EP2025885A2 - Soupape de contrôle d'huile pour déphaseur à came variable - Google Patents

Soupape de contrôle d'huile pour déphaseur à came variable Download PDF

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Publication number
EP2025885A2
EP2025885A2 EP08161391A EP08161391A EP2025885A2 EP 2025885 A2 EP2025885 A2 EP 2025885A2 EP 08161391 A EP08161391 A EP 08161391A EP 08161391 A EP08161391 A EP 08161391A EP 2025885 A2 EP2025885 A2 EP 2025885A2
Authority
EP
European Patent Office
Prior art keywords
bobbin
valve
frame
shoulder
secondary plate
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.)
Withdrawn
Application number
EP08161391A
Other languages
German (de)
English (en)
Other versions
EP2025885A3 (fr
Inventor
Miguel I. Avila
Viswanathan Subramanian
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.)
Delphi Technologies Inc
Original Assignee
Delphi Technologies Inc
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 Delphi Technologies Inc filed Critical Delphi Technologies Inc
Publication of EP2025885A2 publication Critical patent/EP2025885A2/fr
Publication of EP2025885A3 publication Critical patent/EP2025885A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • 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
    • 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
    • F01L2001/3443—Solenoid driven oil control valves
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/128—Encapsulating, encasing or sealing

Definitions

  • the present invention relates generally to oil control valves for variable cam phasers.
  • VCP Variable Cam Phaser
  • the cam lobe angular position of the VCP (i.e., its phase relationship), is controlled by an internal vane mechanism of the VCP that in turn is established by an oil control valve. More specifically, commands from the engine control module (ECM) of the vehicle adjust the position of the oil control valve, which can be mounted in the cylinder head to regulate engine oil flow to either side of the vanes to advance or retard the camshaft position.
  • ECM engine control module
  • the oil control valve has a fluid control portion that is driven by an electromagnetic solenoid.
  • the fluid control portion includes a valve body and an internal spool, with two separate openings being formed in the valve body that are in fluid connection with two separate sides of the VCP.
  • the internal spool has an oil inlet and two separate outlets that correspond to and overlap with the two openings in the valve body.
  • the electromagnetic solenoid of the oil control valve is comprised mainly of a bobbin, which has metal and plastic sections.
  • the bobbin of the electromagnetic solenoid can become dislodged or loose over time due to the differing thermal expansion of its metal and plastic components caused by the heat of the engine. After becoming dislodged or loose, oil from the fluid control portion of the oil control valve can leak through the bobbin into the electromagnetic solenoid. This effect may cause the oil control valve to malfunction.
  • An oil control valve for a variable cam phaser includes a metal frame that is formed with a radially enlarged part with a first inside diameter and a radially smaller part with a second inside diameter less than the first inside diameter.
  • the two parts are coaxial with each other such that a shoulder is established between them. More specifically, the shoulder defines an annular surface that is perpendicular to the axis of the parts.
  • a bobbin that is partially metal is disposed within the frame with the bobbin abutting the surface of the shoulder.
  • An o-ring is disposed between the bobbin and frame. The combination of the o-ring and bobbin abutting the surface of the shoulder substantially prevents oil from leaking to a connector associated with the valve.
  • the connector is substantially coaxial with the axis of the frame and bobbin.
  • the bobbin may include a secondary plate engaged with a plastic body by means of overmolding the plastic body onto the secondary plate, and the secondary plate abuts the surface of the shoulder.
  • the valve can be engaged with the variable cam phaser.
  • an assembly for a vehicle in another aspect, includes a variable cam phaser and an oil control valve engaged with the phaser to selectively port oil to the phaser.
  • the oil control valve has a shoulder defining a metal-to-metal interface between two metal parts of the valve to inhibit oil leakage into an electrical connector of the valve.
  • an oil control valve in yet another aspect, includes an electrical connector and a bobbin including a metal secondary plate.
  • a frame surrounds the bobbin. As set forth further below, the frame defines an axis and an annular surface substantially perpendicular to the axis, with the secondary plate abutting the surface.
  • Figure 1 is a block diagram of a non-limiting environment of the present oil control valve.
  • Figure 2 is a cut-away side view of an exemplary non-limiting embodiment of the present valve.
  • an internal combustion engine 5 is shown with a controller 10.
  • the engine 5 is operably coupled to a variable cam phaser 14 that is controlled by an oil control valve 12, the details of which are further described below.
  • the engine 5 has at least one camshaft 16 with the variable cam phaser 14 attached thereto and a cam position sensor 13.
  • the cam phaser 14 is fluidly connected to the oil control valve 12, which in turn is fluidly connected to a pressurized supply of oil from the engine 5 or other source.
  • the controller 10 is operably connected to an engine torque management system such as the one described in USPN 6,367,462, incorporated by reference.
  • the controller 10 is also operably connected to at least one sensor that is used to monitor engine operation.
  • the engine torque management system may also include a fuel injection system, an ignition system, an electronic throttle control system, an exhaust gas recirculation system, an evaporative control system (not shown), along with the variable cam phaser 14 with the oil control valve 12.
  • the sensor may include an engine speed sensor, a manifold absolute pressure sensor, a throttle position sensor, an oxygen sensor, intake air sensor, mass air flow sensor, EGR position sensor, exhaust pressure sensor, exhaust gas sensor, torque sensor, combustion sensor, or others (not shown), and/or the cam position sensor 13.
  • the controller 10 collects information from the sensors and control output systems, including the engine torque management system, using control algorithms and calibrations internal to the controller 10.
  • the valve 12 includes an electromagnetic solenoid 30 and a valve 32.
  • the valve advantageously may be a spool valve 32 with a single inlet 34 of oil and two outlets of oil 36, 38.
  • a spool 31 is attached to an armature (not shown) of the electromagnetic solenoid 30, and the spool 31 is contained within a valve body 33 coaxial to the longitudinal axis of the body 33.
  • Each of the two outlets 36, 38 of oil is attached to one of the inlets of the cam phaser 14, as described above.
  • the electromechanical solenoid 30 is driven by a pulsewidth-modulated (PWM) signal 40 sent from the controller 10.
  • PWM pulsewidth-modulated
  • a PWM signal 40 is sent to the electromagnetic solenoid 30 to cause the armature (not shown in Figure 1 ) and attached spool 31 to move linearly along the longitudinal axis within the valve body 33.
  • the position of the spool 31 in conjunction with the designs of the spool 31 and the valve body 33 determines the oil flow through the valve 32 from the fluid inlet 34 to each of the two fluid outlets 36, 38.
  • the oil control valve 12 provides sufficient oil flow rate through the valve 32 so that the response time of the cam phaser 14 and corresponding combustion efficiency of the engine 5 can be optimized at typical oil pressures, temperatures and voltage levels.
  • the electromagnetic solenoid 30 shown in Figure 1 is wound around a bobbin 42 that extends past the solenoid and that defines an axis 44.
  • the electromagnetic solenoid in Figure 1 is electrically connected to a connector 46, which is disposed in a connector cavity 48 formed in the bobbin 42.
  • the connector cavity 48 is coaxial with the axis 44 of the bobbin 42 and the connector pin 46 is parallel to and if desired coaxial with the axis 44.
  • the bobbin 42 which may be hollow such that it forms a bobbin chamber 50 as shown, is surrounded by a metal frame 52.
  • the frame 52 is formed with a radially enlarged part 54 with a first inside diameter D1 and a radially smaller part 56 with a second inside diameter D2 which is less than the first inside diameter D1.
  • the radially enlarged part 54 and the radially smaller part 56 are coaxial with each other and with the connector 46.
  • a shoulder 58 is established between the radially enlarged part 54 and the radially smaller part 56.
  • the shoulder 58 defines an annular surface 60 that is perpendicular to the axis 44 of the bobbin 42. Further, the bobbin 42 abuts the surface of the shoulder 58 and is at least partially disposed within the frame 52.
  • the bobbin 42 includes a hollow metal secondary plate 62 that is engaged with the plastic body of the bobbin 42 by means of, e.g., overmolding the plastic body onto the secondary plate 62, and a portion of the secondary plate 62 abuts the surface of the shoulder 58, creating a metal-to-metal interface.
  • a metal-to-metal interface oil is in part prevented from leaking through the bobbin 42 into the connector 46 because the thermal expansion of both metal components will remain equal and the seal between the metal interfaces will remain secure, thereby inhibiting oil from leaking up through the bobbin.
  • a further seal between the bobbin and the frame is created through the existence of an O-ring 64.
  • the O-ring 64 is disposed between the bobbin 42 and frame 52 in a circular groove 66 that is formed in the bobbin 42 as shown. Any oil leaking past the metal-to-metal interface described above will be further impeded by the O-ring 64, which acts as a secondary barrier to ensure that oil does not leak into the connector 46.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP08161391A 2007-08-09 2008-07-29 Soupape de contrôle d'huile pour déphaseur à came variable Withdrawn EP2025885A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11/891,080 US20090038571A1 (en) 2007-08-09 2007-08-09 Oil control valve for variable cam phaser

Publications (2)

Publication Number Publication Date
EP2025885A2 true EP2025885A2 (fr) 2009-02-18
EP2025885A3 EP2025885A3 (fr) 2009-04-15

Family

ID=40089875

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08161391A Withdrawn EP2025885A3 (fr) 2007-08-09 2008-07-29 Soupape de contrôle d'huile pour déphaseur à came variable

Country Status (2)

Country Link
US (1) US20090038571A1 (fr)
EP (1) EP2025885A3 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19504185A1 (de) * 1995-02-09 1996-08-14 Rexroth Mannesmann Gmbh Elektromagnet mit hülsenförmigem Gehäuse
DE19934846A1 (de) * 1999-07-24 2001-01-25 Hydraulik Ring Gmbh Elektromagnet und hydraulisches Ventil mit einem Elektromagneten
DE10238840A1 (de) * 2002-08-23 2004-03-04 Thomas Magnete Gmbh Magnetanordnung
US20050178992A1 (en) * 2004-02-17 2005-08-18 Barron Luis F. Solenoid valve
US20060237672A1 (en) * 2005-04-22 2006-10-26 Alejandro Moreno Normally open high flow hydraulic pressure control actuator
WO2007059898A1 (fr) * 2005-11-24 2007-05-31 Thomas Magnete Gmbh Soupape de commande hydraulique/pneumatique a fonction de securite integree
WO2007065566A1 (fr) * 2005-12-09 2007-06-14 Thomas Magnete Gmbh Systeme modulaire de soupape qui comprend une soupape a actionnement electromagnetique

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6824120B2 (en) * 2001-11-09 2004-11-30 Denso Corporation Flow amount control device
US7007925B2 (en) * 2004-08-05 2006-03-07 Husco International, Inc. Electrohydraulic valve having an armature with a rolling bearing

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19504185A1 (de) * 1995-02-09 1996-08-14 Rexroth Mannesmann Gmbh Elektromagnet mit hülsenförmigem Gehäuse
DE19934846A1 (de) * 1999-07-24 2001-01-25 Hydraulik Ring Gmbh Elektromagnet und hydraulisches Ventil mit einem Elektromagneten
DE10238840A1 (de) * 2002-08-23 2004-03-04 Thomas Magnete Gmbh Magnetanordnung
US20050178992A1 (en) * 2004-02-17 2005-08-18 Barron Luis F. Solenoid valve
US20060237672A1 (en) * 2005-04-22 2006-10-26 Alejandro Moreno Normally open high flow hydraulic pressure control actuator
WO2007059898A1 (fr) * 2005-11-24 2007-05-31 Thomas Magnete Gmbh Soupape de commande hydraulique/pneumatique a fonction de securite integree
WO2007065566A1 (fr) * 2005-12-09 2007-06-14 Thomas Magnete Gmbh Systeme modulaire de soupape qui comprend une soupape a actionnement electromagnetique

Also Published As

Publication number Publication date
EP2025885A3 (fr) 2009-04-15
US20090038571A1 (en) 2009-02-12

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