EP2487339A2 - Dispositif de réglage d'arbres à came à l'aide d'un accumulateur de pression - Google Patents

Dispositif de réglage d'arbres à came à l'aide d'un accumulateur de pression 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
Authority
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)
English (en)
Other versions
EP2487339B1 (fr
EP2487339A3 (fr
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
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 EP2487339A2 publication Critical patent/EP2487339A2/fr
Publication of EP2487339A3 publication Critical patent/EP2487339A3/fr
Application granted granted Critical
Publication of EP2487339B1 publication Critical patent/EP2487339B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force

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)
EP11191381.0A 2011-02-11 2011-11-30 Dispositif de réglage d'arbres à came à l'aide d'un accumulateur de pression Not-in-force EP2487339B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011003991A DE102011003991A1 (de) 2011-02-11 2011-02-11 Nockenwellenversteller mit einem Druckspeicher

Publications (3)

Publication Number Publication Date
EP2487339A2 true EP2487339A2 (fr) 2012-08-15
EP2487339A3 EP2487339A3 (fr) 2013-01-23
EP2487339B1 EP2487339B1 (fr) 2013-09-25

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP11191381.0A Not-in-force EP2487339B1 (fr) 2011-02-11 2011-11-30 Dispositif de réglage d'arbres à came à l'aide d'un accumulateur de pression

Country Status (3)

Country Link
US (1) US8534248B2 (fr)
EP (1) EP2487339B1 (fr)
DE (1) DE102011003991A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009042228A1 (de) * 2009-09-18 2011-03-31 Schaeffler Technologies Gmbh & Co. Kg Vorrichtung zur Veränderung der relativen Winkellage einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine
DE102009054049B4 (de) * 2009-11-20 2020-08-27 Schaeffler Technologies AG & Co. KG Nockenwellenverstellanordnung
DE102012217394A1 (de) * 2012-09-26 2014-03-27 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller
DE102013203245A1 (de) * 2013-02-27 2014-08-28 Schaeffler Technologies Gmbh & Co. Kg Statortopf mit Einlegescheibe zur Reduzierung des Axiallagerspiels
GB201309954D0 (en) 2013-06-04 2013-07-17 Ford Global Tech Llc A method of controlling an engine oil supply
DE102014214125B4 (de) 2014-07-21 2018-01-04 Schaeffler Technologies AG & Co. KG Stelleinrichtung zur Verstellung von Steuerzeiten einer Brennkraftmaschine
DE102017102273A1 (de) 2017-02-06 2018-08-09 Denso Corporation Nockenwellensteller mit Dämpfungs-Akkumulator

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19529277A1 (de) 1995-08-09 1997-02-13 Bayerische Motoren Werke Ag Verfahren zum Betreiben einer hydraulisch gesteuerten/geregelten Nockenwellen-Verstellvorrichtung für Brennkraftmaschinen
EP0806550A1 (fr) 1996-03-28 1997-11-12 Aisin Seiki Kabushiki Kaisha Dispositif de commande du calage des soupapes

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3929621A1 (de) * 1989-09-06 1991-03-07 Bayerische Motoren Werke Ag Vorrichtung zur relativen drehwinkelverstellung einer welle zu einem antriebsrad, insbesondere nockenwelle einer brennkraftmaschine
JP2003328709A (ja) * 2002-03-08 2003-11-19 Aisin Seiki Co Ltd 弁開閉時期制御装置
DE102004028868A1 (de) * 2004-06-15 2006-01-05 Ina-Schaeffler Kg Brennkraftmaschine mit einer hydraulischen Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle
DE102006004760A1 (de) * 2006-02-02 2007-10-11 Schaeffler Kg Hydraulischer Nockenwellenversteller
WO2008140897A1 (fr) * 2007-05-14 2008-11-20 Borgwarner Inc. Accumulateur monté sur came
DE102009024482A1 (de) * 2009-06-10 2010-12-16 Schwäbische Hüttenwerke Automotive GmbH Nockenwellen-Phasensteller mit Druckspeicher
DE102009034804B4 (de) * 2009-07-25 2018-03-01 Schaeffler Technologies AG & Co. KG Druckspeicher zur Unterstützung der Druckmittelversorgung eines Nockenwellenverstellers einer Brennkraftmaschine
DE102009035815A1 (de) * 2009-08-01 2011-02-03 Schaeffler Technologies Gmbh & Co. Kg Volumenspeicher

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19529277A1 (de) 1995-08-09 1997-02-13 Bayerische Motoren Werke Ag Verfahren zum Betreiben einer hydraulisch gesteuerten/geregelten Nockenwellen-Verstellvorrichtung für Brennkraftmaschinen
EP0806550A1 (fr) 1996-03-28 1997-11-12 Aisin Seiki Kabushiki Kaisha Dispositif de commande du calage des soupapes

Also Published As

Publication number Publication date
EP2487339B1 (fr) 2013-09-25
US20120204822A1 (en) 2012-08-16
DE102011003991A1 (de) 2012-08-16
EP2487339A3 (fr) 2013-01-23
US8534248B2 (en) 2013-09-17

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