WO2013174533A1 - Soupape de commande d'un déphaseur d'arbre à cames - Google Patents

Soupape de commande d'un déphaseur d'arbre à cames Download PDF

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Publication number
WO2013174533A1
WO2013174533A1 PCT/EP2013/054761 EP2013054761W WO2013174533A1 WO 2013174533 A1 WO2013174533 A1 WO 2013174533A1 EP 2013054761 W EP2013054761 W EP 2013054761W WO 2013174533 A1 WO2013174533 A1 WO 2013174533A1
Authority
WO
WIPO (PCT)
Prior art keywords
sleeve
control valve
threaded body
designed
camshaft
Prior art date
Application number
PCT/EP2013/054761
Other languages
German (de)
English (en)
Inventor
Markus Kinscher
Jens Hoppe
Alexander Bäcker
Christoph Ross
Alexander Fichtner
Original Assignee
Schaeffler Technologies AG & 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 & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to US14/402,233 priority Critical patent/US20150144211A1/en
Priority to CN201380027485.7A priority patent/CN104350241B/zh
Publication of WO2013174533A1 publication Critical patent/WO2013174533A1/fr

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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L5/00—Slide valve-gear or valve-arrangements
    • F01L5/14—Slide valve-gear or valve-arrangements characterised by the provision of valves with reciprocating and other movements
    • 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
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust

Definitions

  • the invention relates to a control valve of a camshaft adjuster.
  • Camshaft phasers are used in internal combustion engines for varying the timing of the combustion chamber valves in order to be able to variably shape the phase relation between a crankshaft and a camshaft in a defined torque range between a maximum early and a maximum late position. Adjusting the timing to the current load and speed reduces fuel consumption and emissions.
  • camshaft adjuster are integrated into a drive train, via which a torque is transmitted from the crankshaft to the camshaft. This drive train may be formed for example as a belt, chain or gear drive.
  • the output element and the drive element form one or more pairs of mutually acting pressure chambers, which can be acted upon by hydraulic fluid.
  • the drive element and the driven element are arranged coaxially. By filling and emptying individual pressure chambers, a relative movement is generated between the drive element and the output element.
  • the spring acting in a rotational manner between the drive element and the driven element urges the drive element in relation to the driven element into an advantage direction.
  • This advantage direction can be the same or opposite to the direction of rotation.
  • the vane cell dispenser One type of hydraulic camshaft adjuster is the vane cell dispenser.
  • the Flugfzellenversteller has a stator, a rotor and a drive wheel with an external toothing.
  • the rotor is designed as a driven element usually rotatably connected to the cam.
  • the drive element includes the stator and the drive wheel.
  • the stator and the drive wheel are rotatably connected to each other or alternatively formed integrally with each other.
  • the rotor is coaxial with the stator and located inside the stator.
  • the rotor and the stator are characterized by their, radially extending wings, oppositely acting oil chambers, which are acted upon by oil pressure and allow relative rotation between the stator and the rotor
  • the wings are either integrally formed with the rotor or the stator or as "
  • the stator and the sealing cover are secured together via a plurality of screw connections Oil pressure a slide member axially displaced, which generates a helical gear teeth relative rotation between a drive element and an output member.
  • the control valves of the hydraulic camshaft adjuster control the hy- draulikstoff Kunststoffen between the camshaft adjuster and the ⁇ lpumpe or the oil reservoir (tank).
  • the control valve has a hollow cylindrical housing and a rotationally symmetrical control piston.
  • the control piston Within the housing of the control valve, the control piston is arranged.
  • the control piston is movable in the axial direction and guided by the housing.
  • the control piston can be positioned to the housing in any axial position. The positioning takes place by an electromagnet, which contacts with its actuating pin one end of the control piston and can move the control piston.
  • a spring ensures the contact between the control piston and the actuating pin. Due to the axial positioning of the control piston, the various ports of the control valve are hydraulically connected to each other or separated from each other and thus can communicate with each other or not.
  • control pistons and housings are provided with openings, eg grooves and / or bores.
  • the spool has control edges that control flow together with the edges of the housing's openings.
  • the control edges themselves are the edges of the respective opening, eg, of the control piston.
  • the edges of the openings of the housing and the control edges are positioned relative to each other so that an opening of the housing with an opening of the control piston as far as possible faces and forms, over the axial positionability of the Steuerkoibens, variable flow area for the Hydraultkmittei.
  • a control valve designed as a central valve is arranged coaxially to the axis of symmetry or rotation of the camshaft adjuster or the camshaft.
  • the central valve is placed inside the camshaft phaser, i. Central valve and camshaft divider build on each other in the radial direction.
  • the camshaft can be arranged between the camshaft distributor and the central valve.
  • the housing of the central valve may be formed as a central screw, whereby the Nockenwellenversteiler is clamped against rotation with the camshaft.
  • the solenoid is arranged as a central magnet largely aligned with the central valve and usually fixed to the frame, in particular on the cylinder head arranged.
  • the object of the invention is to provide a control valve of a camshaft adjuster, which allows a more economical production.
  • a control valve of a camshaft adjuster wherein the control valve for controlling the camshaft adjuster flows through the hydraulic medium and the control valve has an inflow port, several working ports and a tank port, wherein the control valve has a housing formed as a screw with a cylindrical cavity a control piston is guided axiallybewegbar, wherein the housing designed as a screw is formed in several parts, which has a threaded body and a sleeve, wherein the threaded body is connected to the threaded body peripherally arranged sleeve solved.
  • the housing has a plurality of openings and an axially movable in the cylindrical cavity of the housing control piston. wherein a control edge of the control piston is axially positionable to an opening of the housing for controlling the flow of hydraulic fluid between the inflow port, the working ports and the tank port so as to change the flow area for the hydraulic fluid flow between the ports through the opening.
  • the control valve is preferably designed as a central valve and thus the housing as a central screw, whereby the cam shaft is rotatably braced rotatably with the camshaft.
  • Different threaded bodies can vary in length, thread pitch and thread type and be adapted to an individually provided receptacle, for example the camshaft.
  • the threaded body is preferably designed as a threaded rod and has a threaded section " an expansion section and a form-fitting section.
  • the threaded portion is provided for anchoring, for example with a camshaft.
  • the expansion section is designed to provide the elasticity necessary for the screwdriver connection.
  • the positive connection section is designed for positive fastening with the sleeve.
  • Different sleeves can vary in length, diameter and finishing quality and to an individually provided receptacle, for example the hub of the camshaft adjuster. be adjusted.
  • the sleeve may have at one of its ends an attack body for an assembly tool, preferably for mounting the camshaft adjuster with the camshaft.
  • the attack body is advantageously designed as a hexagon analogous to a hexagon screw alternative screw head shapes may be formed instead of the hexagonal screw head.
  • the threaded body has a form-locking element, which is accommodated in a complementary receptacle of the sleeve, wherein by means of the positive connection, a connection between see the sleeve and the threaded body is formed.
  • the positive connection fixes the sleeve to the threaded body at least in the axial direction to each other.
  • the complementary receptacle may preferably be arranged in the bottom of the sleeve or on an inner circumference or outer circumference of the sleeve.
  • the positive-locking element preferably additionally has surfaces on a peripheral surface. which mate with surfaces of the complementary receptacle of the sleeve such that a torque between the two components can be transmitted.
  • an attack body for an assembly tool is formed by the sleeve.
  • the positive connection between the sleeve and the threaded body can not transmit sufficient torque for fastening the camshaft adjuster to the camshaft.
  • the sleeve and threaded body are axially and / or radially fixed to each other, but the positive locking allows for rotation between the sleeve and the threaded body.
  • the threaded body has an attack body for an assembly tool.
  • the attack body is advantageously designed as a hexagon analogous to a hexagon screw.
  • Alternative screw head shapes may be formed instead of the hexagonal screw head. This rotation can be completely without resistance, so play, or at least up to a certain torque, which is not sufficient for attachment of the camshaft adjuster to the camshaft. be trained without a game.
  • the complementary receptacle is disposed within the sleeve.
  • the complementary receptacle can preferably be arranged in the interior of the sleeve, preferably on an inner circumference or on the bottom on the side of the sleeve facing the inside of the sleeve.
  • the sleeve may have a pin which has the complementary receptacle on its inner circumference.
  • the complementary receptacle is located outside the sleeve.
  • the complementary receptacle may be disposed in the interior of the sleeve, the same case, the sleeve may have a pin which has on its outer circumference the complementary receptacle for the form-fitting element of the threaded body.
  • a machining process preferably turning, may be used to form the final shape of the threaded body.
  • the threaded body can be made exclusively by a machining process, preferably by turning.
  • the threaded body has a central passage opening.
  • this passage opening can be used as a supply connection.
  • the threaded body has an external thread which can be brought into engagement with an internal thread of a camshaft.
  • the threaded body has an internal thread, which can be brought into engagement with an external thread of a camshaft.
  • the thread, internal or external thread, of the threaded body can be adapted to the thread of the camshaft or different threads of the threaded body can be adapted to different camshafts be without having to make design or manufacturing changes to the sleeve, preferably with the control piston arranged therein.
  • control valve Due to the design of the control valve according to the invention, on the one hand a more economical production of the control valve becomes possible and, on the other hand, diverse configurations of different sleeves with different threaded bodies, especially in the assembly, are made possible which allow a high flexibility with regard to a broad spectrum of applications.
  • Fig. 1 is designed as a central valve control valve and 2 shows an inventive multi-part housing of a control valve designed as a central valve,
  • FIG. 1 shows a control valve 1 designed as a central valve.
  • the control valve 1 has a multi-part housing 2, a plastic sleeve 15, a guide sleeve 3, a control piston 4, two compression springs 18 and 20, a valve seat 21, a ball 19. a control piston 4, a Federabstützblech 33 and possibly a spacer 22. All The aforementioned components are arranged coaxially with each other and to a common axis of rotation 34, which is at the same time the axis of rotation 34 of a camshaft adjuster or a camshaft.
  • the multi-part housing 2, which is designed as a screw, is provided for the rotationally fixed attachment of the camshaft adjuster with the camshaft.
  • the multi-part housing 2 consists of a sleeve 6 and a threaded body 5.
  • the plastic sleeve 15 is received by an inner circumference of the sleeve 6.
  • the plastic sleeve 15 has channels and openings to direct hydraulic fluid from an inlet port P of the control valve 1 to the working ports A and B.
  • the working ports A and B are arranged at different, angularly offset positions as radial bores 24 and 25 of the sleeve 6.
  • the inlet connection P is formed by a passage opening 10 of the threaded body 5.
  • the passage opening 10 is formed as a bore coaxial with the axis of rotation 34 and passes completely through the threaded body 5.
  • the tank connection is located on the feed port P opposite end face 13 of the control valve. 1
  • the control piston 4 is subjected to a force by the compression spring 18 and pressed against the retaining ring 17.
  • the locking ring 17 secures the axial position of the plastic sleeve 15 and the control piston 4 within the sleeve 6.
  • the compression spring 18 is supported on the one hand on the control piston 4 and on the other hand on the Federabstützblech 33 from the spring support plate 33 is. as well as the Guide sleeve 18 and the valve seat plate 21, fixedly connected to the plastic sleeve 15.
  • the ball 19 is from the compression spring 20 against the Valvesrtzblech
  • the control piston 4 is guided over its outer circumference by a guide surface 9 of the guide sleeve 16.
  • the housing 2, or the sleeve 6, has a bore 23 which is closed by the spacer 22.
  • the spacer 22 positions the plastic sleeve 15 in such a way.
  • the spacer 22 may have in addition to its coaxial with the axis of rotation 34 arranged passage opening a plurality of radial bores, which may optionally conduct hydraulic fluid from the bore 23 to the control piston 4 and thus the Bore 23 may be available as an additional inlet connection, working connection or tank connection.
  • the sleeve 6 has on the end face 13, on which the tank connection T is arranged, a flange 14 and on the end face 13 opposite end face 30 a perforated bottom 35.
  • the inner peripheral surface 36 of the perforated bottom 35 is circular and coaxial with the axis of rotation 24
  • This inner peripheral surface 36 is part of the complementary receptacle 8 for the form-locking element 7, wherein said inner peripheral surface 36 an outer peripheral surface 37 of the form-fitting portion 27 of the threaded body 5 Tontaktiert and fixed the threaded body 5 radially to the axis of rotation 34. Between the inner peripheral surface 36 and the outer peripheral surface 37, one or no radial clearance may be provided.
  • the complementary receptacle 8 of the sleeve 6 has a further inner circumferential surface 38. which has a larger diameter than the inner peripheral surface 36.
  • the inner peripheral surface 38 adjoins the annular inner surface 40 in the axial direction along the axis of rotation 34 and in the direction of the end face 3.
  • This inner circumferential surface 38 contacts an outer peripheral surface 39 of the form-fitting portion 27 of the threaded body 5 and fixes the threaded body 5 in the radial direction to the axis of rotation 34 with the sleeve 6. Between the inner peripheral surface 38 and the outer peripheral surface 39, one or no radial play can be provided.
  • At least either the inner peripheral surface 38 and the outer peripheral surface 39 or between the inner peripheral surface 36 and the outer peripheral surface 37 of the positive connection is rotatably formed.
  • the inner circumferential surface 38 and the outer peripheral surface 39 and / or the inner peripheral surface 36 and the outer peripheral surface 37 may each have a cylindrical shape and be provided with or without radial play, respectively. If no radial play is provided for at least one surface pairing, this frictional connection, preferably an interference fit, can form the rotationally fixed connection. Is at both surface pairings a radial game provided, the rotationally fixed connection may be formed by shitting, gluing or soldering.
  • the threaded body 5 is divided into three sections, the positive connection section 27, the expansion section 26 and the threaded section 31.
  • the form-fitting portion 27 has the cylindrical outer peripheral surface 37, the annular outer surface 41 and the cylindrical outer peripheral surface 39. In the direction of the axis of rotation 34 joins the cylindrical outer peripheral surface 39 of the form-fitting portion 27 of the expansion portion 26, which has a smaller cross-section than form-fitting portion 27 or the threaded portion 31.
  • the expansion portion 26 is formed in its length and in its cross-section such that the desired preload force can be realized.
  • the threaded portion 31 adjoins the expansion portion 26, which has an external thread for engagement with an internal thread of a camshaft.
  • the threaded body 6 is formed as a forming part.
  • the expansion section 26 and the threaded section 31 are formed by material displacements.
  • the external thread of the threaded section 31 is rolled.
  • the passage opening 10 can either be drilled or formed by an extrusion process. Cutting processes, for example, such as turning or grinding, can additionally find application for the formation of desired tolerance ranges.
  • the sleeve 6 has, starting from the penetrated by the threaded body 5 bottom 35 and then to the complementary receptacle 8 on the cylindrical cavity 3. in which the aforementioned components are arranged.
  • a flange 14 is formed, which is designed as a radially projecting collar.
  • the flange 14 has an attack body 32 with a screw head 12 and a stop surface 28 for contacting with a camshaft adjuster.
  • the attack body 32 points forming a plurality of surfaces to "the screw head 12 on the outer periphery of the flange fourteenth
  • the arrangement of the surfaces corresponding to a hex "on edge the abutment surface 28 is formed as an annular surface and oriented toward the other end side 30th
  • the sleeve 6 is formed as a formed part, preferably as a deep-drawn part or extruded part.
  • the structure of the attack body 32 of the flange 14 designed as a screw head 12 as well as the cylindrical cavity 3 and the complementary receptacle 8 can advantageously be formed by this method.
  • the hole in the bottom 35 as well as the radial bores 23, 24, 25 can be formed by a stamping process. Cutting processes, for example, such as turning or grinding, can additionally be used to form desired tolerance ranges.
  • FIG. 2 shows a multi-part housing 2 according to the invention of a control valve 1 designed as a central valve.
  • the structure is similar to the housing 2 from FIG. 1, therefore only the differences are discussed below.
  • the attack body 32 is formed by the form-fitting portion 27 of the threaded body 5.
  • the screw head 12 of the attack body 32 is designed here as an inner hexagon.
  • the flange 14 has a cylindrical outer lateral surface and, functionally, has only the abutment surface 28, which is provided for contacting with a camshaft adjuster. In addition, the flange 14 is arranged at a distance from the end face 13. The arrangement and the design of the connections (inflow connection, working connection, tank connection) is neglected here in favor of clarifying the invention.
  • the pairing of the inner peripheral surface 38 and the outer peripheral surface 39 may be formed as shown.
  • the inner peripheral surface 38 is formed as a hexagon socket and the ⁇ ußsenindisisation 39 cylindrical. Again, little or no play can be provided in this surface pairing.
  • the formed as a hexagon inner peripheral surface 38 may alternatively be formed as an outer hexagon formed effetheral connection 39, whereby a rotationally fixed connection between the sleeve 6 and the
  • Threaded body 5 can be formed.
  • the multi-part housing 2 is first mounted with a camshaft adjuster and a camshaft, followed by the assembly of the component arranged in the cylindrical cavity.
  • the guide surface 9 of the cylindrical cavity 3 can be contacted directly by a control piston 4.

Landscapes

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

Abstract

Soupape de commande (1) d'un déphaseur d'arbre à cames, comportant un carter (2) en plusieurs parties se présentant sous forme de vis.
PCT/EP2013/054761 2012-05-25 2013-03-08 Soupape de commande d'un déphaseur d'arbre à cames WO2013174533A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US14/402,233 US20150144211A1 (en) 2012-05-25 2013-03-08 Control valve of a camshaft adjuster
CN201380027485.7A CN104350241B (zh) 2012-05-25 2013-03-08 凸轮轴调节器的控制阀

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102012208786.9 2012-05-25
DE102012208786 2012-05-25
DE102013203951A DE102013203951A1 (de) 2012-05-25 2013-03-08 Steuerventil eines Nockenwellenverstellers
DE102013203951.4 2013-03-08

Publications (1)

Publication Number Publication Date
WO2013174533A1 true WO2013174533A1 (fr) 2013-11-28

Family

ID=49547147

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2013/054761 WO2013174533A1 (fr) 2012-05-25 2013-03-08 Soupape de commande d'un déphaseur d'arbre à cames

Country Status (4)

Country Link
US (1) US20150144211A1 (fr)
CN (1) CN104350241B (fr)
DE (1) DE102013203951A1 (fr)
WO (1) WO2013174533A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013104573B4 (de) * 2013-05-03 2018-05-17 Hilite Germany Gmbh Hydraulikventil und Schwenkmotorversteller
DE102014210365B4 (de) * 2014-06-02 2021-05-12 Schaeffler Technologies AG & Co. KG Zentralventil für einen Nockenwellenversteller einer Hubkolbenbrennkraftmaschine
DE102015200542B4 (de) 2015-01-15 2020-10-22 Schaeffler Technologies AG & Co. KG Zentralventil für eine Nockenwellenverstellvorrichtung
CN105781653B (zh) * 2016-03-31 2018-10-09 杰锋汽车动力***股份有限公司 一种连续可变气门正时***用中置阀
US11261765B1 (en) * 2020-08-25 2022-03-01 Borgwamer Inc. Control valve assembly of a variable cam timing phaser

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19944535C1 (de) * 1999-09-17 2001-01-04 Daimler Chrysler Ag Nockenwellenversteller für Brennkraftmaschinen
DE10326886A1 (de) * 2003-06-14 2004-12-30 Daimlerchrysler Ag Nockenwellensteller für eine Brennkraftmaschine
WO2005113943A1 (fr) * 2004-05-22 2005-12-01 Schaeffler Kg Dispositif de reglage d'arbre a cames
DE102005034275A1 (de) * 2005-07-22 2007-01-25 Daimlerchrysler Ag Nockenwellenstellventilvorrichtung
DE102005041393A1 (de) * 2005-09-01 2007-03-08 Schaeffler Kg Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE102006021706A1 (de) * 2006-05-10 2007-11-15 Daimlerchrysler Ag Verstelleinrichtung
DE102008030057A1 (de) * 2008-06-27 2010-01-07 Hydraulik-Ring Gmbh Nockenwellenverstelleinrichtung
DE102008057491A1 (de) * 2008-11-15 2010-05-20 Daimler Ag Nockenwellenverstellvorrichtung
EP2386731A1 (fr) * 2010-05-03 2011-11-16 Hydraulik-Ring GmbH Soupape hydraulique
DE102010023864A1 (de) * 2010-06-15 2011-12-15 Hydraulik-Ring Gmbh Zentralventil

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010012479A1 (de) * 2010-03-24 2011-09-29 Schaeffler Technologies Gmbh & Co. Kg Steuerventil einer Vorrichtung zur Veränderung der relativen Winkellage einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19944535C1 (de) * 1999-09-17 2001-01-04 Daimler Chrysler Ag Nockenwellenversteller für Brennkraftmaschinen
DE10326886A1 (de) * 2003-06-14 2004-12-30 Daimlerchrysler Ag Nockenwellensteller für eine Brennkraftmaschine
WO2005113943A1 (fr) * 2004-05-22 2005-12-01 Schaeffler Kg Dispositif de reglage d'arbre a cames
DE102005034275A1 (de) * 2005-07-22 2007-01-25 Daimlerchrysler Ag Nockenwellenstellventilvorrichtung
DE102005041393A1 (de) * 2005-09-01 2007-03-08 Schaeffler Kg Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE102006021706A1 (de) * 2006-05-10 2007-11-15 Daimlerchrysler Ag Verstelleinrichtung
DE102008030057A1 (de) * 2008-06-27 2010-01-07 Hydraulik-Ring Gmbh Nockenwellenverstelleinrichtung
DE102008057491A1 (de) * 2008-11-15 2010-05-20 Daimler Ag Nockenwellenverstellvorrichtung
EP2386731A1 (fr) * 2010-05-03 2011-11-16 Hydraulik-Ring GmbH Soupape hydraulique
DE102010023864A1 (de) * 2010-06-15 2011-12-15 Hydraulik-Ring Gmbh Zentralventil

Also Published As

Publication number Publication date
DE102013203951A1 (de) 2013-11-28
US20150144211A1 (en) 2015-05-28
CN104350241B (zh) 2016-12-14
CN104350241A (zh) 2015-02-11

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