US20050022763A1 - Variable valve timing control device - Google Patents

Variable valve timing control device Download PDF

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Publication number
US20050022763A1
US20050022763A1 US10/875,736 US87573604A US2005022763A1 US 20050022763 A1 US20050022763 A1 US 20050022763A1 US 87573604 A US87573604 A US 87573604A US 2005022763 A1 US2005022763 A1 US 2005022763A1
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US
United States
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.)
Abandoned
Application number
US10/875,736
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English (en)
Inventor
Masaki Kobayashi
Katsuhiko Eguchi
Kazumi 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
Assigned to AISIN SEIKI KABUSHIKI KAISHA reassignment AISIN SEIKI KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: EGUCHI, KATSUHIKO, KOBAYASHI, MASAKI, OGAWA, KAZUMI
Priority to US11/019,399 priority Critical patent/US7311069B2/en
Publication of US20050022763A1 publication Critical patent/US20050022763A1/en
Abandoned 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
    • F01L2001/3445—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.
  • 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.
  • 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 .
  • the 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 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 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 .
  • four vane grooves 21 and a receiving hole 22 are formed on the inner rotor 20 .
  • 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 R 0 respectively, which are each defined between the outer rotor 30 and the inner rotor 20 and arranged, dividing each fluid pressure chamber R 0 into an advanced angle chamber R 1 and a retarded angle chamber R 2 .
  • 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 R 1 , 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 R 2 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 22 d of the receiving hole 22 . When the lock plate 80 is moved, the operation fluid is supplied to or discharged from the remaining (i.e.
  • 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 .
  • the outer rotor 30 is rotatably supported on the inner rotor 20 .
  • a side face 33 a (stopper) of one convex portion 33 A out of the five convex portions 33 is in contact with a side face 70 a of a vane 70 A, thereby defining a relative rotational angle between the outer rotor 30 and the inner rotor 20 to the advanced angle side.
  • a side face 33 b (stopper) of one convex portion 33 B is in contact with a side face 70 b of a vane 70 B, 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 R 0 mentioned above are formed between five convex portions 33 , respectively.
  • a head portion 80 a of the lock plate 80 i.e. facing the bottom portion 22 d of the receiving hole 22 , has a trapezoidal shape in cross section formed by a convex taper portion extending in the radially inward direction of the outer rotor 30 and a top portion.
  • An inner peripheral face 22 b is formed by a concave taper portion 22 c having a trapezoidal shape in cross section and gradually expanding towards an opening portion 22 a , and the bottom portion 22 d .
  • An end portion 80 b (contact portion) of the top portion of the lock plate 80 is in contact with the inner peripheral face 22 b of the receiving hole 22 on the advanced angle side and the retarded angle side between the opening portion 22 a and the bottom portion 22 d of the receiving hole 22 .
  • a contact width B in the circumferential direction of the contact portion 80 b of the lock plate 80 with which the inner peripheral face 22 b of the receiving hole 22 on the advanced angle side and the retarded angle side is in contact, is larger than a bottom width D in the circumferential direction of the bottom portion 22 d of the receiving hole 22 .
  • the end portion 80 b of the lock plate 80 and the taper portion 22 c of the inner peripheral face 22 b 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 80 a of the lock plate 80 may have a substantially rectangular shape instead of the trapezoidal shape.
  • the end portion 80 b 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 33 a of the convex portion 33 A and the side face 70 a of the vane 70 A. Therefore, when the fluctuation torque by the camshaft 10 is applied to the end portion 80 b and the taper portion 22 c 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.
  • the lock plate 80 and the receiving hole 22 rotate relative to each other, which brings the end portion 80 b of the lock plate 80 to be pushed by the taper portion 22 c of the inner peripheral face 22 b of the receiving hole 22 .
  • the lock plate 80 is thus biased to move from the receiving hole 22 , thereby causing the locked state of the relative rotation between the inner rotor 20 and the outer rotor 30 to be easily released.
  • a size of the gap C is defined such that when the side face 70 a of the vane 70 A is in contact with the side face 33 a of the convex portion 33 A 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 80 a 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 22 b of the receiving hole 22 .
  • the head portion 80 a 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 80 a of the lock plate 80 is further inserted into the radially inward direction of the receiving hole 22 .
  • the end portion 80 b of the lock plate 80 and the taper portion 22 c of the inner peripheral face 22 b 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 R 0 . At this time, the head portion 80 a 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 R 1 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 duty ratio for energizing the switching valve 200 is brought to be large and then the position of the spool 204 is switched.
  • the operation fluid supplied from the oil pump 205 is provided to the retarded angle chamber R 2 by passing through the connecting passage 15 , the retarded angle fluid passage 12 , and the second fluid passage 24 , or by passing through the fluid groove 24 a after supplied to the receiving hole 22 from the lock fluid passage 25 .
  • the operation fluid stored in the advanced angle chamber R 1 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 80 a 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 ).
  • the relative rotation phase may be defined arbitrarily by controlling the duty ratio of the switching valve 200 .
  • the relative rotation between the inner rotor 20 and the outer rotor 30 may be stopped at the intermediate phase.
  • the lock plate 80 is in contact with the inner peripheral face 22 b of the receiving hole 22 on the advanced angle side and the retarded angle side between the opening portion 22 a and the bottom portion 22 d of the receiving hole 22 when the relative rotation between the rotor member 2 and the housing member 3 is restricted.
  • the lock plate 80 and the receiving hole 22 are in contact with each other to thereby restrict the relative rotation between the rotor member 2 and the housing member 3 to the advanced angle side and the retarded angle side.
  • the occurrence of the hitting sound due to the contact between the lock plate 80 and the receiving hole 22 may be prevented accordingly.
  • the lock plate 80 and the receiving hole 22 are in contact with each other since the contact width B in the circumferential direction of the contact portion 80 b of the lock plate 80 , with which the inner peripheral face 22 b of the receiving hole 22 on the advanced angle side and the retarded angle side is in contact, is larger than the bottom width D in the circumferential direction of the bottom portion 22 d of the receiving hole 22 , thereby avoiding the occurrence of the hitting sound.
  • the lock plate 80 and the receiving hole 22 are prevented from being strongly constrained each other under the condition that the fluctuation torque by the camshaft 10 is applied to the contact portion 80 b and the inner peripheral face 22 b in the advanced angle direction and the retarded angle direction alternately since the gap C is formed between the side face 33 a of the convex portion 33 A and the side face 70 a of the vane 70 A.
  • the lock plate 80 is moved from the receiving hole 22 by the operation fluid that is produced when the locked state of the relative rotation is released.
US10/875,736 2003-06-25 2004-06-25 Variable valve timing control device Abandoned US20050022763A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US11/019,399 US7311069B2 (en) 2003-06-25 2004-12-23 Variable valve timing control device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003181475 2003-06-25
JP2003-181475 2003-06-25

Related Child Applications (1)

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US11/019,399 Continuation-In-Part US7311069B2 (en) 2003-06-25 2004-12-23 Variable valve timing control device

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US20050022763A1 true US20050022763A1 (en) 2005-02-03

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US10/875,736 Abandoned US20050022763A1 (en) 2003-06-25 2004-06-25 Variable valve timing control device

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EP (1) EP1491728B1 (fr)
DE (1) DE602004028552D1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9010289B2 (en) 2010-11-08 2015-04-21 Toyota Jidosha Kabushiki Kaisha Control device for hydraulic variable valve timing mechanism
US9206712B2 (en) 2011-04-07 2015-12-08 Toyota Jidosha Kabushiki Kaisha Variable valve timing device
US20170159510A1 (en) * 2014-07-25 2017-06-08 Schaeffler Technologies AG & Co. KG Camshaft adjustement device for an internal combustion engine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6063267B2 (ja) * 2013-01-18 2017-01-18 株式会社ミクニ バルブタイミング変更装置及びその組付け方法

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000230511A (ja) * 1998-12-07 2000-08-22 Mitsubishi Electric Corp ベーン式油圧アクチュエータ
JP3983457B2 (ja) * 2000-06-22 2007-09-26 株式会社日立製作所 内燃機関のバルブタイミング変更装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9010289B2 (en) 2010-11-08 2015-04-21 Toyota Jidosha Kabushiki Kaisha Control device for hydraulic variable valve timing mechanism
US9206712B2 (en) 2011-04-07 2015-12-08 Toyota Jidosha Kabushiki Kaisha Variable valve timing device
US20170159510A1 (en) * 2014-07-25 2017-06-08 Schaeffler Technologies AG & Co. KG Camshaft adjustement device for an internal combustion engine
US10107153B2 (en) * 2014-07-25 2018-10-23 Schaeffler Technologies AG & Co. KG Camshaft adjustment device for an internal combustion engine

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DE602004028552D1 (de) 2010-09-23
EP1491728B1 (fr) 2010-08-11
EP1491728A3 (fr) 2005-11-30
EP1491728A2 (fr) 2004-12-29

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Legal Events

Date Code Title Description
AS Assignment

Owner name: AISIN SEIKI KABUSHIKI KAISHA, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KOBAYASHI, MASAKI;EGUCHI, KATSUHIKO;OGAWA, KAZUMI;REEL/FRAME:015885/0399

Effective date: 20040830

STCB Information on status: application discontinuation

Free format text: EXPRESSLY ABANDONED -- DURING EXAMINATION