator housing to be avoided, or the cost of ensuring a tightness to be minimized.
  • openings are made in the rotor or in the wing walls, which allow inflow or outflow of hydraulic fluid (such as engine oil). These openings are arranged on the circumferentially opposite wing walls. The number of apertures may extend beyond the functionally necessary two opposing apertures on a blade of the rotor, e.g. to optimize the inflow and outflow into the wing. Thus, a plurality of openings can be provided in the circumferential direction on one wing side.
  • a working chamber A If a working chamber A is acted upon by hydraulic fluid, the hydraulic fluid passes through these openings in the wing of the rotor and pushes the control wing from its rest position, which in turn rotates the pressure accumulator housing relative to the rotor and thus exposes the pressure accumulator opening associated with the working chamber A.
  • the hydraulic fluid pressure at engine start is low, but sufficient to move the control wing against the control spring means.
  • the pressure chamber is further filled with hydraulic fluid and the increasing hydraulic fluid pressure further ensures a deflection of the pressure accumulator spring.
  • the hydraulic fluid supply to the working chamber A is separated from the motor pump and the control wing is brought by the control spring means in its rest position, wherein the pressure storage openings are closed again.
  • the relative position of the rotor to the stator can be secured via a locking mechanism, so that the decreasing hydraulic fluid pressure in the working chamber A causes no reverse rotation.
  • the hydraulic fluid volume in the pressure chamber is now biased by the pressure accumulator spring and the pressure accumulator is charged.
  • the supercharged accumulator is advantageous at engine start-up to support the insufficient engine oil pressure.
  • the pressure accumulator also supports adjustment in one direction of rotation during operation.
  • unwanted pressure peaks from cam change moments deflect the control blade through the pressure peak in the working chamber, and thus can escape into the pressure accumulator.
  • a "pumping" from one working chamber into the other working chamber through the pressure chamber of the pressure accumulator which can be adjusted relative to the stator with appropriate control of a control valve for controlling the hydraulic fluid flows a controlled position of the rotor.
  • the pressure accumulator with the accumulator piston has at least one spacer, which in the unprinted state, ie when the pressure accumulator is not charged, biases the pressure accumulator spring and thus maintains a distance in the working direction, which defines a space in which the hydraulic fluid can flow in.
  • This spacer may be formed as a nose or elevation on the pressure accumulator piston, the pressure accumulator housing or both. Several spacers can also be distributed evenly around the circumference.
  • structure and the operation of the pressure accumulator with the control wing can also be realized on the stator and its wings and the example of the rotor can be transferred to the stator.
  • Fig. 1 shows a camshaft adjuster 1 in a cross-sectional view with respect to the working chambers A and B.
  • the camshaft adjuster 1 consists of a drive wheel 22, a stator 2, a rotor 3, a cover 21, a disc 23, a locking mechanism 20, a pressure accumulator 6 and Adapter part 25.
  • the central screw 24 can be seen with the concentrically arranged, known from the prior art, vent hole.
  • the central screw 24 fastens the phaser 1 on the camshaft end 26.
  • the drive wheel 22, the cover 21, the stator 2, the rotor 3, the adapter part 25 and the pressure accumulator 6 are arranged concentrically to one another and to the rotational axis 4 of the camshaft adjuster 1.
  • the accumulator 6 has control wing 11 with control spring means 19, which remain in the unprinted state, ie in the rest position or in the starting position of the camshaft adjuster 1, in a central position relative to the wing 5 of the rotor 3.
  • the axis of rotation 4 of the camshaft adjuster 1 is perpendicular to the plane of the drawing and at the intersection of the central cross.
  • the camshaft adjuster 1 is also arranged concentrically to the camshaft end 26 with the central screw 24, as is known in the prior art.
  • the rotor 3 rotates counterclockwise relative to the stator 2.
  • Stator 3 drive wheel 22, cover 21, disc 23, adapter part 25 and closure member 28th (in Fig. 2 recognizable) rotationally fixed to each other and formed by the joining of adapter part 25 and closure member 28 of this composite is axially secured.
  • the entire composite is driven by the drive wheel 22 by traction means known in the art from the crankshaft.
  • the limited angular range is determined by the arrangement of vanes 5 on the stator 2 and on the rotor 3, which extend radially and define mutually-acting, as far as possible hydraulic medium-tight working chambers A, B.
  • the structure and mode of operation of the camshaft adjuster 1 can be seen from the prior art of the vane cell adjuster and sufficiently well known to the person skilled in the art, so that the differences between the prior art and the mode of operation of the invention will be discussed below.
  • the control wing 11 is now in abutment within the wing 5 of the rotor 3.
  • the adjustment is completed when a wing 5 of the rotor. 3 in the stop with a complementary wing 5 of the stator 2 is located.
  • a wing 5 of the rotor 3 is here equipped with the locking mechanism 20.
  • the locking mechanism 20 is locked without pressure and engages in this stop position of the stator 2 with the rotor 3 a.
  • the hydraulic fluid channel b was opened according to the known oil-pressure Aktuating principle to the tank. As a result, excess hydraulic fluid could be removed from the locking mechanism via the hydraulic fluid channel B.
  • Fig. 2 shows a longitudinal section according to II Fig. 1 to illustrate the path along the hydraulic fluid channel a and the operation of the pressure accumulator 6.
  • the supply line via a camshaft bearing of the camshaft end 26, via radial holes 27, in the receptacle for the central screw 24.
  • Via a passage formed by the radial gap between the central screw 24th and camshaft end 26 and adapter part 25 passes the hydraulic fluid to a radial bore 27 in the adapter part 25 and is directed into the working chamber A.
  • the further path is schematic in Fig. 1 shown along the dashed arrow.
  • the hydraulic fluid which passes through the pressure storage openings 14 into the pressure storage chamber 10, biases the pressure storage spring 8 via the pressure storage piston 9.
  • the accumulator 6 is now charged.
  • Fig. 3 shows a cross section through the camshaft adjuster 1 in the other stop position, the adjustment is completed in a clockwise direction.
  • the hydraulic channel b is now pressurized and the hydraulic channel a is opened to the tank.
  • the pressure of the hydraulic fluid acts on the control wing 11 from the opposite side, as in the adjustment in the counterclockwise direction.
  • the control wing 11 in the wing 5 are first clockwise until it stops in the wing 5.
  • the pressure accumulator openings 14 are closed to the working chamber A and the pressure accumulator openings 14 to the working chamber B opened.
  • the charged pressure accumulator 6 can release the previously enclosed volume of hydraulic fluid through the preloaded pressure accumulator spring 8 and let flow into the working chamber B. It is clear that even smaller amounts of hydraulic fluid on reaching the working chambers A or B can already adjust the control blade 11 before the hydraulic fluid pressure is sufficient to move the rotor 3.
  • the charged pressure accumulator 6 supports the adjustment of the rotor 3 when the engine is started or when the hydraulic fluid supply is insufficient.
  • Fig. 4 shows a longitudinal section according to III-III Fig. 3 to illustrate the path along the hydraulic fluid channel b.
  • hydraulic medium is conducted from the camshaft bearing of the camshaft end 26 into a bore 27 running parallel to the rotational axis 4 into an aligned bore 27 of the adapter part 25.
  • This hydraulic fluid initially collects in a chamber, which is bounded by the adapter part 25, the pressure accumulator housing 7 and the rotor 3.
  • the disc has 23 recesses, or wall thickness reductions, which together with the rotor 3 make an inlet into the working chamber B (see Fig. 5 ).
  • the vent 17 of the spring chamber 18 can be seen.
  • the vent 17 is realized by axially parallel holes to the axis of rotation 4 and carries foreign matter from the spring chamber 18 during operation out.
  • the axially parallel holes of the vent 17 are arranged in the rotor 3, in the stator 2 and in the closure member 28 such that a mutually formed opening cross-section remains.
  • the arrangement of the axis-parallel bores of the vent 17 may ideally be in alignment.
  • Fig. 5 shows a longitudinal section according to III-III Fig. 3 to further illustrate the hydraulic fluid path b.
  • Fig. 4 parallel to the axis of rotation 4 holes 27 can be seen.
  • Fig. 6 shows an isometric view of the disc 23.
  • the inlets along the hydraulic fluid channel a, b to the working chambers A, B, but without the peripheral components, are shown schematically.
  • Fig. 7 shows an isometric view of the open side 15 of the pressure accumulator housing 7.
  • the radially extending as a sheet metal tab 13 control vanes 11 are arranged irregularly on the circumference. This irregularity results from the arrangement of the locking mechanism 20 in the rotor 3, wherein when joining the pressure accumulator housing 7 with the rotor 3, the wing 5 with the locking mechanism 20 remains unoccupied by a control wing 11.
  • the number of control vanes 11 may coincide with the number of vanes 5 in the rotor 3.
  • Fig. 8 shows an isometric view of the opposite side of the pressure accumulator housing 7.
  • the pressure storage openings 14 may have any desired cross-sectional shape, such as square, round, oval, etc., which is useful for adjusting the flow.
  • the accumulator housing 7 is advantageously formed as a sheet metal part and completed by the control wing 11 as sheet metal tabs for attachment to the accumulator housing economically.
  • Fig. 9 shows an isometric view of the pressure accumulator piston 9. This has four, evenly distributed, integrally formed with the accumulator piston, spacer 30.
  • the spacers 30 may take any shape that serves the function of providing a minimum free space in the pressure accumulator chamber 10 is useful .
  • a groove for inserting a sealing ring 29 is provided to seal the pressure storage chamber 10 relative to the spring chamber 18.

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

Abstract

The adjuster (1) has a stator (2) and a rotor (3) including a set of radially orientated vanes (5), where the stator and rotor are rotated relative to each other. The vanes of the rotor and stator form working chambers (A, B) that act opposite to each other, where the working chambers are supplied with a hydraulic medium to rotate the rotor relative to the stator. A pressure accumulator (6) stores the medium and includes a control vane (11) i.e. sheet metal plate, where the vanes of the rotor or stator are projected around the control vane. A control spring (19) acts on the control vane.

Description

Gebiet der ErfindungField of the invention

Die Erfindung betrifft einen Nockenwellenversteller mit einem Druckspeicher.The invention relates to a camshaft adjuster with a pressure accumulator.

Hintergrund der ErfindungBackground of the invention

Nockenwellenversteller werden in Verbrennungsmotoren zur Variation der Steuerzeiten der Brennraumventile eingesetzt. Die Anpassung der Steuerzeiten an die aktuelle Last senkt den Verbrauch und die Emissionen. Der Nockenwellenversteller ist üblicherweise drehfest an einer Nockenwelle der Brennkraftmaschine befestigt und steht in Antriebsverbindung mit einer Kurbelwelle. Diese Antriebsverbindung kann beispielsweise als Riemen-, Ketten-oder Zahnradtrieb realisiert sein. Mittels einer hydraulischen Phasenstelleinrichtung des Nockenwellenverstellers kann durch Druckmittelzufuhr, bzw. - abfuhr eine Phasenrelation zwischen der Kurbelwelle und der Nockenwelle gezielt verändert werden.Camshaft adjusters are used in internal combustion engines for varying the timing of the combustion chamber valves. Adjusting the timing to the current load lowers fuel consumption and emissions. The camshaft adjuster is usually fixed against rotation on a camshaft of the internal combustion engine and is in driving connection with a crankshaft. This drive connection can be realized for example as a belt, chain or gear drive. By means of a hydraulic phase adjusting device of the camshaft adjuster, a phase relation between the crankshaft and the camshaft can be selectively changed by pressure medium supply or removal.

Eine verbreitete Bauart ist der Flügelzellenversteller. Flügelzellenversteller weisen einen Stator, einen Rotor und ein Antriebsrad auf. Der Rotor ist meist mit der Nockenwelle drehfest verbunden. Der Stator und das Antriebsrad werden ebenfalls untereinander verbunden, wobei sich der Rotor koaxial zum Stator und innerhalb des Stators befindet. Rotor und Stator prägen mit deren Flügeln gegensätzlich wirkende Ölkammern aus, welche durch Öldruck beaufschlagbar sind und eine Relativbewegung zwischen Stator und Rotor ermöglichen. Weiterhin weisen die Flügelzellenversteller diverse Abdichtdeckel auf. Der Verbund von Stator, Antriebsrad und Abdichtdeckel wird über mehrere Schraubenverbindungen ausgebildet.A common type is the Flügelzellenversteller. Vane adjusters include a stator, a rotor and a drive wheel. The rotor is usually non-rotatably connected to the camshaft. The stator and the drive wheel are also interconnected with the rotor coaxial with the stator and within the stator. Rotor and stator shape with their wings oppositely acting oil chambers, which can be acted upon by oil pressure and allow a relative movement between the stator and the rotor. Furthermore, the vane cell adjusters have various sealing lids. The composite of stator, drive wheel and sealing cover is formed by a plurality of screw connections.

Ein Nockenwellenversteller ist beispielsweise aus der DE 195 29 277 A1 bekannt. Der Nockenwellenversteller weist ein Abtriebselement auf, welches drehbar zu einem Antriebselement angeordnet ist. Das Antriebselement steht in Antriebsverbindung mit der Kurbelwelle, das Abtriebselement ist drehfest mit der Nockenwelle verbunden. Das Abtriebselement und das Antriebselement begrenzen einen Druckraum, der mittels eines axial verschiebbaren Kolbens in zwei gegeneinander wirkende Druckkammern unterteilt wird. Durch Druckmittelzufuhr zu bzw. Druckmittelabfuhr von den Druckkammern wird der Kolben innerhalb des Druckraums verschoben. Der Kolben weist eine Schrägverzahnung auf, die mit einer Schrägverzahnung der Nockenwelle kämmt. Durch die eine Axialverschiebung des Kolbens kann somit eine gezielte Verdrehung der Nockenwelle zur Kurbelwelle bewirkt werden.A camshaft adjuster is for example from the DE 195 29 277 A1 known. The camshaft adjuster has an output element, which is arranged rotatably to a drive element. The drive element is in drive connection with the crankshaft, the output element is non-rotatably connected to the camshaft. The output element and the drive element define a pressure chamber, which is divided by means of an axially displaceable piston into two counteracting pressure chambers. By supplying pressure medium to or removing pressure medium from the pressure chambers, the piston is displaced within the pressure chamber. The piston has a helical toothing, which meshes with a helical toothing of the camshaft. By an axial displacement of the piston thus a targeted rotation of the camshaft can be effected to the crankshaft.

Des Weiteren ist ein Druckspeicher vorgesehen, der in einem Kurbelgehäuse oder einem Zylinderkopf der Brennkraftmaschine angeordnet ist. Während des normalen Betriebs der Brennkraftmaschine wird der Druckspeicher von einer Druckmittelpumpe der Brennkraftmaschine mit Druckmittel, in der Regel Motoröl, befüllt. Sinkt der von der Druckmittelpumpe gelieferte Systemdruck unter einen Wert, der für den funktionssicheren Betrieb des Nockenwellenverstellers benötigt wird, so kann der Druckspeicher in den Druckmittelkreislauf der Brennkraftmaschine entleert werden. Somit können kurzfristige Mindestdruckunterschreitungen innerhalb des Druckmittelsystems abgefangen bzw. der Volumenstrom erhöht werden.Furthermore, an accumulator is provided, which is arranged in a crankcase or a cylinder head of the internal combustion engine. During normal operation of the internal combustion engine, the pressure accumulator of a pressure medium pump of the internal combustion engine with pressure medium, usually engine oil, filled. If the system pressure delivered by the pressure medium pump drops below a value which is required for the functionally reliable operation of the camshaft adjuster, then the pressure accumulator can be emptied into the pressure medium circuit of the internal combustion engine. Thus, short-term minimum pressure drops can be intercepted within the pressure fluid system or the volume flow can be increased.

Ein weiterer Nockenwellenversteller ist aus der EP 0 806 550 A1 bekannt. Dieser Nockenwellenversteller ist in Form eines Flügelrades ausgebildet, wobei dessen Druckmittelverteiler ebenfalls von einem Druckspeicher unterstützt wird. In dieser Ausführungsform soll der Druckspeicher nach dem Ausschalten der Brennkraftmaschine den Nockenwellenversteller in eine Phasenlage drängen, in der die Brennkraftmaschine sicher wieder gestartet werden kann. Darüber hinaus kann ein Einbruch der Verstellgeschwindigkeit während des Verstellvorgangs verhindert werden. Zu Beginn einer Phasenverstellung wird dem Druckmittelsystem der Brennkraftmaschine einen gewisse Menge Druckmittel entnommen. Als Folge davon sinkt der Systemdruck auf ein geringeres Niveau. Der vor der Verstellung vorhandene Systemdruck steht nicht in vollem Umfang zur Phasenverstellung zur Verfügung. Somit sinkt die Verstellgeschwindigkeit der Phasenverstellung und damit die Performance der gesamten Brennkraftmaschine. Dieser Druckabfall wird bei befülltem Druckspeicher durch diesen abgefangen, die Verstellgeschwindigkeit wird auf einem hohen Niveau gehalten.Another camshaft adjuster is out of the EP 0 806 550 A1 known. This camshaft adjuster is designed in the form of an impeller, wherein the pressure medium distributor is also supported by a pressure accumulator. In this embodiment, the pressure accumulator after switching off the internal combustion engine to urge the camshaft adjuster in a phase position in which the internal combustion engine can be safely restarted. In addition, a collapse of the adjustment speed during the adjustment can be prevented. At the beginning of a phase adjustment of the pressure fluid system of the internal combustion engine is removed a certain amount of pressure medium. As a result, the system pressure drops to a lower level. The existing system pressure prior to adjustment is not fully available for phase adjustment. Thus, the adjustment speed of the phase adjustment and thus the performance of the entire internal combustion engine decreases. This pressure drop is intercepted when filled pressure accumulator through this, the adjustment speed is maintained at a high level.

Zusammenfassung der ErfindungSummary of the invention

Aufgabe der Erfindung ist es, einen Nockenwellenversteller mit einem vorteilhaft angeordneten Druckspeicher anzugeben.The object of the invention is to provide a camshaft adjuster with an advantageously arranged pressure accumulator.

Erfindungsgemäß wird die Aufgabe durch die Merkmale des Anspruchs 1 gelöst.According to the invention the object is achieved by the features of claim 1.

In einer Ausgestaltung der Erfindung beinhaltet der Druckspeicher ein Druckspeichergehäuse, eine Druckspeicherfeder, einen Druckspeicherkolben und einen oder mehrere Steuerflügel. Das Druckspeichergehäuse ist als ein im Querschnitt U-förmiges Bauteil ausgebildet. Darin befindet sich axial beweglich der Druckspeicherkolben in Form einer Ringscheibe. Der Druckspeicherkolben kann durch die verbleibende, offene Seite koaxial montiert werden. Dabei besitzt der Druckspeicherkolben am inneren und äußeren Umfang eine Nut zur Aufnahme von Dichtmitteln, wie z.B. Dichtringen. Somit ist das Druckspeichergehäuse durch den Druckspeicherkolben in zwei gegenseitig dichte Kammern unterteilt, dem Federraum und der Druckkammer. In dem Federraum ist die Druckspeicherfeder angeordnet, welche mit dem Druckspeicherkolben entgegen einem Hydraulikmitteldruck in der Druckkammer wirkt. Zur Erzeugung des Druckes in der Druckkammer wird Hydraulikmittel durch an dem Druckspeichergehäuse angeordnete Druckspeicheröffnungen eingeleitet, wodurch die Druckspeicherfeder vorgespannt wird. Zur Speicherung des Druckes in dem Druckspeicher werden die Druckspeicheröffnungen verschlossen. In dem gewünschten Betriebspunkt des Nockenwellenverstellers kann der gespeicherte Druck über die Druckspeicheröffnungen wieder in den Nockenwellenversteller, speziell in die Arbeitskammern, abgegeben werden und unterstützt so den Betrieb des Nockenwellenverstellers bei Hydraulikmittelmangel.In one embodiment of the invention, the pressure accumulator includes a pressure accumulator housing, a pressure accumulator spring, an accumulator piston and one or more control vanes. The accumulator housing is designed as a U-shaped component in cross-section. In it is axially movable pressure accumulator piston in the form of an annular disc. The accumulator piston can be mounted coaxially through the remaining, open side. In this case, the pressure accumulator piston on the inner and outer circumference has a groove for receiving sealing means, such as sealing rings. Thus, the pressure accumulator housing is divided by the pressure accumulator piston in two mutually tight chambers, the spring chamber and the pressure chamber. In the spring chamber, the pressure accumulator spring is arranged, which acts against the accumulator piston against a hydraulic medium pressure in the pressure chamber. To generate the pressure in the pressure chamber hydraulic fluid is introduced through arranged on the pressure accumulator housing pressure accumulator openings, whereby the Pressure accumulator spring is biased. To store the pressure in the pressure accumulator the pressure storage openings are closed. At the desired operating point of the camshaft adjuster, the stored pressure can be returned via the pressure accumulator openings back into the camshaft adjuster, in particular into the working chambers, thus supporting the operation of the camshaft adjuster in the event of a lack of hydraulic fluid.

Die Druckspeicheröffnungen sind wechselseitig zu den Steuerflügeln angeordnet. Die Steuerflügel sind wiederum von der Wandung des Flügels im Rotor umgrenzt. Durch die Relativbewegung des Steuerflügels zum Rotorflügel werden die Druckspeicheröffnung in oder außer Überdeckung mit der Nabe des Rotors gebracht. Über die Nabe, bzw. dessen Innendurchmesser ist der Druckspeicher bzw. das Druckspeichergehäuse mit seinem Außendurchmesser aufgenommen und konzentrisch dazu angeordnet. Die Konzentrizität ist hier von Vorteil, da die Steuerflügel mit ihren radialen Enden mit dem Rotorflügel während ihrer Relativbewegung dichtend arbeiten müssen. Die als Druckfeder ausgebildete Druckspeicherfeder ist somit ebenfalls weitestgehend konzentrisch zur Anordnung positioniert.The pressure storage openings are arranged mutually to the control wings. The control wings are in turn bounded by the wall of the wing in the rotor. Due to the relative movement of the control blade to the rotor blade, the pressure storage opening are brought into or out of overlap with the hub of the rotor. About the hub, or its inner diameter of the pressure accumulator or accumulator housing is received with its outer diameter and arranged concentrically thereto. The concentricity is advantageous here, since the control vanes must work sealingly with their radial ends with the rotor blade during their relative movement. The accumulator spring constructed as a compression spring is thus likewise positioned largely concentrically with respect to the arrangement.

Der Steuerflügel steuert die Überdeckung der Druckspeicheröffnungen mit der Nabe des Rotors. Dabei kann die Nabe auch durch ein anderes Hülsenbauteil ersetzt werden, welches sich zum Druckspeichergehäuse relativ verdrehen kann. Im Fall des aufgeladenen Druckspeichers, bzw. bei mangelndem äußeren Hydraulikmitteldruck, muss der Steuerflügel ohne Einfluss von dem äußeren Hydraulikmitteldruck die Druckspeicheröffnungen verschließen. Dies wird durch Steuerfedermittel realisiert, die den Steuerflügel in eine Ruhelage bewegen, die die Druckspeicheröffnungen verschließt. Vorteilhafterweise ist diese Stellung in der Symmetriemitte des Flügels, worin sich der Steuerflügel befindet.The control wing controls the overlap of the pressure storage openings with the hub of the rotor. In this case, the hub can also be replaced by another sleeve component, which can rotate relative to the pressure accumulator housing. In the case of the charged accumulator, or in the absence of external hydraulic fluid pressure, the control wing must close the pressure accumulator openings without influence of the external hydraulic fluid pressure. This is realized by control spring means which move the control wing in a rest position, which closes the pressure storage openings. Advantageously, this position is in the symmetry center of the wing, wherein the control wing is located.

Diese Steuerfedermittel können direkt zwischen einem Steuerflügel und einem Rotorflügel angeordnet werden, wobei auch eine Anordnung an jedem Steuerflügel/Rotorflügel Paar denkbar ist. Beispielsweise kann dies durch Blattfedern realisiert werden. Alternativ kann auch eine zentral zum Nockenwellenversteller angeordnete Drehfeder den Steuerflügel und somit den gesamten Druckspeicher in eine Ruhelage bringen. Hierbei würde keine Beeinträchtigung der Druckbeaufschlagung auf den Steuerflügel entstehen und Bauraum optimiert werden. Alternativ kann auch eine Arretierung verwendet werden, um den Steuerflügel in einer Lage zu sichern.This control spring means can be arranged directly between a control wing and a rotor blade, wherein an arrangement on each control wing / rotor blade pair is conceivable. For example, this can be done by leaf springs will be realized. Alternatively, a centrally arranged to camshaft adjuster torsion spring bring the control wing and thus the entire pressure accumulator in a rest position. In this case, no impairment of the pressurization would occur on the control wing and space to be optimized. Alternatively, a lock can be used to secure the control wing in one position.

In einer Ausgestaltung der Erfindung ist das Steuerfedermittel mit der Druckspeicherfeder identisch. Die Druckspeicherfeder kann sowohl axial, als auch umfangsseitig arbeiten. Dazu ist an dem Druckspeichergehäuse für ein Federende, welches druckkolbenseitig angeordnet ist, ein Langloch vorgesehen, welches eine axiale Bewegung des Federendes erlaubt und eine Drehbewegung des Druckspeichergehäuses und somit auch des Steuerflügels ermöglicht.In one embodiment of the invention, the control spring means is identical to the pressure storage spring. The accumulator spring can work both axially and circumferentially. For this purpose, a slot is provided on the pressure accumulator housing for a spring end, which is arranged on the pressure piston side, which allows axial movement of the spring end and allows a rotational movement of the pressure accumulator housing and thus also the control vane.

Die Steuerflügel müssen für eine zuverlässige Funktion eine Druckfläche haben, die in Umfangsrichtung wirkt. Dazu sind die Steuerflügel mit dem Flügel weitestgehend hydraulikmitteldicht angeordnet, damit keine überhöhte Leckage die Funktionalität beeinträchtigt. Hierzu können angefederte und/oder flexible Dichtelemente verwendet werden, welche die erforderliche Dichtheit im Betrieb beibehalten. Diese können einteilig oder separat mit dem Steuerflügel oder dem Flügel ausgebildet sein.The control wings must have a pressure surface acting in the circumferential direction for reliable operation. For this purpose, the control wings are arranged with the wing largely hydraulic medium tight, so that no excessive leakage affects the functionality. For this purpose, sprung and / or flexible sealing elements can be used, which maintain the required tightness during operation. These may be formed integrally or separately with the control wing or the wing.

Die Form der Druckfläche des Steuerflügels kann an den Hydraulikmittelfluss optimiert sein. So kann die Ausbildung der Oberfläche gewölbt, turbinenschaufelartig, radial gerade oder windschief zur radialen und axialen Richtung seinThe shape of the pressure surface of the control wing can be optimized for the hydraulic fluid flow. Thus, the formation of the surface may be curved, turbine blade-like, radially straight or skewed to the radial and axial directions

In einer besonders bevorzugten Ausgestaltung ist der Rotor als ein Blechtopfteil ausgebildet, wodurch die Aufnahme des Druckspeichers mit seinen Steuerflügeln besonders vereinfacht wird. Auch die entsprechenden Zuleitungen und Öffnungen lassen sich einfach und kostengünstig durch Stanzarbeitsgänge fertigen. Die Nutzung von Blechmaterial lässt sich auf die Herstellung der Steuerflügel, sowie auf die Herstellung des Druckspeichergehäuses und des Druckspeicherkolbens erweitern. Die Steuerflügel können als separat gefertigte Blechlasche auf entsprechende Aufnahmen des Druckspeichergehäuses aufgesteckt werden. Eine einteilige Ausbildung ist von Vorteil, wenn Undichtigkeiten an der Fügestelle zwischen Steuerflügel und Druckspeichergehäuse vermieden werden sollen, bzw. der Aufwand der Sicherstellung einer Dichtheit minimiert werden soll.In a particularly preferred embodiment, the rotor is designed as a sheet-metal part, whereby the recording of the pressure accumulator with its control wings is particularly simplified. The corresponding leads and openings can be easily and inexpensively manufactured by punching operations. The use of sheet metal material can be applied to the manufacture of control wings, as well as to the production of the pressure accumulator housing and the Expand accumulator piston. The control wings can be plugged as a separately manufactured sheet metal tab on corresponding receptacles of the accumulator housing. A one-piece design is advantageous if leaks at the joint between the control wing and pressure accumulator housing to be avoided, or the cost of ensuring a tightness to be minimized.

In einer vorteilhaften Ausgestaltung sind in den Rotor bzw. in den Flügelwänden Öffnungen eingearbeitet, die einen Zu- oder Abfluss von Hydraulikmittel (wie z.B. Motoröl) erlauben. Diese Öffnungen sind an den in Umfangsrichtung gegenüberliegenden Flügelwänden angeordnet. Die Anzahl der Öffnungen kann über die funktionell notwendigen zwei gegenüberliegenden Öffnungen an einem Flügel des Rotors hinausgehen, um z.B. den Zu- bzw. Abfluss in den Flügel zu optimieren. So können auf einer Flügelseite mehrere Öffnungen in Umfangsrichtung vorgesehen sein.In an advantageous embodiment, openings are made in the rotor or in the wing walls, which allow inflow or outflow of hydraulic fluid (such as engine oil). These openings are arranged on the circumferentially opposite wing walls. The number of apertures may extend beyond the functionally necessary two opposing apertures on a blade of the rotor, e.g. to optimize the inflow and outflow into the wing. Thus, a plurality of openings can be provided in the circumferential direction on one wing side.

Wird eine Arbeitskammer A mit Hydraulikmittel beaufschlagt, so gelangt das Hydraulikmittel durch diese Öffnungen in den Flügel des Rotors und drückt den Steuerflügel aus seiner Ruhelage, welcher wiederum das Druckspeichergehäuse relativ zum Rotor verdreht und somit die der Arbeitskammer A zugeordnete Druckspeicheröffnung freilegt. Der Hydraulikmitteldruck bei Motorstart ist gering, jedoch ausreichend um den Steuerflügel entgegen der Steuerfedermittel zu bewegen. Nun gelangt Hydraulikmittel in den Druckraum und spannt die Druckspeicherfeder geringfügig vor. Derweil steigt der Hydraulikmitteldruck weiter mit der Drehzahl des Motors an, wobei nun der Rotor gegenüber dem Stator relativ verdreht wird. Beim Verdrehvorgang wird die Druckkammer weiter mit Hydraulikmittel befüllt und der steigende Hydraulikmitteldruck sorgt weiter für eine Auslenkung der Druckspeicherfeder. Ist der Verstellvorgang abgeschlossen wird die Hydraulikmittelzuleitung zur Arbeitskammer A von der Motorpumpe getrennt und der Steuerflügel wird durch die Steuerfedermittel in seine Ruhelage gebracht, wobei die Druckspeicheröffnungen wieder verschlossen werden. Die Relativposition von dem Rotor zum Stator kann über einen Verriegelungsmechanismus gesichert werden, damit der sinkende Hydraulikmitteldruck in der Arbeitskammer A keine Rückwärtsdrehung hervorruft. Das Hydraulikmittelvolumen in der Druckkammer ist nun durch die Druckspeicherfeder vorgespannt und der Druckspeicher ist aufgeladen.If a working chamber A is acted upon by hydraulic fluid, the hydraulic fluid passes through these openings in the wing of the rotor and pushes the control wing from its rest position, which in turn rotates the pressure accumulator housing relative to the rotor and thus exposes the pressure accumulator opening associated with the working chamber A. The hydraulic fluid pressure at engine start is low, but sufficient to move the control wing against the control spring means. Now hydraulic fluid enters the pressure chamber and biases the accumulator spring slightly before. Meanwhile, the hydraulic fluid pressure continues to increase with the speed of the engine, now the rotor relative to the stator is relatively rotated. During the turning process, the pressure chamber is further filled with hydraulic fluid and the increasing hydraulic fluid pressure further ensures a deflection of the pressure accumulator spring. If the adjustment process is completed, the hydraulic fluid supply to the working chamber A is separated from the motor pump and the control wing is brought by the control spring means in its rest position, wherein the pressure storage openings are closed again. The relative position of the rotor to the stator can be secured via a locking mechanism, so that the decreasing hydraulic fluid pressure in the working chamber A causes no reverse rotation. The hydraulic fluid volume in the pressure chamber is now biased by the pressure accumulator spring and the pressure accumulator is charged.

Durch Druckbeaufschlagung der Kammer B erfolgt eine Rückstellung des Rotors relativ zum Stator über den Hydraulikmittelkanal b zur Arbeitskammer B. So wird der ggf. vorhandene Verriegelungsmechanismus entriegelt und der Druck in der Arbeitskammer B beginnt zu steigen. Der Steuerflügel wird entgegen seiner vorherigen Richtung ausgelenkt und öffnet die Druckspeicheröffnungen auf der Gegenseite des Steuerflügels zur Arbeitskammer B hin. Nun kann der hohe Druck im Druckspeicher unterstützend zum ansteigenden Druck in der Arbeitskammer B genutzt werden, um den Verstellvorgang beschleunigt einzuleiten.By pressurizing the chamber B, a provision of the rotor relative to the stator via the hydraulic fluid passage b to the working chamber B. Thus, the possibly existing locking mechanism is unlocked and the pressure in the working chamber B begins to rise. The control wing is deflected against its previous direction and opens the accumulator ports on the opposite side of the control wing to the working chamber B out. Now, the high pressure in the accumulator can be used to support the increasing pressure in the working chamber B, to initiate the adjustment accelerated.

Der aufgeladene Druckspeicher ist vorteilhaft bei Motorstart, um den noch nicht ausreichend vorhandenen Motoröldruck zu unterstützen. Der Druckspeicher unterstützt auch bei laufendem Betrieb die Verstellung in eine Drehrichtung. Zudem lenken unerwünschte Druckspitzen aus Nockenwechselmomenten den Steuerflügel durch den Druckpeak in der Arbeitskammer aus, und können somit in den Druckspeicher entweichen. Auch kann ein "Umpumpen" aus der einen Arbeitskammer in die andere Arbeitskammer durch die Druckkammer des Druckspeichers erfolgen, wodurch sich bei entsprechender Ansteuerung eines Steuerventils zur Steuerung der Hydraulikmittelströme eine geregelte Position des Rotors relativ zum Stator einstellen lässt.The supercharged accumulator is advantageous at engine start-up to support the insufficient engine oil pressure. The pressure accumulator also supports adjustment in one direction of rotation during operation. In addition, unwanted pressure peaks from cam change moments deflect the control blade through the pressure peak in the working chamber, and thus can escape into the pressure accumulator. Also, a "pumping" from one working chamber into the other working chamber through the pressure chamber of the pressure accumulator, which can be adjusted relative to the stator with appropriate control of a control valve for controlling the hydraulic fluid flows a controlled position of the rotor.

In einer weiteren bevorzugten Ausgestaltung der Erfindung hat der Druckspeicher mit dem Druckspeicherkolben zumindest einen Abstandshalter, welcher im unbedruckten Zustand, also wenn der Druckspeicher nicht aufgeladen ist, die Druckspeicherfeder vorspannt und somit einen Abstand in Arbeitsrichtung vorhält, welcher einen Raum definiert, in das das Hydraulikmittel einströmen kann. Dieser Abstandshalter kann als Nase oder Erhebung am Druckspeicherkolben, am Druckspeichergehäuse oder an beiden ausgebildet sein. Mehrere Abstandshalter können zudem gleichmäßig über den Umfang verteilt sein. Selbstverständlich lassen sich Aufbau und die Wirkungsweise des Druckspeichers mit dem Steuerflügel auch an dem Stator und dessen Flügeln realisieren und das Beispiel vom Rotor kann auf den Stator übertragen werden.In a further preferred embodiment of the invention, the pressure accumulator with the accumulator piston has at least one spacer, which in the unprinted state, ie when the pressure accumulator is not charged, biases the pressure accumulator spring and thus maintains a distance in the working direction, which defines a space in which the hydraulic fluid can flow in. This spacer may be formed as a nose or elevation on the pressure accumulator piston, the pressure accumulator housing or both. Several spacers can also be distributed evenly around the circumference. Of course, structure and the operation of the pressure accumulator with the control wing can also be realized on the stator and its wings and the example of the rotor can be transferred to the stator.

Kurze Beschreibung der ZeichnungenBrief description of the drawings Ausführungsbeispiele der Erfindung sind in den Figuren dargestellt.Embodiments of the invention are illustrated in the figures.

Es zeigen:

Fig. 1
einen Querschnitt durch einen Nockenwellenversteller in der einen Anschlagsposition,
Fig. 2
einen Längsschnitt gemäß I-I aus Fig. 1,
Fig. 3
einen Querschnitt durch den Nockenwellenversteller in der anderen Anschlagsposition,
Fig. 4
einen Längsschnitt gemäß III-III aus Fig. 3,
Fig. 5
einen Längsschnitt gemäß II-II aus Fig. 3,
Fig. 6
eine isometrische Ansicht der Scheibe (23),
Fig. 7
eine isometrische Ansicht auf die offene Seite des Druckspeichergehäuses (7),
Fig. 8
eine isometrische Ansicht auf die Gegenseite des Druckspeichergehäuses (7) und
Fig. 9
eine isometrische Ansicht auf den Druckspeicherkolben (9).
Show it:
Fig. 1
a cross section through a camshaft adjuster in the one stop position,
Fig. 2
a longitudinal section according to II Fig. 1 .
Fig. 3
a cross section through the camshaft adjuster in the other stop position,
Fig. 4
a longitudinal section according to III-III Fig. 3 .
Fig. 5
a longitudinal section according to II-II Fig. 3 .
Fig. 6
an isometric view of the disc (23),
Fig. 7
an isometric view of the open side of the pressure accumulator housing (7),
Fig. 8
an isometric view of the opposite side of the pressure accumulator housing (7) and
Fig. 9
an isometric view of the pressure accumulator piston (9).

Detaillierte Beschreibung der ZeichnungenDetailed description of the drawings

Fig. 1 zeigt einen Nockenwellenversteller 1 in einer Querschnittsdarstellung mit Blick auf die Arbeitskammern A und B. Der Nockenwellenversteller 1 besteht aus einem Antriebsrad 22, einem Stator 2, einem Rotor 3, einer Abdeckhaube 21, einer Scheibe 23, einem Verriegelungsmechanismus 20, einem Druckspeicher 6 und dem Adapterteil 25. Weiterhin ist die Zentralschraube 24 mit der konzentrisch angeordneten, aus dem Stand der Technik bekannten, Entlüftungsbohrung zu erkennen. Die Zentralschraube 24 befestigt den Nockenwellenversteller 1 am Nockenwellenende 26. Das Antriebsrad 22, die Abdeckhaube 21, der Stator 2, der Rotor 3, das Adapterteil 25 und der Druckspeicher 6 sind konzentrisch zueinander und zur Drehachse 4 des Nockenwellenverstellers 1 angeordnet. Der Druckspeicher 6 hat Steuerflügel 11 mit Steuerfedermitteln 19, welche im unbedruckten Zustand, also in der Ruhelage oder in der Startposition des Nockenwellenverstellers 1, in einer Mittenposition relativ zum Flügel 5 des Rotors 3 verharren. Die Drehachse 4 des Nockenwellenverstellers1 befindet sich senkrecht zu der Zeichenebene und im Schnittpunkt des Mittelkreuzes. Der Nockenwellenversteller 1 ist mit der Zentralschraube 24 ebenfalls, wie im Stand der Technik bekannt, konzentrisch zum Nockenwellenende 26 angeordnet. Fig. 1 shows a camshaft adjuster 1 in a cross-sectional view with respect to the working chambers A and B. The camshaft adjuster 1 consists of a drive wheel 22, a stator 2, a rotor 3, a cover 21, a disc 23, a locking mechanism 20, a pressure accumulator 6 and Adapter part 25. Furthermore, the central screw 24 can be seen with the concentrically arranged, known from the prior art, vent hole. The central screw 24 fastens the phaser 1 on the camshaft end 26. The drive wheel 22, the cover 21, the stator 2, the rotor 3, the adapter part 25 and the pressure accumulator 6 are arranged concentrically to one another and to the rotational axis 4 of the camshaft adjuster 1. The accumulator 6 has control wing 11 with control spring means 19, which remain in the unprinted state, ie in the rest position or in the starting position of the camshaft adjuster 1, in a central position relative to the wing 5 of the rotor 3. The axis of rotation 4 of the camshaft adjuster 1 is perpendicular to the plane of the drawing and at the intersection of the central cross. The camshaft adjuster 1 is also arranged concentrically to the camshaft end 26 with the central screw 24, as is known in the prior art.

Wird nun durch eine vorgesehene, nicht dargestellte, Zuführung von Hydraulikmittel die Arbeitskammer A druckbeaufschlagt, so dreht sich der Rotor 3 entgegen dem Uhrzeigersinn relativ zum Stator 2. Dabei sind Stator 3, Antriebsrad 22, Abdeckhaube 21, Scheibe 23, Adapterteil 25 und Verschlußteil 28 (in Fig. 2 erkennbar) drehfest zueinander ausgebildet und durch das Fügen von Adapterteil 25 und Verschlußteil 28 wird dieser Verbund axial gesichert. Der gesamte Verbund wird über das Antriebsrad 22 nach im Stand der Technik bekannten Zugmitteln von der Kurbelwelle angetrieben. Der begrenzte Winkelbereich wird bestimmt durch die Anordnung von Flügeln 5 am Stator 2 und am Rotor 3, welche sich radial erstrecken und gegenseitig wirkende, weitestgehend hydraulikmitteldichte Arbeitskammern A, B definieren. Aufbau und Wirkungsweise des Nockenwellenverstellers 1 ist aus dem Stand der Technik der Flügelzellenversteller zu entnehmen und dem Fachmann hinreichend bekannt, so dass hier im Folgenden weiter auf die Unterschiede zum Stand der Technik und die Wirkungsweise der Erfindung eingegangen wird.If the working chamber A is pressurized by an intended, not shown, supply of hydraulic fluid, the rotor 3 rotates counterclockwise relative to the stator 2. Stator 3, drive wheel 22, cover 21, disc 23, adapter part 25 and closure member 28th (in Fig. 2 recognizable) rotationally fixed to each other and formed by the joining of adapter part 25 and closure member 28 of this composite is axially secured. The entire composite is driven by the drive wheel 22 by traction means known in the art from the crankshaft. The limited angular range is determined by the arrangement of vanes 5 on the stator 2 and on the rotor 3, which extend radially and define mutually-acting, as far as possible hydraulic medium-tight working chambers A, B. The structure and mode of operation of the camshaft adjuster 1 can be seen from the prior art of the vane cell adjuster and sufficiently well known to the person skilled in the art, so that the differences between the prior art and the mode of operation of the invention will be discussed below.

Bei Druckbeaufschlagung der Hydraulikmittelversorgung für die Arbeitskammer A gelangt Hydraulikmittel entlang des Hydraulikmittelpfades a in die Arbeitskammer A und durch die Öffnungen 12 in den Flügel 5 des Rotors 3. Dort wird der Steuerflügel 11 entgegen dem Steuerfedermittel 19 betätigt. Der Steuerflügel 11 und das Druckspeichergehäuse 7 verdrehen sich gegenüber dem Rotor 3 in einem begrenzten Winkelbereich, so dass zwischen Druckspeichergehäuse 7 und Rotor 3 eine Druckspeicheröffnung 14 freigelegt wird. Ist diese Druckspeicheröffnung 14 geöffnet, fließt das Hydraulikmittel durch die Druckspeicheröffnung 14 in die Druckspeicherkammer 10. Gleichzeitig zum Öffnungsvorgang wird die auf der Gegenseite des Steuerflügels 11 befindliche Druckspeicheröffnung 14 geschlossen. Der Steuerflügel 11 befindet sich nun im Anschlag innerhalb des Flügels 5 des Rotors 3. Nun erfolgt eine Verstellung des Rotors 3 gegenüber des Stators 2 entgegen dem Uhrzeigersinn bei gleichzeitigem Befüllen der Druckspeicherkammer 10. Die Verstellung ist abgeschlossen, wenn sich ein Flügel 5 des Rotors 3 im Anschlag mit einem komplementären Flügel 5 des Stators 2 befindet. Ein Flügel 5 des Rotors 3 ist hier mit dem Verriegelungsmechanismus 20 ausgerüstet. Der Verriegelungsmechanismus 20 ist drucklos verriegelt und rastet in dieser Anschlagsposition vom Stator 2 mit dem Rotor 3 ein. Während der Verstellung wurde der Hydraulikmittelkanal b gemäß dem bekannten Oil-Pressure-Aktuating Prinzip zum Tank hin geöffnet. Dadurch konnte überschüssiges Hydraulikmittel vom Verriegelungsmechanismus über den Hydraulikmittelkanal B abgeführt werden.When pressurizing the hydraulic fluid supply for the working chamber A hydraulic fluid passes along the hydraulic fluid path a in the working chamber A and through the openings 12 in the wing 5 of the rotor 3. There, the control wing 11 is actuated against the control spring means 19. The control wing 11 and the accumulator housing 7 rotate relative to the rotor 3 in a limited angular range, so that between pressure accumulator housing 7 and rotor 3, an accumulator opening 14 is exposed. If this accumulator opening 14 is opened, the hydraulic fluid flows through the pressure accumulator opening 14 into the pressure accumulator chamber 10. Simultaneously with the opening process, the pressure accumulator opening 14 located on the opposite side of the control wing 11 is closed. The control wing 11 is now in abutment within the wing 5 of the rotor 3. Now, an adjustment of the rotor 3 with respect to the stator 2 counterclockwise while simultaneously filling the pressure storage chamber 10. The adjustment is completed when a wing 5 of the rotor. 3 in the stop with a complementary wing 5 of the stator 2 is located. A wing 5 of the rotor 3 is here equipped with the locking mechanism 20. The locking mechanism 20 is locked without pressure and engages in this stop position of the stator 2 with the rotor 3 a. During the adjustment, the hydraulic fluid channel b was opened according to the known oil-pressure Aktuating principle to the tank. As a result, excess hydraulic fluid could be removed from the locking mechanism via the hydraulic fluid channel B.

Fig. 2 zeigt einen Längsschnitt gemäß I-I aus Fig. 1 zur Verdeutlichung des Pfades entlang dem Hydraulikmittelkanal a und der Funktionsweise des Druckspeichers 6. Die Zuleitung erfolgt über ein Nockenwellenlager des Nockenwellenendes 26, über radiale Bohrungen 27, in die Aufnahme für die Zentralschraube 24. Über eine Passage, gebildet durch den radialen Spalt zwischen Zentralschraube 24 und Nockenwellenende 26 bzw. Adapterteil 25 gelangt das Hydraulikmittel zu einer radialen Bohrung 27 im Adapterteil 25 und wird in die Arbeitskammer A geleitet. Der weitere Pfad ist schematisch in Fig. 1 entlang des gestrichelten Pfeils dargestellt. Fig. 2 shows a longitudinal section according to II Fig. 1 to illustrate the path along the hydraulic fluid channel a and the operation of the pressure accumulator 6. The supply line via a camshaft bearing of the camshaft end 26, via radial holes 27, in the receptacle for the central screw 24. Via a passage formed by the radial gap between the central screw 24th and camshaft end 26 and adapter part 25 passes the hydraulic fluid to a radial bore 27 in the adapter part 25 and is directed into the working chamber A. The further path is schematic in Fig. 1 shown along the dashed arrow.

Das Hydraulikmittel, welches durch die Druckspeicheröffnungen 14 in die Druckspeicherkammer 10 gelangt, spannt die Druckspeicherfeder 8 über den Druckspeicherkolben 9 vor. Der Druckspeicher 6 ist nun aufgeladen.The hydraulic fluid, which passes through the pressure storage openings 14 into the pressure storage chamber 10, biases the pressure storage spring 8 via the pressure storage piston 9. The accumulator 6 is now charged.

Fig. 3 zeigt einen Querschnitt durch den Nockenwellenversteller 1 in der anderen Anschlagsposition, wobei der Verstellvorgang im Uhrzeigersinn abgeschlossen ist. In der Ausgangsposition nach Fig. 1 und dem aufgeladenen Druckspeicher 6 wird nun der Hydraulikkanal b druckbeaufschlagt und der Hydraulikkanal a zum Tank geöffnet. Durch die Zuleitung zur Arbeitskammer B gelangt wiederum Hydraulikmittel durch Arbeitskammer B durch die Öffnungen 12 in das Innere des Flügels 5. Hier wirkt der Druck des Hydraulikmittels auf den Steuerflügel 11 von der gegenüberliegenden Seite, als bei der Verstellung entgegen dem Uhrzeigersinn. Dabei verstellt sind nun der Steuerflügel 11 im Flügel 5 zuerst im Uhrzeigersinn bis zum Anschlag im Flügel 5. Dabei werden die Druckspeicheröffnungen 14 zur Arbeitskammer A geschlossen und die Druckspeicheröffnungen 14 zur Arbeitskammer B geöffnet. Der aufgeladene Druckspeicher 6 kann durch die vorgespannte Druckspeicherfeder 8 das vorher eingeschlossene Hydraulikmittelvolumen wieder freigeben und in die Arbeitskammer B fließen lassen. Es wird deutlich, dass bereits geringere Mengen Hydraulikmittel beim Erreichen der Arbeitskammern A oder B den Steuerflügel 11 bereits verstellen können, bevor der Hydraulikmitteldruck ausreicht, um den Rotor 3 zu bewegen. Der aufgeladene Druckspeicher 6 unterstützt bei Motorstart oder Hydraulikmittelmangelversorgung die Verstellung des Rotors 3. Fig. 3 shows a cross section through the camshaft adjuster 1 in the other stop position, the adjustment is completed in a clockwise direction. In the starting position after Fig. 1 and the charged pressure accumulator 6, the hydraulic channel b is now pressurized and the hydraulic channel a is opened to the tank. Through the supply line to the working chamber B again hydraulic fluid passes through working chamber B through the openings 12 in the interior of the wing 5. Here, the pressure of the hydraulic fluid acts on the control wing 11 from the opposite side, as in the adjustment in the counterclockwise direction. In this case, now the control wing 11 in the wing 5 are first clockwise until it stops in the wing 5. The pressure accumulator openings 14 are closed to the working chamber A and the pressure accumulator openings 14 to the working chamber B opened. The charged pressure accumulator 6 can release the previously enclosed volume of hydraulic fluid through the preloaded pressure accumulator spring 8 and let flow into the working chamber B. It is clear that even smaller amounts of hydraulic fluid on reaching the working chambers A or B can already adjust the control blade 11 before the hydraulic fluid pressure is sufficient to move the rotor 3. The charged pressure accumulator 6 supports the adjustment of the rotor 3 when the engine is started or when the hydraulic fluid supply is insufficient.

Fig. 4 zeigt einen Längsschnitt gemäß III-III aus Fig. 3 zur Verdeutlichung des Pfades entlang des Hydraulikmittelkanals b. Über eine weitere radiale Bohrungen 27 wird aus dem Nockenwellenlager des Nockenwellenendes 26 Hydraulikmittel in eine zur Drehachse 4 parallel verlaufende Bohrung 27 in eine fluchtende Bohrung 27 des Adapterteils 25 geleitet. Dieses Hydraulikmittel sammelt sich vorerst in einer Kammer, welche von dem Adapterteil 25, dem Druckspeichergehäuse 7 und dem Rotor 3 umgrenzt ist. Jedoch besitzt die Scheibe 23 Vertiefungen, bzw. Wanddickenreduzierungen, die zusammen mit dem Rotor 3 einen Zulauf in die Arbeitskammer B herstellen (siehe Fig. 5). Weiterhin ist die Entlüftung 17 des Federraumes 18 erkennbar. Die Entlüftung 17 ist durch achsparallele Bohrungen zur Drehachse 4 realisiert und führt Fremdstoffe aus dem Federraum 18 im Betrieb heraus. Die achsparallelen Bohrungen der Entlüftung 17 sind im Rotor 3, im Stator 2 und in dem Verschlußteil 28 derartig angeordnet, dass ein zueinander gebildeter Öffnungsquerschnitt verbleibt. Die Anordnung der achsparallelen Bohrungen der Entlüftung 17 kann idealerweise fluchtend sein. Fig. 4 shows a longitudinal section according to III-III Fig. 3 to illustrate the path along the hydraulic fluid channel b. Via a further radial bores 27, hydraulic medium is conducted from the camshaft bearing of the camshaft end 26 into a bore 27 running parallel to the rotational axis 4 into an aligned bore 27 of the adapter part 25. This hydraulic fluid initially collects in a chamber, which is bounded by the adapter part 25, the pressure accumulator housing 7 and the rotor 3. However, the disc has 23 recesses, or wall thickness reductions, which together with the rotor 3 make an inlet into the working chamber B (see Fig. 5 ). Furthermore, the vent 17 of the spring chamber 18 can be seen. The vent 17 is realized by axially parallel holes to the axis of rotation 4 and carries foreign matter from the spring chamber 18 during operation out. The axially parallel holes of the vent 17 are arranged in the rotor 3, in the stator 2 and in the closure member 28 such that a mutually formed opening cross-section remains. The arrangement of the axis-parallel bores of the vent 17 may ideally be in alignment.

Fig. 5 zeigt einen Längsschnitt gemäß III-III aus Fig. 3 zur weiteren Veranschaulichung des Hydraulikmittelpfades b. Hierbei sind die in Fig. 4 erwähnten, zur Drehachse 4 parallelen Bohrungen 27 ersichtlich. Des Weiteren eröffnet sich ein Blick auf die Gestaltung des Zulaufes von Hydraulikmittel durch die Öffnungen 12 im Rotor 3. Fig. 5 shows a longitudinal section according to III-III Fig. 3 to further illustrate the hydraulic fluid path b. Here are the in Fig. 4 mentioned, parallel to the axis of rotation 4 holes 27 can be seen. Furthermore, a look at the design of the inlet of hydraulic fluid through the openings 12 in the rotor 3 opens.

Fig. 6 zeigt eine isometrische Ansicht der Scheibe 23. Hierbei sind schematisch die Zuläufe entlang des Hydraulikmittelkanals a, b zu den Arbeitskammern A, B, jedoch ohne die peripheren Bauelemente, dargestellt. Fig. 6 shows an isometric view of the disc 23. Here, the inlets along the hydraulic fluid channel a, b to the working chambers A, B, but without the peripheral components, are shown schematically.

Fig. 7 zeigt eine isometrische Ansicht auf die offene Seite 15 des Druckspeichergehäuses 7. Die sich radial als Blechlasche 13 erstreckenden Steuerflügel 11 sind unregelmäßig am Umfang angeordnet. Diese Unregelmäßigkeit resultiert aus der Anordnung des Verriegelungsmechanismus 20 im Rotor 3, wobei beim Fügen des Druckspeichergehäuses 7 mit dem Rotor 3 der Flügel 5 mit dem Verriegelungsmechanismus 20 von einem Steuerflügel 11 unbesetzt bleibt. Für den Fall, dass ein Verriegelungsmechanismus 20 nicht vorgesehen ist, kann sich die Anzahl der Steuerflügel 11 mit Anzahl der Flügel 5 im Rotor 3 decken. Fig. 7 shows an isometric view of the open side 15 of the pressure accumulator housing 7. The radially extending as a sheet metal tab 13 control vanes 11 are arranged irregularly on the circumference. This irregularity results from the arrangement of the locking mechanism 20 in the rotor 3, wherein when joining the pressure accumulator housing 7 with the rotor 3, the wing 5 with the locking mechanism 20 remains unoccupied by a control wing 11. In the event that a locking mechanism 20 is not provided, the number of control vanes 11 may coincide with the number of vanes 5 in the rotor 3.

Fig. 8 zeigt eine isometrische Ansicht auf die Gegenseite des Druckspeichergehäuses 7. Zu erkennen sind die Druckspeicheröffnungen 14 für die jeweiligen Hydraulikpfade a, b, welche wechselseitig an den Steuerflügeln 11 angeordnet sind. Dabei können die Druckspeicheröffnungen 14 jede beliebige Querschnittsform, wie quadratisch, rund, oval usw. aufweisen, die für eine Einstellung des Durchflusses dienlich ist. Das Druckspeichergehäuse 7 ist vorteilhafterweise als Blechteil ausgebildet und durch die Steuerflügel 11 als Blechlaschen zum Aufstecken auf das Druckspeichergehäuse wirtschaftlich komplettiert. Fig. 8 shows an isometric view of the opposite side of the pressure accumulator housing 7. To recognize the pressure accumulator openings 14 for the respective hydraulic paths a, b, which are mutually arranged on the control vanes 11. In this case, the pressure storage openings 14 may have any desired cross-sectional shape, such as square, round, oval, etc., which is useful for adjusting the flow. The accumulator housing 7 is advantageously formed as a sheet metal part and completed by the control wing 11 as sheet metal tabs for attachment to the accumulator housing economically.

Fig. 9 zeigt eine isometrische Ansicht auf den Druckspeicherkolben 9. Dieser besitzt vier, gleichmäßig am Umfang verteilte, einteilig mit dem Druckspeicherkolben ausgebildete, Abstandshalter 30. Die Abstandshalter 30 können jede beliebige Gestalt annehmen, die der Funktion, einen Mindestfreiraum in der Druckspeicherkammer 10 vorzuhalten, dienlich ist. Am äußeren und am inneren Durchmesser des Druckspeicherkolbens 9 ist eine Nut zum Einsetzen eines Dichtringes 29 vorgesehen, um die Druckspeicherkammer 10 gegenüber dem Federraum 18 abzudichten. Fig. 9 shows an isometric view of the pressure accumulator piston 9. This has four, evenly distributed, integrally formed with the accumulator piston, spacer 30. The spacers 30 may take any shape that serves the function of providing a minimum free space in the pressure accumulator chamber 10 is useful , At the outer and inner diameter of the pressure accumulator piston 9, a groove for inserting a sealing ring 29 is provided to seal the pressure storage chamber 10 relative to the spring chamber 18.

Liste der BezugszahlenList of reference numbers

1)1)
NockenwellenverstellerPhaser
2)2)
Statorstator
3)3)
Rotorrotor
4)4)
Drehachseaxis of rotation
5)5)
Flügelwing
6)6)
Druckspeicheraccumulator
7)7)
DruckspeichergehäuseAccumulator housing
8)8th)
DruckspeicherfederAccumulator spring
9)9)
DruckspeicherkolbenAccumulator piston
10)10)
DruckspeicherkammerPressure storage chamber
11)11)
Steuerflügelcontrol wing
12)12)
Öffnungenopenings
13)13)
Blechlaschesheet tab
14)14)
DruckspeicheröffnungPressure store opening
15)15)
offene Seiteopen side
16)16)
Stirnseitefront
17)17)
Entlüftungvent
18)18)
Federraumspring chamber
19)19)
SteuerfedermittelControl spring means
20)20)
Verriegelungsmechanismuslocking mechanism
21)21)
Abdeckhaubecover
22)22)
Antriebsraddrive wheel
23)23)
Scheibedisc
24)24)
Zentralschraubecentral screw
25)25)
Adapterteiladapter part
26)26)
Nockenwellenendecamshaft end
27)27)
Bohrungdrilling
28)28)
Verschlußteilclosing part
29)29)
Dichtringseal
30)30)
Abstandshalterspacer
A)A)
Arbeitskammer AWorking chamber A
B)B)
Arbeitskammer BWorking chamber B
a)a)
HydraulikmittelpfadHydraulic fluid path
b)b)
HydraulikmittelpfadHydraulic fluid path

Claims (10)

Nockenwellenversteller (1), welcher einen Stator (2) und einen Rotor (3) aufweist, wobei der Rotor (3) und der Stator (2) relativ zueinander verdrehbar sind, wobei der Rotor (3) und der Stator (2) mehrere, radial gerichtete Flügel (5) aufweist, wobei die Flügel (5) gegenseitig wirkende Arbeitskammern (A, B) ausbilden, welche mit Hydraulikmittel beaufschlagbar sind, um den Rotor (3) relativ zum Stator (2) zu verdrehen und der Nockenwellenversteller (1) einen Druckspeicher (6) zur druckbeaufschlagten Speicherung von Hydraulikmittel aufweist dadurch gekennzeichnet, dass der Druckspeicher (6) einen Steuerflügel (11) aufweist, wobei der Steuerflügel (11) von einem Flügel (5) des Rotors (3) oder des Stators (2) umragt wird.Camshaft adjuster (1) having a stator (2) and a rotor (3), wherein the rotor (3) and the stator (2) are rotatable relative to each other, wherein the rotor (3) and the stator (2), radially directed wing (5), said wings (5) forming mutually-acting working chambers (A, B), which are acted upon by hydraulic means to rotate the rotor (3) relative to the stator (2) and the camshaft adjuster (1) an accumulator (6) for the pressurized storage of hydraulic fluid, characterized in that the accumulator (6) has a control wing (11), the control wing (11) being supported by a wing (5) of the rotor (3) or the stator (2) is surmounted. Nockenwellenversteller (1) nach Anspruch 2, dadurch gekennzeichnet, dass der Steuerflügel (11) durch Steuerfedermittel (19) beaufschlagt wird und in einer Mittenposition relativ zum Flügel (5) des Rotors (3) oder des Stators (2) ruht.Camshaft adjuster (1) according to claim 2, characterized in that the control wing (11) by control spring means (19) is acted upon and in a central position relative to the wing (5) of the rotor (3) or the stator (2) rests. Nockenwellenversteller (1) nach Anspruch 2, dadurch gekennzeichnet, dass die Druckspeicherfeder (8) des Druckspeichers (6) als das Steuerfedermittel (19) ausgebildet ist.Camshaft adjuster (1) according to claim 2, characterized in that the pressure accumulator spring (8) of the pressure accumulator (6) as the control spring means (19) is formed. Nockenwellenversteller (1) nach Anspruch 1, dadurch gekennzeichnet, dass der Steuerflügel (11) als eine sich in radialer Richtung erstreckende Blechlasche (13) ausgebildet ist.Camshaft adjuster (1) according to claim 1, characterized in that the control wing (11) is designed as a sheet metal tab (13) extending in the radial direction. Nockenwellenversteller (1) nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass der Flügel (5), welcher den Steuerflügel (11) umragt, Öffnungen (12) zu den Hydraulikkammern (A, B) aufweist, mit denen Hydraulikmittel von den Arbeitskammern (A, B) zu dem Steuerflügel (11) gelangen kann.Camshaft adjuster (1) according to claim 2 or 3, characterized in that the wing (5), which surrounds the control wing (11), openings (12) to the hydraulic chambers (A, B), with which hydraulic means from the working chambers (A , B) can reach the control wing (11). Nockenwellenversteller (1) nach Anspruch 2, dadurch gekennzeichnet, dass der Druckspeicher (6) eine Druckspeicheröffnung (14) aufweist, welche durch den Steuerflügel (11) in eine Offen- bzw. eine Schließstellung bewegt wird.Camshaft adjuster (1) according to claim 2, characterized in that the pressure accumulator (6) has a pressure accumulator opening (14), which is moved by the control vanes (11) in an open or a closed position. Nockenwellenversteller (1) nach Anspruch 1, dadurch gekennzeichnet, dass der Druckspeicher (6) mit dem Steuerflügel (11) einteilig ausgebildet ist.Camshaft adjuster (1) according to claim 1, characterized in that the pressure accumulator (6) with the control vanes (11) is integrally formed. Nockenwellenversteller (1) nach Anspruch 2, dadurch gekennzeichnet, dass der Druckspeicher (6) im Querschnitt ein U-Profil aufweist und mit seiner offenen Seite (15) zu der Stirnseite (16) des Nockenwellenverstellers (1) gerichtet ist und der Federraum (18) des Druckspeichers (6) eine Entlüftung (17) aufweist.Camshaft adjuster (1) according to claim 2, characterized in that the pressure accumulator (6) has a U-profile in cross section and with its open side (15) to the end face (16) of the camshaft adjuster (1) is directed and the spring chamber (18 ) of the pressure accumulator (6) has a vent (17). Nockenwellenversteller (1) nach Anspruch 1, dadurch gekennzeichnet, dass der Druckspeicherkolben (9) und/oder das Druckspeichergehäuse (7) des Druckspeichers (6) mindestens einen Abstandshalter (30) aufweist, welcher die Druckspeicherfeder (8) des Druckspeichers (6) vorspannt.Camshaft adjuster (1) according to claim 1, characterized in that the pressure accumulator piston (9) and / or the accumulator housing (7) of the pressure accumulator (6) has at least one spacer (30) which biases the pressure accumulator spring (8) of the pressure accumulator (6) , Druckspeicher (6) eines Nockenwellenverstellers (1) nach Anspruch 1.Pressure accumulator (6) of a camshaft adjuster (1) according to claim 1.
EP11191381.0A 2011-02-11 2011-11-30 Camshaft adjuster with a pressure storage unit Not-in-force EP2487339B1 (en)

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EP2487339B1 (en) 2013-09-25
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EP2487339A3 (en) 2013-01-23
US20120204822A1 (en) 2012-08-16

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