US20170138225A1 - Valve opening/closing timing control apparatus - Google Patents

Valve opening/closing timing control apparatus Download PDF

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Publication number
US20170138225A1
US20170138225A1 US15/319,072 US201515319072A US2017138225A1 US 20170138225 A1 US20170138225 A1 US 20170138225A1 US 201515319072 A US201515319072 A US 201515319072A US 2017138225 A1 US2017138225 A1 US 2017138225A1
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US
United States
Prior art keywords
rotary body
spring
side rotary
torsion spring
valve opening
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
US15/319,072
Other languages
English (en)
Inventor
Hiroyuki Hamasaki
Yuji Noguchi
Takeo Asahi
Toru SAKAKIBARA
Tomohiro KAJITA
Hideyuki Suganuma
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: SUGANUMA, HIDEYUKI, ASAHI, TAKEO, HAMASAKI, HIROYUKI, KAJITA, Tomohiro, NOGUCHI, YUJI, SAKAKIBARA, TORU
Publication of US20170138225A1 publication Critical patent/US20170138225A1/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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • 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
    • 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
    • F01L2001/34469—Lock movement parallel to camshaft axis
    • 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
    • F01L2001/34479—Sealing of phaser devices
    • 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
    • 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
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/02—Camshaft drives characterised by their transmission means the camshaft being driven by chains
    • 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
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/04—Camshaft drives characterised by their transmission means the camshaft being driven by belts
    • 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
    • F01L2303/00—Manufacturing of components used in valve arrangements
    • 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
    • F01L2810/00—Arrangements solving specific problems in relation with valve gears
    • F01L2810/03—Reducing vibration
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/031—Electromagnets

Definitions

  • the present invention relates to a valve opening/closing timing control apparatus including a torsion spring for displacing a rotational phase between a driving side rotary body and a driven side rotary body in a predetermined direction by an urging force.
  • PTL 1 discloses a technique having a torsion spring for urging a driven side rotary body (“an inner rotor” in the document) relative to a driving side rotary body (“an outer rotor” in the document) in an advancing direction.
  • a cylindrical portion is formed in a front plate which is fixed to a front face of the driving side rotary body and the torsion spring is accommodated in this cylindrical portion, and also one end of the torsion spring is engaged with the front plate and the other end thereof is engaged with the driven side rotary body. Further, in an inner face of the cylindrical portion, there is formed a spiral groove in form of a slope for contacting a first coiling turn of the torsion spring.
  • PTL 2 discloses a technique including a driving side rotary body (“a housing” in the document) and a driven side rotary body (“a vane member” in the document) and the driven side rotary body includes a support member which supports a torsion spring.
  • the support member includes a restricting portion for restricting collapse of the torsion spring, the restricting portion being disposed on an outer side of a front plate provided on a front face side of the driving side rotary body, the torsion spring is disposed between the restricting portion and the front plate, and one end of this torsion spring is supported to the front plate and the other end thereof is supported to the restricting portion of the support member.
  • the arrangement tends to invite intrusion of friction powder debris generated due to contact with the torsion spring at the time of its operation, into the apparatus.
  • An object of the present invention is to configure a valve opening/closing timing control apparatus that supports a torsion spring to an external position in a stable manner.
  • a valve opening/closing timing control apparatus comprises:
  • a driving side rotary body rotatable in synchronism with a crank shaft of an internal combustion engine and a driven side rotary body rotatable in unison and coaxially with a valve opening/closing cam shaft;
  • a fluid pressure type phase control mechanism for displacing a relative rotational phase between the driving side rotary body and the driven side rotary body in either an advancing direction or a retarding direction;
  • an urging mechanism for applying an urging force between the driving side rotary body and the driven side rotary body for displacing the relative rotational phase in a predetermined direction
  • the urging mechanism includes a spring holder protruding along the rotational axis and connected to the driven side rotary body and a torsion spring for providing an urging force to the spring holder and the driving side rotary body;
  • the torsion spring includes a wound-around coil portion, a first arm extending from one end of the coil portion and engaged with the spring holder and a second arm extending from the other end of the coil portion in a radial direction;
  • the spring holder is connected to the driven side rotary body and the coil portion of the torsion spring is disposed in the spring holder, and the first arm of this torsion spring is held by the spring holder. Further, a part of the torsion spring is fitted in the concave spring holding portion formed in the outer wall of the driving side rotary body and the second arm of the torsion spring is fitted in the groove-like arm holding portion formed in the outer wall of the driving side rotary body. As this holding portion allows fitting-in of the second arm in the radial direction, the holding state of the torsion spring can be confined short in the direction of the rotational axis.
  • valve opening/closing timing control apparatus that supports a torsion spring to an external position in a stable manner.
  • the second arm portion extends in the radial direction, there is no need to form a hole portion in the driving side rotary body for holding the second warm portion, unlike e.g. an arrangement that the second arm portion extends in the direction along the rotational axis.
  • size increase of the driving side rotary body in the rotational axis direction can be suppressed.
  • compactization of the apparatus is realized.
  • the spring holding portion may be formed spirally along a shape of the end portion of the coil portion of the torsion spring.
  • the axis of the coil portion of this torsion spring can be disposed under a posture in agreement with the rotational axis. Further, it becomes also possible to reduce a protrusion amount of the torsion spring in the rotational axis direction. As a result, as the gravity center position of the torsion spring is placed on the rotational axis, vibration at the time of rotation can be suppressed.
  • the spring holding portion can have a shape that holds a portion smaller than or equal to one turn amount of the end of the torsion spring.
  • FIG. 1 is a section view of a valve opening/closing timing control apparatus
  • FIG. 2 is a section view taken along a line II-II in FIG. 1 ,
  • FIG. 3 is a view showing position relation between an urging unit and a front plate
  • FIG. 4 is a section view showing the urging unit and the front plate under disassembled state thereof.
  • FIG. 5 is an exploded perspective view of the valve opening/closing timing control apparatus.
  • a valve opening/closing timing control apparatus A includes an outer rotor 20 as a “driving side rotary body”, an inner rotor 30 as a “driven side rotary body”, an urging unit 40 as an “urging mechanism” for urging a relative rotational phase between the outer rotor 20 and the inner rotor 30 in an advancing direction, and an electromagnetic control valve 50 .
  • the outer rotor 20 is operably coupled to a crank shaft 1 of an engine E as an internal combustion engine via a timing belt 7 to be rotatable therewith in synchronism and disposed coaxially with a rotational axis X of an intake cam shaft 5 .
  • the inner rotor 30 is disposed coaxially with the rotational axis X, thus being encased within the outer rotor 20 and connected to the intake cam shaft 5 to be rotatable therewith.
  • This valve opening/closing timing control apparatus A includes the electromagnetic control valve 50 coaxially with the rotational axis X of the inner rotor 30 .
  • the valve opening/closing timing control apparatus A changes a relative rotational phase between the outer rotor 20 and the inner rotor 30 by controlling work oil by the electromagnetic control valve 50 , thereby to control opening/closing timing of an intake valve 5 V.
  • the outer rotor 20 and the inner rotor 30 together function as a “phase control mechanism”.
  • the engine E is to be included in a vehicle such as a passenger car.
  • This engine E includes the crank shaft 1 at a lower portion thereof, and a piston 3 is accommodated in a cylinder bore formed in a cylinder block 2 provided at an upper portion of the engine E.
  • the engine E is configured as a 4 cycle engine with the piston 3 and the crank shaft 1 being connected via a connecting rod 4 .
  • a transmission mechanism for transmitting rotational force of the crank shaft 1 to the valve opening/closing timing control apparatus A may employ a timing chain or may be configured such that the driving force of the crank shaft 1 is transmitted via a gear train having many gears.
  • the intake cam shaft 5 as being rotated, opens/closes the intake valve 5 V.
  • the hydraulic pump P functions to feed lubricant oil reserved in an oil pan of the engine E as the work oil via a feed passage 8 to the electromagnetic control valve 50 .
  • timing belt 7 is routed around an output pulley 6 formed on the crank shaft 1 of the engine E and a timing pulley 23 P, the outer rotor 20 is rotated in synchronism with the crank shaft 1 .
  • a timing pulley is provided also at a front end of the exhaust side cam shaft and the timing belt 7 is routed around this timing pulley also.
  • valve opening/closing timing control apparatus A is provided in the intake cam shaft 5 .
  • valve opening/closing timing control apparatus A may be provided in the exhaust cam shaft or may be provided in both the intake cam shaft 5 and the exhaust cam shaft.
  • the valve opening/closing timing control apparatus A is configured such that the outer rotor 20 is rotated in a driving rotational direction S by the driving force from the crank shaft 1 .
  • the direction of relative rotation of the inner rotor 30 relative to the outer rotor 20 in the same direction as the driving rotational direction S will be referred to as an “advancing direction Sa” and its opposite direction will be referred to as a “retarding direction Sb”, respectively.
  • the valve opening/closing timing control apparatus A includes the outer rotor 20 and the inner rotor 30 and includes also a bush-like adapter 37 at a position sandwiched between the inner rotor 30 and the intake cam shaft 5 .
  • the outer rotor 20 includes an outer rotor main body 21 , a front plate 22 and a rear plate 23 , with these members being integrated to each other by fastening of a plurality of fastener bolts 24 .
  • the timing pulley 23 P is formed in the outer circumference of the rear plate 23 .
  • the outer rotor main body 21 integrally forms a plurality of section portions 21 T that protrude inwards in a radial direction relative to the rotational axis X.
  • the inner rotor 30 includes a cylindrical inner rotor main body 31 that contacts gaplessly protruding ends of the section portions 21 T of the outer rotor main body 21 , and a plurality of (four) vane portions 32 that protrude from the outer circumference of the inner rotor main body 31 between the adjacent section portions 21 T so as to contact the inner circumferential face of the outer rotor main body 21 .
  • a plurality of fluid pressure chambers C are formed on the outer circumferential side of the inner rotor main body 31 . And, as these fluid pressure chambers C are partitioned from each other by the vane portions 32 , advancing chambers Ca and retarding chambers Cb are formed.
  • a connecting bolt 38 forms a bolt head portion 38 H and a male thread portion 38 S.
  • the male thread portion 38 S is threaded to a female thread portion of the intake cam shaft 5
  • the inner rotor 30 is connected to the intake cam shaft 5 .
  • the adapter 37 , the inner rotor 30 and a seat portion 42 of a spring holder 41 will be clamped, thus being integrated to each other.
  • the connecting bolt 38 is formed cylindrical centering about the rotational axis X and in an inner hollow portion thereof, there are accommodated a spool 51 of the electromagnetic control valve 50 and a spool spring (not shown) for urging this in a protruding direction.
  • a spool 51 of the electromagnetic control valve 50 and a spool spring (not shown) for urging this in a protruding direction.
  • the arrangement of this electromagnetic control valve 50 will be described later.
  • This valve opening/closing timing control apparatus A includes, as a phase control mechanism, a lock mechanism L for locking (fixing) the relative rotational phase between the outer rotor 20 and the inner rotor 30 to a most retarded phase.
  • This lock mechanism L includes a locking member 25 that is guided into/out of a guide hole 26 formed in one vane portion 32 under a posture along the rotational axis X, a locking spring that urges the locking member 25 for its protrusion, and a locking recess formed in the rear plate 23 .
  • an urging direction of the urging unit 40 is set to be displaced in the advancing direction Sa relative to the inner rotor 30 .
  • the arrangement of this urging unit 40 will be described later herein.
  • the space for displacing the relative rotational phase in the advancing direction Sa by feeding of work oil is the advancing chamber Ca.
  • the space for displacing the relative rotational phase in the retarding direction Sb by feeding of work oil is the retarding chamber Cb.
  • a relative rotational phase when the vane portion 32 reaches the operational end in the advancing direction Sa (including a phase adjacent the operational end of the vane portion 32 in the advancing direction Sa) will be referred to as the “most advanced phase”.
  • a relative rotational phase when the vane portion 32 reaches the operational end in the retarding direction Sb (including a phase adjacent the operational end of the vane portion 32 in the regarding direction Sb) will be referred to as the “most retarded phase”.
  • the inner rotor main body 31 defines retarding flow passages 33 communicated to the retarding chambers Cb and advancing flow passages 34 communicated to the advancing chambers Ca, and the advancing chambers 34 are communicated to the locking recess.
  • the electromagnetic control valve 50 includes the spool 51 , the spool spring and an electromagnetic solenoid 54 . More particularly, the spool 51 is disposed to be slidable in the direction along the rotational axis X in the inner space of the connecting bolt 38 .
  • the connecting bolt 38 includes a stopper 53 in the form of a stopper ring for fixing an outer end side operational position of the spool 51 .
  • the spool spring applies an urging force that moves this spool 51 in the direction away from the intake cam shaft 5 (protrusion direction).
  • the electromagnetic solenoid 54 includes a plunger 54 a which operates to protrude by an amount in direct proportion with an amount of electric power fed to the solenoid therein. By a pressing force of this plunger 54 a , the spool 51 is operated. Further, the spool 51 is rotated in unison with the inner rotor 30 and the electromagnetic solenoid 54 is supported to the engine E, thus becoming inoperable.
  • the electromagnetic solenoid 54 is disposed at a position that places its plunger 54 a contactable with an outer end of the spool 51 , and is maintained at a non-pressing position under no power supplied state, whereby the spool 51 is maintained at a retarding position. Further, when a predetermined electric power is supplied to the electromagnetic solenoid 54 , the plunger 54 a reaches a pressing position on the inner end side, whereby the spool 51 is maintained at an advancing position.
  • the urging unit 40 as shown in FIG. 1 and FIGS. 3-5 , consists essentially of the spring holder 41 and a torsion spring 46 supported to the spring holder 41 .
  • the seat portion 42 connected to the inner rotor main body 31 and a plurality (three in this embodiment) of protruding portions 43 formed to protrude from the seat portion 42 along the rotational axis X integrally with each other.
  • the spring holder 41 may omit the seat portion 42 .
  • a member connected to the inner rotor main body 31 and protruding along the rotational axis X can be used as the protruding portion 43 .
  • an insertion hole 42 A into which the fastener bolt 24 is to be inserted.
  • an alignment portion 44 protruding outward is formed.
  • a rotation restricting portion 44 A that protrudes outward from the outer end.
  • the spring holder 41 is to be manufactured by press work of a metal plate, and the seat portion 42 , the plurality of alignment portions 44 , and the rotation restricting portion 44 A will be disposed on a same virtual plane that assumes a posture perpendicular to the rotational axis X. Further, the plurality of protruding portions 43 respectively are formed with a set width and are formed in an arcuate shape so that outer circumferential faces thereof will be arranged on a circumference centering about the rotational axis X.
  • a border portion between the base end portion of the protruding portion 43 and the base end portion of the alignment portion 44 is cut away in the direction of the seat portion 42 , thus forming a cutout portion 42 B.
  • first engaging portion 43 A (an example of “engaging supporting portion”) provided in the form of a circumferentially cut-in recess.
  • engaging supporting portion As the plurality of alignment portions 44 are fitted within an engaging recess 31 A of the inner rotor main body 31 , outer end edges 44 E of the respective alignment portions 44 come into contact with a round inner circumferential face 31 AE of the engaging recess 31 A, thus effecting position fixing.
  • a virtual outer circumference circle interconnecting the respective outer end edges 44 E is formed arcuate along the circumference of the circle centering about the rotational axis X.
  • a diameter of the virtual outer circumference circle is an outer end diameter D 3 .
  • the above-described state of the alignment portions 44 being fitted in the engaging recess 31 A is an engaged state of such a degree that allows relative rotation therebetween.
  • the rotation restricting portion 44 A is fitted into a restricting recess 31 B, the respective rotation is restricted.
  • the torsion spring 46 is disposed in a region surrounding the spring holder 41 and includes a wound-around coil portion 46 A, a first arm 46 B (one end) extending radially inward from an outer end position of the coil portion 46 A in the direction along the rotational axis X and a second arm 46 C (the other end) extending radially outward from an inner end position.
  • the coil portion 46 A may be disposed inside a space sectioned by the protruding portions 43 .
  • a through hole 22 A having an inner diameter slightly greater than an outer circumference diameter D 2 of the plurality of protruding portions 43 and a hole diameter D 1 (inner diameter) centered around the rotational axis X.
  • a virtual outer circumferential edge interconnecting outer circumferences of the plurality of protruding portions 43 as viewed in the direction along the rotational axis X constitutes the outer circumference diameter D 2 .
  • an inner diameter of the coil portion 46 A of the torsion spring 46 is set to a value sufficiently greater than the outer circumference diameter D 2 .
  • the outer end diameter D 3 of the virtual outer circumferential edge interconnecting the outer ends of the plurality of alignment portions 44 as viewed in the direction along the rotational axis X is set greater than the hole diameter D 1 .
  • an inner circumference diameter D 4 of the engaging recess 31 A of the inner rotor main body 31 is set to a value slightly greater than the outer end diameter D 3 .
  • This arrangement allows insertion of the protruding portions 43 having the outer circumference diameter D 2 into the through hole 22 A having the hole diameter D 1 .
  • the alignment portions 44 having the outer end diameter D 3 greater than the hole diameter D 1 of the through hole 22 A are non-withdrawably held to the front plate 22 .
  • the arrangement allows fitting of the alignment portions 44 having this outer end diameter D 3 into the engaging recess 31 A having the inner circumference diameter D 4 .
  • a spring holding portion 22 B in the form of a recess into which a part of the inner end position of the coil portion 46 A of the torsion spring 46 is fitted.
  • a second engaging portion 22 C in the form of a groove extending outward continuously from this spring holding portion 22 B.
  • the spring holding portion 22 B is formed spiral along the end shape of the coil portion 46 A of the torsion spring 46 .
  • the spring holding portion 22 B is formed as a tilted face which is tilted relative to the virtual plane perpendicular to the rotational axis X.
  • the depth of the spring holding portion 22 B (the value in the direction along the rotational axis X) is not a constant value, but the depth of this spring holding portion 22 B is set as a depth that allows accommodation of one turn of the torsion spring 46 .
  • torsion spring 46 it is also possible to employ a wire member having a round cross section.
  • the engaging recess 31 A is formed by causing the area centered around the rotational axis X to be receded relative to the front plate side outer end face of the inner rotor main body 31 .
  • This engaging recess 31 A is formed like a circle having the inner circumferential face 31 AE centered around the rotational axis X.
  • the inner circumference diameter D 4 of this engaging recess 31 A, as described hereinbefore, is set to a value slightly greater than the outer end diameter D 3 of the virtual outer circumferential edge interconnecting the outer ends of the plurality of alignment portions 44 , and at its outer circumferential portion, the restricting recess 31 B is formed as a recess (see FIG. 5 ).
  • the restricting recess 31 B may be formed at a plurality of portions of the engaging recess 31 A. Further, in order to restrict relative rotation between the spring holder 41 and the inner rotor 30 , a recess may be formed in the outer circumference of the alignment portion 44 and a protrusion engageable therewith may be formed in the inner circumference of the engaging recess 31 A. Since the restricting recess 31 B is formed in the radial direction as described above, there occurs no increase in the thickness of the inner rotor 30 , in comparison with e.g. an arrangement in the form of a hole along the rotational axis X.
  • the rear plate 23 is disposed at the rear portion of the outer rotor main body 21 and the inner rotor main body 31 is fitted in its inside and the spool 51 etc. are accommodated inside the connecting bolt 38 .
  • the protruding portions 43 of the spring holder 41 are inserted into the through hole 22 A of the front plate 22 from the rear face side thereof and the torsion spring 46 is disposed from the front face side to surround the plurality of protruding portions 43 .
  • the torsion spring 46 When the torsion spring 46 is to be disposed in the manner described above, a portion of the coil portion 46 A is fitted into the spring holding portion 22 B of the front plate 22 and the second arm 46 C of the torsion spring 46 is fitted into the second engaging portion 22 C. Further, the first arm 46 B of the torsion spring 46 is engaged to the first engaging portion 43 A of the protruding portion 43 to be held therein.
  • the alignment portions 44 of the spring holder 41 are fitted into the engaging recess 31 A of the inner rotor main body 31 and the rotation restricting portion 44 A is fitted into the restricting recess 31 B.
  • position-fixing of the spring holder 41 is effected in such a manner as to hold the gravity center position of the spring holder 41 at the position of the rotational axis X.
  • the front plate 22 is placed over the outer rotor main body 21 and these are connected to each other by the fastener bolts 24 . Further, the connecting bolt 38 is inserted into the through hole 42 A of the seat portion 42 of the spring holder 41 and the male thread portion 38 S of this connecting bolt 38 is threaded to the female thread portion of the intake cam shaft 5 , thus completing the fastening.
  • the torsion spring 46 of the urging unit 40 provides an urging force to displace the inner rotor 30 in the advancing direction Sa relative to the outer rotor 20 . Also, as a portion of the coil portion 46 A of the torsion spring 46 which portion is adjacent the front plate 22 is fitted into the spring holding portion 22 B under the tilted posture, the torsion spring 46 can be supported with the axis of the coil portion 46 A of this torsion spring 46 being in agreement with the rotational axis X.
  • the gravity center position of this urging unit 40 be in agreement with the rotational axis X during rotation.
  • the spring holder 41 is attached to the inner rotor main body 31 as provided in the present invention, by fitting the alignment portions 44 into the engaging recess 31 A of the inner rotor main body 31 for position fixing, the gravity center position of the spring holder 41 can be positioned coaxial with the rotational axis X.
  • the spring holder 41 and the inner rotor 30 can be made rotatable in union with each other.
  • the inner end side of the coil portion 46 A of the torsion spring 46 in the direction of the rotational axis X is supported as being fitted into the tilted spring holding portion 28 of the front plate 22 .
  • the axial position of the coil portion 46 A of the torsion spring 46 is in agreement with the rotational axis X and no vibration occurs in the torsion spring 46 during rotation.
  • the portion of the coil portion 46 A of the coil spring 46 comes into contact with the titled face of the spring holding portion 22 B over a large area, reduction of frictional wear due to locally concentrated contact is realized also.
  • the front plate 22 presses down the spring holder 41 , thus preventing float-up of the spring holder 41 .
  • valve opening/closing timing control apparatus A having the above-described configuration, leak of work oil occurs between the outer rotor 20 and the inner rotor 30 . And, by causing such leaked work oil to be discharged to the outside via the through hole 22 A of the front plate 22 , the work oil is fed between the torsion spring 46 and the spring holding portion 22 B, whereby frictional wear of the spring holding portion 22 B can be suppressed.
  • the present invention can be utilized in a valve opening/closing timing control apparatus having a mechanism for urging a relative rotational phase between a driving side rotary body and a driven side rotary body in a predetermined direction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
US15/319,072 2014-10-31 2015-10-28 Valve opening/closing timing control apparatus Abandoned US20170138225A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2014223317A JP6237574B2 (ja) 2014-10-31 2014-10-31 弁開閉時期制御装置
JP2014-223317 2014-10-31
PCT/JP2015/080362 WO2016068180A1 (fr) 2014-10-31 2015-10-28 Dispositif de commande de période d'ouverture/fermeture de soupape

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US20170138225A1 true US20170138225A1 (en) 2017-05-18

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US15/319,072 Abandoned US20170138225A1 (en) 2014-10-31 2015-10-28 Valve opening/closing timing control apparatus

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US (1) US20170138225A1 (fr)
JP (1) JP6237574B2 (fr)
WO (1) WO2016068180A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170260884A1 (en) * 2016-03-14 2017-09-14 ECO Holidng 1 GmbH Cam phaser
US11078813B2 (en) * 2017-05-12 2021-08-03 Denso Corporation Valve timing adjustment device
US11365654B2 (en) 2019-02-21 2022-06-21 Denso Corporation Valve timing adjusting device

Citations (1)

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Publication number Priority date Publication date Assignee Title
US6276321B1 (en) * 2000-01-11 2001-08-21 Delphi Technologies, Inc. Cam phaser having a torsional bias spring to offset retarding force of camshaft friction

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Publication number Priority date Publication date Assignee Title
JP2003247404A (ja) * 2002-02-21 2003-09-05 Aisin Seiki Co Ltd 弁開閉時期制御装置
JP4110479B2 (ja) * 2004-09-28 2008-07-02 アイシン精機株式会社 弁開閉時期制御装置
JP2009222037A (ja) * 2008-03-19 2009-10-01 Denso Corp バルブタイミング調整装置
US8127728B2 (en) * 2008-03-21 2012-03-06 Delphi Technologies, Inc. Vane-type cam phaser having dual rotor bias springs

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6276321B1 (en) * 2000-01-11 2001-08-21 Delphi Technologies, Inc. Cam phaser having a torsional bias spring to offset retarding force of camshaft friction

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170260884A1 (en) * 2016-03-14 2017-09-14 ECO Holidng 1 GmbH Cam phaser
US10240493B2 (en) * 2016-03-14 2019-03-26 ECO Holding 1 GmbH Cam phaser
US10605128B2 (en) * 2016-03-14 2020-03-31 ECO Holdings 1 GmbH Cam phaser
US11078813B2 (en) * 2017-05-12 2021-08-03 Denso Corporation Valve timing adjustment device
US11365654B2 (en) 2019-02-21 2022-06-21 Denso Corporation Valve timing adjusting device

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JP2016089681A (ja) 2016-05-23
WO2016068180A1 (fr) 2016-05-06
JP6237574B2 (ja) 2017-11-29

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