EP2488730B1 - Accumulateur de volume - Google Patents

Accumulateur de volume Download PDF

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Publication number
EP2488730B1
EP2488730B1 EP10773600.1A EP10773600A EP2488730B1 EP 2488730 B1 EP2488730 B1 EP 2488730B1 EP 10773600 A EP10773600 A EP 10773600A EP 2488730 B1 EP2488730 B1 EP 2488730B1
Authority
EP
European Patent Office
Prior art keywords
guide housing
indentation
camshaft
spring
spring element
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP10773600.1A
Other languages
German (de)
English (en)
Other versions
EP2488730A1 (fr
Inventor
Eduard Golovatai-Schmidt
Mathias Boegershausen
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 EP2488730A1 publication Critical patent/EP2488730A1/fr
Application granted granted Critical
Publication of EP2488730B1 publication Critical patent/EP2488730B1/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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—Location oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/20—Accumulator cushioning means
    • F15B2201/21—Accumulator cushioning means using springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/31—Accumulator separating means having rigid separating means, e.g. pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/405—Housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/60—Assembling or methods for making accumulators
    • F15B2201/605—Assembling or methods for making housings therefor

Definitions

  • the invention relates to a volume accumulator with a guide housing, a separating element and a spring element, wherein the separating element is displaceably mounted on an inner circumferential surface of the guide housing and the spring element rests on the one hand on the separating element and on the other hand on the guide housing.
  • Volume accumulators are used, for example, in internal combustion engines to support the pressure medium supply of a hydraulic consumer, for example a camshaft adjuster or an electrohydraulic valve actuation device.
  • Camshaft adjusters are for example from the DE 195 29 277 A1 or the EP 0 806 550 A1 known.
  • a volume memory is for example in the DE 10 2007 041 552 A1 disclosed.
  • the volume accumulator has a hollow-cylindrical guide housing and a separating element received axially displaceably in the guide housing, in the illustrated embodiment a cup-shaped piston which divides the interior of the guide housing into a storage space and a complementary space.
  • the piston By pressurizing the piston, it is displaced against the force of a spring element in the direction of a stop, whereby the volume of the storage space increases at the expense of the volume of the complementary space.
  • the displacement of the piston is limited by the fact that an open end of a jacket portion of the pot-shaped piston on an annular, separate from the guide housing trained stop comes to the plant.
  • the annular stop abuts against a radially extending wall at an axial end of the guide housing.
  • the spring element is supported on the one hand on the piston and on the other hand on the radially extending wall of the guide housing.
  • the invention has for its object to provide a volume storage, the production cost is to be reduced.
  • the object is achieved in that at least one indentation is formed on the guide housing, which projects into the guide housing, wherein the indentation in the direction of the spring element has an open end against which abuts the spring element.
  • the volume accumulator has a separating element, for example a piston, on which is displaceably mounted within a guide housing and separates a storage space from a complementary space.
  • a separating element for example a piston
  • This is displaced within the guide housing against a spring element in the direction of a stop, which limits the displacement path of the separating element in that this comes to rest against the stop.
  • a spring bearing is provided, wherein the spring element is supported on the one hand on the spring bearing and on the other hand on the separating element.
  • the spring bearing is formed from the material of the guide housing.
  • a slot is provided in the example, hollow cylindrical guide housing, which runs along a non-self-contained line.
  • the slot extends at least partially in a plane perpendicular to the direction of displacement of the piston.
  • the slot can be introduced, for example, by punching or fine cutting in the guide housing.
  • In the area of the slot is on the guide housing provided a recess which projects into the interior of the guide housing.
  • an open end of the indentation produced by the slot faces the end of the spring element and serves this as a spring bearing.
  • Conceivable are embodiments with one or more circumferentially spaced indentations. By the open end is meant the area which was connected to the guide housing prior to the insertion of the slot.
  • the spring bearing is formed integrally with the guide housing, so that no additional components are required, which must be connected to the guide housing.
  • the introduction of the indentation can be realized inexpensively.
  • the indentation can take a variety of forms. Conceivable, for example, embodiments in which a slot is introduced into the guide housing, which is arranged completely in a plane perpendicular to the direction of displacement of the piston. Subsequently, the indentation is introduced in the region of the slot in the guide housing. Likewise conceivable are embodiments in which the indentation is designed as a tab. In this case, a deviating from a straight line slot is introduced into the guide housing, which forms a connected to the guide housing tab. This can for example be triangular or square and optionally arched according to the shape of the guide housing and protrudes into the guide housing.
  • the separating element may be formed, for example, as a cup-shaped piston with a bottom and a shell section adjoining thereto, wherein the spring element bears against the bottom.
  • the guide housing and the piston without cutting are each made of a sheet metal blank, for example by means of a deep drawing process.
  • the bottom of the piston serves as a pressure surface, which is acted upon by the inflowing pressure medium with a force, whereby the piston is displaced.
  • the lateral surface serves to support the piston in the guide housing, with the open end of the jacket section coming into contact with the stop when the volume reservoir is completely filled.
  • FIG. 1 an internal combustion engine 1 is sketched, wherein a seated on a crankshaft 2 piston 3 is indicated in a cylinder 4.
  • the crankshaft 2 is in the illustrated embodiment via a respective traction drive 5 with an intake camshaft 6 and exhaust camshaft 7 in combination, with a first and a second camshaft adjuster 11 for a relative rotation between the crankshaft 2 and the camshafts 6, 7 can provide.
  • Cams 8 of the camshafts 6, 7 actuate one or more intake gas exchange valves 9 or one or more Auslassgas scaffoldventile 10.
  • the Figures 2 and 3 show a camshaft adjuster 11 in longitudinal or in cross section.
  • a volume accumulator 15 which is arranged in a camshaft 6, 7, which is non-rotatably connected to the camshaft adjuster 11.
  • the phaser 11 includes a drive element 14, an output element 16 and two side covers 17, 18 which are arranged on the axial side surfaces of the drive element 14.
  • the output element 16 is designed in the form of an impeller and has a substantially cylindrical hub member 19, extend from the outer cylindrical surface in the illustrated embodiment, five wings 20 in the radial direction outwardly.
  • five pressure chambers 22 are provided, wherein in each pressure chamber 22, a wing 20 protrudes.
  • the wings 20 are formed such that they rest against both the side covers 17, 18, and on the peripheral wall 21. Each wing 20 thus divides the respective pressure chamber 22 into two counteracting pressure chambers 23, 24th
  • a sprocket 12 is formed, via which by means of a chain drive, not shown, torque from the crankshaft 2 to the drive element 14 can be transmitted.
  • the output member 16 is rotatably connected by means of a central screw 13 with the camshaft 6,7.
  • the output element 16 is arranged rotatably in a defined Winkelbreich to the drive element 14.
  • the phase position of the drive element 14 to the output element 16 (and thus the phase angle of the camshaft 6, 7 to the crankshaft 2) can be varied.
  • the phase position can be kept constant.
  • the camshaft 6, 7 has a plurality of openings 28, via which pressure medium conveyed by a pressure medium pump 37 passes into its interior.
  • a pressure medium path 29 is formed, which communicates on the one hand with the openings 28 and on the other hand with a control valve 27, which serves to supply the camshaft adjuster 11 with pressure medium.
  • the control valve 27 is arranged in the interior of the central screw 13. By means of the control valve 27, pressure medium can be selectively directed to the first or second pressure chambers 23, 24 and discharged from the respective other pressure chambers 23, 24.
  • a pressure medium channel 30 is provided, which communicates on the one hand with the pressure medium path 29 and on the other hand with a cavity 31 of the hollow camshaft 6, 7.
  • the pressure medium channel 30 is formed as an axial bore, which passes through the threaded portion of the central screw 13.
  • the volume accumulator 15 is arranged in the cavity 31, the volume memory 15 comprises a guide housing 33, a separating element 34 and a force accumulator, which is designed in the illustrated embodiment as a spring element 35 in the form of a helical compression spring.
  • the guide housing 33 is non-positively connected to a wall 36 of the cavity 31. Also conceivable are embodiments in which the guide housing 33 is connected to the wall 36 in a material- or form-fitting manner.
  • the separating element 34 is arranged axially displaceable, which in the illustrated embodiment as cup-shaped piston with a bottom 25 and a jacket portion 26 becamemiger Piston having a bottom 25 and a skirt portion 26 is formed.
  • the jacket section 26 By means of the jacket section 26, the separating element 34 is mounted axially displaceably in the guide housing 33.
  • the outer lateral surface of the separating element 34 is adapted to the inner lateral surface of the guide housing 33 in such a way that the guide housing 33 is separated in a pressure medium-tight manner into a reservoir 45 axially in front of and a complementary space 46 behind the bottom 25 of the separating element 34.
  • the spring element 35 is supported on the one hand on a spring bearing 39 (FIG. FIG.
  • the spring element 35 acts on the separating element 34 with a force in the direction of the pressure medium channel 30.
  • the spring bearing 39 is formed by three radial recess 47 of the guide housing 33, which project into this.
  • 33 three first slots 40 are inserted into the cylindrical guide housing, which extend in the circumferential direction of the guide housing 33 and are spaced in the circumferential direction. Subsequently, the guide housing 33 is deformed radially inwardly in the areas between the first slots 40 and the end remote from the camshaft.
  • the depth of the recesses 47 is selected so that the spring element 35 abuts the recesses 47 even at maximum spring eccentricity at the open ends, which were separated by the first slots 40 of the guide housing 33.
  • the spring bearing 39 is formed integrally with the guide housing 33, whereby the manufacturing cost and the production cost decrease.
  • the displacement of the separating element 34 is limited in the direction of the pressure medium channel 30 by an annular, radially inwardly extending portion of the guide housing 33 which surrounds a housing opening 38 through which the volume memory 15 pressure medium can be supplied.
  • the displacement of the separating element 34 is limited by a stop.
  • the stop is made between the axial ends of the guide housing 33 in the form of three indentations 41, which are formed integrally with the guide housing 33 and project into this ( Figures 4-6 ). Also conceivable are embodiments with more or fewer indentations.
  • Each indentation 41 has an open end on the side facing the separating element 34, the open end having a surface perpendicular to the direction of movement of the separating element 34.
  • each indentation 41 protrudes into the guide housing 33 in such a way that its open end faces the open end of the jacket section 26 of the separating element 34 in its direction of displacement.
  • these open ends of the indentations 41 serve the separation element 34 as a stop.
  • each indentation 41 has a guide section 43 which extends in the axial direction and runs parallel to the axis of the spring element 35.
  • the diameter of the spring element 35 is selected so that it bears against the guide sections 43 in the compressed state.
  • the spring element 35 experiences by the guide portions 43 a bearing, whereby the radial position of the spring element 35 is fixed.
  • the length L of the guide portion 43 is greater than the distance between two spring coils in the relaxed state. This ensures that due to the bearing of the spring element 35 on the guide portions 43, the spring element 35 is not tilted or jammed on the stop of the indentation 41.
  • the guide housing 33 and the separating element 34 are formed as sheet metal parts, which are made for example by a non-cutting manufacturing process, for example, a deep drawing process.
  • this has the advantage that the bearing surfaces of the jacket section 26 and of the guide housing 33 can be produced so precisely by this shaping process that they do not have to be reworked.
  • the first slot 40 describes a curved line with two ends, so that a tab 44 is formed, which projects into the guide housing 33.
  • a volume memory 15 is in FIG. 7 shown in a perspective view.
  • a rectangular tab 44 is formed by an L-shaped second slot 40, which projects into the guide housing 33.
  • a portion of the L-shaped slot 40 extends in the circumferential direction of the guide housing 33, so that the open end formed thereby serves as a spring bearing 39.
  • the second portion of the L-shaped slot 40 extends to the end of the guide housing 33.
  • the tab 44 merges into the guide housing 33 in the axial direction.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (2)

  1. Accumulateur de volume (15) comprenant un boîtier de guidage (33), un élément de séparation (34) et un élément ressort (35), l'élément de séparation (34) étant monté de manière déplaçable sur une surface d'enveloppe intérieure du boîtier de guidage (33) et l'élément ressort (35) s'appliquant d'un côté contre l'élément de séparation (34) et de l'autre côté contre le boîtier de guidage (33),
    caractérisé en ce qu'au moins un renfoncement (47) est réalisé sur le boîtier de guidage (33), lequel renfoncement fait saillie dans le boîtier de guidage (33), le renfoncement (47) présentant, dans la direction de l'élément ressort (35), une extrémité ouverte contre laquelle s'applique l'élément ressort (35).
  2. Accumulateur de volume (15) selon la revendication 1, caractérisé en ce que le renfoncement (47) est réalisé sous forme de languette (44).
EP10773600.1A 2009-10-15 2010-10-14 Accumulateur de volume Not-in-force EP2488730B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009049461A DE102009049461A1 (de) 2009-10-15 2009-10-15 Volumenspeicher
PCT/EP2010/065400 WO2011045368A1 (fr) 2009-10-15 2010-10-14 Accumulateur de volume

Publications (2)

Publication Number Publication Date
EP2488730A1 EP2488730A1 (fr) 2012-08-22
EP2488730B1 true EP2488730B1 (fr) 2013-12-11

Family

ID=43417082

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10773600.1A Not-in-force EP2488730B1 (fr) 2009-10-15 2010-10-14 Accumulateur de volume

Country Status (5)

Country Link
US (1) US20120199231A1 (fr)
EP (1) EP2488730B1 (fr)
CN (1) CN102575535B (fr)
DE (1) DE102009049461A1 (fr)
WO (1) WO2011045368A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011075537A1 (de) * 2011-05-10 2012-11-15 Schaeffler Technologies AG & Co. KG Hubkolbenbrennkraftmaschine mit Nockenwellenverstelleinrichtung
DE102012218802B4 (de) 2012-10-16 2018-05-17 Schaeffler Technologies AG & Co. KG Steuerventil für ein Nockenwellenverstellersystem
CN109373037B (zh) * 2018-11-14 2024-03-26 宁波太平洋电控系统有限公司 一种带有凸轮轴润滑结构的中央阀阀套

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4657230A (en) * 1980-04-21 1987-04-14 American Standard Inc. Overtravel spring assembly for slack adjuster
GB8430562D0 (en) * 1984-12-04 1985-01-09 Carpenter & Paterson Ltd Spring support device
DE3633836C1 (de) * 1986-10-04 1988-03-31 Ford Werke Ag Temperaturkompensiertes Steuerventil,insbesondere Akkumulatorventil fuer hydraulische Steuerung von Kraftfahrzeuggetrieben
DE3941241C2 (de) * 1989-12-14 2002-03-21 Continental Teves Ag & Co Ohg Kolbendruckspeicher, insbesondere für antriebsschlupfgeregelte Bremsanlagen, sowie Schaltanordnung dazu
DE19529277A1 (de) 1995-08-09 1997-02-13 Bayerische Motoren Werke Ag Verfahren zum Betreiben einer hydraulisch gesteuerten/geregelten Nockenwellen-Verstellvorrichtung für Brennkraftmaschinen
FR2740528B1 (fr) * 1995-10-30 1999-09-17 Bernard Claude Andre Francois Dispositif d'assemblage pour supports elastiques de charges mobiles
DE69709231T3 (de) 1996-03-28 2009-01-08 Aisin Seiki K.K., Kariya Ventilzeitsteuerungsvorrichtung
US5996632A (en) * 1998-12-14 1999-12-07 Aeroquip Corporation Pressure relief adapter
US6782856B2 (en) * 2002-04-09 2004-08-31 Ford Global Technologies, Llc Camshaft accumulator
WO2008140897A1 (fr) * 2007-05-14 2008-11-20 Borgwarner Inc. Accumulateur monté sur came
DE102007041552A1 (de) 2007-08-31 2009-03-05 Schaeffler Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
US9038668B2 (en) * 2010-03-16 2015-05-26 Gm Global Technology Operations, Llc Accumulator assembly

Also Published As

Publication number Publication date
US20120199231A1 (en) 2012-08-09
WO2011045368A1 (fr) 2011-04-21
DE102009049461A1 (de) 2011-04-21
EP2488730A1 (fr) 2012-08-22
CN102575535B (zh) 2014-07-02
CN102575535A (zh) 2012-07-11

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