WO2016068179A1 - 弁開閉時期制御装置 - Google Patents

弁開閉時期制御装置 Download PDF

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Publication number
WO2016068179A1
WO2016068179A1 PCT/JP2015/080361 JP2015080361W WO2016068179A1 WO 2016068179 A1 WO2016068179 A1 WO 2016068179A1 JP 2015080361 W JP2015080361 W JP 2015080361W WO 2016068179 A1 WO2016068179 A1 WO 2016068179A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotating body
valve opening
torsion spring
control device
timing control
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.)
Ceased
Application number
PCT/JP2015/080361
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
野口祐司
朝日丈雄
濱崎弘之
榊原徹
梶田知宏
菅沼秀行
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
Priority to CN201580032955.8A priority Critical patent/CN106471225B/zh
Priority to US15/319,082 priority patent/US10280814B2/en
Publication of WO2016068179A1 publication Critical patent/WO2016068179A1/ja
Anticipated expiration legal-status Critical
Ceased 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0476—Camshaft bearings
    • 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
    • F01L2001/34433—Location 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

  • Patent Document 1 urges a driven-side rotator (vane rotor in the literature) in an advance direction with respect to a drive-side rotator (housing in the literature).
  • a technique with a torsion spring (coil spring in the literature) is shown.
  • the torsion spring is arranged outside the valve opening / closing timing control device, even if friction powder is generated due to contact with the torsion spring, it does not enter the device.
  • the valve opening / closing timing control device can be downsized in the direction of the rotational axis.
  • the spring holder is supported with its seat portion in contact with the driven-side rotator, the posture of the spring holder is stabilized. Therefore, the structure which supports easily the torsion spring which makes a biasing force act in the valve timing control apparatus with a spring holder was obtained.
  • the seat portion, the plurality of guide portions, and the plurality of alignment portions are integrally formed by processing a plate-shaped material, and the outer periphery of the seat portion is circumferentially formed.
  • the guide portions and the aligning portions may be alternately arranged along, and a notch portion in which a part of the seat portion is notched in the direction of the rotation axis may be formed at an intermediate position between them.
  • one end of the torsion spring can be supported with a simple configuration by notching a part of the guide portion and forming the support portion in a concave shape that becomes a cut open space.
  • a plurality of the guide portions are integrally formed with the seat portion so as to extend along the rotation axis, and the torsion is provided on an end surface of the plurality of the guide portions where the support portion is formed.
  • An inclined portion that guides the end portion of the spring to the support portion may be formed.
  • the torsion spring when the torsion spring is supported by the guide portion and one end portion of the torsion spring is engaged with the support portion of the guide portion, the one end portion of the torsion spring is placed on the inclined surface of the spring support portion. By making contact, the end portion moves along the inclined surface and can be engaged with the support portion. Thereby, the mounting process of the torsion spring is simplified.
  • the driving-side rotator includes a lid body having a through hole formed in the center, and an outer diameter connecting the outer circumferences of the plurality of guide portions with the rotation axis as a center is an inner diameter of the through hole.
  • a smaller outer end diameter connecting the outer end of the alignment portion around the rotation axis may be set larger than the inner diameter of the through hole.
  • the seat portion of the spring holder is fitted into the fitting portion of the driven side rotating body, the positioning is performed by the alignment portion, and the rotation is regulated by the regulated portion.
  • the lid body is connected to the drive side rotating body in a state where the guide portion is inserted into the through hole of the lid body, the alignment portion is pressed by the lid body, and the spring holder can be prevented from being lifted. .
  • a device having a torsion spring outside the device requires a configuration such as a holder for supporting the torsion spring.
  • a holder for supporting the torsion spring.
  • the valve opening / closing timing control device A is configured to include an urging unit 40 as an urging mechanism and an electromagnetic control valve 50.
  • the external rotor 20 (an example of a drive side rotator) is linked via a timing belt 7 so as to rotate synchronously with the crankshaft 1 of the engine E as an internal combustion engine, and is connected to the rotation axis X of the intake camshaft 5. It is arranged on the coaxial core.
  • the internal rotor 30 (an example of a driven-side rotator) is disposed on the same axis as the rotational axis X so that it is included in the external rotor 20 and connected to the intake camshaft 5 so as to rotate integrally. .
  • the valve opening / closing timing control device A includes an electromagnetic control valve 50 coaxially with the rotation axis X of the internal rotor 30.
  • the valve opening / closing timing control device A changes the relative rotation phase between the external rotor 20 and the internal rotor 30 by controlling the hydraulic oil (an example of fluid) by the electromagnetic control valve 50, thereby controlling the opening / closing timing of the intake valve 5V.
  • the external rotor 20 and the internal rotor 30 function as a phase control mechanism.
  • Engine E (an example of an internal combustion engine) is provided in a vehicle such as a passenger car.
  • This engine E includes a crankshaft 1 at the lower part, a piston 3 is accommodated in a cylinder bore formed in an upper cylinder block 2, and the piston 3 and the crankshaft 1 are connected by a connecting rod 4. It is configured.
  • a timing chain may be used, or a configuration for transmitting the driving force of the crankshaft 1 by a gear train having a large number of gears may be used.
  • an upper portion of the engine E includes an intake camshaft 5 and an exhaust camshaft, and a hydraulic pump P that is driven by the driving force of the crankshaft 1.
  • the intake camshaft 5 opens and closes the intake valve 5V by rotation.
  • the hydraulic pump P supplies the lubricating oil stored in the oil pan of the engine E to the electromagnetic control valve 50 as hydraulic oil (an example of fluid) via the supply flow path 8.
  • the external rotor 20 rotates synchronously with the crankshaft 1 by winding the timing belt 7 around the output pulley 6 formed on the crankshaft 1 of the engine E and the timing pulley 23P.
  • a timing pulley is also provided at the front end of the camshaft on the exhaust side, and a timing belt 7 is wound around this.
  • the external rotor 20 rotates in the driving rotation direction S by the driving force from the crankshaft 1.
  • the direction in which the inner rotor 30 rotates relative to the outer rotor 20 in the same direction as the driving rotation direction S is referred to as an advance angle direction Sa, and the opposite direction is referred to as a retard angle direction Sb.
  • External rotor main body 21 is arranged at a position sandwiched between front plate 22 (an example of a lid) and rear plate 23.
  • the outer rotor main body 21 is integrally formed with a plurality of partition portions 21T that protrude inward in the radial direction with respect to the rotation axis X.
  • the inner rotor 30 protrudes on the outer periphery of the inner rotor body 31 so as to come into contact with the cylindrical inner rotor body 31 that is in close contact with the protruding end of the partition portion 21T of the outer rotor body 21 and the inner peripheral surface of the outer rotor body 21.
  • a plurality of (four) vane portions 32 provided.
  • the number of vane portions 32 is not limited to four and can be set to an arbitrary number.
  • a plurality of fluid pressure chambers C are formed on the outer peripheral side of the inner rotor body 31 at an intermediate position between the partition portions 21T adjacent in the rotation direction. These fluid pressure chambers C are partitioned by the vane portion 32 to form the advance chamber Ca and the retard chamber Cb.
  • the connecting bolt 38 is formed with a bolt head portion 38H and a male screw portion 38S.
  • the male screw portion 38S is screwed into the female screw portion of the intake camshaft 5, whereby the internal rotor 30 is connected to the intake camshaft 5.
  • the adapter 37, the internal rotor 30, and the seat portion 42 of the spring holder 41 are integrated with each other between the bolt head 38 ⁇ / b> H and the intake camshaft 5.
  • the connecting bolt 38 is formed in a cylindrical shape with the rotation axis X as the center, and a spool 51 of the electromagnetic control valve 50 and a spool spring that urges the solenoid control valve 50 in the protruding direction are accommodated in this internal space.
  • the configuration of the electromagnetic control valve 50 will be described later.
  • This valve opening / closing timing control device A includes a lock mechanism L that locks (fixes) the relative rotational phase between the external rotor 20 and the internal rotor 30 as a phase control mechanism at the most retarded phase.
  • the lock mechanism L includes a lock member 25 that is guided in a guide hole 26 formed in a posture along the rotation axis X with respect to one vane portion 32, and a lock that projects and biases the lock member 25.
  • a spring and a lock recess formed in the rear plate 23 are provided.
  • the locking mechanism L is not limited to the one that locks at the most retarded angle phase, and for example, a mechanism that locks at an arbitrary position between the most retarded angle phase and the most advanced angle phase may be provided.
  • the urging direction of the urging unit 40 is set so as to be displaced in the advance direction Sa with respect to the internal rotor 30 so as to suppress the action of the varying torque.
  • the configuration of the urging unit 40 will be described later.
  • the internal rotor body 31 is formed with a retarding passage 33 that communicates with the retarding chamber Cb and an advance passage 34 that communicates with the advance chamber Ca.
  • the advance channel 34 communicates with the lock recess.
  • the electromagnetic solenoid 54 includes a plunger 54a that protrudes and operates in an amount proportional to the electric power supplied to the internal solenoid, and operates the spool 51 by the pressing force of the plunger 54a. Further, the spool 51 rotates integrally with the internal rotor 30, and the electromagnetic solenoid 54 becomes non-rotatable by being supported by the engine E.
  • a flow passage for controlling the fluid from the hydraulic pump P and supplying it to either the retard flow passage 33 or the advance flow passage 34 is formed inside the connecting bolt 38 by the position of the spool 51.
  • the hydraulic pump P is correspondingly operated. A state in which the hydraulic oil is supplied to the retard chamber Cb, a state in which the hydraulic oil is not supplied and discharged, and a state in which the hydraulic oil is supplied to the advance chamber Ca are created in this order.
  • the spring holder 41 includes a seat portion 42 connected to the inner rotor main body 31 and projecting portions as a plurality of (three in the embodiment) guide portions formed in a posture projecting from the seat portion 42 along the rotation axis X. 43 is formed integrally.
  • An insertion hole 42A through which the fastening bolt 24 is inserted is formed at the center position of the seat portion 42.
  • a centering portion 44 having a posture protruding outward is formed in the middle of the projecting portion 43 (an example of a guide portion) in the circumferential direction in the outer periphery of the seat portion 42, and a plurality of (three in the embodiment) alignment centers are formed.
  • One of the portions 44 is further formed with a rotation restricting portion 44A as a restricted portion protruding outward from the outer end.
  • the spring holder 41 is manufactured by pressing a metal plate, and the seat portion 42, the plurality of alignment portions 44, and the rotation restriction portion 44 ⁇ / b> A (an example of the restricted portion) are attached to the rotation axis X. It arrange
  • a portion 42B is formed.
  • the spring holder 41 may be configured by resin molding.
  • a first engaging portion 43A (engaging as a concave supporting portion in which a space for supporting the first arm 46B of the torsion spring 46 is cut out in the circumferential direction is cut open.
  • An example of a part is formed.
  • the outer end edge 44E of each alignment portion 44 is fitted into the fitting recess 31A (fitting portion). In this example, positioning is performed in contact with the circular inner peripheral surface 31AE.
  • a virtual outer circumference circle connecting each outer end edge 44E is formed in an arc shape along the circumference of a circle centering on the rotation axis X.
  • the diameter of the virtual outer circumference circle is the outer end diameter D3.
  • the torsion spring 46 includes a coil portion 46A disposed in a region surrounding the outer peripheral portion of the spring holder 41, and a first arm 46B extending outward from the outer end position in the direction along the rotational axis X at the coil portion 46A. One end) and a second arm 46C (the other end) extending radially outward from the outer end position.
  • the outer end diameter D3 of the virtual outer periphery connecting the outer ends of the plurality of alignment portions 44 in the direction along the rotation axis X is set to be larger than the hole diameter D1.
  • the inner peripheral diameter D4 of the fitting recess 31A of the inner rotor body 31 is set to a value slightly larger than the outer end diameter D3.
  • the protrusion part 43 with the outer peripheral diameter D2 can be inserted into the through hole 22A with the hole diameter D1.
  • the alignment portion 44 having an outer end diameter D3 larger than the hole diameter D1 of the through hole 22A is held in a state of being prevented from coming off from the front plate 22.
  • the alignment portion 44 having the outer end diameter D3 can be fitted into the fitting recess 31A having the inner peripheral diameter D4.
  • the spring holding portion 22 ⁇ / b> B is formed in a spiral shape along the end shape of the coil portion 46 ⁇ / b> A of the torsion spring 46. That is, the spring holding portion 22B is formed on an inclined surface that is inclined with respect to a virtual plane orthogonal to the rotation axis X. Since the spring holding portion 22B is formed in an inclined posture in this way, the depth of the spring holding portion 22B (value in the direction along the rotation axis X) is not a constant value, but the spring holding portion 22B The depth is set so as to accommodate one turn of the torsion spring 46.
  • the torsion spring 46 it is possible to use a wire having a circular cross section.
  • a fitting recess 31A is formed in such a manner that a region centered on the rotation axis X is recessed with respect to the outer end surface on the front plate side of the inner rotor body 31.
  • the fitting recess 31 ⁇ / b> A is formed in a circular shape having an inner peripheral surface 31 ⁇ / b> AE with the rotation axis X as the center.
  • the inner peripheral diameter D4 of the fitting concave portion 31A is set to a value slightly larger than the outer end diameter D3 of the virtual outer peripheral edge connecting the outer ends of the plurality of alignment portions 44, and a part of the outer periphery thereof is set.
  • a restricting recess 31B is formed as a restricting portion that is concave.
  • the seat 42 and the alignment portion 44 of the spring holder 41 are fitted into the fitting recess 31A, and the rotation restricting portion 44A is fitted into the restricting recess 31B (an example of a restricting portion).
  • the depth of the fitting recess 31 ⁇ / b> A and the regulation recess 31 ⁇ / b> B is set to a value that matches the thickness of the alignment portion 44 of the spring holder 41.
  • the regulation recessed part 31B may be formed in several places of the fitting recessed part 31A. Further, in order to restrict the relative rotation between the spring holder 41 and the inner rotor 30, a concave portion on the outer periphery of the alignment portion 44 is formed, and a convex portion to be fitted to this is formed on the inner periphery of the fitting concave portion 31A. Also good. Since the restricting recess 31B is formed in the radial direction as described above, the thickness of the internal rotor 30 is not increased as compared with, for example, a hole formed along the rotation axis X.
  • the rear plate 23 is disposed on the back of the outer rotor main body 21, the inner rotor main body 31 is fitted therein, and the spool 51 and the like are accommodated inside the connecting bolt 38.
  • the protrusions 43 of the spring holder 41 are inserted into the through holes 22A of the front plate 22 from the back side, and the torsion springs 46 are disposed so as to surround the plurality of protrusions 43.
  • the torsion spring 46 When arranging the torsion spring 46 in this way, a part of the coil part 46A is fitted into the spring holding part 22B of the front plate 22, and the second arm 46C of the torsion spring 46 is fitted into the second engagement part 22C. Further, the first arm 46 ⁇ / b> B of the torsion spring 46 is engaged with and held by the first engagement portion 43 ⁇ / b> A (an example of a support portion) of the protrusion 43.
  • the alignment portion 44 of the spring holder 41 is fitted into the fitting recess 31A of the inner rotor body 31, and the rotation restricting portion 44A is fitted into the restricting recess 31B.
  • the outer end edges 44E of the plurality of alignment portions 44 come into contact with the circumferential inner peripheral surface 31AE of the fitting recess 31A, and the center of gravity of the spring holder 41 is held at the position of the rotation axis X.
  • Positioning is performed. Thereby, the internal rotor main body 31 and the spring holder 41 reach a state in which they can rotate integrally.
  • the front plate 22 is superposed on the external rotor body 21 and connected by fastening bolts 24. Further, the connecting bolt 38 is inserted into the insertion hole 42 ⁇ / b> A of the seat 42 of the spring holder 41, and the male screw portion 38 ⁇ / b> S of the connecting bolt 38 is screwed into the female screw portion of the intake camshaft 5 for fastening.
  • the torsion spring 46 of the urging unit 40 applies an urging force that displaces the inner rotor 30 in the advance direction Sa to the outer rotor 20.
  • a portion of the coil portion 46A of the torsion spring 46 that is adjacent to the front plate 22 is fitted into the spring holding portion 22B in an inclined posture, so that the axis of the coil portion 46A of the torsion spring 46 is turned into the rotation axis X.
  • the torsion spring 46 can be supported in a state in which the torsion spring 46 is matched.
  • the inner periphery of the coil portion 46A of the torsion spring 46 is disposed at a position separated from the outer periphery of the protrusion 43, there is no resistance between them when the relative rotational phase changes, and the protrusion 43 It does not wear the outer periphery of the.
  • the urging unit 40 is provided outside the main body portion (phase control mechanism) constituted by the outer rotor 20 and the inner rotor 30, the main body portion can be downsized.
  • the spring holder 41 When the spring holder 41 is attached to the inner rotor body 31 as in the present embodiment, the spring holder 41 is positioned by fitting the alignment portion 44 into the fitting recess 31A of the inner rotor body 31. Can be arranged on the rotation axis X and the coaxial axis. Further, the spring holder 41 can be rotated integrally with the internal rotor 30 only by fitting the rotation restricting portion 44 ⁇ / b> A of the spring holder 41.
  • the internal rotor 30 is not deformed, and the sliding resistance is not increased due to the deformation at the time of press-fitting.
  • the torsion spring 46 is directly engaged with the outer rotor 20 or the inner rotor 30, it is necessary to increase the strength of the engaging portion.
  • the spring holder 41 it is not necessary to increase the strength of either of the rotors, and there is no wear at the portion where the spring is engaged.
  • the inner end side of the coil portion 46A of the torsion spring 46 in the direction of the rotational axis X is supported in a form that is fitted into the spring holding portion 22B of the inclined posture of the front plate 22.
  • the axial center position of the coil part 46A of the torsion spring 46 is made to coincide with the rotational axis X, and the torsion spring 46 is not vibrated during rotation.
  • a part of the coil portion 46A of the torsion spring 46 comes into contact with the inclined surface of the spring holding portion 22B on a wide surface, it is possible to reduce wear caused by local contact.
  • the spring holder 41 Since the hole diameter D1 of the through hole 22A of the front plate 22 is smaller than the outer end diameter D3 of the plurality of alignment portions 44, the spring holder 41 is pressed by the front plate 22 to prevent the spring holder from being lifted.
  • the drop-off preventing portion 43R may be formed at the protruding end of the cylindrically formed protruding portion 43 (the protruding portion 43 is a single unit). Further, a torsion spring 46 having a constant winding diameter may be used.
  • the protruding portions of the plurality of protruding portions 43 are extended in the circumferential direction to prevent the protruding portions 43 from dropping out as extending portions from the protruding ends in the circumferential direction.
  • a portion 43R is formed. As described above, in the dropout prevention part 43R, even if the torsion spring 46 moves in the direction of the protruding end of the protrusion 43, the dropout prevention part 43R is prevented from coming off by contacting the dropout prevention part 43R.
  • the spring holder 41 is held at a fixed position with respect to the internal rotor 30, and the internal rotor 30 can rotate integrally.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
PCT/JP2015/080361 2014-10-31 2015-10-28 弁開閉時期制御装置 Ceased WO2016068179A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201580032955.8A CN106471225B (zh) 2014-10-31 2015-10-28 阀正时控制装置
US15/319,082 US10280814B2 (en) 2014-10-31 2015-10-28 Valve opening/closing timing control apparatus

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014223318A JP6222043B2 (ja) 2014-10-31 2014-10-31 弁開閉時期制御装置
JP2014-223318 2014-10-31

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WO2016068179A1 true WO2016068179A1 (ja) 2016-05-06

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JP (1) JP6222043B2 (enExample)
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Publication number Priority date Publication date Assignee Title
JP2018168776A (ja) * 2017-03-30 2018-11-01 アイシン精機株式会社 弁開閉時期制御装置
DE102019103161A1 (de) * 2019-02-08 2020-08-13 ECO Holding 1 GmbH Nockenwellenversteller und Verfahren zur Montage eines Nockenwellenverstellers
JP6927238B2 (ja) 2019-02-21 2021-08-25 株式会社デンソー バルブタイミング調整装置
JP7343986B2 (ja) * 2019-02-28 2023-09-13 株式会社デンソー バルブタイミング調整装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009062978A (ja) * 2007-09-06 2009-03-26 Delphi Technologies Inc 回転子の権限範囲の一部のみを介して回転子を偏向させるよう予荷重を加えられたばねを有するカム位相制御器
US20090235884A1 (en) * 2008-03-21 2009-09-24 Fischer Thomas H Vane-type cam phaser having dual rotor bias springs
JP2012092739A (ja) * 2010-10-27 2012-05-17 Aisin Seiki Co Ltd 弁開閉時期制御装置

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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
JP4170370B2 (ja) 2007-07-30 2008-10-22 株式会社日立製作所 内燃機関のバルブタイミング制御装置
JP2013185459A (ja) * 2012-03-06 2013-09-19 Denso Corp バルブタイミング調整装置
JP5991091B2 (ja) 2012-09-04 2016-09-14 アイシン精機株式会社 弁開閉時期制御装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009062978A (ja) * 2007-09-06 2009-03-26 Delphi Technologies Inc 回転子の権限範囲の一部のみを介して回転子を偏向させるよう予荷重を加えられたばねを有するカム位相制御器
US20090235884A1 (en) * 2008-03-21 2009-09-24 Fischer Thomas H Vane-type cam phaser having dual rotor bias springs
JP2012092739A (ja) * 2010-10-27 2012-05-17 Aisin Seiki Co Ltd 弁開閉時期制御装置

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Publication number Publication date
CN106471225A (zh) 2017-03-01
JP6222043B2 (ja) 2017-11-01
US20170145872A1 (en) 2017-05-25
US10280814B2 (en) 2019-05-07
CN106471225B (zh) 2019-01-11
JP2016089682A (ja) 2016-05-23

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