EP2142766A1 - Soupape de commande - Google Patents

Soupape de commande

Info

Publication number
EP2142766A1
EP2142766A1 EP08716844A EP08716844A EP2142766A1 EP 2142766 A1 EP2142766 A1 EP 2142766A1 EP 08716844 A EP08716844 A EP 08716844A EP 08716844 A EP08716844 A EP 08716844A EP 2142766 A1 EP2142766 A1 EP 2142766A1
Authority
EP
European Patent Office
Prior art keywords
control piston
closure element
control
opening
valve
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.)
Ceased
Application number
EP08716844A
Other languages
German (de)
English (en)
Inventor
Jens Hoppe
Andreas Röhr
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 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 KG filed Critical Schaeffler KG
Publication of EP2142766A1 publication Critical patent/EP2142766A1/fr
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • F16K11/0716—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides with fluid passages through the valve member
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • 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 control valve, in particular for a device for changing the timing of an internal combustion engine, having a substantially hollow cylindrical valve housing, an arranged inside the valve housing and axially displaceable control piston, and a closure element, wherein the control piston has at least one hollow advertisedroad- th section which opens into an opening of the control piston and wherein the closure element is arranged in the opening. Furthermore, the invention relates to a method for producing a control valve, in particular for a device for changing the timing of an internal combustion engine, having a substantially hollow cylindrical valve housing, a valve housing arranged within the axially displaceable control piston, and a closure element, wherein the control piston has at least one hollow portion which opens into an opening of the control piston.
  • Such control valves are used to control pressure medium flows in hydraulic devices, such as hydraulic devices for changing the timing of an internal combustion engine (camshaft adjusters).
  • hydraulic devices such as hydraulic devices for changing the timing of an internal combustion engine (camshaft adjusters).
  • camshaft adjusters Such a control valve and a camshaft adjuster is known for example from DE 10 2004 038 252 A1.
  • the camshaft adjuster has two components which can be rotated relative to one another and two pressure chambers which act against one another, whereby by selective pressurization or pressure relief of the pressure chambers, the relative phase of the two components can be optionally varied or changed.
  • the control of the pressure medium flows to and from the pressure chambers by means of a control valve, in this case a 4/3-way proportional valve.
  • a control valve in this case a 4/3-way proportional valve.
  • the control valve consists essentially of an electromagnetic actuator, a hollow cylindrical valve housing and a likewise substantially hollow cylindrical, arranged within the valve housing and axially displaceable control piston.
  • the valve housing is provided with one connection each for the pressure chambers (working connection), a connection to the pressure medium pump and at least one connection to a tank.
  • the control piston can be brought by means of an electromagnetic actuator against the spring force of a spring element axially in any position between two defined end positions.
  • control piston is further provided with annular grooves and control edges, whereby the individual pressure chambers can be optionally connected to the pressure medium pump or the tank NEN. Likewise, a position of the control piston may be provided, in which the pressure medium chambers are separated from both the pressure medium pump and the pressure medium tank.
  • the control piston can be moved by means of the actuator which acts against a spring element, within the valve housing in any position.
  • an axial opening of the control piston which faces the actuator, closed by a sealing element pressure-tight.
  • On this closure element acts a linearly movable from the actuator push rod.
  • the closure element is connected by means of a frictional connection, for example by pressing the closure element with excess in the opening of the control piston, with the control piston.
  • the invention is therefore based on the object to avoid these disadvantages and thus to provide a hydraulic control valve, in particular a deterioration of the performance and the control accuracy of the control valve to be prevented during operation.
  • this object is achieved in that the closure element has a peripheral wall, which is adapted to an inner circumferential surface of the control piston in the region of the opening substantially, wherein the peripheral wall has at least one material receiving smaller outer diameter, wherein in the axial direction of the closure element to the material receptacle on the opening facing away from the th side an area of larger outer diameter connects and wherein the inner circumferential surface of the control piston engages in the material receptacle.
  • the material receptacle is formed as an annular groove extending in the circumferential direction of the closure element.
  • the material receptacle may be formed as a pocket.
  • the material receptacle is formed as a chamfer of a peripheral edge of an axial side wall of the closure element.
  • the outer diameter of the control piston in the region of the material receptacle is made smaller than a maximum outer diameter of the control piston.
  • closure element (37b) may be provided to connect the closure element (37b) to the control piston (37) by means of a material connection, an adhesive connection, a solder connection or a welded connection.
  • the object is achieved in that the closure element is connected by means of a material connection, an adhesive bond, a solder joint or a welded joint with the control piston.
  • the object is achieved by a method according to the invention with the following steps: positioning the closure element within the opening of the control piston,
  • control piston is displaced radially inwardly by radial Anlessnessgen, radial circumferential or radial segment calking of the control piston.
  • material of the control piston is displaced radially inward by axial pressing, axial ring or axial segment staking an axial side surface of the control piston.
  • a control piston is arranged to be axially displaceable within a substantially hollow-cylindrical valve housing.
  • the control piston is hollow at least in one section, this section ending in an opening of the control piston. It can be provided that the opening is formed on an axial side surface of the control piston.
  • control piston may be formed, for example, as a substantially hollow cylindrical component or in a longitudinal section U-shaped.
  • the closure element may for example be cylindrical or cup-shaped and serve, for example, to close the opening pressure medium-tight.
  • the closure element serves as a contact element for a push rod, via which an actuating movement of an actuator can be transmitted to the control piston.
  • the radially outer peripheral wall of the closure element is adapted to an inner circumferential surface of the control piston in the region of the opening.
  • the peripheral wall of the closure element has at least one material receptacle of smaller outer diameter, wherein the inner circumferential surface of the control piston engages in the material receptacle.
  • a region of the closure element whose outer diameter is larger than the outer diameter in the region of the material receptacle can adjoin the material receptacle in the axial direction.
  • a cohesive connection an adhesive connection, a solder connection or a welded connection between the closure element and the control piston can be provided.
  • the material displacements may be formed along the entire circumference of the control piston or only in segments.
  • FIG. 1 shows a longitudinal section through a device for changing the timing of an internal combustion engine
  • FIG. 2 shows a cross section through the device shown in FIG. 1,
  • FIG. 3 shows a longitudinal section through a control valve according to the invention
  • FIG. 4a shows a longitudinal section through a first embodiment of a control piston of a control valve according to the invention
  • FIG. 4b is a perspective view of the control piston of Figure 4a
  • FIG. 5a shows a cross section through a second embodiment of a control piston of a control valve according to the invention
  • Figure 5b shows a longitudinal section through the control piston of Figure 5a along the line A-A.
  • FIGS 1 and 2 show a device 1 for changing the timing of an internal combustion engine.
  • the device 1 consists essentially of a stator 2 and a concentrically arranged rotor 3.
  • a drive wheel 4 is rotatably connected to the stator 2 and formed in the illustrated embodiment as a sprocket.
  • the stator 2 is rotatably mounted on the rotor 3, wherein five circumferentially spaced recesses 5 are provided on the inner circumferential surface of the stator 2 in the illustrated embodiment.
  • the recesses 5 are bounded in the radial direction by the stator 2 and the rotor 3, in the circumferential direction by two side walls 6 of the stator 2 and in the axial direction by a first and a second side cover 7, 8.
  • Each of the recesses 5 is sealed pressure-tight manner in this way.
  • each vane groove 10 On the outer circumferential surface of the rotor 3 axially extending vane grooves 10 are formed, wherein in each vane groove 10, a radially extending vane 11 is arranged. In each recess 5, a wing 11 extends, wherein the wings 11 in the radial direction on the stator 2 and in the axial direction on the side tende 7, 8 abut. Each wing 11 divides a recess 5 into two counteracting pressure chambers 12, 13th By means of first and second pressure medium lines 16, 17, the first and second pressure chambers 12, 13 can be connected via a control valve 18 to a pressure medium pump 19 or a tank 20. As a result, an actuator is formed, which allows a relative rotation of the stator 2 relative to the rotor 3.
  • the first pressure chambers 12 When the first pressure chambers 12 are connected to the pressure medium pump 19 and the second pressure chambers 13 are connected to the tank 20, the first pressure chambers 12 expand at the expense of the second pressure chambers 13. This results in a displacement of the wings 11 in the circumferential direction, in the direction represented by the arrow 21. By moving the vanes 11, the rotor 3 is rotated relative to the stator 2.
  • the pressure medium lines 16, 17 are designed in the illustrated embodiment as a substantially radially arranged bores extending from a central bore 22 of the rotor 3 to the outer lateral surface.
  • a central valve not shown, can be arranged, via which the pressure chambers 12, 13 can be selectively connected to the pressure medium pump 19 and the tank 20.
  • Another possibility is to arrange within the central bore 22 a pressure medium distributor, which connects the pressure medium lines 16, 17 via pressure medium channels and annular grooves with the terminals of an externally mounted control valve 18.
  • a substantially hollow cylindrical valve housing 34 is provided with a radial pressure medium connection P, a radial tank connection T 1 , two working connections A, B and an axial tank connection T 2 . det.
  • the radial ports P, T 1 , A, B are formed as axially spaced first annular grooves 35, which are formed on the outer circumferential surface of the valve housing 34.
  • the first annular grooves 35 are provided with a plurality of first bores 36, which open into the interior of the valve housing 34.
  • a control piston 37 which is likewise designed substantially hollow-cylindrical, is arranged to be axially displaceable.
  • control piston 37 An axial end of the control piston 37 is limited pressure-tight by means of a wall portion 37a.
  • a closure element 39 is arranged in a wall portion 37a opposite opening 37b of the control piston 37.
  • the closure element 39 is designed such that it closes the opening 37b in a pressure-tight manner.
  • the control piston 37 can be brought and held by means of a push rod 32a against the spring force of a spring element 33 within two extreme values in an arbitrary position.
  • the push rod 32 a of the actuator 32 abuts against the closure element 39. Linear actuating movements of the actuator 32 are thus transmitted via the push rod 32a to the closure element 39 and thus to the control piston 37.
  • the outer circumferential surface of the control piston 37 is provided with 3 axially spaced second annular grooves 38.
  • the two outer annular grooves 38 communicate with the interior of the control piston 37 via second bores 41.
  • pressure medium can be supplied from the pressure medium connection P, depending on the position of the control piston 37 within the valve housing 34, are led to the first or second working ports A, B, wherein the interior of the control piston 37 is connected in each position with the pressure medium connection P.
  • pressure medium at certain positions of the control piston 37 relative to the valve housing 34, from the second working port B via the middle annular groove 38 to the radial tank port T 1 and from the first working port A to the axial tank port T 2 reach.
  • pressure medium at certain positions of the control piston 37 relative to the valve housing 34 pressure medium to certain pressure chambers 12, 13 and discharged from the other pressure chambers 12, 13 are discharged, resulting in a relative change in the phase angle between the rotor 3 and stator 2, and thus between Crankshaft and camshaft leads.
  • connection between the control piston 37 and the closure element 39 is to be strengthened. This can be achieved for example by a positive and / or cohesive connection and / or a strengthening of the non-positive connection. Also conceivable are adhesive bonds or combinations of these types of connections.
  • FIGS. 4a and 4b show a first embodiment of a control piston 37 according to the invention.
  • the closure element 39 is cup-shaped in this embodiment, with a cylindrical peripheral wall 39a of the closure element 39 comes to rest on the inner circumferential surface 37d of the opening 37b.
  • material 37c of the control piston 37 is forced radially inward. This can be done for example by radial embossing or caulking.
  • the material displacement along the entire circumference of the control piston 37 in the form of an annular groove or segmentally, as shown in the embodiment take place. This leads to a reinforcement of the frictional connection between control piston 37 and closure element 39.
  • the outer diameter of the control piston 37 at the edges of the pressure-loaded area may be slightly larger. To prevent this increase in diameter leads to jamming of the control piston 37 within the valve housing 34, it is provided, the outer diameter of the control piston 37 in the region of the material displacement less than the maximum outer diameter of the control piston 37, in particular less than the inner diameter of the valve housing 34 to execute ,
  • FIGS. 5a and 5b show a second embodiment of a control piston 37 according to the invention.
  • the closure element 39 has been positioned within the control piston 37, for example by means of a press-fit operation of the closure element 39 with LJ dimensions into the opening 37b of the control piston 37 37c of the control piston 37 is displaced radially inwards.
  • this is done by axial Anlessnessgen by means of a ring relationship or segment bracing.
  • the tool is pressed into the axial side surface (annular wall 37e) of the control piston 37.
  • the frictional connection between the closure element 39 and the control piston 37 is increased and a positive connection is created in the direction of descent, whereby the relative position of the closure element 39 to the control piston 37 is determined.
  • material receptacles 40 can also be provided here.
  • the material Receiving 40 realized by a suitably dimensioned phase 40a or a suitably dimensioned radius of the opening-side bottom of the closure element 39.
  • the chamfer 40a, as well as the material displacement can run along the entire outer circumference of the floor, or be formed only in segments.
  • closure element 39 As an alternative to the cup-shaped embodiment of the closure element 39 shown, other embodiments, for example a cylindrical closure element 39, may be provided.
  • closure element 39 may be provided to connect the closure element 39 to the control piston 37 by means of a glued, soldered or welded connection.
  • a glued, soldered or welded connection may be provided to connect the closure element 39 to the control piston 37 by means of a glued, soldered or welded connection.
  • combinations of the first and second embodiments with a glued, soldered or welded connection may be provided to connect the closure element 39 to the control piston 37 by means of a glued, soldered or welded connection.

Landscapes

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

Abstract

La présente invention concerne une soupape de commande (18) destinée en particulier à un dispositif (1) pour faire varier les temps de commande d'un moteur à combustion interne, ladite soupape comprenant un boîtier de soupape (34) de forme sensiblement cylindrique, un piston de commande (37) disposé dans le boîtier de soupape (34) et pouvant effectuer un mouvement axial et un élément de fermeture (39). Le piston de commande (37) présente au moins une section creuse qui débouche dans une ouverture (37b) du piston de commande (37) et l'élément de fermeture (39) se trouve dans l'ouverture (37b).
EP08716844A 2007-03-30 2008-02-14 Soupape de commande Ceased EP2142766A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007015333.5A DE102007015333B4 (de) 2007-03-30 2007-03-30 Steuerventil und Herstellungsverfahren für das Steuerventil
PCT/EP2008/051775 WO2008119591A1 (fr) 2007-03-30 2008-02-14 Soupape de commande

Publications (1)

Publication Number Publication Date
EP2142766A1 true EP2142766A1 (fr) 2010-01-13

Family

ID=39414930

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08716844A Ceased EP2142766A1 (fr) 2007-03-30 2008-02-14 Soupape de commande

Country Status (5)

Country Link
US (1) US20110000447A1 (fr)
EP (1) EP2142766A1 (fr)
CN (1) CN101652537B (fr)
DE (1) DE102007015333B4 (fr)
WO (1) WO2008119591A1 (fr)

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KR101279833B1 (ko) * 2009-07-24 2013-06-28 쯔지앙 산화 클라이메이트 앤드 어플라이언스 컨트롤스 그룹 컴퍼니 리미티드 엔드 커버 및 그것을 사용하는 4-방향 리버싱 밸브와 그것의 조립 방법
DE102013209862A1 (de) * 2013-05-28 2014-12-04 Schaeffler Technologies Gmbh & Co. Kg Anordnung eines Elektromagneten zur Ansteuerung eines Zentralventils
JP5900533B2 (ja) * 2013-08-22 2016-04-06 株式会社デンソー バルブタイミング調整装置
DE102014212991A1 (de) * 2014-07-04 2016-01-07 Schaeffler Technologies AG & Co. KG Steuerventilkolben aus Kunststoff
US10072765B2 (en) 2015-07-02 2018-09-11 Caterpillar Inc. Valve having spool assembly with insert divider
US9915355B2 (en) 2015-10-06 2018-03-13 Caterpillar Inc. Valve having open-center spool with separated inserts
DE102015224656A1 (de) 2015-12-09 2017-06-14 Schaeffler Technologies AG & Co. KG Steuerventil für einen Nockenwellenversteller mit hohlem Steuerkolben

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Also Published As

Publication number Publication date
CN101652537B (zh) 2012-06-13
WO2008119591A1 (fr) 2008-10-09
DE102007015333A1 (de) 2008-10-02
CN101652537A (zh) 2010-02-17
DE102007015333B4 (de) 2020-08-27
US20110000447A1 (en) 2011-01-06

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