EP2488730A1 - Accumulateur de volume - Google Patents

Accumulateur de volume

Info

Publication number
EP2488730A1
EP2488730A1 EP10773600A EP10773600A EP2488730A1 EP 2488730 A1 EP2488730 A1 EP 2488730A1 EP 10773600 A EP10773600 A EP 10773600A EP 10773600 A EP10773600 A EP 10773600A EP 2488730 A1 EP2488730 A1 EP 2488730A1
Authority
EP
European Patent Office
Prior art keywords
guide housing
indentation
spring element
separating element
camshaft
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
EP10773600A
Other languages
German (de)
English (en)
Other versions
EP2488730B1 (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

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • 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 having a guide housing, a separating element and a spring element, wherein the separating element is displaceably mounted on an inner lateral 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 known, for example, from DE 195 29 277 A1 or EP 0 806 550 A1.
  • a volume memory is disclosed, for example, in DE 10 2007 041 552 A1.
  • 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.
  • a cup-shaped piston which divides the interior of the guide housing into a storage space and a complementary space.
  • 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 foundedsgefeldu- se, 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. Embodiments are conceivable, for example, in which a slot is made in the guide housing, which is arranged completely in a plane perpendicular to the displacement direction of the piston. Subsequently, the indentation is introduced in the region of the slot in the guide housing.
  • the indentation is designed as a tab.
  • a slot deviating from a straight line is introduced into the guide housing, which forms a tab connected to the guide housing.
  • 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 can be designed, for example, as a cup-shaped piston with a base and a jacket section adjoining it, the spring element resting against the base.
  • 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 shows very schematically an internal combustion engine
  • FIG. 2 shows a longitudinal section through a camshaft adjuster, which is fastened to a camshaft, in which a first embodiment of a volume accumulator is arranged
  • FIG. 3 shows a cross section through the camshaft adjuster from FIG. 2 along the line III-III, the central screw not being shown, FIG.
  • FIG. 4 shows detail X from FIG. 2 without camshaft
  • Figure 5 shows a cross section through the volume storage along the line
  • Figure 6 is a perspective view of the first embodiment of a
  • Figure 7 is a perspective view of a second embodiment of a volume memory.
  • FIG. 1 shows 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, wherein a first and a second camshaft adjuster 1 1 for relative rotation between the crankshaft 2 and the camshafts 6, 7 can provide.
  • Cams 8 of the camshafts 6, 7 actuate one or more inlet gas exchange valves 9 or one or more exhaust gas exchange valves 10. Equally, it may be provided only one of the camshafts 6, 7 with a Nockenwellenvers- teller 1 1, or only a camshaft 6, 7 provide, which is provided with a camshaft adjuster 1 1.
  • Figures 2 and 3 show a camshaft adjuster 1 1 in the longitudinal or in the cross section.
  • Figure 2 shows a volume accumulator 15 which is arranged in a camshaft 6, 7, which is non-rotatably connected to the camshaft adjuster 1 1.
  • the camshaft adjuster 1 1 comprises 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 driven element 16 is designed in the form of an impeller and has a substantially cylindrical hub element 19, from the outer cylindrical surface of which in the illustrated embodiment, five wings 20 extend in the radial direction to the outside.
  • each pressure chamber 22 is 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 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 1 1 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 to be axially displaceable, wherein in the illustrated embodiment this is designed as a cup-shaped piston with a bottom 25 and a jacket section 26. miger piston with 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. 4), which is formed on the end of the guide housing 33 remote from the camshaft adjuster 11, and on the other hand on the bottom 25 of the separating element 34.
  • 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 indentations 47 even at maximum spring eccentricity at the open ends which have been separated from the guide housing 33 by the first slots 40.
  • the spring bearing 39 is formed integrally with the guide housing 33, whereby the manufacturing cost and the manufacturing 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.
  • the indentations 41 are produced in two stages. First, a second slot 42 is inserted into the guide housing 33, which extends in the circumferential direction of the guide housing 33. Subsequently, the material of the guide housing 33 in the region of the second slot 42 is plastically deformed into the guide housing and thus the indentation 41 is formed.
  • 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. In addition to low manufacturing costs, 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 shown in Figure 7 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.

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)

Abstract

La présente invention concerne un accumulateur de volume (15) comprenant un boîtier de guidage (33), un élément de séparation (34) et un élément de rappel (35), l'élément de rappel (34) étant monté pour pouvoir coulisser contre une surface périphérique intérieure du boîtier de guidage (33), et l'élément de rappel (35) étant en contact d'un côté avec l'élément de séparation (34) et d'un autre côté avec le boîtier de guidage (33). Selon l'invention, dans le boîtier de guidage (33) est formée au moins une rainure (47) qui s'étend vers l'intérieur du boîtier de guidage (33), la rainure (47) présentant en direction de l'élément de rappel (35) une extrémité ouverte contre laquelle l'élément de rappel (35) vient en contact.
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 true EP2488730A1 (fr) 2012-08-22
EP2488730B1 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

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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

Non-Patent Citations (1)

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Title
See references of WO2011045368A1 *

Also Published As

Publication number Publication date
DE102009049461A1 (de) 2011-04-21
EP2488730B1 (fr) 2013-12-11
WO2011045368A1 (fr) 2011-04-21
US20120199231A1 (en) 2012-08-09
CN102575535A (zh) 2012-07-11
CN102575535B (zh) 2014-07-02

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