US20110000447A1 - Control valve - Google Patents

Control valve Download PDF

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Publication number
US20110000447A1
US20110000447A1 US12/593,628 US59362808A US2011000447A1 US 20110000447 A1 US20110000447 A1 US 20110000447A1 US 59362808 A US59362808 A US 59362808A US 2011000447 A1 US2011000447 A1 US 2011000447A1
Authority
US
United States
Prior art keywords
control piston
closing element
control
orifice
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.)
Abandoned
Application number
US12/593,628
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English (en)
Inventor
Jens Hoppe
Andreas Roehr
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
Assigned to SCHAEFFLER KG reassignment SCHAEFFLER KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ROEHR, ANDREAS, HOPPE, JENS
Publication of US20110000447A1 publication Critical patent/US20110000447A1/en
Assigned to SCHAEFFLER TECHNOLOGIES GMBH & CO. KG reassignment SCHAEFFLER TECHNOLOGIES GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SCHAEFFLER KG
Assigned to Schaeffler Technologies AG & Co. KG reassignment Schaeffler Technologies AG & Co. KG CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG
Abandoned legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16KVALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06Multiple-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
    • F16K11/065Multiple-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
    • F16K11/07Multiple-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
    • F16K11/0716Multiple-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-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
    • F01L1/344Valve-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
    • F01L1/3442Valve-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16KVALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06Multiple-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
    • F16K11/065Multiple-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
    • F16K11/07Multiple-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-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
    • F01L1/344Valve-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
    • F01L1/3442Valve-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
    • F01L2001/34423Details relating to the hydraulic feeding circuit
    • F01L2001/34426Oil control valves

Definitions

  • the invention relates to a control valve, in particular for a device for varying the control times of an internal combustion engine, with an essentially hollow-cylindrically designed valve housing, an axially displaceable control piston arranged inside the valve housing, and a closing element, the control piston having at least one portion of hollow design which issues into an orifice of the control piston, and the closing element being arranged in the orifice.
  • the invention relates, further, to a method for producing a control valve, in particular for a device for varying the control times of an internal combustion engine, with an essentially hollow-cylindrically designed valve housing, an axially displaceable control piston arranged inside the valve housing, and a closing element, the control piston having at least one portion of hollow design which issues into an orifice of the control piston.
  • Control valves of this type are used in order to control pressure medium streams in hydraulic devices, for example hydraulic devices for varying the control times of an internal combustion engine (camshaft adjusters).
  • a control valve of this type and a camshaft adjuster are known, for example, from DE 10 2004 038 252 A1.
  • the camshaft adjuster has two components rotatable in relation to one another and two pressure chambers acting counter to one another, the relative phase of the two components being capable of being selectively varied or changed by the pressure chambers being loaded with or relieved of pressure in a directed manner.
  • control of the pressure medium streams to and from the pressure chambers takes place 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.
  • Other types of directional valves may also be envisaged, however, in particular with different numbers of connections and/or control positions.
  • the control valve consists essentially of an electromagnetic actuating drive, of a hollow-cylindrically designed valve housing and of a likewise essentially hollow-cylindrically designed axially displaceable control piston arranged inside the valve housing.
  • the valve housing is provided in each case with a connection for the pressure chambers (working connection), with a connection to the pressure medium pump and with at least one connection to a tank.
  • the control piston can be brought axially into any position between two defined end positions, counter to the spring force of a spring element, by means of an electromagnetic actuating member.
  • the control piston is provided, furthermore, with annular grooves and control edges, with the result that the individual pressure chambers can be connected selectively to the pressure medium pump or to the tank.
  • a position of the control piston may likewise be provided in which the pressure medium chambers are separated both from the pressure medium pump and from the pressure medium tank.
  • the control piston can be displaced into any desired position inside the valve housing by means of the actuating drive which acts counter to a spring element.
  • an axial orifice of the control piston which stands opposite the actuating drive, is closed, tight to pressure medium, by means of a closing element.
  • a tappet rod movable linearly by the actuating drive acts on this closing element.
  • the closing element is connected to the control piston by means of a nonpositive connection, for example by the closing element being pressed with oversize into the orifice of the control piston.
  • the object on which the invention is based is to avoid these outlined disadvantages and therefore to provide a hydraulic control valve, in which, in particular, a deterioration in the performance and regulating accuracy of the control valve during operation is to be prevented.
  • this object is achieved, according to the invention, in that the closing element has a circumferential wall which is adapted essentially to an inner surface area of the control piston in the region of the orifice, the circumferential wall having at least one material receptacle of smaller outside diameter, the material receptacle being followed in the axial direction of the closing element by a region of larger outside diameter on the side facing away from the orifice, and the inner surface area of the control piston engaging into the material receptacle.
  • the material receptacle may be designed as an annular groove proceeding in the circumferential direction of the closing element.
  • the material receptacle may be designed as a pocket.
  • the material receptacle is designed as a chamfer of a circumferential edge of an axial sidewall of the closing element.
  • the outside diameter of the control piston is made smaller in the region of the material receptacle than a maximum outside diameter of the control piston.
  • the object is achieved, according to the invention, in that the closing element is connected to the control piston by means of a materially integral connection, an adhesive bond, a soldered joint or a welded joint.
  • the object is by means of a method according to the invention having the following steps:
  • control piston there may be provision for the material of the control piston to be displaced radially inward by means of radial embossing, radial circumferential calking or radial segmental calking of the control piston.
  • control piston there may be provision for the material of the control piston to be displaced radially inward by means of axial embossing, axial annular calking or axial segmental calking of an axial side face of the control piston.
  • the material may be displaced into at least one material receptacle formed on a circumferential face of the closing element.
  • a control piston is arranged axially displaceably inside an essentially hollow-cylindrically designed valve housing.
  • the control piston is of hollow design at least in one portion, this portion ending in an orifice of the control piston.
  • the orifice may be formed on an axial side face of the control piston.
  • control piston in addition to this orifice, further orifices, in particular radial bores, may be provided, via which the portion of hollow design of the control piston communicates, for example, with a pressure medium pump or with working connections or, via these, with a consumer.
  • the control piston may, for example, be designed as an essentially hollow-cylindrical structural element or may have a U-shaped design in longitudinal section.
  • a closing element is arranged inside the orifice.
  • the closing element may, for example, be of cylindrical or pot-shaped design and serve, for example, for closing the orifice tight to pressure medium. Furthermore, there may be provision for the closing element to serve as a bearing element for a tappet rod, via which an actuating movement of an actuating member can be transmitted to the control piston.
  • a nonpositive connection between the closing element and the control element This may be implemented, for example, by pressing the closing element designed with oversize into the orifice.
  • displacing material of the control piston radially inward after the positioning of the closing element inside the orifice This may be implemented, for example, by means of the radial embossing, radial circumferential calking or radial segmental calking or by means of the axial embossing, axial annular calking or axial segmental calking of an axial side face of the control piston radially inward.
  • the circumferential wall of the closing element may have at least one material receptacle of smaller outside diameter, the inner surface area of the control piston engaging into the material receptacle.
  • the material receptacle may be followed in the axial direction by a region of the closing element, the outside diameter of which is designed to be larger than the outside diameter in the region of the material receptacle.
  • a materially integral connection, an adhesive bond, a soldered joint or a welded joint may be provided between the closing element and the control piston.
  • the material displacements may take place along the entire circumference of the control piston or only segmentally.
  • FIG. 1 shows a longitudinal section through a device for varying the control times of an internal combustion engine, together with a pressure medium circuit
  • FIG. 2 shows a cross section through the device illustrated in FIG. 1 ;
  • FIG. 3 shows a longitudinal section through a control valve according to the invention
  • FIG. 4 a shows a longitudinal section through a first embodiment of a control piston of a control valve according to the invention
  • FIG. 4 b shows a perspective view of the control piston from FIG. 4 a;
  • FIG. 5 a shows a cross section through a second embodiment of a control piston of a control valve according to the invention.
  • FIG. 5 b shows a longitudinal section through the control piston from FIG. 5 a along the line A-A.
  • FIGS. 1 and 2 show a device 1 for varying the control times of an internal combustion engine.
  • the device 1 consists essentially of a stator 2 and of a rotor 3 arranged concentrically thereto.
  • a drive wheel 4 is connected fixedly in terms of rotation to the stator 2 and, in the embodiment illustrated, is designed as a chain wheel.
  • the stator 2 is mounted rotatably on the rotor 3 , in the embodiment illustrated five recesses 5 spaced apart in the circumferential direction being provided on the inner surface area of the stator 2 .
  • the recesses 5 are delimited in the radial direction by the stator 2 and the rotor 3 , in the circumferential direction by two sidewalls 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 closed, pressure-tight, in this way.
  • Vane grooves 10 proceeding axially are formed on the outer surface area of the rotor 3 , a radially extending vane 11 being arranged in each vane groove 10 .
  • a vane 11 extends into each recess 5 , the vanes 11 bearing in the radial direction against the stator 2 and in the axial direction against the side covers 7 , 8 .
  • Each vane 11 subdivides a recess 5 into two pressure chambers 12 , 13 acting counter to one another.
  • 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 to a tank 20 .
  • An actuating drive is thereby formed which allows a relative rotation of the stator 2 with respect 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 to the tank 20 , the first pressure chambers 12 expand at the expense of the second pressure chambers 13 .
  • the rotor 3 is rotated with respect to the stator 2 .
  • the pressure medium lines 16 , 17 are designed as essentially radially arranged bores which extend from a central bore 22 of the rotor 3 to the outer surface area of the latter.
  • a central valve not illustrated, may be arranged, via which the pressure chambers 12 , 13 can be connected to the pressure medium pump 19 or to the tank 20 in a directed manner.
  • a further possibility is to arrange inside the central bore 22 a pressure medium distributor which connects the pressure medium lines 16 , 17 to the connections of an externally mounted control valve 18 via pressure medium ducts and annular grooves.
  • FIG. 3 illustrates a control valve 18 according to the invention in longitudinal section.
  • An essentially hollow-cylindrically designed valve housing 34 is designed with a radial pressure medium connection P, with a radial tank connection T 1 , with two working connections A, B and with an axial tank connection T 2 .
  • the radial connections P, T 1 , A, B are designed as first annular grooves 35 which are spaced axially apart from one another and which are formed on the outer surface area of the valve housing 34 .
  • the first annular grooves 35 are provided with a plurality of first bores 36 which issue into the interior of the valve housing 34 .
  • a likewise essentially hollow-cylindrically designed control piston 37 is arranged axially displaceably inside the valve housing 34 .
  • One axial end of the control piston 37 is delimited, pressure-tight, by means of a wall portion 37 a .
  • a closing element 39 is arranged in an orifice 37 b , lying opposite the wall portion 37 a , of the control piston 37 .
  • the closing element 39 is designed in such a way that it closes the orifice 37 b pressure-tight.
  • the control piston 37 can be brought into and held in any desired position within two extreme values, counter to the spring force of a spring element 33 , by means of a tappet rod 32 a .
  • the tappet rod 32 a of the actuating member 32 bears against the closing element 39 . Linear actuating movements of the actuating member 32 are thus transmitted via the tappet rod 32 a to the closing element 39 and therefore to the control piston 37 .
  • the outer surface area of the control piston 37 is provided with three axially spaced-apart second annular grooves 38 .
  • the two outer annular grooves 38 communicate via second bores 41 with the interior of the control piston 37 .
  • pressure medium can be conducted from the pressure medium connection P to the first or second working connections A, B as a function of the position of the control piston 37 inside the valve housing 34 , the interior of the control piston 37 being connected to the pressure medium connection P in any position.
  • pressure medium can pass from the second working connection B via the middle annular groove 38 to the radial tank connection T 1 and from the first working connection A to the axial tank connection T 2 .
  • pressure medium can be conducted to specific pressure chambers 12 , 13 and be discharged from the other pressure chambers 12 , 13 , thus leading to a relative change in the phase position between the rotor 3 and stator 2 and, consequently, between the crankshaft and camshaft.
  • the connection between the control piston 37 and the closing element 39 is to be strengthened. This may be achieved, for example, by means of a positive and/or materially integral connection and/or a strengthening of the nonpositive connection. Adhesive bonds or combinations of these types of connection may likewise be envisaged.
  • FIGS. 4 a and 4 b show a first embodiment according to the invention of a control piston 37 .
  • the closing element 39 is of pot-shaped design, a cylindrical circumferential wall 39 a of the closing element 39 coming to bear against the inner surface area 37 d of the orifice 37 b .
  • material 37 c of the control piston 37 is displaced radially inward in the region of the cylindrical circumferential wall 39 a .
  • This may take place, for example, by means of radial embossing or calking.
  • the material displacement may take place along the entire circumference of the control piston 37 in the form of an annular groove or segmentally, as illustrated in the embodiment. This leads to a reinforcement of the nonpositive connection between the control piston 37 and closing element 39 .
  • the flowing material can be received on the inner surface area 37 d of the control piston 37 .
  • the outside diameter of the control piston 37 may become slightly larger at the margins of the pressure-loaded region.
  • FIGS. 5 a and 5 b show a second embodiment according to the invention of a control piston 37 .
  • material 37 c of the control piston 37 is displaced radially inward.
  • this takes place by axial embossing by means of annular or segmental calking.
  • the tool is pressed into the axial side face (annular wall 37 e ) of the control piston 37 .
  • the nonpositive connection between the closing element 39 and the control piston 37 is increased, and a positive connection occurs in the creeping direction, and therefore the relative position of the closing element 39 with respect to the control piston 37 is secured.
  • material receptacles 40 may be provided here, too.
  • the material receptacle 40 is implemented by means of a suitably dimensioned phase 40 a or a suitably dimensioned radius of the orifice-side bottom of the closing element 39 .
  • both the chamfer 40 a and the material displacement may extend over the entire outer circumference of the bottom or may be formed only segmentally.
  • a cylindrical closing element 39 may be provided.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Valve Device For Special Equipments (AREA)
US12/593,628 2007-03-30 2008-02-14 Control valve Abandoned US20110000447A1 (en)

Applications Claiming Priority (3)

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

Publications (1)

Publication Number Publication Date
US20110000447A1 true US20110000447A1 (en) 2011-01-06

Family

ID=39414930

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/593,628 Abandoned US20110000447A1 (en) 2007-03-30 2008-02-14 Control valve

Country Status (5)

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

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110017319A1 (en) * 2009-07-24 2011-01-27 Zhejiang Sanhua Climate And Appliance Controls Group Co., Ltd End cover and four-way reversing valve using the same and assembling method thereof
US20150053156A1 (en) * 2013-08-22 2015-02-26 Denso Corporation Valve timing control apparatus
US9822899B2 (en) 2013-05-28 2017-11-21 Schaeffler Technologies AG & Co. KG Arrangement of an electromagnet for controlling a central valve
US9915355B2 (en) 2015-10-06 2018-03-13 Caterpillar Inc. Valve having open-center spool with separated inserts
US10072765B2 (en) 2015-07-02 2018-09-11 Caterpillar Inc. Valve having spool assembly with insert divider

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014212991A1 (de) * 2014-07-04 2016-01-07 Schaeffler Technologies AG & Co. KG Steuerventilkolben aus Kunststoff
DE102015224656A1 (de) 2015-12-09 2017-06-14 Schaeffler Technologies AG & Co. KG Steuerventil für einen Nockenwellenversteller mit hohlem Steuerkolben

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US2852843A (en) * 1955-04-25 1958-09-23 Aerojet General Co Method of making metal joint
US3055100A (en) * 1957-07-01 1962-09-25 Zeller Corp Method of forming interlocking joint between telescoped members
US3848325A (en) * 1972-05-01 1974-11-19 C Bimba Method for assembling body and end sections for fluid power cylinder
US4789002A (en) * 1986-01-17 1988-12-06 Commercial Shearing, Inc. Fluid valve structures
US5014601A (en) * 1988-06-15 1991-05-14 Sundholm Goeran Working cylinder
US20010027721A1 (en) * 2000-02-16 2001-10-11 Takayuki Kato Hollow piston for compressor
US20040022652A1 (en) * 2002-08-02 2004-02-05 Aisan Kogyo Kabushiki Kaisha Low noise impeller pumps
US20050252561A1 (en) * 2004-05-14 2005-11-17 Andreas Strauss Control valve for a device for changing the control times of an internal combust ion engine
WO2006079382A1 (de) * 2005-01-27 2006-08-03 Schaeffler Kg Elektromagnetisches hydraulikventil
WO2008006717A1 (de) * 2006-07-08 2008-01-17 Schaeffler Kg Hydraulisches steuerventil

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DE1751946A1 (de) * 1968-08-22 1971-09-09 Eckerle Otto Schnellschlussventil fuer eine OElbrennerpumpe
DE3608757A1 (de) * 1986-03-15 1987-09-24 Hemscheidt Maschf Hermann 3/2-wegeventil mit druckausgleich fuer druckfluessigkeiten
DE10036268B4 (de) * 2000-07-26 2017-06-29 Daimler Ag Nockenwellenversteller für eine Brennkraftmaschine
US6554014B2 (en) * 2000-10-13 2003-04-29 Hydraforce, Inc. Proportional pilot operated directional valve
US6871621B2 (en) * 2003-05-12 2005-03-29 Hydraulik-Ring Gmbh Camshaft adjuster for internal combustion engines of motor vehicles
DE102004036096B4 (de) * 2004-07-24 2017-09-14 Schaeffler Technologies AG & Co. KG Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE102005034276A1 (de) * 2005-07-22 2007-01-25 Daimlerchrysler Ag Nockenwellenstellvorrichtung
DE102005037480A1 (de) * 2005-08-09 2007-02-15 Schaeffler Kg Steuerventil und Verfahren zur Herstellung desselben

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2852843A (en) * 1955-04-25 1958-09-23 Aerojet General Co Method of making metal joint
US3055100A (en) * 1957-07-01 1962-09-25 Zeller Corp Method of forming interlocking joint between telescoped members
US3848325A (en) * 1972-05-01 1974-11-19 C Bimba Method for assembling body and end sections for fluid power cylinder
US4789002A (en) * 1986-01-17 1988-12-06 Commercial Shearing, Inc. Fluid valve structures
US5014601A (en) * 1988-06-15 1991-05-14 Sundholm Goeran Working cylinder
US20010027721A1 (en) * 2000-02-16 2001-10-11 Takayuki Kato Hollow piston for compressor
US20040022652A1 (en) * 2002-08-02 2004-02-05 Aisan Kogyo Kabushiki Kaisha Low noise impeller pumps
US20050252561A1 (en) * 2004-05-14 2005-11-17 Andreas Strauss Control valve for a device for changing the control times of an internal combust ion engine
WO2006079382A1 (de) * 2005-01-27 2006-08-03 Schaeffler Kg Elektromagnetisches hydraulikventil
WO2008006717A1 (de) * 2006-07-08 2008-01-17 Schaeffler Kg Hydraulisches steuerventil

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110017319A1 (en) * 2009-07-24 2011-01-27 Zhejiang Sanhua Climate And Appliance Controls Group Co., Ltd End cover and four-way reversing valve using the same and assembling method thereof
US8770225B2 (en) 2009-07-24 2014-07-08 Zhejiang Sanhua Climate And Appliance Controls Group Co., Ltd End cover and four-way reversing valve using the same and assembling method thereof
US9822899B2 (en) 2013-05-28 2017-11-21 Schaeffler Technologies AG & Co. KG Arrangement of an electromagnet for controlling a central valve
US20150053156A1 (en) * 2013-08-22 2015-02-26 Denso Corporation Valve timing control apparatus
US9528400B2 (en) * 2013-08-22 2016-12-27 Denso Corporation Valve timing control apparatus
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

Also Published As

Publication number Publication date
DE102007015333A1 (de) 2008-10-02
CN101652537A (zh) 2010-02-17
DE102007015333B4 (de) 2020-08-27
EP2142766A1 (de) 2010-01-13
CN101652537B (zh) 2012-06-13
WO2008119591A1 (de) 2008-10-09

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