EP1491728A2 - Déphaseur d'arbre à cames - Google Patents

Déphaseur d'arbre à cames Download PDF

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Publication number
EP1491728A2
EP1491728A2 EP20040014612 EP04014612A EP1491728A2 EP 1491728 A2 EP1491728 A2 EP 1491728A2 EP 20040014612 EP20040014612 EP 20040014612 EP 04014612 A EP04014612 A EP 04014612A EP 1491728 A2 EP1491728 A2 EP 1491728A2
Authority
EP
European Patent Office
Prior art keywords
housing member
receiving hole
rotor
relative rotation
contact
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
EP20040014612
Other languages
German (de)
English (en)
Other versions
EP1491728B1 (fr
EP1491728A3 (fr
Inventor
Masaki c/o I.P.D AISIN SEIKI KAB. KAISHA Kobayashi
Katsuhiko c/o I.P.D AISIN SEIKI KAB KAISHA Eguchi
Kazumi c/o I.P.D AISIN SEIKI KAB. KAISHA Ogawa
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.)
Aisin Corp
Original Assignee
Aisin Seiki Co Ltd
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 Aisin Seiki Co Ltd filed Critical Aisin Seiki Co Ltd
Publication of EP1491728A2 publication Critical patent/EP1491728A2/fr
Publication of EP1491728A3 publication Critical patent/EP1491728A3/fr
Application granted granted Critical
Publication of EP1491728B1 publication Critical patent/EP1491728B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • 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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34483—Phaser return springs

Definitions

  • This invention generally relates to a variable valve timing control device. More particularly, the present invention pertains to a variable valve timing control device for controlling an opening and closing timing of an intake valve and exhaust valve of an internal combustion engine.
  • variable valve timing control devices are disclosed in Japanese Patent Nos. 3266013 and 3146956.
  • the disclosed variable valve timing control devices each include a housing member integrally rotating with one of a crankshaft and a camshaft of an internal combustion engine, a rotor member assembled to the housing member so as to be rotatable relative thereto and being slidable on a convex portion formed on the housing member.
  • the rotor member includes vane portions each forming an advanced angle chamber and a retarded angle chamber within the housing member, and integrally rotating with the other one of the crankshaft and the camshaft.
  • the variable valve timing control device also includes a stopper formed on the convex portion and being in contact with at least one of the vane portions for defining the relative rotation between the housing member and the rotor member to an advanced angle side or a retarded angle side.
  • the variable valve timing control device further includes a lock mechanism for restricting the relative rotation between the housing member and the rotor member by a lock member disposed on the housing member to be inserted into a receiving hole formed on the rotor member when a relative rotation phase between the housing member and the rotor member is positioned at a predetermined phase, and a fluid pressure circuit for controlling an operation oil to be supplied to or discharged from the advanced angle chamber, the retarded angle chamber, and the lock mechanism.
  • the lock member when the lock member is in contact with an opening edge portion of a receiving hole within which the lock member is positioned, plastic flow of material forming the receiving hole may be caused due to tangential stress. Then, the opening edge portion may be raised towards the housing member side. Further, the opening edge portion being raised may interfere with the relative rotation between the housing member and the rotor member.
  • the lock member includes an engaging taper face on a side of the receiving hole while the receiving hole includes a guiding taper face gradually expanding towards an opening side of the receiving hole. The lock member is in contact with an inner peripheral face of the receiving hole under the condition that a taper angle of the guiding taper face is larger than that of the engaging taper face. Then, the plastic flow may be prevented from occurring in the opening edge portion of the receiving hole.
  • variable valve timing control device disclosed in Japanese Patent No. 3146956, a clearance is formed between the lock member and the receiving hole considering a receiving performance of the lock member in the receiving hole.
  • the advanced angle chamber or the retarded angle chamber is not sufficiently supplied with the operation fluid from an oil pump at a time of an engine start, the rotor member and the housing member starts rotating relative to each other due to the fluctuation torque of the cam being applied.
  • the clearance is formed between the lock member and the receiving hole, an inner periphery of the receiving hole and an outer periphery of the lock member may become in contact with each other repeatedly, thereby causing a hitting sound.
  • a taper face is formed on at least one of the lock member and the receiving hole being in contact with each other. Then, a biasing force to bias the rotor member in the rotational direction is generated in the housing member to strongly press the stopper and the vane portion to each other so that the rotor member and the housing member are constrained at a locked position.
  • the lock member can be in contact with the inner circumferential face of the receiving face.
  • a clearance may be formed between the lock member and the receiving hole, which causes a looseness therebetween. Further, the hitting sound due to the looseness may occur.
  • variable valve timing control device disclosed in Japanese Patent No. 3146956, the rotor member and the housing member are constrained at the locked position and thus the lock member may not be able to move from the receiving hole.
  • variable valve timing control device which can prevent an occurrence of hitting sound due to a relative rotation between a lock member and a receiving hole in case of the relative rotation being locked.
  • a variable valve timing control device includes a housing member integrally rotating with one of a crankshaft and a camshaft of an internal combustion engine, and a rotor member assembled to the housing member so as to be rotatable relative thereto and being slidable on a convex portion formed on the housing member, the rotor member including vane portions each forming an advanced angle chamber and a retarded angle chamber within the housing member, the rotor member integrally rotating with the other one of the crankshaft and the camshaft.
  • the variable valve timing control device also includes a stopper formed on the convex portion and being in contact with at least one of the vane portions for defining a relative rotation between the housing member and the rotor member to an advanced angle side or a retarded angle side, a lock mechanism for restricting the relative rotation between the housing member and the rotor member by a lock member disposed on the housing member to be inserted into a receiving hole formed on the rotor member when a relative rotation phase between the housing member and the rotor member is positioned at a predetermined phase, and a fluid pressure circuit for controlling an operation oil to be supplied to or discharged from the advanced angle chamber, the retarded angle chamber, and the lock mechanism.
  • the lock member is in contact with an inner peripheral face of the receiving hole on the advanced angle side and the retarded angle side between an opening portion and a bottom portion of the receiving hole.
  • the lock member is in contact with the inner peripheral face of the receiving hole on the advanced angle side and the retarded angle side between the opening portion and the bottom portion of the receiving hole when the relative rotation between the rotor member and the housing member is restricted.
  • the lock member and the receiving hole are in contact with each other to thereby restrict the relative rotation between the rotor member and the housing member to the advanced angle side and the retarded angle side. The occurrence of the hitting sound due to the contact between the lock member and the receiving hole may be prevented accordingly.
  • a variable valve timing control device includes a housing member integrally rotating with one of a crankshaft and a camshaft of an internal combustion engine, and a rotor member assembled to the housing member so as to be rotatable relative thereto and being slidable on a convex portion formed on the housing member, the rotor member including vane portions each forming an advanced angle chamber and a retarded angle chamber within the housing member, the rotor member integrally rotating with the other one of the crankshaft and the camshaft.
  • the variable valve timing control device also includes a stopper formed on the convex portion and being in contact with at least one of the vane portions for defining a relative rotation between the housing member and the rotor member to an advanced angle side or a retarded angle side, a lock mechanism for restricting the relative rotation between the housing member and the rotor member by a lock member disposed on the housing member to be inserted into a receiving hole formed on the rotor member when a relative rotation phase between the housing member and the rotor member is positioned at a predetermined phase, and a fluid pressure circuit for controlling an operation oil to be supplied to or discharged from the advanced angle chamber, the retarded angle chamber, and the lock mechanism.
  • a contact width in a circumferential direction of a contact portion of the lock member, with which an inner peripheral face of the receiving hole on the advanced angle side and the retarded angle side is in contact is larger than a bottom width in the circumferential direction of a bottom portion of the receiving hole.
  • the lock member and the receiving hole are in contact with each other since the contact width in the circumferential direction of the contact portion of the lock member, with which the inner peripheral face of the receiving hole on the advanced angle side and the retarded angle side is in contact, is larger than the bottom width in the circumferential direction of the bottom portion of the receiving hole, thereby avoiding the occurrence of the hitting sound.
  • Fig. 1 is a longitudinal sectional view of a variable valve timing control device according to an embodiment of the present invention
  • Fig. 2 is a cross-sectional view taken along the ling A-A of Fig. 1;
  • Fig. 3 is an enlarged view of E portion of Fig. 2;
  • Fig. 4 is an enlarged view of F portion of Fig. 3.
  • a variable valve timing control device 1 shown in Figs. 1 to 3 includes a rotor member 2 for opening/closing a valve, which includes a camshaft 10 rotatably supported on a cylinder head 100 of an internal combustion engine and an inner rotor 20 integrally fixed to a tip end portion of the camshaft 10.
  • the variable valve timing control device 1 also includes a housing member 3 having an outer rotor 30 being rotatable relative to the inner rotor 20 within a predetermined range, a front plate 40, and a rear plate 50.
  • a timing sprocket 31 is integrally formed on an outer periphery of the outer rotor 30.
  • variable valve timing control device 1 includes a torsion spring 60 disposed between the inner rotor 20 and the front plate 40, four vanes 70 assembled to the inner rotor 20, and a lock plate 80 (lock member) (see Fig. 2) assembled to the outer rotor 30.
  • the timing sprocket 31 receives the rotation force in the clockwise direction thereof, which is shown as a rotation direction of camshaft in Fig. 2.
  • the rotation force is transmitted from a crankshaft (not shown) via a crank sprocket (not shown) and a timing chain (not shown).
  • the camshaft 10 includes a known cam (not shown) for opening/closing an exhaust valve (not shown).
  • An advanced angle fluid passage (fluid pressure circuit) 11 and a retarded angle fluid passage (fluid pressure circuit) 12 extending in an axial direction of the camshaft 10 are provided inside of the camshaft 10.
  • the advanced angle fluid passage 11 is connected to a first connecting port 201 of a switching valve 200 via a passage 71 provided on the camshaft 10 in the radial direction thereof, an annular groove 14, and a connecting passage 16 provided on the cylinder head 100.
  • retarded angle fluid passage 12 is connected to a second connecting port 202 of the switching valve 200 via a passage 72 provided on the camshaft 10 in the radial direction thereof, an annular groove 13, and a connecting passage 15 provided on the cylinder head 100.
  • the switching valve 200 is a known type in which a spool 204 is moved against a biasing force of a spring (not shown) by energizing a solenoid 203.
  • a solenoid 203 When the solenoid 203 is de-energized, a supply port 206 connected to an oil pump 205 that is driven by the internal combustion engine communicates with the first connecting port 201 as shown in Fig. 1.
  • the second connecting port 202 communicates with a discharge port 207.
  • the solenoid 203 When the solenoid 203 is energized, the supply port 206 communicates with the second connecting port 202 and at the same time the first connecting port 201 communicates with the discharge port 207.
  • the operation fluid (fluid pressure) is supplied to the advanced angle fluid passage 11.
  • the operation fluid is supplied to the retarded angle fluid passage 12.
  • Energization of the solenoid 203 of the switching valve 200 is duty-controlled by which a ratio of energization/de-energization per unit time is changed. For example, when the switching valve 200 is duty-controlled at 50%, the first and second ports 201 and 202, and the supply and discharge ports 206 and 207 are not connected to each other.
  • the inner rotor 20 is integrally fixed to the camshaft 10 via an installation bolt 91. As shown in Fig. 2, four vane grooves 21 and a receiving hole 22 are formed on the inner rotor 20. In addition, four first fluid passages 23 (fluid pressure circuit), three second fluid passages 24 (fluid pressure circuit) extending in the radial direction of the inner rotor 20, a fluid groove 24a (fluid pressure circuit), and a lock fluid passage 25 for connecting a bottom portion 22d of the receiving hole 22 to the advanced angle fluid passage 11.
  • the vanes 70 are positioned in the vane grooves 21 respectively, being movable in the radial direction of the inner rotor 20.
  • the four vanes 70 are movable within four fluid pressure chambers R0 respectively, which are each defined between the outer rotor 30 and the inner rotor 20 and arranged, dividing each fluid pressure chamber R0 into an advanced angle chamber R1 and a retarded angle chamber R2.
  • Each vane 70 is biased in the radially outward direction by a vane spring 73 (see Fig. 1) disposed between the bottom portion of each vane groove 21 and the bottom face of each vane 70.
  • the operation fluid (fluid pressure) is supplied to or discharged from the four advanced angle chambers R1, which are defined and divided by the vanes 70, via the advanced angle fluid passage 11 and the first fluid passage 23.
  • the operation fluid is supplied to or discharged from three retarded angle chambers R2 out of four via the retarded angle fluid passage 12 and the second fluid passage 24.
  • the operation fluid is supplied to the lock plate 80 from the lock fluid passage 25 formed on the bottom portion 22d of the receiving hole 22.
  • the operation fluid is supplied to or discharged from the remaining (i.e. one out of four) retarded angle chamber R2 via the fluid groove 24a connecting the lock fluid passage 25 and that retarded angle chamber R2. Accordingly, for one retarded angle chamber R2 out of four, the second fluid passage 24 is not provided and the lock fluid passage 25 is shared to be used, which may achieve a simple structure of the fluid pressure circuit.
  • Both side portions of the outer rotor 30 in the axial direction thereof are integrally fixed to the annular shaped front plate 40 and the rear plate 50 respectively via five connecting bolts 92.
  • the timing sprocket 31 is integrally formed on an outer periphery of the outer rotor 30 and on an end side in the axial direction thereof to which the rear plate 50 is connected.
  • five convex portions 33 are formed on the inner circumference of the outer rotor 30 in the circumferential direction thereof so as to project in the radially inward direction.
  • Each inner circumferential face of each convex portion 33 is slidably in contact with an outer circumferential face of the inner rotor 20. That is, the outer rotor 30 is rotatably supported on the inner rotor 20.
  • a side face 33a (stopper) of one convex portion 33A out of the five convex portions 33 is in contact with a side face 70a of a vane 70A, thereby defining a relative rotational angle between the outer rotor 30 and the inner rotor 20 to the advanced angle side.
  • a side face 33b (stopper) of one convex portion 33B is in contact with a side face 70b of a vane 70B, thereby defining the relative rotational angle between the outer rotor 30 and the inner rotor 20 to the retarded angle side.
  • a retracting groove portion 34 for accommodating the lock plate 80, and a receiving bore 35 connected to the retracting groove portion 34 for accommodating a coil spring 81 that biases the lock plate 80 in the radially inward direction of the outer rotor 30 are formed between the two convex portions 33 out of five.
  • the four fluid pressure chambers R0 mentioned above are formed between five convex portions 33, respectively.
  • the end portion 80b of the lock plate 80 and the taper portion 22c of the inner peripheral face 22b of the receiving hole 22 are in contact with each other on the advanced angle side and the retarded angle side, thereby restricting the relative rotation between the inner rotor 20 and the outer rotor 30.
  • the head portion 80a of the lock plate 80 may have a substantially rectangular shape instead of the trapezoidal shape.
  • the end portion 80b of the lock plate 80 may be chamfered.
  • the lock plate 80 When the relative rotation between the inner rotor 20 and the outer rotor 30 is restricted, the lock plate 80 is positioned in the receiving hole 22. At the same time, a gap C is formed between the side face 33a of the convex portion 33A and the side face 70a of the vane 70A. Therefore, when the fluctuation torque by the camshaft 10 is applied to the end portion 80b and the taper portion 22c in the advanced angle direction and the retarded angle direction alternately under the condition that the operation fluid is supplied to the receiving hole 22 and thus the relative rotation between the inner rotor 20 and the outer rotor 30 is permitted, i.e. the locked state thereof is released, the lock plate 80 and the receiving hole 22 are prevented from being strongly constrained each other.
  • a size of the gap C is defined such that when the side face 70a of the vane 70A is in contact with the side face 33a of the convex portion 33A to thereby restrict the relative rotation between the inner rotor 20 and the outer rotor 30 at the most advanced angle phase, the head portion 80a of the lock plate 80 is guided in radially inward direction of the receiving hole 22 with being in contact with the inner peripheral face 22b of the receiving hole 22.
  • the head portion 80a of the lock plate 80 is guided in the radially inward direction of the receiving hole 22. Then, when the vane 70 is separated from the convex portion 33 due to the fluctuation torque of the cam, the head portion 80a of the lock plate 80 is further inserted into the radially inward direction of the receiving hole 22.
  • the end portion 80b of the lock plate 80 and the taper portion 22c of the inner peripheral face 22b of the receiving hole 22 are in contact with each other on the advanced angle side and the retarded angle side, thereby restricting the relative rotation between the inner rotor 20 and the outer rotor 30.
  • the torsion spring 60 is provided by engaging with the front plate 40 at one end and the inner rotor 20 at the other end.
  • the torsion spring 60 biases the inner rotor 20 towards the advanced angle side (clockwise direction in Fig. 2) relative to the outer rotor 30, the front plate 40 and the rear plate 50.
  • the operation response of the inner rotor 20 to the advanced angle side may be improved.
  • the oil pump 205 when the internal combustion engine is stopped, the oil pump 205 is stopped and also the switching valve 200 is not energized. Thus, the operation fluid is not supplied to the fluid pressure chambers R0. At this time, the head portion 80a of the lock plate 80 is positioned within the receiving hole 22 of the inner rotor 20 and thus the relative rotation between the inner rotor 20 and the outer rotor 30 is restricted. Even when the internal combustion engine is started and the oil pump 205 is driven, the operation fluid supplied from the oil pump 205 is only virtually provided to the advanced angle chamber R1 via the connecting passage 16, the advanced angle fluid passage 11, and the first fluid passage 23 while the duty ratio is small for energizing the switching valve 200 (i.e. the ratio of energizing time relative to the de-energizing time per unit time is small). Therefore, the variable valve timing control device 1 is maintained in a locked state.
  • the operation fluid stored in the advanced angle chamber R1 is sent to the first fluid passage 23, the advanced angle fluid passage 11, and the connecting passage 16 to be discharged from the discharge port 207 of the switching valve 200. Therefore, the lock plate 80 is moved against the biasing force of the spring 81, thereby moving the head portion 80a from the receiving hole 22. Then, the locked state between the inner rotor 20 and the outer rotor 30 is released. At the same time, the inner rotor 20 integrally rotating with the camshaft 10 and each vane 70 rotate relative to the outer rotor 30, the front plate 40, and the rear plate 50 in the retarded angle direction (counterclockwise direction in Fig. 2). Due to the aforementioned relative rotation, the timing of the cam is brought in the advanced angle state.
  • the relative rotation phase may be defined arbitrarily by controlling the duty ratio of the switching valve 200. For example, the relative rotation between the inner rotor 20 and the outer rotor 30 may be stopped at the intermediate phase.
EP04014612A 2003-06-25 2004-06-22 Déphaseur d'arbre à cames Expired - Fee Related EP1491728B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003181475 2003-06-25
JP2003181475 2003-06-25

Publications (3)

Publication Number Publication Date
EP1491728A2 true EP1491728A2 (fr) 2004-12-29
EP1491728A3 EP1491728A3 (fr) 2005-11-30
EP1491728B1 EP1491728B1 (fr) 2010-08-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP04014612A Expired - Fee Related EP1491728B1 (fr) 2003-06-25 2004-06-22 Déphaseur d'arbre à cames

Country Status (3)

Country Link
US (1) US20050022763A1 (fr)
EP (1) EP1491728B1 (fr)
DE (1) DE602004028552D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2947286A4 (fr) * 2013-01-18 2016-11-23 Mikuni Kogyo Kk Dispositif de distribution à programme variable et son procédé d'assemblage

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BRPI1010626B1 (pt) 2010-11-08 2020-09-15 Toyota Jidosha Kabushiki Kaisha Dispositivo de controle para mecanismo de regulagem de válvula variável hidráulico
US9206712B2 (en) 2011-04-07 2015-12-08 Toyota Jidosha Kabushiki Kaisha Variable valve timing device
DE102014214610B4 (de) * 2014-07-25 2017-05-18 Schaeffler Technologies AG & Co. KG Nockenwellenverstellvorrichtung für eine Brennkraftmaschine

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1008729A2 (fr) * 1998-12-07 2000-06-14 Mitsubishi Denki Kabushiki Kaisha Actionneur hydraulique à ailettes
US20010054405A1 (en) * 2000-06-22 2001-12-27 Unisia Jecs Corporation Variable valve control apparatus for an internal combustion engine

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1008729A2 (fr) * 1998-12-07 2000-06-14 Mitsubishi Denki Kabushiki Kaisha Actionneur hydraulique à ailettes
US20010054405A1 (en) * 2000-06-22 2001-12-27 Unisia Jecs Corporation Variable valve control apparatus for an internal combustion engine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2947286A4 (fr) * 2013-01-18 2016-11-23 Mikuni Kogyo Kk Dispositif de distribution à programme variable et son procédé d'assemblage

Also Published As

Publication number Publication date
US20050022763A1 (en) 2005-02-03
EP1491728B1 (fr) 2010-08-11
DE602004028552D1 (de) 2010-09-23
EP1491728A3 (fr) 2005-11-30

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