EP2992190A1 - Soupape hydraulique et dispositif de réglage de moteur oscillant - Google Patents

Soupape hydraulique et dispositif de réglage de moteur oscillant

Info

Publication number
EP2992190A1
EP2992190A1 EP14711951.5A EP14711951A EP2992190A1 EP 2992190 A1 EP2992190 A1 EP 2992190A1 EP 14711951 A EP14711951 A EP 14711951A EP 2992190 A1 EP2992190 A1 EP 2992190A1
Authority
EP
European Patent Office
Prior art keywords
channel
hydraulic valve
piston
hollow piston
pressure
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
EP14711951.5A
Other languages
German (de)
English (en)
Other versions
EP2992190B1 (fr
Inventor
Christian SCHEIBE
Dietmar Schulze
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.)
Hilite Germany GmbH
Original Assignee
Hilite Germany GmbH
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 Hilite Germany GmbH filed Critical Hilite Germany GmbH
Publication of EP2992190A1 publication Critical patent/EP2992190A1/fr
Application granted granted Critical
Publication of EP2992190B1 publication Critical patent/EP2992190B1/fr
Active 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
    • 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
    • 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

Definitions

  • the invention relates to a hydraulic valve for a Schwenkmotorversteller, the
  • Hydraulic valve comprising a sleeve member having a longitudinal channel, a outgoing from the longitudinal channel first transverse channel and an outgoing from the longitudinal channel second transverse channel and within the longitudinal channel between a first end position and a second end position axially displaceable pressure-balanced hollow piston, the longitudinal channel having a first
  • the hollow piston having a longitudinal channel with an axial opening, at least one transverse channel, a first piston portion with a larger outer diameter and a second piston portion with a smaller outer diameter, wherein the hollow piston with its first
  • a Schwenkmotorversteller is known with a hydraulic valve having a stepped bore with outgoing from this working ports, within the bore a pressure-balanced hollow piston is axially displaceable and with a first outer diameter within a bore portion sealingly displaced displaced is, wherein the hollow piston following this first outer diameter adjacent a lateral surface having a large outer diameter in the axial regions of a working port and a lateral surface having a small outer diameter in the region of the other working port, wherein departing from the two lateral surfaces each have a feed edge and a drain edge, said the two inlet edges facing away from each other and assign the trailing edges to each other, so that one introduced into a cavity of the hollow piston Supply pressure on the one hand rests against a projected circular area, which is formed by the small outer diameter, so that a force in an axial direction is effective, whereas the supply pressure on the other hand rests against a projected annular surface, resulting from the large outer diameter
  • Hydraulic valve to create, the pressure medium connection, the two
  • the invention has for its object to improve an initially mentioned hydraulic valve structurally and / or functionally.
  • a should be any initially mentioned hydraulic valve structurally and / or functionally.
  • Production costs can be reduced in particular of the hollow piston.
  • a flow resistance should be reduced.
  • an at least largely rotationally symmetrical structure, in particular of the hollow piston should be achieved.
  • slopes should be avoided.
  • the hydraulic valve having a sleeve member having a longitudinal channel, a outgoing from the longitudinal channel first transverse channel and a outgoing from the longitudinal channel second transverse channel and one within the longitudinal channel between a first end position and a second end position
  • the longitudinal channel having a first channel portion with a larger inner diameter and a second channel portion with a smaller inner diameter, the first transverse channel of the first channel portion and the second transverse channel of the second channel portion, the hollow piston having a longitudinal channel with an axial Opening, at least one transverse channel, a first piston portion having a larger outer diameter and a second piston portion having a smaller outer diameter, wherein the hollow piston with its first Piston portion sealingly tolerated at the first channel portion of the longitudinal channel and with its second piston portion sealingly tolerated on the second
  • the hollow piston has a plurality of first pressure surfaces for acting on the hollow piston in the direction of the first end position and a plurality of second pressure surfaces for acting on the hollow piston in the direction of the second end position and an overall surface of the first pressure surfaces of an overall surface of the second pressure surfaces at least approximately.
  • the hydraulic valve can serve an adjustment of a
  • the hydraulic valve may be a first
  • the hydraulic valve may have a second
  • the hydraulic valve may have a tank connection.
  • the hydraulic valve may be actuatable by means of an electromagnetic actuator.
  • the hydraulic valve may be a 4/2-way valve.
  • Hydraulic valve can be a proportional valve.
  • the hydraulic valve may have a longitudinal axis.
  • the sleeve part may have a hollow cylindrical shape.
  • the longitudinal channel of the sleeve part may extend along the longitudinal axis.
  • the longitudinal channel may have a first end and a second end.
  • the longitudinal channel may have a first axial opening and a second axial opening.
  • the first channel portion and the second channel portion may be arranged axially in succession.
  • the longitudinal channel can essentially have two different inner diameters.
  • the inner diameter of the first channel section may be larger than the inner diameter of the second channel section.
  • the inner diameter of the second channel portion may be smaller than the inner diameter of the first
  • the hollow piston may be displaceable in the extension direction of the longitudinal axis.
  • the hollow piston may have a hollow cylindrical shape.
  • the longitudinal channel of the hollow piston may have a first end and a second end.
  • the longitudinal channel of the hollow piston may have an axial opening.
  • the longitudinal channel can be closed on one side.
  • the longitudinal channel of the hollow piston can at one of the opening be closed opposite end.
  • the first piston portion and the second piston portion may be arranged axially sequentially.
  • the first piston section may be arranged along the longitudinal channel opening.
  • the hollow piston can essentially have two different outer diameters. Of the
  • Outer diameter of the first piston portion may be larger than the
  • the outer diameter of the second piston portion may be smaller than the outer diameter of the first piston portion.
  • the first piston portion may have an annular rib-like shape.
  • the first piston section may have at least one control edge.
  • the at least one control edge of the first piston portion may serve to control a flow through the first transverse channel of the sleeve portion.
  • the second piston portion may have an annular rib-like shape.
  • the second piston portion may have at least one control edge.
  • the at least one control edge of the second piston portion may serve to control a flow through the second transverse channel of the sleeve portion.
  • a passage between the axial opening and the first transverse channel may be closed.
  • a passage between the axial opening and the second transverse channel may be opened.
  • a passage between the axial opening and the second transverse channel may be closed.
  • the pressure surfaces of the hollow piston can each be axial pressure surfaces.
  • the pressure surfaces of the hollow piston can each be arranged at right angles to the longitudinal axis.
  • the pressure surfaces of the hollow piston may each have a ring-like shape.
  • the first pressure surfaces may be at the open end of the
  • the second pressure surfaces can to the
  • the hollow piston may have three first pressure surfaces and two second pressure surfaces.
  • the hollow piston may have axially between the first piston portion and the second piston portion a radially recessed third piston portion to form an annular space, and the at least one transverse channel may connect the annular space with the longitudinal channel.
  • the hollow piston can at its third
  • Piston section have a step.
  • the step can be right-angled. With the step, a pressure surface can be formed.
  • the hollow piston can at a front end associated with the opening a first pressure surface, at the first piston portion a second pressure surface, at the stage of the third piston portion a second pressure surface on the second
  • Piston portion having a first pressure surface and at the closed end of the longitudinal channel having a first pressure surface.
  • the hollow piston may have pressure surfaces on the annular space formed with the third piston portion.
  • the hollow piston may have pressure surfaces on its longitudinal channel.
  • the sleeve part may have an axial opening and, starting from the opening, first the first transverse channel and subsequently the second transverse channel may be arranged. Between the opening of the sleeve part and the first transverse channel may be arranged a third transverse channel.
  • a check valve In the opening of the sleeve part, a check valve may be arranged. The check valve can in a
  • Inlet direction may be directed from the outside into the longitudinal channel.
  • Outlet direction may be directed from the longitudinal channel to the outside.
  • Non-return valve may be self-evident and / or closable under the influence of a pressure medium flow.
  • the opening of the sleeve part may be a pressure port
  • the first transverse channel may be a first working port
  • the second transverse channel may be a second
  • Working connection and the third transverse channel may be assigned a tank connection.
  • the pressure medium connection can be an axial connection.
  • the Working ports and the tank port may have orthogonal axes to the longitudinal axis.
  • the working connections and the tank connection can be radial connections.
  • a working port can be flowed through in both
  • Schwenkmotorversteller for controlling a rotation of the rotor having such a hydraulic valve.
  • the Schwenkmotorversteller may be a camshaft adjuster.
  • Internal combustion engine may have a drive shaft, such as crankshaft.
  • the internal combustion engine may have at least one camshaft.
  • Internal combustion engine may have valves.
  • the at least one camshaft can be used to actuate the valves.
  • the internal combustion engine can be used to drive the motor vehicle.
  • the Schwenkmotorversteller can be used for arrangement in a valve train of the internal combustion engine between the drive shaft and the at least one camshaft.
  • the Schwenkmotorversteller can be used to adjust a relative rotational position between the drive shaft and the at least one
  • Camshaft serve.
  • the Schwenkmotorversteller can serve for phase adjustment of the camshaft.
  • the Schwenkmotorversteller can serve to adjust timing.
  • the swivel motor adjuster can be used to adjust towards early and / or late. "Early" may mean valves of the
  • the Schwenkmotorversteller may have an axis of rotation about which the stator and the rotor together rotatable and relative
  • a production cost, in particular of the hollow piston is reduced.
  • a flow resistance is reduced.
  • An at least largely rotationally symmetrical structure, in particular of the hollow piston is achieved. Sloping is avoided.
  • Fig. 1 in a sectional view a Schwenkmotorversteller and
  • Fig. 2 in a sectional view of a hydraulic valve for controlling
  • the Schwenkmotorversteller 14 has a cylindrical stator 1 which is rotatably connected to the drive wheel 2.
  • the drive wheel 2 is a sprocket over which a chain, not shown, is guided.
  • the drive wheel 2 may also be a toothed belt, via which a drive belt as
  • the stator 1 comprises a cylindrical stator base body 3, on the inside of which protrude webs 4 at equal intervals radially inwardly. Intermediate spaces 5 are formed between adjacent webs 4, in which, controlled by a centrally arranged in Fig. 2 centrally arranged hydraulic valve, pressure medium
  • Pressure chambers 9 and 10 are assigned to the adjustment in the direction of "early", whereas the other pressure chamber is associated with the adjustment in the "late” direction.
  • the webs 4 lie with their end faces sealingly against the outer circumferential surface of the rotor hub 7.
  • the wings 6 in turn lie with their end faces sealingly against the cylindrical inner wall of the stator main body 3.
  • the rotor 8 is rotatably connected to the camshaft 18. In order to change the angular position between the camshaft 18 and the drive wheel 2, the rotor 8 is rotated relative to the stator 1. For this purpose, depending on the desired direction of rotation, the pressure medium in the pressure chambers 9 or 10 is pressurized, while the respective other pressure chambers 10 or 9 are relieved to the tank T. In order to pivot the rotor 8 counterclockwise relative to the stator 1 into the illustrated position, an annular first annular rotor channel in the rotor hub 7 is pressurized by the hydraulic valve. From this first rotor channel then lead more channels 1 1 in the pressure chambers 10. This first rotor channel is assigned to the first working port A.
  • a second annular rotor channel in the rotor hub 7 is pressurized by the hydraulic valve, open into the channels 13.
  • This second rotor channel is assigned to the second working port B.
  • the Schwenkmotorversteller 14 is placed on the designed as a hollow tube 16 built camshaft 18th
  • the rotor 8 is placed on the camshaft 18.
  • the hollow tube 16 has bores which connect the two working ports A, B associated rotor channels hydraulically with transverse bores in a socket of the hydraulic valve.
  • the Schwenkmotorversteller 14 is pivotable by means of a hydraulic valve.
  • FIG. 2 shows a hydraulic valve 30 for controlling a Schwenkmotorverstellers, such as Schwenkmotorversteller 14 of FIG. 1st
  • the hydraulic valve 30 has a sleeve part
  • the hydraulic valve 30 has a hollow piston 32.
  • the hydraulic valve 30 has a support element 33.
  • the hydraulic valve 30 has a spring 34.
  • the hydraulic valve 30 has a check valve 35.
  • the hydraulic valve 30 has a longitudinal axis 36.
  • the hollow piston 32 is limited relative to the sleeve member 31 in the axial direction between a first end position and a second end position displaced. By means of the spring 34, the hollow piston 32 is acted upon in the direction of the first end position.
  • An actuator 37 serves to act on the hollow piston
  • Hydraulic valve 30 has a pressure port P, a tank port T, a first working port A and a second working port B.
  • the working connections A, B serve for the hydraulic connection with pressure chambers of a
  • Schwenkmotorverstellers such as pressure chambers 9, 10 of a Schwenkmotorverstellers 14 of FIG. 1st
  • the sleeve part 31 has a central longitudinal channel 38.
  • the longitudinal channel 38 extends along the longitudinal axis 36.
  • the longitudinal channel 38 has an axial opening 39.
  • the longitudinal channel 38 has a first channel portion 40 with a larger inner diameter D and a second channel portion 41 with a smaller d inner diameter.
  • the first channel section 40 is arranged on the side of the longitudinal channel 38, on which the opening 39 is arranged. Between the first channel section 40 and the second channel section 41, the longitudinal channel 38 has a step.
  • the opening 39 is associated with the pressure port P of the hydraulic valve 30.
  • the sleeve part 31 has transverse channels 42, 43, 44.
  • the transverse channels 42, 43 are arranged on the first channel portion 40 of the longitudinal channel 38.
  • the cross channel 42 of the tank port T of the hydraulic valve 30 is assigned.
  • the transverse channel 43 is associated with the first working port A of the hydraulic valve 30.
  • the transverse channel 44 is arranged on the second channel section 41 of the longitudinal channel 38.
  • the transverse channel 44 is the second working port B of the
  • Hydraulic valve 30 assigned. From the pressure connection P, the tank connection T follows in the axial direction, followed by the first working connection A, followed by the second working connection B.
  • a groove for receiving a seal is arranged on the sleeve part 31.
  • the groove is arranged in the axial direction between the transverse channels 43, 44.
  • the sleeve part 31 has an external thread.
  • the sleeve part 31 has a collar portion.
  • the hollow piston 32 is arranged within the sleeve part 31.
  • the hollow piston 32 has a central longitudinal channel 45.
  • the longitudinal channel 45 extends along the longitudinal axis 36.
  • the longitudinal channel 45 has an axial opening 46. At its opposite end of the longitudinal channel 45 is closed.
  • the hollow piston 32 has transverse channels, such as 47 on.
  • the hollow piston 32 has radially outward
  • the hollow piston 32 has a multi-stepped outer diameter.
  • the hollow piston 32 has a first
  • Piston portion 48 whose outer diameter D corresponds to an inner diameter of the first channel portion 40 of the longitudinal channel 38 of the sleeve member 31.
  • the first piston portion 48 of the hollow piston 32 has a ring-web-like shape.
  • the hollow piston 32 is with its first piston portion 48 at the first
  • Hollow piston 32 has a second piston portion 49, whose
  • the second piston portion 49 of the hollow piston 32 has a ring-web-like shape.
  • the hollow piston 32 is guided with its second piston portion 49 to the second channel portion 41 of the longitudinal channel 38 of the sleeve member 31 tight.
  • the hollow piston 32 has a
  • Piston section 48 smaller outer diameter.
  • Piston sections 48, 50 is formed a step which serves as an axial abutment surface for the spring 34. Between these piston portions 48, 50, a first annular space 51 is formed. Axially between the first piston portion 48 and the second
  • Piston portion 49 the hollow piston 32 has a third piston portion 52 having a smaller diameter relative to the diameter of the second piston portion 49.
  • the third piston portion 52 has a step.
  • a second annular space 53 is formed, which is connected by means of the transverse channels 47 with the longitudinal channel 45.
  • the hollow piston 32 has control edges 54, 55, 56.
  • the control edges 54, 55 are arranged on the first piston portion 48 of the hollow piston 32.
  • Control edges 54, 55 are directed axially away from each other.
  • the control edges 54, 55 correspond to the transverse channel 43 of the sleeve part 31.
  • the control edge 56 is arranged on the second piston portion 49 of the hollow piston 32.
  • the control edge 56 is directed axially against the control edge 55.
  • the hollow piston 32 has first pressure surfaces 57, 58, 59 and second pressure surfaces 60, 61.
  • the pressure surfaces are axially directed surfaces.
  • the first pressure surfaces 57, 58, 59 and the second pressure surfaces 60, 61 are directed opposite to each other.
  • the first pressure surfaces 57, 58, 59 have a total area, the one
  • Total area of the second 60, 61 pressure surfaces corresponds.
  • the hollow piston 32 is pressure balanced.
  • a first pressure surface 57 is arranged at the end of the hollow piston 32, on which the opening 46 is arranged.
  • a first pressure surface 58 is disposed on the second piston portion 49 of the hollow piston 32, to the control edge 56 and directed to the second annular space 53 out.
  • a first pressure surface 59 is formed at the closed end of the longitudinal channel 45.
  • a second pressure surface 60 is disposed on the first piston portion 48 of the hollow piston 32, to the control edge 55 and subsequently to the second annular space 53 directed.
  • a second pressure surface 60 is formed with the step of the third piston portion 52.
  • the support element 33 has a sleeve-like shape.
  • the support element 33 is arranged in the longitudinal channel 38 of the sleeve part 31.
  • the support element 33 is arranged at an opening 39 of the longitudinal channel 38 side facing axially adjacent to the transverse channel 42.
  • the support element 33 is fixedly connected to the sleeve part 31.
  • the support element 33 is pressed into the sleeve part 31.
  • the spring 34 is supported on the support element 33.
  • the spring 34 is a
  • Helical compression spring By an adapted positioning of the support element 33 in the sleeve part 31, a spring preload is adjustable.
  • the hollow piston 32 is connected at its end 46 opposite the opening with the actuator 37.
  • the actuator is an electromagnetic actuator with a
  • Push rod which is connected to the hollow piston 32.
  • the push rod is pressed into the hollow piston 32.
  • the push rod closes the longitudinal channel 45 of the hollow piston 32 at the end.
  • the push rod forms with its longitudinal channel-side end face a first pressure surface 59.
  • Hollow piston 32 relative to Fig. 2 shifted to the right. In the second end position of the hollow piston 32, a passage between the opening 39 and the transverse channel 43 is formed. In the second end position, the pressure port P and the first
  • Working port A of the hydraulic valve 30 fluidly connected to each other and the first working port A can be hydraulically pressurized.
  • the check valve 35 is arranged in the opening 39 of the longitudinal channel 38 of the sleeve part 31.
  • the check valve 35 serves to allow a flow from the pressure port P to the working ports A, B and to block a return flow from the working ports A, B to the pressure port P.

Landscapes

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

Abstract

L'invention concerne une soupape hydraulique (30) pour un dispositif de réglage de moteur oscillant, la soupape hydraulique (30) présentant une partie douille (31) comprenant un canal longitudinal (38), un premier canal transversal (43) partant du canal longitudinal (38) et un deuxième canal transversal (44) partant du canal longitudinal (38) et un piston creux (32) à pression équilibrée disposé axialement déplaçable dans le canal longitudinal (38) entre une première position terminale et une deuxième position terminale. Le canal longitudinal (38) présente une première section (40) de canal ayant un plus grand diamètre intérieur (D) et une deuxième section (41) de canal ayant un plus petit diamètre intérieur (d). Le premier canal transversal (43) part de la première section (40) de canal et le deuxième canal transversal (44) part de la deuxième section (41) de canal. Le piston creux (32) présente plusieurs premières surfaces de pression (57, 58, 59) pour agir sur le piston creux (32) en direction de la première position terminale et plusieurs deuxièmes surfaces de pression (60, 61) pour agir sur le piston creux (32) en direction de la deuxième position terminale et une surface totale des premières surfaces de pression (57, 58, 59) correspond au moins approximativement à une surface totale des deuxièmes surfaces de pression (60, 61). L'invention concerne également un dispositif de réglage de moteur oscillant comprenant un stator, un rotor pouvant tourner par rapport au stator entre une première position terminale et une deuxième position terminale pour régler un arbre à cames d'un moteur à combustion interne et une soupape hydraulique (30) de ce type pour commander une rotation du rotor.
EP14711951.5A 2013-05-03 2014-03-17 Vanne de commande hydraulique et dephaseur de type à palettes Active EP2992190B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013104575.8A DE102013104575B4 (de) 2013-05-03 2013-05-03 Hydraulikventil und Schwenkmotorversteller
PCT/EP2014/055233 WO2014177317A1 (fr) 2013-05-03 2014-03-17 Soupape hydraulique et dispositif de réglage de moteur oscillant

Publications (2)

Publication Number Publication Date
EP2992190A1 true EP2992190A1 (fr) 2016-03-09
EP2992190B1 EP2992190B1 (fr) 2018-06-27

Family

ID=50346000

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14711951.5A Active EP2992190B1 (fr) 2013-05-03 2014-03-17 Vanne de commande hydraulique et dephaseur de type à palettes

Country Status (5)

Country Link
US (1) US10119432B2 (fr)
EP (1) EP2992190B1 (fr)
CN (1) CN105102774B (fr)
DE (1) DE102013104575B4 (fr)
WO (1) WO2014177317A1 (fr)

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DE102014115903B4 (de) * 2014-10-31 2020-07-30 Hilite Germany Gmbh Hydraulikventil und Schwenkmotorversteller
US10432754B2 (en) * 2015-09-16 2019-10-01 Profire Energy, Inc Safety networking protocol and method
US10041385B2 (en) 2016-03-14 2018-08-07 ECO Holding 1 GmbH Piston for a hydraulic valve for a cam phaser and hydraulic valve for the cam phaser
US10113451B2 (en) 2017-03-28 2018-10-30 ECO Holding 1 GmbH Hydraulic valve for a cam phaser
US10612430B2 (en) 2017-06-20 2020-04-07 ECO Holding 1 GmbH Oil control valve to control a cam phaser with a spool positioned by external actuator
DE102017115237A1 (de) 2017-07-07 2019-01-10 ECO Holding 1 GmbH Hydraulikventil insbesondere für einen Nockenwellenversteller einer Nockenwelle sowie Rückschlagventil
EP3460209B1 (fr) 2017-09-19 2021-05-26 ECO Holding 1 GmbH Soupape de commande d'huile permettant la commande d'un dispositif de réglage d'arbre à cames doté d'un piston positionné par un actionneur extérieur
US10883616B2 (en) 2019-02-06 2021-01-05 ECO Holding 1 GmbH Control valve for cam phaser and method for mounting the control valve
US11092045B1 (en) 2020-03-22 2021-08-17 ECO Holding 1 GmbH Control valve for cam phaser and method for mounting the control valve

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Also Published As

Publication number Publication date
EP2992190B1 (fr) 2018-06-27
DE102013104575B4 (de) 2018-03-08
CN105102774A (zh) 2015-11-25
WO2014177317A1 (fr) 2014-11-06
US10119432B2 (en) 2018-11-06
US20160032792A1 (en) 2016-02-04
CN105102774B (zh) 2018-11-30
DE102013104575A1 (de) 2014-11-06

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