EP2488731B1 - Volumenspeicher - Google Patents

Volumenspeicher Download PDF

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Publication number
EP2488731B1
EP2488731B1 EP20100781450 EP10781450A EP2488731B1 EP 2488731 B1 EP2488731 B1 EP 2488731B1 EP 20100781450 EP20100781450 EP 20100781450 EP 10781450 A EP10781450 A EP 10781450A EP 2488731 B1 EP2488731 B1 EP 2488731B1
Authority
EP
European Patent Office
Prior art keywords
guide housing
indentation
guide
spring 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.)
Not-in-force
Application number
EP20100781450
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2488731A1 (de
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 EP2488731A1 publication Critical patent/EP2488731A1/de
Application granted granted Critical
Publication of EP2488731B1 publication Critical patent/EP2488731B1/de
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
    • 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
    • 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
    • F01L2001/34446—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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7784—Responsive to change in rate of fluid flow
    • Y10T137/7792—Movable deflector or choke

Definitions

  • the invention relates to a volume accumulator with a guide housing and a separating element, wherein the separating element is displaceably mounted on an inner circumferential surface of 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 shell portion of the cup-shaped piston comes to rest on an annular, formed separately to the guide housing stop.
  • the annular stop abuts a radially extending wall at an axial end of the guide housing, at the same time the spring element is supported.
  • 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 separating element has an open end, which serves as a stop for the separating element.
  • the volume accumulator has a separating element, for example a piston, which is displaceably mounted within a guide housing and separates a storage space from a complementary space.
  • a separating element for example a piston
  • the latter is displaced within the guide housing in the direction of a stop which limits the displacement path of the separating element in that it comes into contact with the stop.
  • the stop secures the separator against unwanted leakage from the guide housing during its operation.
  • suitable spring strengths and spring lengths can be used and so the volume storage characteristics are designed appropriately.
  • the stopper 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 created by the slot is opposite the piston and serves as a stop.
  • the open end is meant the area which was connected to the guide housing prior to the insertion of the slot.
  • the stop is on the one hand formed integrally with the guide housing, so that no additional components are needed.
  • 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.
  • the indentation is designed as a tab.
  • 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.
  • a spring element is arranged, which passes through the region of the recess, wherein the indentation has a guide portion for the spring element whose length in the direction of force of the spring element is greater than the distance between two turns of the spring element.
  • the guide portion provides a guide surface for the spring element, the the piston against the force of the pressure medium applied with a force.
  • the spring element may be formed, for example, as a helical or helical compression spring. It is ensured by the appropriate choice of the length of the guide portion that always one turn of the spring element is arranged in this area and thus the spring element is sufficiently guided so that the spring coils do not tilt on the stop of the tab.
  • the separating element can be designed, for example, as a cup-shaped piston with a bottom and a shell section adjoining it.
  • 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 jacket portion of the piston and the inner circumferential surface of the guide housing may be formed, for example, cylindrical or polygonal in cross-section.
  • 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.
  • the sealing of the storage space relative to the complementary space via a closely tolerated clearance between the shell portion and the inner circumferential surface of the guide housing.
  • 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 inlet 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 formed on the one hand communicates 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, wherein this is formed in the illustrated embodiment as a cup-shaped piston having a bottom 25 and a jacket portion 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 as a radial indentation 47 of the guide housing 33.
  • a first slot 40 is inserted into the cylindrical guide housing 33, which extends in the circumferential direction of the guide housing 33.
  • the guide housing 33 is deformed radially inwardly in the region between the first slot 40 and the end remote from the camshaft.
  • the depth of the indentation 47 produced thereby is selected so that the spring element 35 bears against the open end of the spring bearing 39 even at maximum spring eccentricity, which has been separated from the guide housing 33 by the first slot 40.
  • 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. In the direction of the spring bearing 39, the displacement of the separating element 34 is limited by a stop.
  • the abutment is embodied 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 protrude 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 preparation of the indentations 41 takes place 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 projects into the guide housing 33 in such a way that the open end faces the open end of the jacket section 26 of the separating element 34 in its direction of displacement. Thus, these open ends of the indentations 41 serve the separation element 34 as a stop.
  • each indentation 41 has a guide portion 43 which extends in the axial direction and parallel to the axis of the spring element 35 runs.
  • 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 second slot 42 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 a U-shaped second slot 42, which projects into the guide housing 33.
  • a leg of the U-shaped slot 42 extends in a plane perpendicular to the direction of movement of the separating element 34, so that the stop is formed.
  • 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)
EP20100781450 2009-10-15 2010-10-14 Volumenspeicher Not-in-force EP2488731B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009049459A DE102009049459A1 (de) 2009-10-15 2009-10-15 Volumenspeicher
PCT/EP2010/065402 WO2011045369A1 (de) 2009-10-15 2010-10-14 Volumenspeicher

Publications (2)

Publication Number Publication Date
EP2488731A1 EP2488731A1 (de) 2012-08-22
EP2488731B1 true EP2488731B1 (de) 2014-09-03

Family

ID=43500227

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20100781450 Not-in-force EP2488731B1 (de) 2009-10-15 2010-10-14 Volumenspeicher

Country Status (5)

Country Link
US (1) US8707998B2 (zh)
EP (1) EP2488731B1 (zh)
CN (1) CN102549242B (zh)
DE (1) DE102009049459A1 (zh)
WO (1) WO2011045369A1 (zh)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010018203A1 (de) 2010-04-26 2011-10-27 Schaeffler Technologies Gmbh & Co. Kg Druckspeicheranordnung für ein Nockenwellenverstellsystem
DE102011075537A1 (de) * 2011-05-10 2012-11-15 Schaeffler Technologies AG & Co. KG Hubkolbenbrennkraftmaschine mit Nockenwellenverstelleinrichtung
DE102012201558B4 (de) * 2012-02-02 2017-09-07 Schaeffler Technologies AG & Co. KG Gestaltung eines Tankanschlusses in einem Nockenwellenversteller mit Volumenspeicher

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB8430562D0 (en) * 1984-12-04 1985-01-09 Carpenter & Paterson Ltd Spring support device
DE3705642A1 (de) * 1986-07-02 1988-01-14 Man Nutzfahrzeuge Gmbh Energiespeicher- und abgabeeinrichtung
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
DE4234217C2 (de) 1992-10-10 1996-07-11 Hemscheidt Fahrwerktech Gmbh Hydropneumatisches Federungssystem
JP3212384B2 (ja) * 1992-11-11 2001-09-25 株式会社ニチリン アキュムレータ
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
DE19725240A1 (de) * 1997-06-14 1998-12-17 Itt Mfg Enterprises Inc Druckmittelspeicher insbesondere für Hydraulikaggregate von elektronischen Bremssystemen für Kfz
US5996632A (en) * 1998-12-14 1999-12-07 Aeroquip Corporation Pressure relief adapter
DE102005015262A1 (de) * 2005-04-04 2006-10-05 Robert Bosch Gmbh Druckmittelspeicher, Speichereinheit aus mehreren Druckmittelspeichern und Verfahren zur Herstellung eines Druckmittelspeichers
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
CN102549242B (zh) 2014-04-09
US8707998B2 (en) 2014-04-29
EP2488731A1 (de) 2012-08-22
CN102549242A (zh) 2012-07-04
US20120199230A1 (en) 2012-08-09
WO2011045369A1 (de) 2011-04-21
DE102009049459A1 (de) 2011-04-21

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