WO2018055951A1 - Valve timing control device for internal combustion engine and seal structure for valve timing control device - Google Patents

Valve timing control device for internal combustion engine and seal structure for valve timing control device Download PDF

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Publication number
WO2018055951A1
WO2018055951A1 PCT/JP2017/029261 JP2017029261W WO2018055951A1 WO 2018055951 A1 WO2018055951 A1 WO 2018055951A1 JP 2017029261 W JP2017029261 W JP 2017029261W WO 2018055951 A1 WO2018055951 A1 WO 2018055951A1
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WO
WIPO (PCT)
Prior art keywords
valve timing
timing control
combustion engine
internal combustion
control device
Prior art date
Application number
PCT/JP2017/029261
Other languages
French (fr)
Japanese (ja)
Inventor
陽輔 岩瀬
正登 真子
寛幸 板倉
山田　吉彦
Original Assignee
日立オートモティブシステムズ株式会社
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Application filed by 日立オートモティブシステムズ株式会社 filed Critical 日立オートモティブシステムズ株式会社
Publication of WO2018055951A1 publication Critical patent/WO2018055951A1/en

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    • 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
    • F01L1/352—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 bevel or epicyclic gear
    • 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
    • F01L1/356—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 making the angular relationship oscillate, e.g. non-homokinetic drive

Definitions

  • the present invention relates to a valve timing control device for an internal combustion engine and a seal structure of the valve timing control device.
  • Patent Document 1 As a valve timing control device for an internal combustion engine, a device described in Patent Document 1 below is known.
  • This valve timing control device is provided with a cover member arranged with a predetermined clearance on the front end side of the motor housing of the electric motor.
  • the cover member has an outer peripheral portion fixed to the front end portion of the chain case by a plurality of bolts.
  • An annular oil seal is interposed between the outer peripheral surface of the motor housing and the inner peripheral surface of the outer peripheral portion of the cover member.
  • the annular base portion provided on the outer peripheral portion is press-fitted and fixed to the inner peripheral surface of the cover member, while the seal portion provided on the inner peripheral portion is slidably elastically contacted with the outer peripheral surface of the motor housing together with the seal lip.
  • the present invention has been devised in view of the above-described conventional technical problems, and an object thereof is to provide a valve timing control device for an internal combustion engine that can ensure the coaxiality of an electric motor and a seal member. .
  • an outer peripheral annular fixed portion sandwiched and fixed between the closing member and the case member, and an inner periphery of the fixed portion, the driving rotating body or the electric motor
  • a sealing member having an annular seal portion that elastically contacts the outer peripheral surface
  • the coaxiality of the electric motor and the seal member can be ensured.
  • FIG. 2 is a sectional view taken along line AA in FIG. 1. It is a B arrow line view of FIG. It is a principal part enlarged view of FIG. A is a front view of an oil seal provided in the present embodiment, and B is a cross-sectional view taken along the line CC of FIG. It is a principal part expanded sectional view which shows the seal ring with which this embodiment is provided. It is a longitudinal cross-sectional view which shows the 1st assembly
  • valve timing control device for an internal combustion engine according to the present invention will be described with reference to the drawings. Although this embodiment is applied to the valve timing control device on the intake valve side, it can also be applied to the exhaust valve side.
  • the valve timing control device is rotatably supported on a timing sprocket 1 that is a driving rotating body that is rotationally driven by a crankshaft of an internal combustion engine, and a cylinder head 01 via a bearing 02.
  • the camshaft 2 is provided between the timing sprocket 1 and the camshaft 2 so as to be relatively rotatable with respect to the timing sprocket 1, and the relative rotational phases of both 1 and 2 are set according to the engine operating state.
  • positioned at the front end of this phase change mechanism 3 are provided.
  • the timing sprocket 1 includes a sprocket main body 1a that is entirely formed of a ferrous metal in a cylindrical shape, and a crankshaft that is integrally provided on the outer periphery of the sprocket main body 1a and wound via a wound timing chain (not shown).
  • the gear part 1b which receives the rotational force of this, and the internal-tooth structure part 5 integrally provided in the front-end side of the sprocket main body 1a are comprised.
  • the inner tooth component 5 is formed integrally with the front end of the sprocket body 1a in a cylindrical shape, and a plurality of wave-shaped inner teeth 5a are formed on the inner periphery. Further, a motor housing 14 of an electric motor 12 described later is coupled to the outer end surface in the axial direction of the internal tooth component 5 from the axial direction via each bolt 7.
  • a large-diameter ball bearing 43 is interposed between the sprocket body 1a and a driven member 9 which is a driven rotating body (described later) provided at one axial end portion 2a of the camshaft 2.
  • the timing sprocket 1 is supported by the driven member 9 (camshaft 2) so as to be relatively rotatable.
  • a holding plate 8 is fixed to the rear end surface of the sprocket body 1a on the side opposite to the internal tooth component 5.
  • the holding plate 8 is formed in an annular shape by a metal plate material, and has an outer diameter substantially the same as the outer diameter of the sprocket body 1a.
  • the holding plate 8 is formed such that the inner diameter of the central hole 8a at the center is smaller than the inner diameter of the outer ring 43a of the large-diameter ball bearing 43, and the inner side surface of the inner peripheral portion is minute on the other end surface in the axial direction of the outer ring 43a. Opposite from the axial direction through the gap.
  • a stopper convex portion 8b protruding inward in the radial direction, that is, in the central axis direction shown in FIG. 4, is integrally provided.
  • This stopper convex part 8b is formed in substantially fan shape, and the front end surface 8c is formed in the circular arc shape along the circular arc internal peripheral surface of the stopper concave groove 11c of the adapter 11 mentioned later.
  • six bolt insertion holes 1c and 8d through which six bolts 7 are inserted are formed in the outer peripheral portions of the sprocket main body 1a, the internal tooth component 5 and the holding plate 8 at substantially equal intervals in the circumferential direction. ing.
  • the camshaft 2 has two drive cams per cylinder for opening an intake valve (not shown) on the outer periphery.
  • a driven member 9 is coupled to the one end portion 2 a of the camshaft 2 in the axial direction through an adapter 11 from the axial direction by a cam bolt 10.
  • the driven member 9 and the adapter 11 constitute a driven rotating body.
  • the driven member 9 is integrally formed of iron-based metal, and as shown in FIGS. 1 and 2, a disk-like fixed end portion 9a formed on the rear end side (camshaft 2 side), and the fixed end It is mainly composed of a cylindrical portion 9b that protrudes in the axial direction from the inner peripheral front end face of the portion 9a, and a bolt insertion hole 9c that is formed through the center.
  • the fixed end portion 9a has an outer surface opposed to the front end surface side of the one end portion 2a of the camshaft 2, and a convex inner peripheral portion 11b, which will be described later, of the adapter 11 is fitted to a substantially central position of the outer surface.
  • a first fitting groove 9d is formed.
  • the inner peripheral surface of the first fitting groove 9d is disposed at a position overlapping the outer ring 43a of the large-diameter ball bearing 43 in the radial direction.
  • the cylindrical portion 9 b has a bolt insertion hole 9 c into which the shaft portion 10 b of the cam bolt 10 is inserted in the inner axial direction.
  • a small-diameter ball bearing 35 and a needle bearing 36 are provided in parallel in the axial direction.
  • the axial end surface of the head 10 a supports the inner ring of the small-diameter ball bearing 35 from the axial direction.
  • a male screw 10c is formed that is screwed to the female screw 2c formed in the inner axial direction from the end portion of the cam shaft 2.
  • the adapter 11 is formed by bending a disk-shaped metal plate having a certain thickness into a substantially crank shape by press forming, and has a flange-shaped outer peripheral portion 11 a and an electric motor. A bottomed cylindrical inner peripheral portion 11b protruding in 12 directions.
  • the outer peripheral portion 11a is formed so that the outer diameter is slightly larger than the outer diameter of the fixed end portion 9a of the driven member 9, and the outer peripheral side of the inner surface on the electric motor 12 side is configured as a first restricting surface.
  • the first restricting surface is in contact with the other axial end surface of the inner ring 43b of the large-diameter ball bearing 43 to restrict the movement outward in the axial direction.
  • a stopper concave groove 11c into which the stopper convex portion 8b of the holding plate 8 is engaged is formed along the circumferential direction.
  • the stopper groove 11c is formed in a circular arc shape having a predetermined length in the circumferential direction, and both side surfaces 8e and 8f of the stopper convex portion 8b rotated within this length range abut against the circumferential facing surfaces.
  • the inner peripheral portion 11b of the adapter 11 is formed in a bottomed cylindrical convex shape protruding toward the electric motor 12, and the one end portion 2a of the camshaft 2 is fitted in the opposite concave groove from the axial direction. Further, an insertion hole 11d through which the shaft portion 10b of the cam bolt 10 is inserted is formed in the center position of the adapter 11.
  • the inner circumferential portion 11b is fitted into the first fitting groove 9d of the fixed end portion 9a of the driven member 9 by press fitting from the axial direction, and in this fitted state, the tip wall of the inner circumferential portion 11b is
  • the cam bolt 10 is coupled in a state of being sandwiched between one end 2 a of the camshaft 2 and the fixed end 9 a of the driven member 9.
  • the phase changing mechanism 3 is mainly composed of an electric motor 12 disposed on the front end side of the cylindrical portion 9b of the driven member 9, and a speed reducing mechanism 13 that reduces the rotational speed of the electric motor 12 and transmits it to the camshaft 2. Has been.
  • the electric motor 12 is a brushed DC motor, and is provided with a motor housing 14 that is a yoke that rotates integrally with the timing sprocket 1, and is rotatably provided inside the motor housing 14.
  • a motor output shaft 15, four arc-shaped permanent magnets 16 each serving as a stator fixed to the inner peripheral surface of the motor housing 14, and a power feeding plate 17 fixed to the front end portion of the motor housing 14 are provided. .
  • the motor housing 14 is formed in a bottomed cylindrical shape with a ferrous metal material, has an outer diameter that is the same as the outer diameter of the sprocket body 1 a, and has a partition at the rear end side.
  • the wall 14a is integrally formed.
  • the partition wall 14a is formed in a disk shape, and a shaft insertion hole 14b is formed on the inner periphery of a cylindrical extension portion 14c having substantially the center.
  • a shaft insertion hole 14b is formed on the inner periphery of a cylindrical extension portion 14c having substantially the center.
  • six female screw holes 14d to which the tip portions of the bolts 7 are screwed are formed at equal intervals in the circumferential direction.
  • the timing sprocket 1 (internal gear component 5), the holding plate 8 and the motor housing 14 are coupled in the axial direction by the bolts 7 inserted and screwed into these.
  • the motor output shaft 15 is formed in a stepped cylindrical shape and functions as an armature, and has a large diameter portion 15a on the camshaft 2 side and a small diameter on the cover member 4 side through a stepped portion formed at a substantially central position in the axial direction. Part 15b.
  • the large-diameter portion 15a has an iron core rotor 18 fixed to the outer periphery, and an eccentric shaft portion 37 that is an eccentric cam constituting a part of the speed reduction mechanism 13 is integrally coupled to a rear end surface in the rotation axis direction.
  • the commutator 20 which is a commutator is fixed to the outer periphery of the small diameter portion 15b.
  • This commutator 20 is provided in the outer periphery of the annular member 20a press-fit in the outer peripheral surface of the small diameter part 15b.
  • This commutator 20 is formed in an annular shape by a conductive material, and ends of coil wires from which coils 19 to be described later are electrically connected to each segment divided into the same number as the number of poles of the iron core rotor 18. Yes.
  • the iron core rotor 18 is formed of a magnetic material having a plurality of magnetic poles, and the outer peripheral side is configured as a bobbin having a slot around which the coil wire of the coil 19 is wound.
  • the iron core rotor 18 is fixed while the inner peripheral portion thereof is positioned in the axial direction on the outer periphery of the stepped portion of the motor output shaft 15.
  • Each permanent magnet 16 is disposed with a predetermined gap in the circumferential direction, is formed in a cylindrical shape as a whole, and has a plurality of magnetic poles in the circumferential direction.
  • the power feeding plate 17 includes a disk-shaped metal plate portion 17a made of an iron-based metal material, and disk-shaped resin portions 17b molded on both front and rear sides of the metal plate portion 17a. It is composed of
  • the metal plate portion 17a is positioned and fixed by caulking in an annular stepped concave groove formed on the inner periphery of the front end portion of the motor housing 14 at an outer peripheral portion not covered with the resin portion 17b. Further, a shaft insertion hole 17c through which the small diameter portion 15b of the motor output shaft 15 and the like are inserted is formed through the central portion of the metal plate portion 17a. Further, the metal plate portion 17a is formed by punching two holding holes (not shown) at predetermined positions continuous to the inner peripheral edge of the shaft insertion hole 17c.
  • the power feeding plate 17 is disposed inside each holding hole of the metal plate portion 17a, and a pair of copper cylindrical brush holders 23a and 23b fixed to the front end portion of the resin portion 17b by a plurality of rivets,
  • Each of the brush holders 23a and 23b has a pair of switching brushes 25a and 25b accommodated and slidably disposed along the radial direction, and a front end portion side of the resin portion 17b with the respective outer surfaces exposed.
  • the inner and outer double power supply slip rings 26a and 26b, which are fixed by molding, and the switching brushes 25a and 25b and the harnesses (not shown) for electrically connecting the slip rings 26a and 26b are provided. Yes.
  • the arcuate tip surfaces are in elastic contact with the outer peripheral surface of the commutator 20 from the radial direction by the spring force of the coil springs 24a and 24b.
  • the motor output shaft 15 and the eccentric shaft portion 37 are provided on the outer peripheral surface of the small diameter ball bearing 35 on the outer peripheral surface of the shaft portion 10 b of the cam bolt 10 and on the outer peripheral surface of the cylindrical portion 9 b of the driven member 9. It is rotatably supported by a needle bearing 36 disposed on the direction side portion.
  • a small-diameter oil seal 38 is provided between the outer peripheral surface of the large-diameter portion 15a of the motor output shaft 15 and the inner peripheral surface of the extending portion 14c of the motor housing 14.
  • the oil seal 38 seals between the electric motor 12 and the speed reduction mechanism 13 to prevent leakage of oil (lubricating oil) from the inside of the speed reduction mechanism 13 into the electric motor 12.
  • the cover member 4 is formed in a substantially disk shape, and also has a front end side of the motor housing 14, that is, a front end side of the power feeding plate 17 (the rotation of the motor output shaft 15 in the power feeding plate 17). It is arranged opposite to the camshaft 2 in the axial direction.
  • the cover member 4 includes a disc plate-shaped cover main body 28 and a synthetic resin cap portion 29 that covers the front end portion of the cover main body 28.
  • the cover main body 28 is mainly formed of a synthetic resin material to a predetermined thickness, and a metal reinforcing plate 28a is molded and fixed inside.
  • the cover main body 28 is provided with arc-shaped boss portions 28b at four locations on the outer peripheral portion.
  • a bolt insertion hole 28c into which a bolt fixed to the chain case 22 as a case member is inserted is formed by a metal sleeve (not shown).
  • a pair of rectangular tube-shaped brush holders 30a and 30b made of a copper material are fixed along the axial direction at positions facing the slip rings 26a and 26b in the axial direction.
  • a pair of power supply brushes 31a, 31b whose tip surfaces are in sliding contact with the slip rings 26a, 26b are slidably held in the axial direction.
  • Each of the slip rings 26a and 26b and the power supply brushes 31a and 31b constitute a power supply mechanism.
  • the cover main body 28 has a window hole 32 penetratingly formed at a substantially central position.
  • the window hole 32 is formed in a circular shape so that the tip 51b of the detected portion 51 whose inner diameter will be described later can be inserted.
  • a large-diameter groove 32a larger than the inner diameter of the window hole 32 is formed at the hole edge of the window hole 32 on the motor output shaft 15 side.
  • the large-diameter groove 32a functions as an escape portion into which a flange portion 51c of the detected portion 51 described later is inserted when the cover member 4 is assembled to the front end side of the electric motor 12.
  • cover main body 28 is not shown in the figure for urging the power supply brushes 31a and 31b in the direction of the slip rings 26a and 26b in the rectangular housing groove at the substantially central position of the outer end surface on the cap portion 29 side.
  • a pair of torsion coil springs are accommodated.
  • a power supply connector 33 for supplying current from a power supply battery to the power supply brushes 31a and 31b via a control unit (not shown) is integrally provided at the lower end of the cover body 28. ing.
  • a signal connector 34 for outputting a rotation angle signal to the control unit is provided at the lower end portion of the cover body 28 so as to protrude in parallel with the power supply connector 33 and in the radial direction.
  • the power supply connector 33 is connected to the pigtail harness at one end of a pair of terminal pieces (not shown), which is a conductive material partially embedded in the cover body 28. Further, a pair of other end portions exposed to the outside are connected to female connector terminals (not shown) on the control unit side.
  • the signal connector 34 is electrically connected to the integrated circuit 56 of the printed circuit board 55 of the angle sensor 50 described later at each exposed end portion 34a of a plurality of terminal pieces made of a conductive material partially embedded in the cover body 28. While being connected, the other end 34b exposed to the outside is connected to a female connector terminal (not shown) on the control unit side.
  • the cap portion 29 is formed in a disk plate shape, and a hook-shaped locking projection 29a formed integrally with the outer peripheral edge is locked in a step locking groove formed in the outer peripheral portion of the cover body 28 from the axial direction. It is fixed.
  • an angle sensor 50 that is a rotation angle detection mechanism for detecting the rotation angle position of the motor output shaft 15 is provided.
  • the angle sensor 50 is of an electromagnetic induction type, and is fixed at a substantially central position of the detected part 51 and the cover body 28 fixed in the small diameter part 15b of the motor output shaft 15 as shown in FIG. , And a detection circuit 52 that receives a detection signal from the detected part 51.
  • the detected portion 51 includes a substantially bottomed cylindrical support portion 51a made of a synthetic resin material, and three leaves fixed to the bottom wall surface of the tip portion 51b in the axial direction of the support portion 51a.
  • the three to-be-detected rotors 53 and an annular flange portion 51c that is press-fitted into the small diameter portion 15b of the motor output shaft 15 are integrally provided on the outer periphery of the rear end portion of the support portion 51a.
  • an oil seal 54 made of a rubber material is fitted and fixed in an annular seal groove formed at a substantially central position in the axial direction on the rear end side of the flange portion 51c.
  • the oil seal 54 seals between the inner peripheral surface of the small diameter portion 15b and the front end portion 51b side in a state where almost the entire rear end side of the support portion 51a is inserted into the small diameter portion 15b of the motor output shaft 15. It is supposed to be.
  • the to-be-detected rotor 53 is formed of an excitation conductor, and three ohmic magnetic materials are arranged at 120 ° in the circumferential direction on the front end surface of the front end portion of the support portion 51a.
  • the rotor 53 to be detected is formed so that the entire outer diameter is substantially the same as the outer diameter of the front end portion 51b of the support portion 51a, and is fixed to the mold while being exposed from the front end surface of the front end portion 51b.
  • the flange portion 51c is integrally formed of an insulating synthetic resin material like the support portion 51a, and when the rear end portion of the support portion 51a is inserted into the inside of the small diameter portion 15b at the maximum, the inner surface is the small diameter portion 15b. A further tip insertion is restricted by abutting on the tip edge of the lip from the axial direction.
  • the rotor 53 to be detected is disposed so as to face the receiving coil and the exciting coil of the printed circuit board 55 (to be described later) of the detection circuit 52 through the window hole 32 through the minute clearance C from the axial direction.
  • the detection circuit 52 includes a printed circuit board 55 which is a rectangular circuit board, an integrated circuit (ASIC) 56 provided on the outer surface of one end portion in the longitudinal direction of the printed circuit board 55, and the integrated circuit. 56, a receiving coil and an exciting coil (not shown) provided on the other end side of the same outer surface.
  • ASIC integrated circuit
  • the printed circuit board 55 has three small positioning holes at both corners at one end in the longitudinal direction where the receiving coil and the exciting coil are provided, that is, at both corners avoiding the receiving and exciting coils, and at the central position on the integrated circuit 56 side. Is formed through.
  • the cover main body 28 is integrally provided with three positioning protrusions that engage with the positioning holes and position the printed circuit board 55.
  • the cover main body 28 is integrally provided with three positioning protrusions that engage with the positioning holes and position the printed circuit board 55.
  • the printed circuit board 55 is fixed to the cover body 28 by an unillustrated adhesive filled between the outer peripheral portion and the cover body 28.
  • the printed board 55 is coated with an insulating material on the entire side surface where the receiving coil and the exciting coil are provided.
  • the detecting unit 51 detects a change in inductance between the receiving coil and the exciting coil and the detected rotor 53 and the receiving coil, and the integrated circuit 56 detects the rotation angle of the motor output shaft 15. That is, an induction current flows between the exciting coil and the rotor to be detected, and the integrated circuit 56 detects the rotational angle position of the motor output shaft 15 by this electromagnetic induction action, and outputs this information signal to the control unit. It has become.
  • the control unit detects the current engine operating state based on information signals from various sensors such as a crank angle sensor, an air flow meter, a water temperature sensor, an accelerator opening sensor, and an angle sensor 50 (not shown). Based on the engine control.
  • the control unit also controls the rotation of the motor output shaft 15 by energizing the coil 19 of the electric motor 12 via the power supply brushes 31a and 31b, the slip rings 26a and 26b, the switching brushes 25a and 25b, the commutator 20, and the like. It is carried out.
  • the speed reduction mechanism 13 decelerates the rotational force of the motor output shaft 15 to control the relative rotation phase of the camshaft 2 with respect to the timing sprocket 1.
  • the speed reduction mechanism 13 includes an eccentric shaft portion 37 that is an eccentric rotating body that performs an eccentric rotational motion, a medium-diameter ball bearing 39 provided on the outer periphery of the eccentric shaft portion 37, A roller 40 provided on the outer periphery of the medium-diameter ball bearing 39, a holder 41 that allows the roller 40 to move in the rolling direction while holding the roller 40 in the rolling direction, and a driven member 9 that is integral with the holder 41; Is mainly composed of
  • the eccentric shaft portion 37 is formed in a cylindrical shape, and the rotational axis Y of the cam surface 37 a formed on the outer peripheral surface is slightly in the radial direction from the rotational axis X of the motor output shaft 15. Eccentric.
  • the medium-diameter ball bearing 39 is disposed so as to substantially overlap the entire needle bearing 36 in the radial direction, and includes an inner ring 39a, an outer ring 39b, and a ball 39c interposed between the wheels 39a, 39b. And a cage (not shown) for holding the ball 39c.
  • the inner ring 39a is disposed on the outer peripheral surface of the eccentric shaft portion 37 with a minute gap.
  • the outer ring 39b is in a free state without being fixed in the axial direction.
  • the outer ring 39b has a minute end formed between the one end surface on the electric motor 12 side in the axial direction and no other part, and the other end surface in the axial direction is opposed to the back surface of the cage 41 facing the outer ring 39b. Through free clearance.
  • the outer ring 39 b is in contact with the outer peripheral surface of each roller 40 so that it can roll, and between the outer peripheral surface and the inner surface of the roller holding portion 41 b of the cage 41.
  • An annular clearance is formed. Through this clearance, the entire medium-diameter ball bearing 39 can move in the radial direction along with the eccentric rotation of the eccentric shaft portion 37, that is, can move eccentrically.
  • the retainer 41 is bent in a substantially L-shaped cross section forward from the front end of the outer peripheral portion of the fixed end portion 9a, and is formed on the front end side of the outer peripheral portion of the fixed end portion 9a. It is mainly composed of an annular base portion 41a extending along the radial direction and a cylindrical roller holding portion 41b extending from the outer end of the base portion 41a in a direction substantially perpendicular to the axis.
  • the roller holding portion 41b extends in the direction of the partition wall 14a through an annular concave accommodation space in which the tip portion is partitioned by the internal tooth constituent portion 5, the partition wall 14a of the motor housing 14, and the like.
  • the roller holding portion 41b is formed with a plurality of substantially rectangular roller holding holes 41c at the circumferentially equidistant positions, each of which holds the plurality of rollers 40 so as to roll freely at substantially equidistant positions in the circumferential direction. Yes.
  • the roller holding hole 41 c is formed in a rectangular shape elongated in the front-rear direction with the tip end side closed, and the total number thereof (number of rollers 40) is larger than the total number of teeth of the inner teeth 5 a of the inner tooth component 5. It is running low. By reducing the number of rollers 40 and the total number of teeth of the internal teeth 5a, the reduction ratio is obtained.
  • Each roller 40 is formed of an iron-based metal, and is fitted into the inner teeth 5a of the inner tooth component 5 while moving in the radial direction in accordance with the eccentric movement of the medium-diameter ball bearing 39. While being guided in the circumferential direction by both side edges of 41c, it swings in the radial direction.
  • the chain case 22 is integrally formed of a metal material such as an aluminum alloy material. As shown in FIG. 1, the chain case 22 is arranged such that the front end covers the entire outer periphery of the phase change mechanism 3. On the other hand, the rear end portion (not shown) is arranged and fixed along the vertical direction so as to cover the entire timing chain (not shown) wound around the timing sprocket 1 on the cylinder head 01 and the front end side of the cylinder block (not shown). Yes.
  • an annular inner side surface 28f on the camshaft 2 side of the cover body 28 is disposed opposite to the front end surface 22b on the cover member 4 side of the outer peripheral portion 22a.
  • the chain case 22 has a female screw hole 22d formed on the front end side on the cover member 4 side.
  • the cover member 4 is fastened and fixed to the chain case 22 by four bolts 44 which are fixing elements that are inserted into the bolt insertion holes 28c formed in the boss portions 28b and screwed into the female screw holes 22d. Yes.
  • the fixing element may be a screw or a rivet.
  • an oil seal that is a seal member that seals between the inner peripheral surface of the chain case 22 and the outer peripheral surface of the motor housing 14 between the front end surface 22b of the chain case 22 and the inner side surface 28f of the motor housing 14. 42 is interposed.
  • the chain case 22 extends in the axial direction so as to cover the entire phase change mechanism 3, and the rear end side is bolted to the cylinder head or the cylinder block.
  • the oil seal 42 is formed in a substantially annular shape, and includes an outer peripheral fixing portion 45 and an inner peripheral seal portion 46.
  • the fixing portion 45 is formed by bending a thin metal plate, for example, an aluminum alloy material into a substantially crank-shaped longitudinal section by press molding.
  • the fixing portion 45 is formed on the outer circumferential side of the annular portion 45a, the cylindrical portion 45b integrally formed on the inner peripheral edge of the annular portion 45a, and on the opposite side of the annular portion 45a of the cylindrical portion 45b in the axial direction.
  • a small-diameter ring portion 45c is formed by bending a thin metal plate, for example, an aluminum alloy material into a substantially crank-shaped longitudinal section by press molding.
  • the fixing portion 45 is formed on the outer circumferential side of the annular portion 45a, the cylindrical portion 45b integrally formed on the inner peripheral edge of the annular portion 45a, and on the opposite side of the annular portion 45a of the cylindrical portion 45b in the axial direction.
  • the annular portion 45 a has a radial width W that is substantially the same as the radial width of the inner side surface 28 f of the cover body 28.
  • the annular portion 45a is sandwiched between the front end surface 22b of the chain case 22 and the inner side surface 28f of the cover body 28 when the cover body 28 is coupled to the chain case 22 by the bolts 44. It is supposed to be fixed in the state.
  • annular portion 45a is provided with protruding portions 45d protruding in the radial direction at four locations on the outer peripheral edge.
  • Each projecting portion 45d is formed corresponding to each boss portion 28b of the cover main body 28 and is formed in a substantially arc shape.
  • Each protrusion 45d is formed with a bolt insertion hole 45e, which is a through hole into which the shaft portion 44a of the bolt 44 is inserted, in the center.
  • Each of the four bolt insertion holes 45e is formed to have the same inner diameter d, and each inner diameter d is formed to be larger than the outer diameter of the shaft portion 44a of the bolt 44.
  • a gap is formed between the outer peripheral surface. That is, the inner diameter d of the bolt insertion hole 45e can be slightly moved in the radial direction with respect to the shaft portion 44a of the bolt 44 in the state before the bolt 44 is fastened to the female screw hole 22d. It is set to a size.
  • the oil seal 42 is connected to the camshaft 2 via the bolt insertion holes 45e before the fixing portion 45 is coupled by the bolts 44 while being sandwiched between the chain case 22 and the cover body 28.
  • the movement can be adjusted along the direction perpendicular to the axis (radial direction).
  • the cylindrical portion 45b is formed such that its axial length L is approximately the center position of the outer peripheral portion 22a of the chain case 22 in the axial direction. Further, the inner diameter d1 of the cylindrical portion 45b is determined by the size of the radial gap between the inner peripheral surface of the outer peripheral portion 22a of the chain case 22 and the outer peripheral surface of the motor housing 14, and the cylindrical portion 45b is cylindrical within the radial clearance. It is arbitrarily set so that the portion 45b is located.
  • the length L of the cylindrical portion 45b can be freely set according to the relationship between the fixing position of the fixing portion 45 and the axial length of the motor housing 14.
  • the small-diameter ring portion 45c is formed in such a size that its radial width is appropriately vulcanized and bonded to the seal portion 46.
  • the annular seal portion 46 is formed of a synthetic rubber material so as to have a substantially V-shaped cross section, and a base portion 46a on one end side in the axial direction is integrally fixed to the small diameter ring portion 45c by vulcanization adhesion.
  • the V-shaped concave portion 46b on the other end side is formed to be elastically deformable in the radial direction with the base portion 46a as a fulcrum, and the inner peripheral edge is directed radially inward with respect to the outer peripheral surface of the motor housing 14. It is in elastic contact.
  • an annular backup spring 59 is provided on the outer periphery of the recess 46 b to force the inner periphery of the recess 46 b to elastically contact the outer periphery of the motor housing 14.
  • a seal lip 46c that elastically contacts the outer peripheral surface of the motor housing 14 is integrally provided on the inner periphery of the base portion 46a, and the seal lip 46c and the recess 46b cooperate to exert a sealing function. It has become.
  • a pair of seal rings 47a and 47b are elastically arranged on both side surfaces of the annular portion 45a.
  • Each of the seal rings 47a and 47b is formed in a circular shape in cross section, and includes a first seal groove 28g formed on the annular inner side surface 28f of the cover main body 28, and an outer peripheral front end surface of the chain case 22.
  • Each of the second seal grooves 22e formed in 22b is elastically accommodated and disposed.
  • the seal rings 47a and 47b seal the three sides of the inner side surface 28f, the outer peripheral front end surface 22b, and the annular portion 45a, and externally feed the electric motor 12 and the slip rings 26a and 26b to the power supply.
  • the oil is prevented from entering between the brushes 31a and 31b.
  • the timing sprocket 1, the electric motor 12, and the speed reduction mechanism 13 are connected in advance by six bolts 7 to unitize the phase changing mechanism 3.
  • This unitized phase change mechanism 3 is coupled to one end 2 a of the camshaft 2 by a cam bolt 10.
  • a chain case 22 is disposed on the outer periphery of the phase change mechanism 3, and the chain case 22 is fixed to a cylinder head (not shown) with a bolt.
  • the seal ring 47b is accommodated and held in the second seal groove 22e of the front end surface 22b of the outer peripheral portion 22a of the chain case 22.
  • the oil seal 42 is temporarily held between the motor housing 14 and the chain case 22.
  • the recess 46b and the seal lip 46c which are the seal portions 46 of the oil seal 42, are inserted while sliding the outer peripheral surface along the axial direction from the front end side of the motor housing 14 using its own elastic force.
  • This maximum movement position is regulated by the annular portion 45a of the oil seal 42 coming into contact with the seal ring 47b of the chain case 22.
  • the oil seal 42 that has moved to the maximum is supported by its own elastic reaction force against the outer peripheral surface of the motor housing 14.
  • the oil seal 42 is supported on the outer peripheral surface of the motor housing 14 by the elastic reaction force of the fixed portion 45 and the rubber seal 46 which are lightened by the aluminum alloy material. Therefore, the oil seal 42 does not shift downward in the direction of gravity due to its own weight, and its axis is substantially coaxial with the rotation axis X of the motor housing 14 (rotation axis of the camshaft 2).
  • each bolt insertion hole 45e of the oil seal 42 and each female screw hole 22d of the chain case 22 are in a substantially matched state.
  • the cover member 4 is disposed on the front end side of the chain case 22 through the fixing portion 45 of the oil seal 42 so as to cover the front end side of the motor housing 14.
  • the seal ring 47a is accommodated in the first seal groove 28g on the inner side surface 28f of the cover body 28.
  • the shaft portions 44 a of the respective bolts 44 are inserted into the respective bolt insertion holes 28 c and 45 e of the cover main body 28 and the oil seal 42 to be inserted into the female screw holes 22 d of the chain case 22. Screw and fasten.
  • the annular portion 45 a of the fixing portion 45 is interposed and fixed between the cover main body 28 and the chain case 22 in the oil seal 42.
  • the seal rings 47a and 47b elastically contact with both side surfaces of the annular portion 45a to exert a sealing function, and the sealing portion 46 exhibits a sealing function between the motor housing 14 and the chain case 22.
  • the timing sprocket 1 rotates through the timing chain in accordance with the rotational drive of the crankshaft of the engine.
  • the rotational force is transmitted to the motor housing 14 via the internal tooth component 5, and the motor housing 14 rotates synchronously.
  • the rotational force of the internal tooth component 5 is transmitted from each roller 40 to the camshaft 2 via the cage 41 and the driven member 9.
  • the cam of the camshaft 2 opens and closes the intake valve.
  • a control current from the control unit is energized to the coil 19 of the electric motor 12 through the power supply brushes 31a and 31b, the slip rings 26a and 26b, and the motor output shaft 15 rotates. Driven. This rotational force is decelerated and transmitted to the camshaft 2 via the deceleration mechanism 13.
  • the camshaft 2 is rotated forward and backward relative to the timing sprocket 1 and the relative rotational phase is converted, so that the opening / closing timing of the intake valve is controlled to be advanced or retarded.
  • the maximum position restriction (angular position restriction) of the forward and reverse relative rotation of the camshaft 2 with respect to the timing sprocket 1 is such that either one of the opposing surfaces 11e, 11f of the stopper groove 11c is the respective side surface 8e, 8f of the stopper convex portion 8b. This is done by contacting one of the two. As a result, the opening / closing timing of the intake valve is converted to the maximum on the advance side or the retard side, and the fuel efficiency and output of the engine can be improved.
  • the detected portion 51 of the angle sensor 50 rotates with the rotation of the motor output shaft 15 of the electric motor 12
  • an induced current flows between the detection circuit 52 and the integrated circuit 56 outputs the motor output by this electromagnetic induction action.
  • the rotation angle of the shaft 15 is detected, and the current rotation angle position of the motor output shaft 15 is detected in the control unit by this detection signal.
  • the control unit outputs a rotational drive signal to the electric motor 12 according to the rotational angle position and the rotational position of the crankshaft, and accurately controls the relative rotational phase of the camshaft 2 with respect to the crankshaft according to the current engine operating state. It is like that.
  • the oil seal 42 does not press-fit and fix the fixing base portion to the inner peripheral surface of the chain case 22 as in the prior art, but the fixing portion 45 is connected to the cover body 28 and the chain case 22. It was made to fix in the state pinched
  • the axis Z of the oil seal 42 is automatically arranged coaxially with the rotational axis X of the motor housing 14 by the elastic reaction force of the seal portion 46 (automatic alignment). Therefore, in the state where the fixing portion 45 is sandwiched and fixed between the cover main body 28 and the chain case 22 by the bolts 44, the oil seal 42 is configured such that the entire recess 46b and the seal lip 46c of the sealing portion 46 are disposed in the motor housing. 14 can be brought into close contact with the outer peripheral surface. That is, the coaxiality between the axis X of the motor housing 14 and the axis Z of the oil seal 42 is ensured.
  • the pair of seal rings 47a and 47b are in elastic contact with both side surfaces of the annular portion 45a of the oil seal 42, the chain case 22 and the cover member 4 and the phase change mechanism 3
  • the sealing function between the two is effectively exhibited, and the intrusion of oil from the outside to the inside of the electric motor 12 or the like can be suppressed.
  • the elastic force of the seal rings 47a and 47b is prevented from affecting the coaxiality with the axis Z of the oil seal 42 by being sandwiched between the pair of seal rings 47a and 47b from the rotational axis direction of the camshaft.
  • the oil seal 42 is formed of a thin plate-like aluminum alloy material so that the oil seal 42 is sufficiently lightened, the entire load when the seal portion 46 is assembled to the outer peripheral surface of the motor housing 14 is achieved. Can be stably supported by the elastic reaction force of the seal portion 46. That is, the oil seal 42 can maintain the original shape of the ring without bending and deforming the upper part in the gravity direction of the seal portion 46 due to the entire load, so that the coaxiality with the motor housing 14 can be maintained. Can be secured.
  • the fixing portion 45 can be formed of titanium or a hard resin material that can be reduced in weight in addition to the aluminum alloy material.
  • the tip 51b of the detected portion 51 of the angle sensor 50 is inserted and disposed in the window hole 32 formed in the cover main body 28 of the cover member 4.
  • the axial length of the apparatus can be shortened by the amount of insertion.
  • the mountability of the valve timing control device in the engine room is improved.
  • the window hole 32 is formed so as to penetrate therethrough, the axial length of the apparatus can be further shortened.
  • the tip 51b of the detected part 51 is inserted into the window hole 32 formed in the cover main body 28 of the cover member 4, but the tip 51b faces the window hole 32.
  • the tip 51b faces the window hole 32.
  • it may be provided near the window hole 32.
  • it is necessary to set a predetermined amount of clearance between the cover main body 28 and the tip end portion 51b of the detected portion 51 in consideration of the influence of manufacturing error, vibration of the internal combustion engine, and the like.
  • the window hole 32 since the window hole 32 is present, it is not necessary to consider the space between the inner surface of the cover main body 28 and the distal end portion 51b of the detected portion 51, so that the axial length of the apparatus can be shortened.
  • the tip end portion 51 b of the detected portion 51 is deeply inserted into the window hole 32 by this amount. Therefore, the axial length of the apparatus can be further shortened.
  • each detected rotor 53 at the tip 51b directly faces the receiving coil and the exciting coil through the minute clearance C without involving an inclusion such as a resin material, the output of the angle sensor 50 Therefore, the rotation detection accuracy of the motor output shaft 15 can be improved.
  • the tip 51b of the detected portion 51 is inserted and arranged in the window hole 32, and the position of the detected rotor 53 is in sliding contact with the slip rings 26a and 26b and the power supply brushes 31a and 31b. Since the rotor is offset from the position (on the cap portion 29 side), the detected rotors 53a to 53c are covered with the inner peripheral surface of the window hole 32. Therefore, it is possible to sufficiently suppress the metal wear powder generated during sliding between the power feeding brushes 31a and 31b and the slip rings 26a and 26b from adhering to the rotor 53 to be detected.
  • FIG. 12 shows a second embodiment, in which the seal rings 47a and 47b are fixed to both side surfaces of the fixing portion 45 of the oil seal 42 by vulcanization adhesion.
  • the seal rings 47a and 47b are formed to have a substantially triangular cross section, and each of the acute-angled tip portions 47c and 47d is axially connected to the inner side surface 28f of the cover body 28 and the front end surface 22b of the outer peripheral portion 22a of the chain case 22. It is touching from.
  • FIG. 13 shows a third embodiment.
  • the synthetic rubber material is fixed to both side surfaces of the fixing portion 45 of the oil seal 42 by the vulcanization adhesion.
  • the cross-sectional shape of is substantially square.
  • FIG. 14 shows a fourth embodiment in which the arrangement of the power supply brushes 31a and 31b and the slip rings 26a and 26b is changed and the structure of the oil seal 42 is changed.
  • slip rings 26 a and 26 b are fixed to the outer peripheral surface of the outer peripheral cylindrical portion 48 a of the annular member 48 made of a nonmagnetic material provided at the step portion of the front end portion of the motor housing 14.
  • Each of the power supply brushes 31a and 31b is provided along the gravity direction inside a power supply connector 49 provided along the radial direction on the outer periphery of the cover body 28 of the cover member 4.
  • the power supply brushes 31a and 31b are elastically contacted in the radial direction in the direction of the slip rings 26a and 26b by the spring force of a coil spring (not shown) which is a spring member.
  • a pair of terminals 58 whose one ends are electrically connected to the power supply brushes 31 a and 31 b are provided inside the power supply connector 49. The other end of each terminal 58 is connected to the control unit via a male connector (not shown).
  • the oil seal 42 is formed in a flat disk shape without the fixing portion 45 being bent, and the fixing portion 45 is sandwiched between the inner side surface 28f of the cover body 28 and the front end surface 22b of the chain case 22. It is.
  • cover main body 28 and the chain case 22 are, as in the first embodiment, the four boss portions 28b on the outer peripheral portion, the bolt insertion holes 28c formed in the front end portion of the chain case 22, and the bolts inserted and screwed into the female screw holes 22d. 44 is connected from the axial direction.
  • the oil seal 42 is connected to each boss 28b and the chain case by the bolts 44 inserted through the radial gaps in the bolt insertion holes 45e of the four protrusions 45d on the outer periphery of the annular part 45a of the fixing part 45. It is being fixed in the state pinched
  • the seal portion 46 vulcanized and bonded to the inner periphery of the fixed portion 45 has a recess 46 b elastically contacting the outer peripheral surface of the motor housing 14 by a backup spring 59.
  • two seal lips 46c and 46d that elastically contact the outer peripheral surface of the motor housing 14 are integrally provided on the inner periphery of the base 46a.
  • the fixing portion 45 is formed of a thin disc-shaped aluminum alloy material, as in the first embodiment.
  • a seal ring 47a is accommodated in the first seal groove formed on the inner side surface 28f of the cover main body 28, and the space between the inner side surface 28f and the fixing portion 45 is sealed by this one seal ring 47a. It has become.
  • this embodiment also maintains the original shape by the elastic reaction force of the seal portion 46 when the oil seal 42 is assembled to the outer peripheral surface of the motor housing 14 via the seal portion 46 as in the first embodiment. . For this reason, the coaxiality of the oil seal 42 and the motor housing 14 is ensured, and the entire seal portion 46 can be brought into close contact with the outer peripheral surface of the motor housing 14. Therefore, a stable and good sealing function by the oil seal 42 can be exhibited.
  • the two sealing lips 46c and 46d can perform double sealing, the sealing performance can be improved and the original shape of the sealing portion 46 can be further maintained. This makes it possible to further exhibit a sealing function.
  • the recess 46b is forcibly pressed against the outer peripheral surface of the motor housing 14 by the backup spring 59, the coaxiality between the oil seal 42 and the motor housing 14 can be further obtained in this respect.
  • the fixing portion 45 is formed into a flat straight shape without being bent, the molding operation is facilitated.
  • the power supply brushes 31a and 31b are arranged along the radial direction of the motor housing 14, the axial length of the entire apparatus including the cover member 4 can be further shortened.
  • a different rotation detection mechanism is used as a rotation detection mechanism for detecting the rotation position of the motor output shaft 15 of the electric motor 12 instead of the electromagnetic induction type used in the above embodiments. Yes.
  • a plug body 60 that press-fits oil from the speed reduction mechanism 13 side toward the electric motor 12 is press-fitted and fixed inside the motor output shaft 15.
  • the present invention is not limited to the configuration of each of the above-described embodiments.
  • the number of the protrusions 45d of the oil seal 42 and the number of the bosses 28b of the cover main body 28 are increased or decreased depending on the specifications or size of the engine. It is also possible.
  • the gap between the inner peripheral edge of each projecting portion 45d of the oil seal 42 and the outer peripheral surface of the shaft portion 44a of each bolt 44 should be of a size if the movement of the oil seal 42 in the radial direction can be permitted. It can be changed arbitrarily.
  • the drive rotor may be a timing pulley in addition to the timing sprocket.
  • the case member is the chain case 22, but it may be a fixing member such as a spacer attached to the chain case 22, for example.
  • a fixing member is attached to the chain case 22, and the fixing portion 45 of the oil seal 42 is sandwiched and fixed between the fixing member and the cover member 4.
  • valve timing control device for an internal combustion engine based on the embodiment described above, for example, the following modes can be considered.
  • a driving rotating body to which a rotational force from a crankshaft is transmitted A driven rotor fixed to the camshaft;
  • An electric motor that changes the relative rotational phase of the driven rotating body and the driven rotating body by rotationally driving;
  • a closing member that is disposed opposite to the electric motor from the direction of the rotation axis of the electric motor and is fixed to a case member that is disposed on the outer periphery of the electric motor;
  • An annular fixing portion that is sandwiched and fixed between the closing member and the case member, and an annular seal portion that is provided on the inner periphery of the fixing portion and elastically contacts the outer peripheral surface of the drive rotating body or the electric motor.
  • a sealing member a sealing member.
  • the closing member and the case member are coupled by a plurality of fixing elements, and the fixing portion of the seal member has a plurality of through holes into which the fixing elements are inserted with a radial gap.
  • each of the through holes is formed in a protruding portion on the outer periphery of the fixed portion.
  • the sealing member is fixed in a state where the fixing portion is sandwiched between the closing member and the case member by the fixing element via the fixing portion.
  • the fixing portion has a section perpendicular to the rotation axis of the electric motor bent in a crank shape, and is formed on the outer periphery of the cylindrical portion and one end portion in the axial direction of the cylindrical portion. It has the annular part which has a protrusion part, and the said seal
  • the outer diameter of the cylindrical portion is smaller than the inner diameter of the case portion.
  • the sealing member has the fixing portion in an annular and plate shape, and the sealing portion is provided on a radially inner peripheral portion of the fixing portion.
  • the closing member has a power feeding mechanism that supplies power from the power source to the electric motor radially inward of the seal portion of the seal member.
  • seal ring that seals between the inside and the outside of the case portion between the fixing portion and the case member and between the fixing portion and the closing member.
  • the seal ring is a pair of O-rings interposed between the fixed portion and the case member and between the fixed portion and the closing member.
  • the seal ring is configured as a pair fixed to both side surfaces of the fixed portion by vulcanization adhesion, and each outer end portion is in elastic contact with the facing surfaces of the case member and the closing member.
  • the pair of seal rings are formed in a triangular cross section.
  • each of the pair of seal rings is formed in a quadrangular cross section.
  • each of the seal rings is a synthetic rubber material.
  • a drive rotator to which a rotational force is transmitted from the crankshaft;
  • a driven rotor fixed to the camshaft;
  • An electric motor that changes a relative rotational phase of the drive rotator and the driven rotator by rotating an output shaft;
  • a closing member that is disposed opposite to the electric motor from the direction of the rotation axis of the electric motor and is fixed to a case member that is disposed on the outer periphery of the electric motor;
  • An annular fixing portion that is sandwiched and fixed between the closing member and the case member, and an annular seal portion that is provided on the inner periphery of the fixing portion and elastically contacts the outer peripheral surface of the drive rotating body or the electric motor.
  • a sealing member having With The seal member is provided so that its position can be adjusted along the direction perpendicular to the axis of the camshaft.
  • the seal member is perpendicular to the axis of the camshaft by elastic force due to elastic contact of the seal portion with the outer peripheral surface of the drive rotating body or the electric motor before the fixing portion is fixed.
  • the position of the direction can be adjusted.
  • a drive rotator to which a rotational force is transmitted from the crankshaft;
  • a driven rotor fixed to the camshaft;
  • An electric motor that changes a relative rotational phase of the drive rotator and the driven rotator by rotating an output shaft;
  • a closing member that is disposed opposite to the electric motor from the direction of the rotation axis of the electric motor and is fixed to a case member that is disposed on the outer periphery of the electric motor;
  • An annular fixing portion sandwiched and fixed between the closing member and the case member, and an annular seal provided on the inner periphery of the fixing portion and elastically contacting the outer peripheral surface of the drive rotating body or the electric motor
  • a sealing member whose position is adjustable along the direction perpendicular to the axis of the camshaft.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

The present invention is equipped with: an electric motor 12 for changing the relative rotational phase of a sprocket 1 and a camshaft 2; a cover member 4; a chain case 22 arranged on the outer peripheral side of a motor housing 14; and an oil seal 42 for sealing between the motor housing and the chain case. The oil seal is secured with bolts 44 while securing parts 45 on the outer peripheral side of the oil seal are sandwiched between an inside surface 28f of a cover main body 28 and a front-end surface 22b of the chain case, and the oil seal has an annular seal part 46 elastically contacting the outer peripheral surface of the motor housing. Before the oil seal is secured with the bolts the entire oil seal is able to move in the radial direction via bolt insertion holes 45e. Thus, a reduction in sealing performance can be prevented while ensuring concentricity of the motor housing and the oil seal.

Description

内燃機関のバルブタイミング制御装置及び該バルブタイミング制御装置のシール構造Valve timing control device for internal combustion engine and seal structure of valve timing control device
　本発明は、内燃機関のバルブタイミング制御装置及び該バルブタイミング制御装置のシール構造に関する。 The present invention relates to a valve timing control device for an internal combustion engine and a seal structure of the valve timing control device.
　内燃機関のバルブタイミング制御装置としては、以下の特許文献１に記載されているものが知られている。 As a valve timing control device for an internal combustion engine, a device described in Patent Document 1 below is known.
　このバルブタイミング制御装置は、電動モータのモータハウジングの前端側に、所定のクリアランスをもって配置されたカバー部材が設けられている。このカバー部材は、外周部がチェーンケースの前端部に複数のボルトによって固定されている。また、前記モータハウジングの外周面とカバー部材の外周部の内周面との間には、円環状のオイルシールが介装されている。このオイルシールは、外周部に有する環状基部がカバー部材の内周面に圧入固定されている一方、内周部に有するシール部がシールリップと共にモータハウジングの外周面に摺動可能に弾接している。 This valve timing control device is provided with a cover member arranged with a predetermined clearance on the front end side of the motor housing of the electric motor. The cover member has an outer peripheral portion fixed to the front end portion of the chain case by a plurality of bolts. An annular oil seal is interposed between the outer peripheral surface of the motor housing and the inner peripheral surface of the outer peripheral portion of the cover member. In this oil seal, the annular base portion provided on the outer peripheral portion is press-fitted and fixed to the inner peripheral surface of the cover member, while the seal portion provided on the inner peripheral portion is slidably elastically contacted with the outer peripheral surface of the motor housing together with the seal lip. Yes.
特開２０１５－１７８８２２号公報Japanese Patent Laid-Open No. 2015-178822
　前記従来のバルブタイミング制御装置にあっては、カバー部材をチェーンケースへの取り付ける際に、該カバー部材の自重によって位置ずれを起こしやすい。このため、カバー部材とモータハウジングとの同軸度を精度良く取ることが困難になるおそれがあった。この結果、オイルシールとモータハウジングとの同軸性が得られないおそれがあった。 In the conventional valve timing control device, when the cover member is attached to the chain case, the cover member is likely to be displaced due to its own weight. For this reason, there is a possibility that it is difficult to accurately obtain the coaxiality between the cover member and the motor housing. As a result, the coaxiality between the oil seal and the motor housing may not be obtained.
　本発明は、前記従来の技術的課題に鑑みて案出されたもので、電動モータとシール部材との同軸性を確保し得る内燃機関のバルブタイミング制御装置を提供することを一つの目的としている。 The present invention has been devised in view of the above-described conventional technical problems, and an object thereof is to provide a valve timing control device for an internal combustion engine that can ensure the coaxiality of an electric motor and a seal member. .
　本発明の好ましい態様によれば、とりわけ、閉塞部材とケース部材との間に挟まれて固定される外周の環状の固定部及び該固定部の内周に設けられて駆動回転体または電動モータの外周面に弾接する環状シール部と、を有するシール部材を備えたことを特徴としている。 According to a preferred aspect of the present invention, among other things, an outer peripheral annular fixed portion sandwiched and fixed between the closing member and the case member, and an inner periphery of the fixed portion, the driving rotating body or the electric motor And a sealing member having an annular seal portion that elastically contacts the outer peripheral surface.
　この発明によれば、電動モータとシール部材の同軸性を確保することができる。 According to this invention, the coaxiality of the electric motor and the seal member can be ensured.
本発明に係るバルブタイミング制御装置の一実施形態を示す縦断面図である。It is a longitudinal section showing one embodiment of a valve timing control device concerning the present invention. 本実施形態における主要な構成部材を示す分解斜視図である。It is a disassembled perspective view which shows the main structural members in this embodiment. 図１のＡ－Ａ線断面図である。FIG. 2 is a sectional view taken along line AA in FIG. 1. 図１のＢ矢視図である。It is a B arrow line view of FIG. 図１の要部拡大図である。It is a principal part enlarged view of FIG. Ａは本実施形態に供されるオイルシールの正面図、Ｂは図６のＣ－Ｃ線断面図である。A is a front view of an oil seal provided in the present embodiment, and B is a cross-sectional view taken along the line CC of FIG. 本実施形態に供されるシールリングを示す要部拡大断面図である。It is a principal part expanded sectional view which shows the seal ring with which this embodiment is provided. 本実施形態におけるオイルシールの組み付け手順の第１組付工程を示す縦断面図であるIt is a longitudinal cross-sectional view which shows the 1st assembly | attachment process of the assembly procedure of the oil seal in this embodiment. 第２組付工程を示す縦断面図である。It is a longitudinal cross-sectional view which shows a 2nd assembly | attachment process. 第３組付工程を示す縦断面図である。It is a longitudinal cross-sectional view which shows a 3rd assembly | attachment process. 第４組付工程を示す縦断面図である。It is a longitudinal cross-sectional view which shows a 4th assembly | attachment process. 第２実施形態を示す要部断面図である。It is principal part sectional drawing which shows 2nd Embodiment. 第３実施形態を示す要部断面図である。It is principal part sectional drawing which shows 3rd Embodiment. 第４実施形態のバルブタイミング制御装置を示す縦断面図である。It is a longitudinal cross-sectional view which shows the valve timing control apparatus of 4th Embodiment.
　以下、本発明に係る内燃機関のバルブタイミング制御装置の実施形態を図面に基づいて説明する。なお、この実施形態では、吸気弁側のバルブタイミング制御装置に適用したものであるが、排気弁側にも適用可能である。 Hereinafter, an embodiment of a valve timing control device for an internal combustion engine according to the present invention will be described with reference to the drawings. Although this embodiment is applied to the valve timing control device on the intake valve side, it can also be applied to the exhaust valve side.
　バルブタイミング制御装置は、図１及び図２に示すように、内燃機関のクランクシャフトによって回転駆動する駆動回転体であるタイミングスプロケット１と、シリンダヘッド０１上に軸受０２を介して回転自在に支持されていると共に、タイミングスプロケット１に相対回転自在に設けられたカムシャフト２と、タイミングスプロケット１とカムシャフト２との間に配置されて、機関運転状態に応じて両者１，２の相対回転位相を変更する位相変更機構３と、該位相変更機構３の前端に配置された閉塞部材であるカバー部材４と、を備えている。 As shown in FIGS. 1 and 2, the valve timing control device is rotatably supported on a timing sprocket 1 that is a driving rotating body that is rotationally driven by a crankshaft of an internal combustion engine, and a cylinder head 01 via a bearing 02. In addition, the camshaft 2 is provided between the timing sprocket 1 and the camshaft 2 so as to be relatively rotatable with respect to the timing sprocket 1, and the relative rotational phases of both 1 and 2 are set according to the engine operating state. The phase change mechanism 3 to change and the cover member 4 which is a closure member arrange | positioned at the front end of this phase change mechanism 3 are provided.
　タイミングスプロケット１は、全体が鉄系金属によって筒状に形成されたスプロケット本体１ａと、該スプロケット本体１ａの外周に一体に設けられて、巻回された図外のタイミングチェーンを介してクランクシャフトからの回転力を受ける歯車部１ｂと、スプロケット本体１ａの前端側に一体に設けられた内歯構成部５と、から構成されている。 The timing sprocket 1 includes a sprocket main body 1a that is entirely formed of a ferrous metal in a cylindrical shape, and a crankshaft that is integrally provided on the outer periphery of the sprocket main body 1a and wound via a wound timing chain (not shown). The gear part 1b which receives the rotational force of this, and the internal-tooth structure part 5 integrally provided in the front-end side of the sprocket main body 1a are comprised.
　内歯構成部５は、スプロケット本体１ａの前端部に円筒状一体に形成されていると共に、内周に波形状の複数の内歯５ａが形成されている。また、この内歯構成部５の軸方向の外端面には、後述する電動モータ１２のモータハウジング１４が各ボルト７を介して軸方向から結合されている。 The inner tooth component 5 is formed integrally with the front end of the sprocket body 1a in a cylindrical shape, and a plurality of wave-shaped inner teeth 5a are formed on the inner periphery. Further, a motor housing 14 of an electric motor 12 described later is coupled to the outer end surface in the axial direction of the internal tooth component 5 from the axial direction via each bolt 7.
　スプロケット本体１ａとカムシャフト２の軸方向の一端部２ａに設けられた後述する従動回転体である従動部材９との間には、１つの大径ボールベアリング４３が介装されている。この大径ボールベアリング４３は、タイミングスプロケット１が従動部材９(カムシャフト２)に相対回転自在に軸受けされている。 A large-diameter ball bearing 43 is interposed between the sprocket body 1a and a driven member 9 which is a driven rotating body (described later) provided at one axial end portion 2a of the camshaft 2. In this large-diameter ball bearing 43, the timing sprocket 1 is supported by the driven member 9 (camshaft 2) so as to be relatively rotatable.
　さらに、スプロケット本体１ａの内歯構成部５と反対側の後端面には、保持プレート８が固定されている。この保持プレート８は、図４に示すように、金属板材によって円環状に形成され、外径が前記スプロケット本体１ａの外径とほぼ同一に形成されている。また、保持プレート８は、中央の中央孔８ａの内径が大径ボールベアリング４３の外輪４３ａの内径よりも小さく形成されて、内周部の内側面が前記外輪４３ａの軸方向の他端面に微小隙間を介して軸方向から対峙している。 Furthermore, a holding plate 8 is fixed to the rear end surface of the sprocket body 1a on the side opposite to the internal tooth component 5. As shown in FIG. 4, the holding plate 8 is formed in an annular shape by a metal plate material, and has an outer diameter substantially the same as the outer diameter of the sprocket body 1a. In addition, the holding plate 8 is formed such that the inner diameter of the central hole 8a at the center is smaller than the inner diameter of the outer ring 43a of the large-diameter ball bearing 43, and the inner side surface of the inner peripheral portion is minute on the other end surface in the axial direction of the outer ring 43a. Opposite from the axial direction through the gap.
　また、保持プレート８の中央孔８ａの内周縁所定位置には、図４に示す径方向内側、つまり中心軸方向に向かって突出したストッパ凸部８ｂが一体に設けられている。このストッパ凸部８ｂは、ほぼ扇状に形成されて、先端面８ｃが後述するアダプタ１１のストッパ凹溝１１ｃの円弧状内周面に沿った円弧状に形成されている。 Further, at a predetermined position on the inner peripheral edge of the central hole 8a of the holding plate 8, a stopper convex portion 8b protruding inward in the radial direction, that is, in the central axis direction shown in FIG. 4, is integrally provided. This stopper convex part 8b is formed in substantially fan shape, and the front end surface 8c is formed in the circular arc shape along the circular arc internal peripheral surface of the stopper concave groove 11c of the adapter 11 mentioned later.
　また、スプロケット本体１ａと内歯構成部５及び保持プレート８の各外周部には、６本のボルト７が挿入する６つのボルト挿入孔１ｃ、８ｄが周方向のほぼ等間隔位置に貫通形成されている。 In addition, six bolt insertion holes 1c and 8d through which six bolts 7 are inserted are formed in the outer peripheral portions of the sprocket main body 1a, the internal tooth component 5 and the holding plate 8 at substantially equal intervals in the circumferential direction. ing.
　カムシャフト２は、外周に図外の吸気弁を開作動させる一気筒当たり２つの駆動カムを有している。また、カムシャフト２の軸方向の一端部２ａには、アダプタ１１を介して従動部材９がカムボルト１０によって軸方向から結合されている。なお、前記従動部材９とアダプタ１１とによって従動回転体を構成している。 The camshaft 2 has two drive cams per cylinder for opening an intake valve (not shown) on the outer periphery. A driven member 9 is coupled to the one end portion 2 a of the camshaft 2 in the axial direction through an adapter 11 from the axial direction by a cam bolt 10. The driven member 9 and the adapter 11 constitute a driven rotating body.
　従動部材９は、鉄系金属によって一体に形成され、図１及び図２に示すように、後端側(カムシャフト２側)に形成された円板状の固定端部９ａと、該固定端部９ａの内周前端面から軸方向へ突出した円筒部９ｂと、中央に貫通形成されたボルト挿入孔９ｃと、から主として構成されている。 The driven member 9 is integrally formed of iron-based metal, and as shown in FIGS. 1 and 2, a disk-like fixed end portion 9a formed on the rear end side (camshaft 2 side), and the fixed end It is mainly composed of a cylindrical portion 9b that protrudes in the axial direction from the inner peripheral front end face of the portion 9a, and a bolt insertion hole 9c that is formed through the center.
　固定端部９ａは、外側面がカムシャフト２の一端部２ａの前端面側に対向配置され、この外側面のほぼ中央位置に前記アダプタ１１の後述する凸状の内周部１１ｂが嵌合する第１嵌合溝９ｄが形成されている。この第１嵌合溝９ｄの内周面は、大径ボールベアリング４３の外輪４３ａに径方向で重なる位置に配置されている。 The fixed end portion 9a has an outer surface opposed to the front end surface side of the one end portion 2a of the camshaft 2, and a convex inner peripheral portion 11b, which will be described later, of the adapter 11 is fitted to a substantially central position of the outer surface. A first fitting groove 9d is formed. The inner peripheral surface of the first fitting groove 9d is disposed at a position overlapping the outer ring 43a of the large-diameter ball bearing 43 in the radial direction.
　円筒部９ｂは、図１に示すように、内部軸心方向に前記カムボルト１０の軸部１０ｂが挿入されるボルト挿入孔９ｃを有している。円筒部９ｂの外周側には、小径ボールベアリング３５とニードルベアリング３６が軸方向に並列に設けられている。 As shown in FIG. 1, the cylindrical portion 9 b has a bolt insertion hole 9 c into which the shaft portion 10 b of the cam bolt 10 is inserted in the inner axial direction. On the outer peripheral side of the cylindrical portion 9b, a small-diameter ball bearing 35 and a needle bearing 36 are provided in parallel in the axial direction.
　カムボルト１０は、図１に示すように、頭部１０ａの軸方向端面が小径ボールベアリング３５の内輪を軸方向から支持している。カムボルト１０の軸部１０ｂの外周には、カムシャフト２の端部から内部軸方向に形成された雌ねじ２ｃに螺着する雄ねじ１０ｃが形成されている。 In the cam bolt 10, as shown in FIG. 1, the axial end surface of the head 10 a supports the inner ring of the small-diameter ball bearing 35 from the axial direction. On the outer periphery of the shaft portion 10b of the cam bolt 10, a male screw 10c is formed that is screwed to the female screw 2c formed in the inner axial direction from the end portion of the cam shaft 2.
　アダプタ１１は、図１及び図４に示すように、一定の肉厚を有する円盤状の金属板をプレス成形によって縦断面ほぼクランク状に折曲形成され、フランジ状の外周部１１ａと、電動モータ１２方向へ突出した有底円筒状の内周部１１ｂと、から構成されている。 As shown in FIGS. 1 and 4, the adapter 11 is formed by bending a disk-shaped metal plate having a certain thickness into a substantially crank shape by press forming, and has a flange-shaped outer peripheral portion 11 a and an electric motor. A bottomed cylindrical inner peripheral portion 11b protruding in 12 directions.
　外周部１１ａは、外径が従動部材９の固定端部９ａの外径よりも僅かに大きく形成されて、電動モータ１２側の内側面の外周側が第１規制面として構成されている。この第１規制面は、大径ボールベアリング４３の内輪４３ｂの軸方向他端面に当接して軸方向外側への移動を規制するようになっている。 The outer peripheral portion 11a is formed so that the outer diameter is slightly larger than the outer diameter of the fixed end portion 9a of the driven member 9, and the outer peripheral side of the inner surface on the electric motor 12 side is configured as a first restricting surface. The first restricting surface is in contact with the other axial end surface of the inner ring 43b of the large-diameter ball bearing 43 to restrict the movement outward in the axial direction.
　外周部１１ａの外周面には、保持プレート８のストッパ凸部８ｂが係入するストッパ凹溝１１ｃが円周方向に沿って形成されている。このストッパ凹溝１１ｃは、円周方向へ所定長さの円弧状に形成され、この長さ範囲で回動したストッパ凸部８ｂの両側面８ｅ、８ｆが周方向の対向面にそれぞれ当接する。これによって、タイミングスプロケット１に対するカムシャフト２の最大進角側、あるいは最大遅角側の相対回転位置を機械的に規制するようになっている。 On the outer peripheral surface of the outer peripheral portion 11a, a stopper concave groove 11c into which the stopper convex portion 8b of the holding plate 8 is engaged is formed along the circumferential direction. The stopper groove 11c is formed in a circular arc shape having a predetermined length in the circumferential direction, and both side surfaces 8e and 8f of the stopper convex portion 8b rotated within this length range abut against the circumferential facing surfaces. As a result, the relative rotational position of the camshaft 2 relative to the timing sprocket 1 on the maximum advance angle side or the maximum retard angle side is mechanically restricted.
　アダプタ１１の内周部１１ｂは、電動モータ１２側に突出した有底円筒状の凸状に形成され、反対側の凹溝にカムシャフト２の一端部２ａが軸方向から嵌合している。また、アダプタ１１の中央位置には、前記カムボルト１０の軸部１０ｂが挿入する挿入孔１１ｄが貫通形成されている。 The inner peripheral portion 11b of the adapter 11 is formed in a bottomed cylindrical convex shape protruding toward the electric motor 12, and the one end portion 2a of the camshaft 2 is fitted in the opposite concave groove from the axial direction. Further, an insertion hole 11d through which the shaft portion 10b of the cam bolt 10 is inserted is formed in the center position of the adapter 11.
　内周部１１ｂは、前記従動部材９の固定端部９ａの前記第１嵌合溝９ｄ内に軸方向から圧入によって嵌合し、この嵌合した状態で、前記内周部１１ｂの先端壁が、カムボルト１０によってカムシャフト２の一端部２ａと従動部材９の固定端部９ａとの間に挟まれた状態で結合されている。 The inner circumferential portion 11b is fitted into the first fitting groove 9d of the fixed end portion 9a of the driven member 9 by press fitting from the axial direction, and in this fitted state, the tip wall of the inner circumferential portion 11b is The cam bolt 10 is coupled in a state of being sandwiched between one end 2 a of the camshaft 2 and the fixed end 9 a of the driven member 9.
　位相変更機構３は、従動部材９の円筒部９ｂの前端側に配置された電動モータ１２と、該電動モータ１２の回転速度を減速してカムシャフト２に伝達する減速機構１３と、から主として構成されている。 The phase changing mechanism 3 is mainly composed of an electric motor 12 disposed on the front end side of the cylindrical portion 9b of the driven member 9, and a speed reducing mechanism 13 that reduces the rotational speed of the electric motor 12 and transmits it to the camshaft 2. Has been.
　電動モータ１２は、図１に示すように、ブラシ付きのＤＣモータであって、タイミングスプロケット１と一体に回転するヨークであるモータハウジング１４と、該モータハウジング１４の内部に回転自在に設けられたモータ出力軸１５と、モータハウジング１４の内周面に固着されたステータであるそれぞれ円弧状の４つの永久磁石１６と、モータハウジング１４の前端部に固定された給電プレート１７と、を備えている。 As shown in FIG. 1, the electric motor 12 is a brushed DC motor, and is provided with a motor housing 14 that is a yoke that rotates integrally with the timing sprocket 1, and is rotatably provided inside the motor housing 14. A motor output shaft 15, four arc-shaped permanent magnets 16 each serving as a stator fixed to the inner peripheral surface of the motor housing 14, and a power feeding plate 17 fixed to the front end portion of the motor housing 14 are provided. .
　モータハウジング１４は、図１に示すように、鉄系金属材によって有底円筒状に形成され、外径がスプロケット本体１ａの外径と同じ大きさに形成されていると共に、後端側に仕切壁１４ａが一体に形成されている。 As shown in FIG. 1, the motor housing 14 is formed in a bottomed cylindrical shape with a ferrous metal material, has an outer diameter that is the same as the outer diameter of the sprocket body 1 a, and has a partition at the rear end side. The wall 14a is integrally formed.
　前記仕切壁１４ａは、円盤状に形成され、ほぼ中央に有する円筒状の延出部１４ｃの内周に軸挿入孔１４ｂが形成されている。また、前記仕切壁１４ａ外周部の各ボルト挿入孔１ｃ、８ｄと対応した位置には、前記各ボルト７の先端部が螺着する６つの雌ねじ孔１４ｄが周方向の等間隔位置に形成されており、これらに挿入、螺着した前記各ボルト７によって前記タイミングスプロケット１(内歯構成部５)と保持プレート８及びモータハウジング１４が軸方向から結合されている。 The partition wall 14a is formed in a disk shape, and a shaft insertion hole 14b is formed on the inner periphery of a cylindrical extension portion 14c having substantially the center. In addition, at the positions corresponding to the bolt insertion holes 1c and 8d on the outer peripheral portion of the partition wall 14a, six female screw holes 14d to which the tip portions of the bolts 7 are screwed are formed at equal intervals in the circumferential direction. The timing sprocket 1 (internal gear component 5), the holding plate 8 and the motor housing 14 are coupled in the axial direction by the bolts 7 inserted and screwed into these.
　モータ出力軸１５は、段差円筒状に形成されてアーマチュアとして機能し、軸方向のほぼ中央位置に形成された段差部を介してカムシャフト２側の大径部１５ａと、カバー部材４側の小径部１５ｂと、から構成されている。 The motor output shaft 15 is formed in a stepped cylindrical shape and functions as an armature, and has a large diameter portion 15a on the camshaft 2 side and a small diameter on the cover member 4 side through a stepped portion formed at a substantially central position in the axial direction. Part 15b.
　大径部１５ａは、外周に鉄心ロータ１８が固定されていると共に、回転軸方向の後端面に減速機構１３の一部を構成する偏心カムである偏心軸部３７が一体に結合されている。 The large-diameter portion 15a has an iron core rotor 18 fixed to the outer periphery, and an eccentric shaft portion 37 that is an eccentric cam constituting a part of the speed reduction mechanism 13 is integrally coupled to a rear end surface in the rotation axis direction.
　一方、小径部１５ｂは、外周に整流子であるコミュテータ２０が固定されている。このコミュテータ２０は、小径部１５ｂの外周面に圧入された円環部材２０ａの外周に設けられている。このコミュテータ２０は、導電材によって円環状に形成されて、前記鉄心ロータ１８の極数と同数に分割された各セグメントに後述のコイル１９の引き出されたコイル線の端末が電気的に接続されている。 On the other hand, the commutator 20 which is a commutator is fixed to the outer periphery of the small diameter portion 15b. This commutator 20 is provided in the outer periphery of the annular member 20a press-fit in the outer peripheral surface of the small diameter part 15b. This commutator 20 is formed in an annular shape by a conductive material, and ends of coil wires from which coils 19 to be described later are electrically connected to each segment divided into the same number as the number of poles of the iron core rotor 18. Yes.
　鉄心ロータ１８は、複数の磁極を持つ磁性材によって形成され、外周側がコイル１９のコイル線を巻回させるスロットを有するボビンとして構成されている。この鉄心ロータ１８は、内周部が前記モータ出力軸１５の段差部外周に軸方向へ位置決めされつつ固定されている。 The iron core rotor 18 is formed of a magnetic material having a plurality of magnetic poles, and the outer peripheral side is configured as a bobbin having a slot around which the coil wire of the coil 19 is wound. The iron core rotor 18 is fixed while the inner peripheral portion thereof is positioned in the axial direction on the outer periphery of the stepped portion of the motor output shaft 15.
　各永久磁石１６は、円周方向に所定隙間をもって配設されて全体が円筒状に形成され、円周方向に複数の磁極を有している。 Each permanent magnet 16 is disposed with a predetermined gap in the circumferential direction, is formed in a cylindrical shape as a whole, and has a plurality of magnetic poles in the circumferential direction.
　給電プレート１７は、図１に示すように、鉄系金属材からなる円板状の金属プレート部１７ａと、該金属プレート部１７ａの前後両側面にモールドされた円板状の樹脂部１７ｂと、から構成されている。 As shown in FIG. 1, the power feeding plate 17 includes a disk-shaped metal plate portion 17a made of an iron-based metal material, and disk-shaped resin portions 17b molded on both front and rear sides of the metal plate portion 17a. It is composed of
　金属プレート部１７ａは、前記樹脂部１７ｂに覆われていない外周部が前記モータハウジング１４の前端部内周に形成された円環段差状の凹溝にカシメによって位置決め固定されている。さらに金属プレート部１７ａの中央部には、モータ出力軸１５の小径部１５ｂなどが挿入される軸挿入孔１７ｃが貫通形成されている。また、金属プレート部１７ａは、前記軸挿入孔１７ｃの内周縁に連続した所定の位置に図外の２つの保持孔が打ち抜きにより形成されている。 The metal plate portion 17a is positioned and fixed by caulking in an annular stepped concave groove formed on the inner periphery of the front end portion of the motor housing 14 at an outer peripheral portion not covered with the resin portion 17b. Further, a shaft insertion hole 17c through which the small diameter portion 15b of the motor output shaft 15 and the like are inserted is formed through the central portion of the metal plate portion 17a. Further, the metal plate portion 17a is formed by punching two holding holes (not shown) at predetermined positions continuous to the inner peripheral edge of the shaft insertion hole 17c.
　また、給電プレート１７には、金属プレート部１７ａの各保持孔の内側に配置されて、樹脂部１７ｂの前端部に複数のリベットにより固定された銅製筒状の一対のブラシホルダ２３ａ、２３ｂと、該各ブラシホルダ２３ａ、２３ｂの内部に径方向に沿って摺動自在に収容配置された一対の切換用ブラシ２５ａ、２５ｂと、樹脂部１７ｂの前端部側に、それぞれの外側面を露出した状態でモールド固定された内外二重の給電用の各スリップリング２６ａ，２６ｂと、各切換用ブラシ２５ａ、２５ｂと各スリップリング２６ａ，２６ｂを電気的に接続する図外のハーネスと、が設けられている。 Further, the power feeding plate 17 is disposed inside each holding hole of the metal plate portion 17a, and a pair of copper cylindrical brush holders 23a and 23b fixed to the front end portion of the resin portion 17b by a plurality of rivets, Each of the brush holders 23a and 23b has a pair of switching brushes 25a and 25b accommodated and slidably disposed along the radial direction, and a front end portion side of the resin portion 17b with the respective outer surfaces exposed. The inner and outer double power supply slip rings 26a and 26b, which are fixed by molding, and the switching brushes 25a and 25b and the harnesses (not shown) for electrically connecting the slip rings 26a and 26b are provided. Yes.
　一対の切換用ブラシ２５ａ、２５ｂは、コイルスプリング２４ａ、２４ｂのばね力で円弧状の各先端面がコミュテータ２０の外周面に径方向から弾接している。 In the pair of switching brushes 25a and 25b, the arcuate tip surfaces are in elastic contact with the outer peripheral surface of the commutator 20 from the radial direction by the spring force of the coil springs 24a and 24b.
　モータ出力軸１５と偏心軸部３７は、カムボルト１０の軸部１０ｂの外周面に設けられた小径ボールベアリング３５と、従動部材９の円筒部９ｂの外周面に設けられて小径ボールベアリング３５の軸方向側部に配置されたニードルベアリング３６と、によって回転自在に支持されている。 The motor output shaft 15 and the eccentric shaft portion 37 are provided on the outer peripheral surface of the small diameter ball bearing 35 on the outer peripheral surface of the shaft portion 10 b of the cam bolt 10 and on the outer peripheral surface of the cylindrical portion 9 b of the driven member 9. It is rotatably supported by a needle bearing 36 disposed on the direction side portion.
　また、モータ出力軸１５の大径部１５ａの外周面とモータハウジング１４の延出部１４ｃの内周面との間には、小径なオイルシール３８が設けられている。このオイルシール３８は、電動モータ１２と減速機構１３との間をシールして減速機構１３の内部から電動モータ１２内へのオイル（潤滑油）のリークを阻止するようになっている。 A small-diameter oil seal 38 is provided between the outer peripheral surface of the large-diameter portion 15a of the motor output shaft 15 and the inner peripheral surface of the extending portion 14c of the motor housing 14. The oil seal 38 seals between the electric motor 12 and the speed reduction mechanism 13 to prevent leakage of oil (lubricating oil) from the inside of the speed reduction mechanism 13 into the electric motor 12.
　カバー部材４は、図１及び図２に示すように、ほぼ円盤状に形成されていると共に、モータハウジング１４の前端側、つまり給電プレート１７の前端側（給電プレート１７におけるモータ出力軸１５の回転軸方向のカムシャフト２と反対側）に対向して配置されている。カバー部材４は、円板プレート状のカバー本体２８と、該カバー本体２８の前端部を覆う合成樹脂製のキャップ部２９と、から構成されている。 As shown in FIGS. 1 and 2, the cover member 4 is formed in a substantially disk shape, and also has a front end side of the motor housing 14, that is, a front end side of the power feeding plate 17 (the rotation of the motor output shaft 15 in the power feeding plate 17). It is arranged opposite to the camshaft 2 in the axial direction. The cover member 4 includes a disc plate-shaped cover main body 28 and a synthetic resin cap portion 29 that covers the front end portion of the cover main body 28.
　カバー本体２８は、主として合成樹脂材によって所定の肉厚に形成されていると共に、内部には金属製の補強プレート２８ａがモールド固定されている。 The cover main body 28 is mainly formed of a synthetic resin material to a predetermined thickness, and a metal reinforcing plate 28a is molded and fixed inside.
　また、カバー本体２８は、図１及び図２に示すように、外周部の４箇所に円弧状のボス部２８ｂが設けられている。この各ボス部２８ｂには、ケース部材であるチェーンケース２２に固定されるボルトが挿入されるボルト挿入孔２８ｃが図外の金属製スリーブによってそれぞれ形成されている。 Further, as shown in FIGS. 1 and 2, the cover main body 28 is provided with arc-shaped boss portions 28b at four locations on the outer peripheral portion. In each boss portion 28b, a bolt insertion hole 28c into which a bolt fixed to the chain case 22 as a case member is inserted is formed by a metal sleeve (not shown).
　カバー本体２８は、前記各スリップリング２６ａ、２６ｂと軸方向から対向する位置に銅材からなる一対の角筒状のブラシホルダ３０ａ、３０ｂが軸方向に沿って固定されている。この各ブラシホルダ３０ａ、３０ｂの内部には、各先端面が各スリップリング２６ａ、２６ｂに摺接する一対の給電用ブラシ３１ａ、３１ｂが軸方向へ摺動自在に保持されている。前記各スリップリング２６ａ、２６ｂと給電用ブラシ３１ａ、３１ｂによって給電機構が構成されている。 In the cover body 28, a pair of rectangular tube-shaped brush holders 30a and 30b made of a copper material are fixed along the axial direction at positions facing the slip rings 26a and 26b in the axial direction. Inside each brush holder 30a, 30b, a pair of power supply brushes 31a, 31b whose tip surfaces are in sliding contact with the slip rings 26a, 26b are slidably held in the axial direction. Each of the slip rings 26a and 26b and the power supply brushes 31a and 31b constitute a power supply mechanism.
　また、カバー本体２８は、図１に示すように、ほぼ中央位置に窓孔３２が貫通形成されている。この窓孔３２は、円形状に形成されて、内径が後述する被検出部５１の先端部５１ｂが挿入可能に形成されている。 Further, as shown in FIG. 1, the cover main body 28 has a window hole 32 penetratingly formed at a substantially central position. The window hole 32 is formed in a circular shape so that the tip 51b of the detected portion 51 whose inner diameter will be described later can be inserted.
　また、この窓孔３２のモータ出力軸１５側の孔縁には、窓孔３２の内径よりも大きな大径溝３２ａが形成されている。この大径溝３２ａは、カバー部材４を電動モータ１２の前端側に組み付けた際に、後述する被検出部５１のフランジ部５１ｃが挿入される逃げ部として機能するようになっている。 Further, a large-diameter groove 32a larger than the inner diameter of the window hole 32 is formed at the hole edge of the window hole 32 on the motor output shaft 15 side. The large-diameter groove 32a functions as an escape portion into which a flange portion 51c of the detected portion 51 described later is inserted when the cover member 4 is assembled to the front end side of the electric motor 12.
　さらに、カバー本体２８は、キャップ部２９側の外端面のほぼ中央位置に有する矩形状の収容溝の内部には各給電用ブラシ３１ａ、３１ｂをスリップリング２６ａ、２６ｂ方向へ付勢する図外の一対の捩りコイルばねが収容されている。 Further, the cover main body 28 is not shown in the figure for urging the power supply brushes 31a and 31b in the direction of the slip rings 26a and 26b in the rectangular housing groove at the substantially central position of the outer end surface on the cap portion 29 side. A pair of torsion coil springs are accommodated.
　また、カバー本体２８の下端部には、図２に示すように、各給電用ブラシ３１ａ、３１ｂに図外のコントロールユニットを介して電源バッテリーから電流を供給する給電用コネクタ３３が一体に設けられている。 Further, as shown in FIG. 2, a power supply connector 33 for supplying current from a power supply battery to the power supply brushes 31a and 31b via a control unit (not shown) is integrally provided at the lower end of the cover body 28. ing.
　同じくカバー本体２８の下端部には、回転角度信号をコントロールユニットに出力する信号用コネクタ３４が給電用コネクタ３３と並行かつ径方向に沿って突設されている。 Similarly, a signal connector 34 for outputting a rotation angle signal to the control unit is provided at the lower end portion of the cover body 28 so as to protrude in parallel with the power supply connector 33 and in the radial direction.
　給電用コネクタ３３は、部分的にカバー本体２８の内部に埋設された導電材である図外の一対の端子片の各一端部がピグテールハーネスに接続されている。また、外部に露出した一対の他端部が、コントロールユニット側の図外の雌コネクタ端子に接続されるようになっている。 The power supply connector 33 is connected to the pigtail harness at one end of a pair of terminal pieces (not shown), which is a conductive material partially embedded in the cover body 28. Further, a pair of other end portions exposed to the outside are connected to female connector terminals (not shown) on the control unit side.
　信号用コネクタ３４は、カバー本体２８内に一部が埋設された導電材である複数の端子片の露出した各一端部３４ａが後述する角度センサ５０のプリント基板５５の集積回路５６に電気的に接続されていると共に、外部に露出した他端部３４ｂがコントロールユニット側の図外の雌コネクタ端子に接続されるようになっている。 The signal connector 34 is electrically connected to the integrated circuit 56 of the printed circuit board 55 of the angle sensor 50 described later at each exposed end portion 34a of a plurality of terminal pieces made of a conductive material partially embedded in the cover body 28. While being connected, the other end 34b exposed to the outside is connected to a female connector terminal (not shown) on the control unit side.
　キャップ部２９は、円盤プレート状に形成されて、外周縁に一体に形成されたフック状の係止凸部２９ａがカバー本体２８の外周部に形成された段差係止溝に軸方向から係止固定されている。 The cap portion 29 is formed in a disk plate shape, and a hook-shaped locking projection 29a formed integrally with the outer peripheral edge is locked in a step locking groove formed in the outer peripheral portion of the cover body 28 from the axial direction. It is fixed.
　モータ出力軸１５の小径部１５ｂとカバー本体２８との間には、モータ出力軸１５の回転角度位置を検出する回転角検出機構である角度センサ５０が設けられている。 Between the small diameter portion 15b of the motor output shaft 15 and the cover body 28, an angle sensor 50 that is a rotation angle detection mechanism for detecting the rotation angle position of the motor output shaft 15 is provided.
　この角度センサ５０は、電磁誘導型であって、図１に示すように、モータ出力軸１５の小径部１５ｂ内に固定された被検出部５１と、カバー本体２８のほぼ中央位置に固定されて、被検出部５１からの検出信号を受信する検出回路５２と、から構成されている。 The angle sensor 50 is of an electromagnetic induction type, and is fixed at a substantially central position of the detected part 51 and the cover body 28 fixed in the small diameter part 15b of the motor output shaft 15 as shown in FIG. , And a detection circuit 52 that receives a detection signal from the detected part 51.
　被検出部５１は、図２にも示すように、合成樹脂材からなるほぼ有底円筒状の支持部５１ａと、該支持部５１ａの軸方向の先端部５１ｂの底壁面に固定された３葉形状の３つの被検出ロータ５３と、支持部５１ａの後端部外周にモータ出力軸１５の小径部１５ｂの内部に圧入される円環状のフランジ部５１ｃが一体に設けられている。 As shown in FIG. 2, the detected portion 51 includes a substantially bottomed cylindrical support portion 51a made of a synthetic resin material, and three leaves fixed to the bottom wall surface of the tip portion 51b in the axial direction of the support portion 51a. The three to-be-detected rotors 53 and an annular flange portion 51c that is press-fitted into the small diameter portion 15b of the motor output shaft 15 are integrally provided on the outer periphery of the rear end portion of the support portion 51a.
　また、支持部５１ａは、フランジ部５１ｃよりも後端側の軸方向のほぼ中央位置に形成された円環状のシール溝にゴム材からなるオイルシール５４が嵌着固定されている。このオイルシール５４は、支持部５１ａの後端側のほぼ全体がモータ出力軸１５の小径部１５ｂ内に挿入された状態で、小径部１５ｂの内周面と先端部５１ｂ側との間をシールするようになっている。 Further, in the support portion 51a, an oil seal 54 made of a rubber material is fitted and fixed in an annular seal groove formed at a substantially central position in the axial direction on the rear end side of the flange portion 51c. The oil seal 54 seals between the inner peripheral surface of the small diameter portion 15b and the front end portion 51b side in a state where almost the entire rear end side of the support portion 51a is inserted into the small diameter portion 15b of the motor output shaft 15. It is supposed to be.
　被検出ロータ５３は、励起導体によって形成されて、支持部５１ａの先端部の前端面にオーム形状の３つの磁性材を円周方向の１２０°位置に配置されている。この被検出ロータ５３は、全体の外径が支持部５１ａの先端部５１ｂの外径とほぼ同じに形成されていると共に、該先端部５１ｂの前端面から露出した状態でモールド固定されている。 The to-be-detected rotor 53 is formed of an excitation conductor, and three ohmic magnetic materials are arranged at 120 ° in the circumferential direction on the front end surface of the front end portion of the support portion 51a. The rotor 53 to be detected is formed so that the entire outer diameter is substantially the same as the outer diameter of the front end portion 51b of the support portion 51a, and is fixed to the mold while being exposed from the front end surface of the front end portion 51b.
　フランジ部５１ｃは、支持部５１ａと同じく絶縁材の合成樹脂材によって一体に形成され、支持部５１ａの後端部が小径部１５ｂの内部に最大に挿入された際に、内側面が小径部１５ｂの先端縁に軸方向から当接してそれ以上の挿入を規制するようになっている。 The flange portion 51c is integrally formed of an insulating synthetic resin material like the support portion 51a, and when the rear end portion of the support portion 51a is inserted into the inside of the small diameter portion 15b at the maximum, the inner surface is the small diameter portion 15b. A further tip insertion is restricted by abutting on the tip edge of the lip from the axial direction.
　また、支持部５１ａは、フランジ部５１ｃを介してモータ出力軸１５の小径部１５ｂの先端から突出した先端部５１ｂの一部が、カバー本体２８の窓孔３２内に挿入配置されている。これによって、被検出ロータ５３が窓孔３２を介して検出回路５２の後述するプリント基板５５の受信コイルと励磁コイルに軸方向から微少クリアランスＣを介して対向配置されている。 Further, in the support portion 51a, a part of the tip portion 51b protruding from the tip of the small diameter portion 15b of the motor output shaft 15 through the flange portion 51c is inserted and arranged in the window hole 32 of the cover body 28. As a result, the rotor 53 to be detected is disposed so as to face the receiving coil and the exciting coil of the printed circuit board 55 (to be described later) of the detection circuit 52 through the window hole 32 through the minute clearance C from the axial direction.
　検出回路５２は、図１に示すように、長方形状の回路基板であるプリント基板５５と、該プリント基板５５の長手方向の一端部外面に設けられた集積回路(ＡＳＩＣ)５６と、該集積回路５６と同じ外面の他端部側に設けられた図外の受信コイル及び励磁コイルと、を備えている。 As shown in FIG. 1, the detection circuit 52 includes a printed circuit board 55 which is a rectangular circuit board, an integrated circuit (ASIC) 56 provided on the outer surface of one end portion in the longitudinal direction of the printed circuit board 55, and the integrated circuit. 56, a receiving coil and an exciting coil (not shown) provided on the other end side of the same outer surface.
　プリント基板５５は、受信コイルと励磁コイルが設けられた長手方向の一端部の両角部、つまり受信、励磁コイルを避けた両角部位置と、集積回路５６側の中央位置に３つの小さな位置決め用孔が貫通形成されている。 The printed circuit board 55 has three small positioning holes at both corners at one end in the longitudinal direction where the receiving coil and the exciting coil are provided, that is, at both corners avoiding the receiving and exciting coils, and at the central position on the integrated circuit 56 side. Is formed through.
　一方、カバー本体２８には、各位置決め用孔に係入してプリント基板５５を位置決めする３つの位置決め突起が一体に設けられている。このように、プリント基板５５が位置決めされることによって、被検出ロータ５３の中心と受信、励磁コイルの中心が位置決めされる。 On the other hand, the cover main body 28 is integrally provided with three positioning protrusions that engage with the positioning holes and position the printed circuit board 55. Thus, by positioning the printed circuit board 55, the center of the rotor 53 to be detected and the center of the receiving and exciting coils are positioned.
　また、プリント基板５５は、その外周部とカバー本体２８との間に充填された図外の接着剤によってカバー本体２８に固定されている。 Further, the printed circuit board 55 is fixed to the cover body 28 by an unillustrated adhesive filled between the outer peripheral portion and the cover body 28.
　また、プリント基板５５は、受信コイルと励磁コイルが設けられた一側面全体に絶縁材がコーティングされている。 Also, the printed board 55 is coated with an insulating material on the entire side surface where the receiving coil and the exciting coil are provided.
　検出部５１は、受信コイル及び励磁コイルと、被検出ロータ５３と受信コイルとの間のインダクタンスの変化を検出してモータ出力軸１５の回転角度を集積回路５６が検出する。つまり、励磁コイルと被検出ロータとの間に誘導電流が流れて、この電磁誘導作用によって集積回路５６がモータ出力軸１５の回転角度位置を検出して、この情報信号をコントロールユニットに出力するようになっている。 The detecting unit 51 detects a change in inductance between the receiving coil and the exciting coil and the detected rotor 53 and the receiving coil, and the integrated circuit 56 detects the rotation angle of the motor output shaft 15. That is, an induction current flows between the exciting coil and the rotor to be detected, and the integrated circuit 56 detects the rotational angle position of the motor output shaft 15 by this electromagnetic induction action, and outputs this information signal to the control unit. It has become.
　コントロールユニットは、図外のクランク角センサやエアーフローメータ、水温センサ、アクセル開度センサ、さらに角度センサ５０など各種のセンサ類からの情報信号に基づいて現在の機関運転状態を検出して、これに基づいて機関制御を行っている。また、コントロールユニットは、給電用ブラシ３１ａ、３１ｂや各スリップリング２６ａ，２６ｂ、切換用ブラシ２５ａ、２５ｂ、コミュテータ２０などを介して電動モータ１２のコイル１９に通電してモータ出力軸１５の回転制御を行っている。このモータ出力軸１５の回転力を、減速機構１３が減速してカムシャフト２のタイミングスプロケット１に対する相対回転位相を制御するようになっている。 The control unit detects the current engine operating state based on information signals from various sensors such as a crank angle sensor, an air flow meter, a water temperature sensor, an accelerator opening sensor, and an angle sensor 50 (not shown). Based on the engine control. The control unit also controls the rotation of the motor output shaft 15 by energizing the coil 19 of the electric motor 12 via the power supply brushes 31a and 31b, the slip rings 26a and 26b, the switching brushes 25a and 25b, the commutator 20, and the like. It is carried out. The speed reduction mechanism 13 decelerates the rotational force of the motor output shaft 15 to control the relative rotation phase of the camshaft 2 with respect to the timing sprocket 1.
　減速機構１３は、図１～図３に示すように、偏心回転運動を行う偏心回転体である偏心軸部３７と、該偏心軸部３７の外周に設けられた中径ボールベアリング３９と、該中径ボールベアリング３９の外周に設けられたローラ４０と、該ローラ４０を転動方向に保持しつつ径方向の移動を許容する保持器４１と、該保持器４１と一体の従動部材９と、から主として構成されている。 As shown in FIGS. 1 to 3, the speed reduction mechanism 13 includes an eccentric shaft portion 37 that is an eccentric rotating body that performs an eccentric rotational motion, a medium-diameter ball bearing 39 provided on the outer periphery of the eccentric shaft portion 37, A roller 40 provided on the outer periphery of the medium-diameter ball bearing 39, a holder 41 that allows the roller 40 to move in the rolling direction while holding the roller 40 in the rolling direction, and a driven member 9 that is integral with the holder 41; Is mainly composed of
　偏心軸部３７は、図１に示すように、円筒状に形成されて、外周面に形成されたカム面３７ａの回転軸心Ｙがモータ出力軸１５の回転軸心Ｘから径方向へ僅かに偏心している。 As shown in FIG. 1, the eccentric shaft portion 37 is formed in a cylindrical shape, and the rotational axis Y of the cam surface 37 a formed on the outer peripheral surface is slightly in the radial direction from the rotational axis X of the motor output shaft 15. Eccentric.
　中径ボールベアリング３９は、ニードルベアリング３６に対して径方向で全体がほぼオーバーラップする状態に配置され、内輪３９ａと外輪３９ｂ及び該両輪３９ａ、３９ｂとの間に介装されたボール３９ｃと、該ボール３９ｃを保持する図外のケージと、から構成されている。 The medium-diameter ball bearing 39 is disposed so as to substantially overlap the entire needle bearing 36 in the radial direction, and includes an inner ring 39a, an outer ring 39b, and a ball 39c interposed between the wheels 39a, 39b. And a cage (not shown) for holding the ball 39c.
　内輪３９ａは、偏心軸部３７の外周面に微小隙間をもって配置されている。これに対して、外輪３９ｂは、軸方向で固定されることなくフリーな状態になっている。つまり、この外輪３９ｂは、軸方向の電動モータ１２側の一端面がどの部位にも接触せず、また軸方向の他端面がこれに対向する保持器４１の背面との間に形成された微小なクリアランスを介してフリーな状態になっている。 The inner ring 39a is disposed on the outer peripheral surface of the eccentric shaft portion 37 with a minute gap. On the other hand, the outer ring 39b is in a free state without being fixed in the axial direction. In other words, the outer ring 39b has a minute end formed between the one end surface on the electric motor 12 side in the axial direction and no other part, and the other end surface in the axial direction is opposed to the back surface of the cage 41 facing the outer ring 39b. Through free clearance.
　外輪３９ｂは、外周面が図１にも示すように、各ローラ４０の外周面が転動自在に当接していると共に、この外周面と保持器４１のローラ保持部４１ｂの内面との間に円環状のクリアランスが形成されている。このクリアランスを介して中径ボールベアリング３９全体が、偏心軸部３７の偏心回転に伴って径方向へ移動可能、つまり偏心動可能になっている。 As shown in FIG. 1, the outer ring 39 b is in contact with the outer peripheral surface of each roller 40 so that it can roll, and between the outer peripheral surface and the inner surface of the roller holding portion 41 b of the cage 41. An annular clearance is formed. Through this clearance, the entire medium-diameter ball bearing 39 can move in the radial direction along with the eccentric rotation of the eccentric shaft portion 37, that is, can move eccentrically.
　この保持器４１は、図１～図３に示すように、固定端部９ａの外周部前端から前方へ断面ほぼＬ字形状に折曲形成されて、該固定端部９ａの外周部前端側に径方向に沿って延出した円環状の基部４１ａと、該基部４１ａの外端からほぼ軸直角方向へ延出した円筒状のローラ保持部４１ｂと、から主として構成されている。 As shown in FIGS. 1 to 3, the retainer 41 is bent in a substantially L-shaped cross section forward from the front end of the outer peripheral portion of the fixed end portion 9a, and is formed on the front end side of the outer peripheral portion of the fixed end portion 9a. It is mainly composed of an annular base portion 41a extending along the radial direction and a cylindrical roller holding portion 41b extending from the outer end of the base portion 41a in a direction substantially perpendicular to the axis.
　ローラ保持部４１ｂは、先端部が内歯構成部５やモータハウジング１４の仕切壁１４ａなどによって仕切られた円環凹状の収容空間を介して仕切壁１４ａ方向へ延出している。また、このローラ保持部４１ｂは、周方向のほぼ等間隔位置に複数のローラ４０をそれぞれ転動自在に保持するほぼ長方形状の複数のローラ保持孔４１ｃが周方向の等間隔位置に形成されている。このローラ保持孔４１ｃは、先端部側が閉塞されて前後方向に細長い長方形状に形成され、その全体の数(ローラ４０の数)が内歯構成部５の内歯５ａの全体の歯数よりも少なくなっている。このローラ４０の数と内歯５ａの全体の歯数よりも少なくすることによって、減速比を得るようになっている。 The roller holding portion 41b extends in the direction of the partition wall 14a through an annular concave accommodation space in which the tip portion is partitioned by the internal tooth constituent portion 5, the partition wall 14a of the motor housing 14, and the like. The roller holding portion 41b is formed with a plurality of substantially rectangular roller holding holes 41c at the circumferentially equidistant positions, each of which holds the plurality of rollers 40 so as to roll freely at substantially equidistant positions in the circumferential direction. Yes. The roller holding hole 41 c is formed in a rectangular shape elongated in the front-rear direction with the tip end side closed, and the total number thereof (number of rollers 40) is larger than the total number of teeth of the inner teeth 5 a of the inner tooth component 5. It is running low. By reducing the number of rollers 40 and the total number of teeth of the internal teeth 5a, the reduction ratio is obtained.
　各ローラ４０は、鉄系金属によって形成され、中径ボールベアリング３９の偏心動に伴って径方向へ移動しつつ内歯構成部５の内歯５ａに嵌入すると共に、保持器４１のローラ保持孔４１ｃの両側縁によって周方向にガイドされつつ径方向へ揺動運動するようになっている。 Each roller 40 is formed of an iron-based metal, and is fitted into the inner teeth 5a of the inner tooth component 5 while moving in the radial direction in accordance with the eccentric movement of the medium-diameter ball bearing 39. While being guided in the circumferential direction by both side edges of 41c, it swings in the radial direction.
　チェーンケース２２は、金属材である例えばアルミニウム合金材によって一体に形成されている。このチェーンケース２２は、図１に示すように、前端部が位相変更機構３の外周全体を覆う状態に配置されている。一方、図外の後端部が、シリンダヘッド０１と図外のシリンダブロックの前端側にタイミングスプロケット１に巻回された図外のタイミングチェーン全体を覆うように上下方向に沿って配置固定されている。 The chain case 22 is integrally formed of a metal material such as an aluminum alloy material. As shown in FIG. 1, the chain case 22 is arranged such that the front end covers the entire outer periphery of the phase change mechanism 3. On the other hand, the rear end portion (not shown) is arranged and fixed along the vertical direction so as to cover the entire timing chain (not shown) wound around the timing sprocket 1 on the cylinder head 01 and the front end side of the cylinder block (not shown). Yes.
　また、このチェーンケース２２は、外周部２２ａのカバー部材４側の前端面２２ｂに、前記カバー本体２８のカムシャフト２側の環状の内側面２８ｆが対向配置されている。チェーンケース２２は、カバー部材４側の前端側に雌ねじ孔２２ｄが形成されている。一方、カバー部材４は、各ボス部２８ｂに形成されたボルト挿入孔２８ｃを挿入して前記各雌ねじ孔２２ｄに螺着する固定要素である４本のボルト４４によってチェーンケース２２に締結固定されている。なお、固定要素としては、ボルト４４の他に、ビスやリベットなどであっても良い。 In the chain case 22, an annular inner side surface 28f on the camshaft 2 side of the cover body 28 is disposed opposite to the front end surface 22b on the cover member 4 side of the outer peripheral portion 22a. The chain case 22 has a female screw hole 22d formed on the front end side on the cover member 4 side. On the other hand, the cover member 4 is fastened and fixed to the chain case 22 by four bolts 44 which are fixing elements that are inserted into the bolt insertion holes 28c formed in the boss portions 28b and screwed into the female screw holes 22d. Yes. In addition to the bolt 44, the fixing element may be a screw or a rivet.
　さらに、このチェーンケース２２の前端面２２ｂとモータハウジング１４の内側面２８ｆとの間には、チェーンケース２２の内周面とモータハウジング１４の外周面との間をシールするシール部材であるオイルシール４２が介装されている。 Further, an oil seal that is a seal member that seals between the inner peripheral surface of the chain case 22 and the outer peripheral surface of the motor housing 14 between the front end surface 22b of the chain case 22 and the inner side surface 28f of the motor housing 14. 42 is interposed.
　なお、チェーンケース２２は、位相変更機構３全体を覆う形で軸方向に延びていると共に、後端側がシリンダヘッドあるいはシリンダブロックにボルト固定されている。 The chain case 22 extends in the axial direction so as to cover the entire phase change mechanism 3, and the rear end side is bolted to the cylinder head or the cylinder block.
　オイルシール４２は、図５及び図６Ａ，Ｂに示すように、ほぼ円環状に形成されて、外周側の固定部４５と、内周側のシール部４６とから構成されている。 As shown in FIGS. 5 and 6A and 6B, the oil seal 42 is formed in a substantially annular shape, and includes an outer peripheral fixing portion 45 and an inner peripheral seal portion 46.
　固定部４５は、薄肉な金属板、例えばアルミニウム合金材をプレス成形によって縦断面ほぼクランク状に折曲形成されている。この固定部４５は、外周側の円環部４５ａと、該円環部４５ａの内周縁に一体に有する円筒部４５ｂと、該円筒部４５ｂの前記円環部４５ａと軸方向反対側に形成された小径環部４５ｃと、を備えている。 The fixing portion 45 is formed by bending a thin metal plate, for example, an aluminum alloy material into a substantially crank-shaped longitudinal section by press molding. The fixing portion 45 is formed on the outer circumferential side of the annular portion 45a, the cylindrical portion 45b integrally formed on the inner peripheral edge of the annular portion 45a, and on the opposite side of the annular portion 45a of the cylindrical portion 45b in the axial direction. A small-diameter ring portion 45c.
　円環部４５ａは、その径方向幅Ｗがカバー本体２８の内側面２８ｆの径方向幅とほぼ同一に形成されている。また、この円環部４５ａは、前記各ボルト４４によってチェーンケース２２にカバー本体２８が結合された際に、前記チェーンケース２２の前端面２２ｂとカバー本体２８の内側面２８ｆとの間に挟まれた状態で固定されるようになっている。 The annular portion 45 a has a radial width W that is substantially the same as the radial width of the inner side surface 28 f of the cover body 28. The annular portion 45a is sandwiched between the front end surface 22b of the chain case 22 and the inner side surface 28f of the cover body 28 when the cover body 28 is coupled to the chain case 22 by the bolts 44. It is supposed to be fixed in the state.
　また、この円環部４５ａは、外周縁の４箇所に径方向へ突出した突出部４５ｄが設けられている。この各突出部４５ｄは、カバー本体２８の各ボス部２８ｂに対応して形成されてほぼ円弧状に形成されている。また、この各突出部４５ｄは、中央に前記ボルト４４の軸部４４ａが挿入される貫通孔であるボルト挿入孔４５ｅがそれぞれ貫通形成されている。 Further, the annular portion 45a is provided with protruding portions 45d protruding in the radial direction at four locations on the outer peripheral edge. Each projecting portion 45d is formed corresponding to each boss portion 28b of the cover main body 28 and is formed in a substantially arc shape. Each protrusion 45d is formed with a bolt insertion hole 45e, which is a through hole into which the shaft portion 44a of the bolt 44 is inserted, in the center.
　この各ボルト挿入孔４５ｅは、４つとも同じ内径ｄに形成されていると共に、この各内径ｄが前記ボルト４４の軸部４４ａの外径よりも大きく形成されて、内周縁と軸部４４ａの外周面との間に隙間が形成されている。つまり、ボルト挿入孔４５ｅの内径ｄは、前述したボルト４４が雌ねじ孔２２ｄに締結される前の状態では、オイルシール４２全体がボルト４４の軸部４４ａに対して径方向へ僅かながらも移動可能となる大きさに設定されている。 Each of the four bolt insertion holes 45e is formed to have the same inner diameter d, and each inner diameter d is formed to be larger than the outer diameter of the shaft portion 44a of the bolt 44. A gap is formed between the outer peripheral surface. That is, the inner diameter d of the bolt insertion hole 45e can be slightly moved in the radial direction with respect to the shaft portion 44a of the bolt 44 in the state before the bolt 44 is fastened to the female screw hole 22d. It is set to a size.
　つまり、オイルシール４２は、固定部４５が前記ボルト４４によってチェーンケース２２とカバー本体２８との間に挟まれた状態で結合される前には、前記各ボルト挿入孔４５ｅを介してカムシャフト２の軸直角方向（径方向）に沿って移動調整可能になっている。 That is, the oil seal 42 is connected to the camshaft 2 via the bolt insertion holes 45e before the fixing portion 45 is coupled by the bolts 44 while being sandwiched between the chain case 22 and the cover body 28. The movement can be adjusted along the direction perpendicular to the axis (radial direction).
　円筒部４５ｂは、その軸方向の長さＬが前記チェーンケース２２の外周部２２ａの軸方向のほぼ中央位置までの長さに形成されている。また、円筒部４５ｂは、その内径ｄ１がチェーンケース２２の外周部２２ａの内周面とモータハウジング１４の外周面との間の径方向隙間の大きさによって決定され、該径方向隙間内に円筒部４５ｂが位置するように任意に設定されている。前記円筒部４５ｂの長さＬは、固定部４５の固定位置とモータハウジング１４の軸方向の長さとの関係で自由に設定することが可能である。 The cylindrical portion 45b is formed such that its axial length L is approximately the center position of the outer peripheral portion 22a of the chain case 22 in the axial direction. Further, the inner diameter d1 of the cylindrical portion 45b is determined by the size of the radial gap between the inner peripheral surface of the outer peripheral portion 22a of the chain case 22 and the outer peripheral surface of the motor housing 14, and the cylindrical portion 45b is cylindrical within the radial clearance. It is arbitrarily set so that the portion 45b is located. The length L of the cylindrical portion 45b can be freely set according to the relationship between the fixing position of the fixing portion 45 and the axial length of the motor housing 14.
　小径環部４５ｃは、その径方向幅が前記シール部４６に適正に加硫接着される程度の大きさに形成されている。 The small-diameter ring portion 45c is formed in such a size that its radial width is appropriately vulcanized and bonded to the seal portion 46.
　円環状のシール部４６は、合成ゴム材によって断面ほぼＶ字形状に形成されて、軸方向一端側の基部４６ａが前記小径環部４５ｃに加硫接着によって一体的に固定されている。一方、他端側のＶ字状の凹部４６ｂは、前記基部４６ａを支点として径方向へ弾性変形可能に形成されて、内周縁が前記モータハウジング１４の外周面に対して径方向内側に向かって弾接している。また、この凹部４６ｂの外周には、該凹部４６ｂの内周部をモータハウジング１４の外周面に強制的に弾接させる円環状のバックアップスプリング５９が設けられている。 The annular seal portion 46 is formed of a synthetic rubber material so as to have a substantially V-shaped cross section, and a base portion 46a on one end side in the axial direction is integrally fixed to the small diameter ring portion 45c by vulcanization adhesion. On the other hand, the V-shaped concave portion 46b on the other end side is formed to be elastically deformable in the radial direction with the base portion 46a as a fulcrum, and the inner peripheral edge is directed radially inward with respect to the outer peripheral surface of the motor housing 14. It is in elastic contact. Further, an annular backup spring 59 is provided on the outer periphery of the recess 46 b to force the inner periphery of the recess 46 b to elastically contact the outer periphery of the motor housing 14.
　また、前記基部４６ａの内周には、モータハウジング１４の外周面に弾接するシールリップ４６ｃが一体に有しており、このシールリップ４６ｃと凹部４６ｂが協働してシール機能を発揮するようになっている。 A seal lip 46c that elastically contacts the outer peripheral surface of the motor housing 14 is integrally provided on the inner periphery of the base portion 46a, and the seal lip 46c and the recess 46b cooperate to exert a sealing function. It has become.
　円環部４５ａの両側面には、図５及び図７に示すように、一対のシールリング４７ａ、４７ｂが弾接配置されている。この各シールリング４７ａ、４７ｂは、それぞれが横断面円形状に形成されて、前記カバー本体２８の環状の内側面２８ｆに形成された第１シール溝２８ｇと、前記チェーンケース２２の外周部前端面２２ｂに形成された第２シール溝２２ｅにそれぞれ弾性的に収容配置されている。この各シールリング４７ａ、４７ｂによって、前記内側面２８ｆと外周部前端面２２ｂ及び円環部４５ａとの三者間がシールされて、外部から電動モータ１２内や各スリップリング２６ａ、２６ｂと給電用ブラシ３１ａ、３１ｂとの間へのオイルの侵入を抑制するようになっている。
〔シール部材の組み付け手順〕
　以下では、前記カバー本体２８とチェーンケース２２との間に前記オイルシール４２を組み付ける手順について説明する。 As shown in FIGS. 5 and 7, a pair of seal rings 47a and 47b are elastically arranged on both side surfaces of the annular portion 45a. Each of the seal rings 47a and 47b is formed in a circular shape in cross section, and includes a first seal groove 28g formed on the annular inner side surface 28f of the cover main body 28, and an outer peripheral front end surface of the chain case 22. Each of the second seal grooves 22e formed in 22b is elastically accommodated and disposed. The seal rings 47a and 47b seal the three sides of the inner side surface 28f, the outer peripheral front end surface 22b, and the annular portion 45a, and externally feed the electric motor 12 and the slip rings 26a and 26b to the power supply. The oil is prevented from entering between the brushes 31a and 31b.
[Assembly procedure of seal member]
Hereinafter, a procedure for assembling the oil seal 42 between the cover body 28 and the chain case 22 will be described.
　まず、図８に示すように、予めタイミングスプロケット１と電動モータ１２及び減速機構１３を、６本のボルト７によって結合して位相変更機構３をユニット化しておく。このユニット化された位相変更機構３を、カムボルト１０によってカムシャフト２の一端部２ａに結合する。 First, as shown in FIG. 8, the timing sprocket 1, the electric motor 12, and the speed reduction mechanism 13 are connected in advance by six bolts 7 to unitize the phase changing mechanism 3. This unitized phase change mechanism 3 is coupled to one end 2 a of the camshaft 2 by a cam bolt 10.
　次に、図９に示すように、位相変更機構３の外周にチェーンケース２２を配置すると共に、このチェーンケース２２を、図外のシリンダヘッドにボルトによって固定する。このとき、前記チェーンケース２２の外周部２２ａの前端面２２ｂの第２シール溝２２ｅ内にシールリング４７ｂを収容保持しておく。 Next, as shown in FIG. 9, a chain case 22 is disposed on the outer periphery of the phase change mechanism 3, and the chain case 22 is fixed to a cylinder head (not shown) with a bolt. At this time, the seal ring 47b is accommodated and held in the second seal groove 22e of the front end surface 22b of the outer peripheral portion 22a of the chain case 22.
　続いて、図１０に示すように、オイルシール４２をモータハウジング１４とチェーンケース２２との間に仮止め状態に保持する。 Subsequently, as shown in FIG. 10, the oil seal 42 is temporarily held between the motor housing 14 and the chain case 22.
　すなわち、オイルシール４２のシール部４６である凹部４６ｂとシールリップ４６ｃを、自身の弾性力を利用してモータハウジング１４の前端側から外周面を軸方向に沿って摺接させながら嵌挿する。この最大移動位置は、前記オイルシール４２の円環部４５ａが、前記チェーンケース２２のシールリング４７ｂに当接することによって規制される。 That is, the recess 46b and the seal lip 46c, which are the seal portions 46 of the oil seal 42, are inserted while sliding the outer peripheral surface along the axial direction from the front end side of the motor housing 14 using its own elastic force. This maximum movement position is regulated by the annular portion 45a of the oil seal 42 coming into contact with the seal ring 47b of the chain case 22.
　また、この最大に移動したオイルシール４２は、モータハウジング１４の外周面に対して自身の弾性反力によって支持されている。つまり、オイルシール４２は、アルミニウム合金材により軽量化された固定部４５とゴム材のシール部４６全体が自らの弾性反力でモータハウジング１４の外周面に支持されている。したがって、オイルシール４２は、自重によって重力方向下方側へずれることなく、その軸心がモータハウジング１４の回転軸心Ｘ（カムシャフト２の回転軸心）とほぼ同軸上になっている。このとき、前記オイルシール４２の各ボルト挿入孔４５ｅとチェーンケース２２の各雌ねじ孔２２ｄはほぼ合致した状態になっている。 Also, the oil seal 42 that has moved to the maximum is supported by its own elastic reaction force against the outer peripheral surface of the motor housing 14. In other words, the oil seal 42 is supported on the outer peripheral surface of the motor housing 14 by the elastic reaction force of the fixed portion 45 and the rubber seal 46 which are lightened by the aluminum alloy material. Therefore, the oil seal 42 does not shift downward in the direction of gravity due to its own weight, and its axis is substantially coaxial with the rotation axis X of the motor housing 14 (rotation axis of the camshaft 2). At this time, each bolt insertion hole 45e of the oil seal 42 and each female screw hole 22d of the chain case 22 are in a substantially matched state.
　その後、図１１に示すように、カバー部材４を、モータハウジング１４の前端側を覆う形でチェーンケース２２の前端側にオイルシール４２の固定部４５を介して配設する。このとき、カバー本体２８の内側面２８ｆの第１シール溝２８ｇにシールリング４７ａが収容配置されている。 Thereafter, as shown in FIG. 11, the cover member 4 is disposed on the front end side of the chain case 22 through the fixing portion 45 of the oil seal 42 so as to cover the front end side of the motor housing 14. At this time, the seal ring 47a is accommodated in the first seal groove 28g on the inner side surface 28f of the cover body 28.
　続いて、図５にも示すように、各ボルト４４の軸部４４ａを、カバー本体２８とオイルシール４２のそれぞれの各ボルト挿入孔２８ｃ、４５ｅに挿入して、チェーンケース２２の雌ねじ孔２２ｄに螺着して締結する。これによって、オイルシール４２は、固定部４５の円環部４５ａがカバー本体２８とチェーンケース２２との間に介装固定される。同時に、円環部４５ａの両側面に前記各シールリング４７ａ、４７ｂが弾接してシール機能を発揮すると共に、シール部４６によってモータハウジング１４とチェーンケース２２との間でシール機能を発揮する。 Subsequently, as shown in FIG. 5, the shaft portions 44 a of the respective bolts 44 are inserted into the respective bolt insertion holes 28 c and 45 e of the cover main body 28 and the oil seal 42 to be inserted into the female screw holes 22 d of the chain case 22. Screw and fasten. As a result, the annular portion 45 a of the fixing portion 45 is interposed and fixed between the cover main body 28 and the chain case 22 in the oil seal 42. At the same time, the seal rings 47a and 47b elastically contact with both side surfaces of the annular portion 45a to exert a sealing function, and the sealing portion 46 exhibits a sealing function between the motor housing 14 and the chain case 22.
　なお、位相変更機構３（従動部材９）をカムシャフト２に組み付ける際には、カムシャフト２の一端部に設けられた図外の位置決め用のピンを介して径方向及び周方向の位置決めがなされる。また、図２に示すように、チェーンケース２２の前端部に一対の位置決め用のピン(図示せず)が設けられている一方、カバー本体２８の２つのボス部２８ｂに一対の位置決め用の孔６２が形成されている。これら各位置決め用のピンに位置決め用の孔６２に軸方向から挿入することによって周方向及び径方向の位置決めがなされるようになっている。
〔本実施形態の作動〕
　以下、本実施形態におけるバルブタイミング制御装置の作動について簡単に説明すると、まず、機関のクランクシャフトの回転駆動に伴ってタイミングチェーンを介してタイミングスプロケット１が回転する。その回転力が内歯構成部５を介してモータハウジング１４に伝達されて、該モータハウジング１４が同期回転する。一方、内歯構成部５の回転力が、各ローラ４０から保持器４１及び従動部材９を経由してカムシャフト２に伝達される。これによって、カムシャフト２のカムが吸気弁を開閉作動させる。 When the phase changing mechanism 3 (driven member 9) is assembled to the camshaft 2, the positioning in the radial direction and the circumferential direction is performed via positioning pins (not shown) provided at one end of the camshaft 2. The As shown in FIG. 2, a pair of positioning pins (not shown) are provided at the front end of the chain case 22, while a pair of positioning holes are formed in the two bosses 28 b of the cover body 28. 62 is formed. Positioning in the circumferential direction and the radial direction is performed by inserting these positioning pins into the positioning holes 62 from the axial direction.
[Operation of this embodiment]
Hereinafter, the operation of the valve timing control device in the present embodiment will be briefly described. First, the timing sprocket 1 rotates through the timing chain in accordance with the rotational drive of the crankshaft of the engine. The rotational force is transmitted to the motor housing 14 via the internal tooth component 5, and the motor housing 14 rotates synchronously. On the other hand, the rotational force of the internal tooth component 5 is transmitted from each roller 40 to the camshaft 2 via the cage 41 and the driven member 9. As a result, the cam of the camshaft 2 opens and closes the intake valve.
　機関始動後の所定の機関運転時には、コントロールユニットからの制御電流が給電用ブラシ３１ａ、３１ｂや各スリップリング２６ａ，２６ｂなどを介して電動モータ１２のコイル１９に通電されてモータ出力軸１５が回転駆動される。この回転力が減速機構１３を介してカムシャフト２に対し減速されて伝達される。 During a predetermined engine operation after the engine is started, a control current from the control unit is energized to the coil 19 of the electric motor 12 through the power supply brushes 31a and 31b, the slip rings 26a and 26b, and the motor output shaft 15 rotates. Driven. This rotational force is decelerated and transmitted to the camshaft 2 via the deceleration mechanism 13.
　これにより、カムシャフト２は、タイミングスプロケット１に対して正逆相対回転して相対回転位相が変換されて、吸気弁の開閉タイミングを進角側あるいは遅角側に変換制御するのである。 As a result, the camshaft 2 is rotated forward and backward relative to the timing sprocket 1 and the relative rotational phase is converted, so that the opening / closing timing of the intake valve is controlled to be advanced or retarded.
　タイミングスプロケット１に対するカムシャフト２の正逆相対回転の最大位置規制(角度位置規制)は、ストッパ凹溝１１ｃの各対向面１１ｅ、１１ｆのいずれか一方が、ストッパ凸部８ｂの各側面８ｅ、８ｆの一方に当接することによって行われる。これによって、吸気弁の開閉タイミングが進角側あるいは遅角側へ最大に変換されて、機関の燃費や出力の向上が図れる。 The maximum position restriction (angular position restriction) of the forward and reverse relative rotation of the camshaft 2 with respect to the timing sprocket 1 is such that either one of the opposing surfaces 11e, 11f of the stopper groove 11c is the respective side surface 8e, 8f of the stopper convex portion 8b. This is done by contacting one of the two. As a result, the opening / closing timing of the intake valve is converted to the maximum on the advance side or the retard side, and the fuel efficiency and output of the engine can be improved.
　また、電動モータ１２のモータ出力軸１５の回転に伴って角度センサ５０の被検出部５１が回転すると、検出回路５２との間の誘導電流が流れ、この電磁誘導作用によって集積回路５６がモータ出力軸１５の回転角度を検出して、この検出信号によってコントロールユニットにおいてモータ出力軸１５の現在の回転角度位置を検出する。この回転角度位置とクランクシャフトとの回転位置によってコントロールユニットが電動モータ１２に回転駆動信号を出力して、現在の機関運転状態に応じてクランクシャフトに対するカムシャフト２の相対回転位相を精度良く制御するようになっている。 Further, when the detected portion 51 of the angle sensor 50 rotates with the rotation of the motor output shaft 15 of the electric motor 12, an induced current flows between the detection circuit 52 and the integrated circuit 56 outputs the motor output by this electromagnetic induction action. The rotation angle of the shaft 15 is detected, and the current rotation angle position of the motor output shaft 15 is detected in the control unit by this detection signal. The control unit outputs a rotational drive signal to the electric motor 12 according to the rotational angle position and the rotational position of the crankshaft, and accurately controls the relative rotational phase of the camshaft 2 with respect to the crankshaft according to the current engine operating state. It is like that.
　そして、本実施形態では、前記オイルシール４２は、従来技術のように、固定用基部をチェーンケース２２の内周面に圧入固定させるのではなく、固定部４５をカバー本体２８とチェーンケース２２との間に挟まれた状態で固定するようにした。このため、前述したオイルシール４２は、固定部４５がチェーンケース２２とカバー本体２８との間に組み付け固定される前は、各ボルト挿入孔４５ｅを介して全体に径方向へ移動可能になっている。つまり、モータハウジング１４の外周面に組み付けられたシール部４６の弾性力によってオイルシール４２全体がフロート状態になる。 In the present embodiment, the oil seal 42 does not press-fit and fix the fixing base portion to the inner peripheral surface of the chain case 22 as in the prior art, but the fixing portion 45 is connected to the cover body 28 and the chain case 22. It was made to fix in the state pinched | interposed between. For this reason, before the fixing part 45 is assembled and fixed between the chain case 22 and the cover main body 28, the oil seal 42 described above can be moved in the radial direction as a whole via the bolt insertion holes 45e. Yes. That is, the entire oil seal 42 is floated by the elastic force of the seal portion 46 assembled to the outer peripheral surface of the motor housing 14.
　したがって、オイルシール４２は、その軸心Ｚがシール部４６の弾性反力によってモータハウジング１４の回転軸心Ｘと自動的に同軸上に配置される（自動調心）。このため、オイルシール４２は、固定部４５がカバー本体２８とチェーンケース２２との間でボルト４４によって挟まれて固定された状態において、シール部４６の凹部４６ｂとシールリップ４６ｃの全体をモータハウジング１４の外周面に緊密に当接させることが可能になる。つまり、モータハウジング１４の軸心Ｘとオイルシール４２の軸心Ｚとの同軸性が確保される。 Therefore, the axis Z of the oil seal 42 is automatically arranged coaxially with the rotational axis X of the motor housing 14 by the elastic reaction force of the seal portion 46 (automatic alignment). Therefore, in the state where the fixing portion 45 is sandwiched and fixed between the cover main body 28 and the chain case 22 by the bolts 44, the oil seal 42 is configured such that the entire recess 46b and the seal lip 46c of the sealing portion 46 are disposed in the motor housing. 14 can be brought into close contact with the outer peripheral surface. That is, the coaxiality between the axis X of the motor housing 14 and the axis Z of the oil seal 42 is ensured.
　よって、オイルシール４２による安定かつ良好なシール機能が発揮される。 Therefore, a stable and good sealing function by the oil seal 42 is exhibited.
　しかも、オイルシール４２の円環部４５ａの両側面に、前記一対のシールリング４７ａ、４７ｂが挟まれた状態で弾接していることから、チェーンケース２２やカバー部材４と位相変更機構３との間のシール機能も有効に発揮されて、外部から電動モータ１２などの内部へのオイルの侵入を抑制することができる。このように、カムシャフトの回転軸方向から一対のシールリング４７ａ、４７ｂで挟むことで、シールリング４７ａ、４７ｂの弾性力がオイルシール４２の軸心Ｚとの同軸性へ影響することが抑制される。 Moreover, since the pair of seal rings 47a and 47b are in elastic contact with both side surfaces of the annular portion 45a of the oil seal 42, the chain case 22 and the cover member 4 and the phase change mechanism 3 In addition, the sealing function between the two is effectively exhibited, and the intrusion of oil from the outside to the inside of the electric motor 12 or the like can be suppressed. In this way, the elastic force of the seal rings 47a and 47b is prevented from affecting the coaxiality with the axis Z of the oil seal 42 by being sandwiched between the pair of seal rings 47a and 47b from the rotational axis direction of the camshaft. The
　したがって、前記オイルシール４２のモータハウジング１４に対する同軸性と相俟って、オイルシール４２による全体のシール機能を効果的に発揮できる。 Therefore, combined with the coaxiality of the oil seal 42 with respect to the motor housing 14, the entire sealing function by the oil seal 42 can be effectively exhibited.
　また、オイルシール４２は、固定部４５が薄肉板状のアルミニウム合金材で形成されて十分に軽量化が図られているから、シール部４６をモータハウジング１４の外周面に組み付けた際の全体荷重を、シール部４６の弾性反力によって安定して支持することができる。つまり、オイルシール４２は、全体の荷重によってシール部４６の重力方向の上側の一部が撓み変形することなく、円環の原形状を維持することができるので、モータハウジング１４との同軸性を確保することができる。 In addition, since the oil seal 42 is formed of a thin plate-like aluminum alloy material so that the oil seal 42 is sufficiently lightened, the entire load when the seal portion 46 is assembled to the outer peripheral surface of the motor housing 14 is achieved. Can be stably supported by the elastic reaction force of the seal portion 46. That is, the oil seal 42 can maintain the original shape of the ring without bending and deforming the upper part in the gravity direction of the seal portion 46 due to the entire load, so that the coaxiality with the motor housing 14 can be maintained. Can be secured.
　なお、固定部４５は、アルミニウム合金材以外に、軽量化が図れるチタンや硬質樹脂材などによって形成することも可能である。 Note that the fixing portion 45 can be formed of titanium or a hard resin material that can be reduced in weight in addition to the aluminum alloy material.
　また、本実施形態では、前述のように、角度センサ５０の被検出部５１の先端部５１ｂが、カバー部材４のカバー本体２８に形成された窓孔３２内に挿入配置されていることから、この挿入量の分だけ装置の軸方向の長さを短くすることができる。 In the present embodiment, as described above, the tip 51b of the detected portion 51 of the angle sensor 50 is inserted and disposed in the window hole 32 formed in the cover main body 28 of the cover member 4. The axial length of the apparatus can be shortened by the amount of insertion.
　この結果、バルブタイミング制御装置のエンジンルーム内への搭載性が向上する。特に、窓孔３２を貫通形成したことから、装置の軸方向の長さをさらに短くすることができる。 As a result, the mountability of the valve timing control device in the engine room is improved. In particular, since the window hole 32 is formed so as to penetrate therethrough, the axial length of the apparatus can be further shortened.
　また、本実施形態では、被検出部５１の先端部５１ｂが、カバー部材４のカバー本体２８に形成された窓孔３２内に挿入配置されているが、先端部５１ｂが窓孔３２に対向していれば良く、例えば、窓孔３２の近傍に設けても良い。また、窓孔３２がない場合は、カバー本体２８と被検出部５１の先端部５１ｂとの間のクリアランスを製造誤差や内燃機関の振動などの影響を考慮して所定量設定しておく必要があるが、窓孔３２が存在することによって、カバー本体２８の内面と被検出部５１の先端部５１ｂと間を考慮しなくて良いため、装置の軸方向の長さを短くすることができる。 In the present embodiment, the tip 51b of the detected part 51 is inserted into the window hole 32 formed in the cover main body 28 of the cover member 4, but the tip 51b faces the window hole 32. For example, it may be provided near the window hole 32. Further, when there is no window hole 32, it is necessary to set a predetermined amount of clearance between the cover main body 28 and the tip end portion 51b of the detected portion 51 in consideration of the influence of manufacturing error, vibration of the internal combustion engine, and the like. However, since the window hole 32 is present, it is not necessary to consider the space between the inner surface of the cover main body 28 and the distal end portion 51b of the detected portion 51, so that the axial length of the apparatus can be shortened.
　また、窓孔３２の内側孔縁に形成された大径溝３２ａに被検出部５１のフランジ部５１ｃを嵌入させることによって、この嵌入分だけ被検出部５１の先端部５１ｂを窓孔３２の奥深くまで挿入できるので、装置の軸方向の長さをさらに短くすることができる。 Further, by inserting the flange portion 51 c of the detected portion 51 into the large-diameter groove 32 a formed at the inner hole edge of the window hole 32, the tip end portion 51 b of the detected portion 51 is deeply inserted into the window hole 32 by this amount. Therefore, the axial length of the apparatus can be further shortened.
　しかも、先端部５１ｂの各被検出ロータ５３が、樹脂材などの介在物を介さずに微小クリアランスＣを介して直接的に受信コイルと励磁コイルに対峙していることから、角度センサ５０の出力を高めることができるので、モータ出力軸１５の回転検出精度の向上が図れる。 In addition, since each detected rotor 53 at the tip 51b directly faces the receiving coil and the exciting coil through the minute clearance C without involving an inclusion such as a resin material, the output of the angle sensor 50 Therefore, the rotation detection accuracy of the motor output shaft 15 can be improved.
　また、本実施形態では、被検出部５１の先端部５１ｂが窓孔３２内に挿入配置されて、被検出ロータ５３の位置が各スリップリング２６ａ、２６ｂと給電用ブラシ３１ａ、３１ｂとの摺接位置よりも外側(キャップ部２９側)にオフセット配置されていることから、被検出ロータ５３ａ～５３ｃが窓孔３２の内周面に覆われた状態になる。したがって、給電用ブラシ３１ａ、３１ｂと各スリップリング２６ａ、２６ｂとの摺動時に発生した金属摩耗粉の被検出ロータ５３への付着を十分に抑制することができる。 In the present embodiment, the tip 51b of the detected portion 51 is inserted and arranged in the window hole 32, and the position of the detected rotor 53 is in sliding contact with the slip rings 26a and 26b and the power supply brushes 31a and 31b. Since the rotor is offset from the position (on the cap portion 29 side), the detected rotors 53a to 53c are covered with the inner peripheral surface of the window hole 32. Therefore, it is possible to sufficiently suppress the metal wear powder generated during sliding between the power feeding brushes 31a and 31b and the slip rings 26a and 26b from adhering to the rotor 53 to be detected.
　この結果、斯かる金属摩耗粉の影響による角度センサ５０の回転検出精度の低下を抑制することができると共に、耐久性の向上が図れる。
〔第２実施形態〕
　図１２は第２実施形態を示し、前記シールリング４７ａ、４７ｂを、オイルシール４２の固定部４５の両側面に合成ゴム材を加硫接着によって固着している。このシールリング４７ａ、４７ｂは、断面ほぼ三角形状に形成されて、鋭角状の各先端部４７ｃ、４７ｄが前記カバー本体２８の内側面２８ｆとチェーンケース２２の外周部２２ａの前端面２２ｂに軸方向から弾接している。 As a result, it is possible to suppress a decrease in rotation detection accuracy of the angle sensor 50 due to the influence of such metal wear powder, and it is possible to improve durability.
[Second Embodiment]
FIG. 12 shows a second embodiment, in which the seal rings 47a and 47b are fixed to both side surfaces of the fixing portion 45 of the oil seal 42 by vulcanization adhesion. The seal rings 47a and 47b are formed to have a substantially triangular cross section, and each of the acute-angled tip portions 47c and 47d is axially connected to the inner side surface 28f of the cover body 28 and the front end surface 22b of the outer peripheral portion 22a of the chain case 22. It is touching from.
　この実施形態によれば、各シールリング４７ａ、４７ｂの鋭角状の先端部４７ｃ、４７ｄが、内側面２８ｆと前端面２２ｂに弾接することから、各先端部４７ｃ、４７ｄの撓み変形が大きくなって、シール機能をさらに効果的に発揮できる。
〔第３実施形態〕
　図１３は第３実施形態を示し、第２実施形態と同じく、前記シールリング４７ａ、４７ｂをオイルシール４２の固定部４５の両側面に合成ゴム材を加硫接着によって固着しているが、それぞれの横断面形状がほぼ四角形状に形成されている。これらの先端部４７ｃ、４７ｄが前記カバー本体２８の内側面２８ｆとチェーンケース２２の外周部２２ａの前端面２２ｂに軸方向から面接触で弾接している。 According to this embodiment, since the acute-angled tip portions 47c and 47d of the seal rings 47a and 47b are in elastic contact with the inner side surface 28f and the front end surface 22b, the bending deformation of the tip portions 47c and 47d is increased. The sealing function can be exhibited more effectively.
[Third Embodiment]
FIG. 13 shows a third embodiment. As in the second embodiment, the synthetic rubber material is fixed to both side surfaces of the fixing portion 45 of the oil seal 42 by the vulcanization adhesion. The cross-sectional shape of is substantially square. These front end portions 47c and 47d are in elastic contact with the inner side surface 28f of the cover main body 28 and the front end surface 22b of the outer peripheral portion 22a of the chain case 22 by surface contact from the axial direction.
　このように、各先端面実施形態によれば、各シールリング４７ａ、４７ｂの平坦な先端部４７ｃ、４７ｄが、内側面２８ｆと前端面２２ｂに面接触で弾接することからシール性能が良好になる。
〔第４実施形態〕
　図１４は第４実施形態を示し、前記各給電用ブラシ３１ａ、３１ｂと各スリップリング２６ａ、２６ｂの配置を変更すると共に、オイルシール４２の構造を変更したものである。 Thus, according to each front end surface embodiment, since the flat front end portions 47c and 47d of the seal rings 47a and 47b are elastically contacted with the inner side surface 28f and the front end surface 22b by surface contact, the sealing performance is improved. .
[Fourth Embodiment]
FIG. 14 shows a fourth embodiment in which the arrangement of the power supply brushes 31a and 31b and the slip rings 26a and 26b is changed and the structure of the oil seal 42 is changed.
　すなわち、各スリップリング２６ａ、２６ｂは、モータハウジング１４の前端部の段差部に設けられた非磁性材からなる円環部材４８の外周筒状部４８ａの外周面にモールド固定されている。 That is, the slip rings 26 a and 26 b are fixed to the outer peripheral surface of the outer peripheral cylindrical portion 48 a of the annular member 48 made of a nonmagnetic material provided at the step portion of the front end portion of the motor housing 14.
　各給電用ブラシ３１ａ、３１ｂは、カバー部材４のカバー本体２８の外周部に径方向に沿って設けられた給電用コネクタ４９の内部に重力方向に沿って設けられている。なお、各給電用ブラシ３１ａ、３１ｂは、ばね部材である図外のコイルスプリングのばね力によって各スリップリング２６ａ、２６ｂ方向へ径方向から弾接している。また、給電用コネクタ４９の内部には、一端部が各給電用ブラシ３１ａ、３１ｂと電気的に接続された一対の端子５８が設けられている。この各端子５８の他端部は図外の雄コネクタを介してコントロールユニットに接続されている。 Each of the power supply brushes 31a and 31b is provided along the gravity direction inside a power supply connector 49 provided along the radial direction on the outer periphery of the cover body 28 of the cover member 4. The power supply brushes 31a and 31b are elastically contacted in the radial direction in the direction of the slip rings 26a and 26b by the spring force of a coil spring (not shown) which is a spring member. In addition, a pair of terminals 58 whose one ends are electrically connected to the power supply brushes 31 a and 31 b are provided inside the power supply connector 49. The other end of each terminal 58 is connected to the control unit via a male connector (not shown).
　オイルシール４２は、固定部４５が折曲されることなく平坦な円板状に形成されて、該固定部４５がカバー本体２８の内側面２８ｆとチェーンケース２２の前端面２２ｂとの間に挟まれている。 The oil seal 42 is formed in a flat disk shape without the fixing portion 45 being bent, and the fixing portion 45 is sandwiched between the inner side surface 28f of the cover body 28 and the front end surface 22b of the chain case 22. It is.
　また、カバー本体２８とチェーンケース２２は、第１実施形態と同じく外周部の４つのボス部２８ｂとチェーンケース２２の前端部に形成されたボルト挿入孔２８ｃと雌ねじ孔２２ｄに挿入螺着するボルト４４によって軸方向から結合されている。オイルシール４２は、同じく固定部４５の円環部４５ａの外周の４つの突出部４５ｄに有する各ボルト挿入孔４５ｅに径方向の隙間を介して挿入した前記ボルト４４によって各ボス部２８ｂとチェーンケース２２の前端面の間に挟まれた状態で固定されている。 Further, the cover main body 28 and the chain case 22 are, as in the first embodiment, the four boss portions 28b on the outer peripheral portion, the bolt insertion holes 28c formed in the front end portion of the chain case 22, and the bolts inserted and screwed into the female screw holes 22d. 44 is connected from the axial direction. The oil seal 42 is connected to each boss 28b and the chain case by the bolts 44 inserted through the radial gaps in the bolt insertion holes 45e of the four protrusions 45d on the outer periphery of the annular part 45a of the fixing part 45. It is being fixed in the state pinched | interposed between 22 front-end surfaces.
　固定部４５の内周に加硫接着されたシール部４６は、凹部４６ｂがバックアップスプリング５９によってモータハウジング１４の外周面に弾接している。また、基部４６ａの内周には、前記モータハウジング１４の外周面に弾接する２つのシールリップ４６ｃ、４６ｄが一体に設けられている。なお、固定部４５は、薄板円板状のアルミニウム合金材によって形成されていることは第１実施形態と同じである。 The seal portion 46 vulcanized and bonded to the inner periphery of the fixed portion 45 has a recess 46 b elastically contacting the outer peripheral surface of the motor housing 14 by a backup spring 59. In addition, two seal lips 46c and 46d that elastically contact the outer peripheral surface of the motor housing 14 are integrally provided on the inner periphery of the base 46a. Note that the fixing portion 45 is formed of a thin disc-shaped aluminum alloy material, as in the first embodiment.
　また、カバー本体２８の内側面２８ｆに形成された第１シール溝内にシールリング４７ａが収容配置されており、この一つのシールリング４７ａによって内側面２８ｆと固定部４５との間をシールするようになっている。 Further, a seal ring 47a is accommodated in the first seal groove formed on the inner side surface 28f of the cover main body 28, and the space between the inner side surface 28f and the fixing portion 45 is sealed by this one seal ring 47a. It has become.
　したがって、この実施形態も第１実施形態と同じく、オイルシール４２を、シール部４６を介してモータハウジング１４の外周面に組み付けた際に、シール部４６の弾性反力によって原形状が維持される。このため、オイルシール４２とモータハウジング１４の同軸性が確保されて、シール部４６全体をモータハウジング１４の外周面に緊密に当接させることが可能になる。よって、オイルシール４２による安定かつ良好なシール機能を発揮させることができる。 Therefore, this embodiment also maintains the original shape by the elastic reaction force of the seal portion 46 when the oil seal 42 is assembled to the outer peripheral surface of the motor housing 14 via the seal portion 46 as in the first embodiment. . For this reason, the coaxiality of the oil seal 42 and the motor housing 14 is ensured, and the entire seal portion 46 can be brought into close contact with the outer peripheral surface of the motor housing 14. Therefore, a stable and good sealing function by the oil seal 42 can be exhibited.
　また、この実施形態では、２つのシールリップ４６ｃ、４６ｄによって二重にシールすることができるので、シール性能の向上が図れると共に、シール部４６の原形状をさらに維持することが可能になる。これによって、シール機能をさらに発揮することが可能になる。 Further, in this embodiment, since the two sealing lips 46c and 46d can perform double sealing, the sealing performance can be improved and the original shape of the sealing portion 46 can be further maintained. This makes it possible to further exhibit a sealing function.
　さらに、凹部４６ｂを、バックアップスプリング５９によって強制的にモータハウジング１４の外周面に押し付けるので、この点でもオイルシール４２とモータハウジング１４の同軸性をさらに得ることができる。 Further, since the recess 46b is forcibly pressed against the outer peripheral surface of the motor housing 14 by the backup spring 59, the coaxiality between the oil seal 42 and the motor housing 14 can be further obtained in this respect.
　固定部４５を折曲することなく平坦なストレート状に形成したことから、その成形作業が容易になる。 Since the fixing portion 45 is formed into a flat straight shape without being bent, the molding operation is facilitated.
　各給電用ブラシ３１ａ、３１ｂを、モータハウジング１４の径方向に沿って配置したことから、カバー部材４を含めた装置全体の軸方向の長さを一層短尺化することができる。 Since the power supply brushes 31a and 31b are arranged along the radial direction of the motor housing 14, the axial length of the entire apparatus including the cover member 4 can be further shortened.
　なお、本実施形態では、電動モータ１２のモータ出力軸１５の回転位置を検出する回転検出機構として、前記各実施形態に用いられた電磁誘導型ではなく、別異の回転検出機構が用いられている。また、前記モータ出力軸１５の内部には、減速機構１３側から電動モータ１２方向へのオイルの流入を阻止する栓体６０が圧入固定されている。 In this embodiment, a different rotation detection mechanism is used as a rotation detection mechanism for detecting the rotation position of the motor output shaft 15 of the electric motor 12 instead of the electromagnetic induction type used in the above embodiments. Yes. In addition, a plug body 60 that press-fits oil from the speed reduction mechanism 13 side toward the electric motor 12 is press-fitted and fixed inside the motor output shaft 15.
　本発明は、前記各実施形態の構成に限定されるもではなく、例えば、オイルシール４２の各突出部４５ｄやカバー本体２８のボス部２８ｂの数を、機関の仕様や大きさなどによって増減することも可能である。 The present invention is not limited to the configuration of each of the above-described embodiments. For example, the number of the protrusions 45d of the oil seal 42 and the number of the bosses 28b of the cover main body 28 are increased or decreased depending on the specifications or size of the engine. It is also possible.
　また、オイルシール４２の各突出部４５ｄの内周縁と各ボルト４４の軸部４４ａの外周面との間の隙間は、オイルシール４２の径方向の移動を許容できるのであれば、その大きさを任意に変更することができる。 Further, the gap between the inner peripheral edge of each projecting portion 45d of the oil seal 42 and the outer peripheral surface of the shaft portion 44a of each bolt 44 should be of a size if the movement of the oil seal 42 in the radial direction can be permitted. It can be changed arbitrarily.
　駆動回転体としては、前記タイミングスプロケットの他に、タイミングプーリなどであっても良い。 The drive rotor may be a timing pulley in addition to the timing sprocket.
　なお、本実施例では、ケース部材を、チェーンケース２２としているが、例えば、チェーンケース２２に取り付けられるスペーサ等の固定部材であっても良い。この場合は、チェーンケース２２に固定部材が取り付けられ、固定部材とカバー部材４の間にオイルシール４２の固定部４５が挟まれ固定される。 In this embodiment, the case member is the chain case 22, but it may be a fixing member such as a spacer attached to the chain case 22, for example. In this case, a fixing member is attached to the chain case 22, and the fixing portion 45 of the oil seal 42 is sandwiched and fixed between the fixing member and the cover member 4.
　以上説明した実施形態に基づく内燃機関のバルブタイミング制御装置としては、例えば、以下に述べる態様のものが考えられる。 As a valve timing control device for an internal combustion engine based on the embodiment described above, for example, the following modes can be considered.
　本発明に係る内燃機関のバルブタイミング制御装置は、その一つの態様において、クランクシャフトからの回転力が伝達される駆動回転体と、
　カムシャフトに固定される従動回転体と、
　回転駆動することによって前記駆動回転体と従動回転体の相対回転位相を変更する電動モータと、
　該電動モータに前記電動モータの回転軸方向から対向配置され、前記電動モータの外周に配置されたケース部材に固定される閉塞部材と、
　前記閉塞部材とケース部材との間に挟まれて固定される環状の固定部と、該固定部の内周に設けられて前記駆動回転体または電動モータの外周面に弾性接触する環状のシール部と、を有するシール部材と、を備えている。 In one aspect of the valve timing control device for an internal combustion engine according to the present invention, a driving rotating body to which a rotational force from a crankshaft is transmitted,
A driven rotor fixed to the camshaft;
An electric motor that changes the relative rotational phase of the driven rotating body and the driven rotating body by rotationally driving;
A closing member that is disposed opposite to the electric motor from the direction of the rotation axis of the electric motor and is fixed to a case member that is disposed on the outer periphery of the electric motor;
An annular fixing portion that is sandwiched and fixed between the closing member and the case member, and an annular seal portion that is provided on the inner periphery of the fixing portion and elastically contacts the outer peripheral surface of the drive rotating body or the electric motor. And a sealing member.
　さらに好ましい態様としては、前記閉塞部材とケース部材は、複数の固定要素によって結合され、前記シール部材の固定部は、前記固定要素が径方向の隙間をもって挿入される複数の貫通孔を有している。 As a further preferred aspect, the closing member and the case member are coupled by a plurality of fixing elements, and the fixing portion of the seal member has a plurality of through holes into which the fixing elements are inserted with a radial gap. Yes.
　さらに好ましい態様としては、前記各貫通孔は、前記固定部の外周に有する突出部に形成されている。 As a further preferred aspect, each of the through holes is formed in a protruding portion on the outer periphery of the fixed portion.
　さらに好ましい態様としては、前記シール部材は、前記固定部を介して前記固定要素によって前記固定部が閉塞部材とケース部材との間に挟まれた状態で固定されている。 As a further preferred aspect, the sealing member is fixed in a state where the fixing portion is sandwiched between the closing member and the case member by the fixing element via the fixing portion.
　さらに好ましい態様としては、前記固定部は、前記電動モータの回転軸直角方向の断面がクランク状に折曲しており、円筒部と、該円筒部の軸方向の一端部外周に形成されて前記突出部を有する円環部と、前記円筒部の軸方向の他端部内周に配置された前記シール部と、を有している。 As a more preferable aspect, the fixing portion has a section perpendicular to the rotation axis of the electric motor bent in a crank shape, and is formed on the outer periphery of the cylindrical portion and one end portion in the axial direction of the cylindrical portion. It has the annular part which has a protrusion part, and the said seal | sticker part arrange | positioned at the other end part inner periphery of the other end of the said cylindrical part in the axial direction.
　さらに好ましい態様としては、前記円筒部の外径は、前記ケース部の内径よりも小さくなっている。 In a more preferred aspect, the outer diameter of the cylindrical portion is smaller than the inner diameter of the case portion.
　さらに好ましい態様としては、前記シール部材は、前記固定部が環状かつ板状であり、前記固定部の径方向内周部に前記シール部が設けられている。 In a more preferred aspect, the sealing member has the fixing portion in an annular and plate shape, and the sealing portion is provided on a radially inner peripheral portion of the fixing portion.
　さらに好ましい態様としては、前記閉塞部材は、前記シール部材の前記シール部よりも径方向内側に電源からの電力を前記電動モータに供給する給電機構を有している。 As a further preferred aspect, the closing member has a power feeding mechanism that supplies power from the power source to the electric motor radially inward of the seal portion of the seal member.
　さらに好ましい態様としては、前記固定部とケース部材との間、及び前記固定部と前記閉塞部材との間に、前記ケース部の内部と外部との間をシールするシールリングを有している。 As a further preferred aspect, there is a seal ring that seals between the inside and the outside of the case portion between the fixing portion and the case member and between the fixing portion and the closing member.
　さらに好ましい態様としては、前記シールリングは、前記固定部とケース部材との間、及び固定部と閉塞部材との間に介装された一対のＯリングである。 In a further preferred aspect, the seal ring is a pair of O-rings interposed between the fixed portion and the case member and between the fixed portion and the closing member.
　さらに好ましい態様としては、前記シールリングは、前記固定部の両側面に加硫接着によってそれぞれ固定された一対で構成され、各外端部が前記ケース部材と閉塞部材の対向面に弾接している。 As a more preferable aspect, the seal ring is configured as a pair fixed to both side surfaces of the fixed portion by vulcanization adhesion, and each outer end portion is in elastic contact with the facing surfaces of the case member and the closing member. .
　さらに好ましい態様としては、前記一対のシールリングは、断面三角形状に形成されている。 In a more preferred aspect, the pair of seal rings are formed in a triangular cross section.
　さらに好ましい態様としては、前記一対のシールリングは、それぞれが断面四角形状に形成されている。 In a more preferred embodiment, each of the pair of seal rings is formed in a quadrangular cross section.
　さらに好ましい態様としては、前記各シールリングは、合成ゴム材である。 In a more preferred embodiment, each of the seal rings is a synthetic rubber material.
　別の好ましい態様として、クランクシャフトから回転力が伝達される駆動回転体と、
　カムシャフトに固定される従動回転体と、
　出力軸を回転させることによって前記駆動回転体と前記従動回転体の相対回転位相を変更する電動モータと、
　該電動モータに前記電動モータの回転軸方向から対向配置され、前記電動モータの外周に配置されたケース部材に固定される閉塞部材と、
　前記閉塞部材とケース部材との間に挟まれて固定される環状の固定部と、該固定部の内周に設けられて前記駆動回転体または電動モータの外周面に弾性接触する環状のシール部と、を有するシール部材と、
　を備え、
　前記シール部材は、その位置が前記カムシャフトの軸直角方向に沿って調整可能に設けられている。 As another preferred embodiment, a drive rotator to which a rotational force is transmitted from the crankshaft;
A driven rotor fixed to the camshaft;
An electric motor that changes a relative rotational phase of the drive rotator and the driven rotator by rotating an output shaft;
A closing member that is disposed opposite to the electric motor from the direction of the rotation axis of the electric motor and is fixed to a case member that is disposed on the outer periphery of the electric motor;
An annular fixing portion that is sandwiched and fixed between the closing member and the case member, and an annular seal portion that is provided on the inner periphery of the fixing portion and elastically contacts the outer peripheral surface of the drive rotating body or the electric motor. And a sealing member having
With
The seal member is provided so that its position can be adjusted along the direction perpendicular to the axis of the camshaft.
　さらに好ましい態様としては、前記シール部材は、前記固定部が固定される前の状態において、前記シール部の前記駆動回転体または電動モータの外周面に対する弾性接触による弾性力によって前記カムシャフトの軸直角方向の位置が調整可能になっている。 In a more preferred aspect, the seal member is perpendicular to the axis of the camshaft by elastic force due to elastic contact of the seal portion with the outer peripheral surface of the drive rotating body or the electric motor before the fixing portion is fixed. The position of the direction can be adjusted.
　別の好ましい態様として、クランクシャフトから回転力が伝達される駆動回転体と、
　カムシャフトに固定される従動回転体と、
　出力軸を回転させることによって前記駆動回転体と前記従動回転体の相対回転位相を変更する電動モータと、
　該電動モータに前記電動モータの回転軸方向から対向配置され、前記電動モータの外周に配置されたケース部材に固定される閉塞部材と、
　前記閉塞部材とケース部材との間に挟まれて固定される円環状の固定部と、該固定部の内周に設けられて前記駆動回転体または電動モータの外周面に弾性接触する環状のシール部と、を有し、その位置がカムシャフトの軸直角方向に沿って調整可能なシール部材と、を備えている。 As another preferred embodiment, a drive rotator to which a rotational force is transmitted from the crankshaft;
A driven rotor fixed to the camshaft;
An electric motor that changes a relative rotational phase of the drive rotator and the driven rotator by rotating an output shaft;
A closing member that is disposed opposite to the electric motor from the direction of the rotation axis of the electric motor and is fixed to a case member that is disposed on the outer periphery of the electric motor;
An annular fixing portion sandwiched and fixed between the closing member and the case member, and an annular seal provided on the inner periphery of the fixing portion and elastically contacting the outer peripheral surface of the drive rotating body or the electric motor And a sealing member whose position is adjustable along the direction perpendicular to the axis of the camshaft.

Claims (17)

  1. 　クランクシャフトからの回転力が伝達される駆動回転体と、
    　カムシャフトに固定される従動回転体と、
    　回転駆動することによって前記駆動回転体と従動回転体の相対回転位相を変更する電動モータと、
    　該電動モータに前記電動モータの回転軸方向から対向配置され、前記電動モータの外周に配置されたケース部材に固定される閉塞部材と、
    　前記閉塞部材とケース部材との間に挟まれて固定される環状の固定部と、該固定部の内周に設けられて前記駆動回転体または電動モータの外周面に弾性接触する環状のシール部と、を有するシール部材と、
    　を備えたことを特徴とする内燃機関のバルブタイミング制御装置。     A driving rotating body to which the rotational force from the crankshaft is transmitted;
    A driven rotor fixed to the camshaft;
    An electric motor that changes the relative rotational phase of the driven rotating body and the driven rotating body by rotationally driving;
    A closing member that is disposed opposite to the electric motor from the direction of the rotation axis of the electric motor and is fixed to a case member that is disposed on the outer periphery of the electric motor;
    An annular fixed portion sandwiched and fixed between the closing member and the case member, and an annular seal portion provided on the inner periphery of the fixed portion and elastically contacting the outer peripheral surface of the drive rotating body or the electric motor And a sealing member having
    A valve timing control apparatus for an internal combustion engine, comprising:
  2. 　請求項１に記載の内燃機関のバルブタイミング制御装置において、
    　前記閉塞部材とケース部材は、複数の固定要素によって結合され、
    　前記シール部材の固定部は、前記固定要素が径方向の隙間をもって挿入される複数の貫通孔を有することを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control apparatus for an internal combustion engine according to claim 1,
    The closing member and the case member are coupled by a plurality of fixing elements,
    The valve timing control device for an internal combustion engine, wherein the fixing portion of the seal member has a plurality of through holes into which the fixing elements are inserted with radial gaps.
  3. 　請求項２に記載の内燃機関のバルブタイミング制御装置において、
    　前記各貫通孔は、前記固定部の外周に有する突出部に形成されていることを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control device for an internal combustion engine according to claim 2,
    Each said through-hole is formed in the protrusion part which has in the outer periphery of the said fixing | fixed part, The valve timing control apparatus of the internal combustion engine characterized by the above-mentioned.
  4. 　請求項３に記載の内燃機関のバルブタイミング制御装置において、
    　前記シール部材は、前記固定部を介して前記固定要素によって前記固定部が閉塞部材とケース部材との間に挟まれた状態で固定されていることを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control apparatus for an internal combustion engine according to claim 3,
    The valve timing control device for an internal combustion engine, wherein the sealing member is fixed in a state where the fixing portion is sandwiched between a closing member and a case member by the fixing element via the fixing portion.
  5. 　請求項３に記載の内燃機関のバルブタイミング制御装置において、
    　前記固定部は、前記電動モータの回転軸直角方向の断面がクランク状に折曲しており、円筒部と、該円筒部の軸方向の一端部外周に形成されて前記突出部を有する円環部と、前記円筒部の軸方向の他端部内周に配置された前記シール部と、を有することを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control apparatus for an internal combustion engine according to claim 3,
    The fixing portion has a cross section perpendicular to the rotation axis of the electric motor bent in a crank shape, a cylindrical portion, and an annular ring formed on the outer periphery of one end portion in the axial direction of the cylindrical portion and having the protruding portion. And a valve timing control device for an internal combustion engine, comprising: a sealing portion disposed on an inner periphery of the other end portion in the axial direction of the cylindrical portion.
  6. 　請求項５に記載の内燃機関のバルブタイミング制御装置において、
    　前記円筒部の外径は、前記ケース部材の内径よりも小さいことを特徴とする内燃機関のバルブタイミング制御装置。     In the internal combustion engine valve timing control device according to claim 5,
    The valve timing control device for an internal combustion engine, wherein an outer diameter of the cylindrical portion is smaller than an inner diameter of the case member.
  7. 　請求項２に記載の内燃機関のバルブタイミング制御装置において、
    　前記シール部材は、前記固定部が環状かつ板状であり、前記固定部の径方向内周部に前記シール部が設けられていることを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control device for an internal combustion engine according to claim 2,
    The valve timing control device for an internal combustion engine, wherein the sealing member has an annular and plate-shaped fixing portion, and the sealing portion is provided on a radially inner peripheral portion of the fixing portion.
  8. 　請求項１に記載の内燃機関のバルブタイミング制御装置において、
    　前記閉塞部材は、前記シール部材の前記シール部よりも径方向内側に電源からの電力を前記電動モータに供給する給電機構を有することを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control apparatus for an internal combustion engine according to claim 1,
    The valve timing control device for an internal combustion engine, wherein the closing member has a power feeding mechanism that supplies electric power from a power source to the electric motor on a radially inner side of the seal portion of the seal member.
  9. 　請求項１に記載の内燃機関のバルブタイミング制御装置において、
    　前記固定部とケース部材との間、及び前記固定部と前記閉塞部材との間に、前記ケース部材の内部と外部との間をシールするシールリングを有することを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control apparatus for an internal combustion engine according to claim 1,
    A valve timing for an internal combustion engine, comprising seal rings for sealing between the inside and the outside of the case member between the fixed portion and the case member and between the fixed portion and the closing member. Control device.
  10. 　請求項９に記載の内燃機関のバルブタイミング制御装置において、
    　前記シールリングは、前記固定部とケース部材との間、及び固定部と閉塞部材との間に介装された一対のＯリングであることを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control device for an internal combustion engine according to claim 9,
    The valve timing control device for an internal combustion engine, wherein the seal ring is a pair of O-rings interposed between the fixed portion and the case member and between the fixed portion and the closing member.
  11. [規則91に基づく訂正 20.09.2017]　
    　請求項９に記載の内燃機関のバルブタイミング制御装置において、
    　前記シールリングは、前記固定部の両側面に加硫接着によってそれぞれ固定された一対で構成され、各外端部が前記ケース部材と閉塞部材の対向面に弾接することを特徴とする内燃機関のバルブタイミング制御装置。     [Correction based on Rule 91 20.09.2017]
    The valve timing control device for an internal combustion engine according to claim 9,
    The seal ring is composed of a pair fixed to both side surfaces of the fixed portion by vulcanization adhesion, and each outer end portion is elastically contacted with the facing surfaces of the case member and the closing member. Valve timing control device.
  12. 　請求項１１に記載の内燃機関のバルブタイミング制御装置において、
    　前記一対のシールリングは、断面三角形状に形成されていることを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control apparatus for an internal combustion engine according to claim 11,
    The valve timing control device for an internal combustion engine, wherein the pair of seal rings are formed in a triangular shape in cross section.
  13. 　請求項１１に記載の内燃機関のバルブタイミング制御装置において、
    　前記一対のシールリングは、それぞれが断面四角形状に形成されていることを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control apparatus for an internal combustion engine according to claim 11,
    The valve timing control device for an internal combustion engine, wherein each of the pair of seal rings is formed in a quadrangular cross section.
  14. 　請求項９に記載の内燃機関のバルブタイミング制御装置において、
    　前記シールリングは、合成ゴム材であることを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control device for an internal combustion engine according to claim 9,
    The valve timing control device for an internal combustion engine, wherein the seal ring is made of a synthetic rubber material.
  15. 　クランクシャフトから回転力が伝達される駆動回転体と、
    　カムシャフトに固定される従動回転体と、
    　出力軸を回転させることによって前記駆動回転体と前記従動回転体の相対回転位相を変更する電動モータと、
    　該電動モータに前記電動モータの回転軸方向から対向配置され、前記電動モータの外周に配置されたケース部材に固定される閉塞部材と、
    　前記閉塞部材とケース部材との間に挟まれて固定される環状の固定部と、該固定部の内周に設けられて前記駆動回転体または電動モータの外周面に弾性接触する環状のシール部と、を有するシール部材と、
    　を備え、
    　前記シール部材は、その位置が前記カムシャフトの軸直角方向に沿って調整可能に設けられていることを特徴とする内燃機関のバルブタイミング制御装置。     A driving rotating body to which rotational force is transmitted from the crankshaft;
    A driven rotor fixed to the camshaft;
    An electric motor that changes a relative rotational phase of the drive rotator and the driven rotator by rotating an output shaft;
    A closing member that is disposed opposite to the electric motor from the direction of the rotation axis of the electric motor and is fixed to a case member that is disposed on the outer periphery of the electric motor;
    An annular fixing portion that is sandwiched and fixed between the closing member and the case member, and an annular seal portion that is provided on the inner periphery of the fixing portion and elastically contacts the outer peripheral surface of the drive rotating body or the electric motor. And a sealing member having
    With
    The valve timing control apparatus for an internal combustion engine, wherein the position of the seal member is adjustable along a direction perpendicular to the axis of the camshaft.
  16. 　請求項１５に記載の内燃機関のバルブタイミング制御装置において、
    　前記シール部材は、前記固定部が固定される前の状態において、前記シール部の前記駆動回転体または電動モータの外周面に対する弾性接触による弾性力によって前記カムシャフトの軸直角方向の位置が調整可能になっていることを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control device for an internal combustion engine according to claim 15,
    The position of the seal member in the direction perpendicular to the axis of the camshaft can be adjusted by elastic force due to elastic contact of the seal portion with the outer peripheral surface of the drive rotating body or the electric motor before the fixing portion is fixed. A valve timing control device for an internal combustion engine, characterized in that
  17. 　クランクシャフトから回転力が伝達される駆動回転体と、
    　カムシャフトに固定される従動回転体と、
    　出力軸を回転させることによって前記駆動回転体と前記従動回転体の相対回転位相を変更する電動モータと、
    　該電動モータに前記電動モータの回転軸方向から対向配置され、前記電動モータの外周に配置されたケース部材に固定される閉塞部材と、
    　前記閉塞部材とケース部材との間に挟まれて固定される円環状の固定部と、該固定部の内周に設けられて前記駆動回転体または電動モータの外周面に弾性接触する環状のシール部と、を有し、その位置がカムシャフトの軸直角方向に沿って調整可能なシール部材と、
    　を備えたことを特徴とする内燃機関のバルブタイミング制御装置のシール構造。     A driving rotating body to which rotational force is transmitted from the crankshaft;
    A driven rotor fixed to the camshaft;
    An electric motor that changes a relative rotational phase of the drive rotator and the driven rotator by rotating an output shaft;
    A closing member that is disposed opposite to the electric motor from the direction of the rotation axis of the electric motor and is fixed to a case member that is disposed on the outer periphery of the electric motor;
    An annular fixing portion sandwiched and fixed between the closing member and the case member, and an annular seal provided on the inner periphery of the fixing portion and elastically contacting the outer peripheral surface of the drive rotating body or the electric motor And a seal member whose position is adjustable along the direction perpendicular to the axis of the camshaft.
    A seal structure for a valve timing control device for an internal combustion engine, comprising:
PCT/JP2017/029261 2016-09-20 2017-08-14 Valve timing control device for internal combustion engine and seal structure for valve timing control device WO2018055951A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015093423A1 (en) * 2013-12-19 2015-06-25 日立オートモティブシステムズ株式会社 Valve timing control device for internal combustion engine and controller for valve timing control device
JP2016048053A (en) * 2014-08-28 2016-04-07 日立オートモティブシステムズ株式会社 Valve timing control device and valve timing control system for internal combustion engine

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015093423A1 (en) * 2013-12-19 2015-06-25 日立オートモティブシステムズ株式会社 Valve timing control device for internal combustion engine and controller for valve timing control device
JP2016048053A (en) * 2014-08-28 2016-04-07 日立オートモティブシステムズ株式会社 Valve timing control device and valve timing control system for internal combustion engine

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