WO2018055951A1 - Dispositif de commande de réglage de distribution pour moteur à combustion interne et structure d'étanchéité pour dispositif de commande de réglage de distribution - Google Patents

Dispositif de commande de réglage de distribution pour moteur à combustion interne et structure d'étanchéité pour dispositif de commande de réglage de distribution 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
English (en)
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/fr

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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

La présente invention est équipée : d'un moteur électrique (12) pour changer la phase de rotation relative d'un pignon (1) et d'un arbre à cames (2); d'un élément de couvercle (4); d'un boîtier de chaîne (22) disposé sur le côté périphérique externe du carter de moteur (14); et un joint d'étanchéité d'huile (42) pour assurer l'étanchéité entre le carter de moteur et le boîtier de chaîne. Le joint d'étanchéité à huile est fixé avec des boulons (44), tandis que des parties de fixation (45) sur le côté périphérique externe du joint à huile sont intercalées entre une surface intérieure (28f) d'un corps principal de couvercle (28) et une surface d'extrémité avant (22b) du boîtier de chaîne, et le joint d'étanchéité à l'huile comprend une partie d'étanchéité annulaire (46) en contact élastique avec la surface périphérique externe du carter de moteur. Avant qu'il soit fixé avec les boulons, l'ensemble du joint d'étanchéité à l'huile est capable de se déplacer dans la direction radiale par l'intermédiaire de trous d'insertion de boulon (45e). Ainsi, une réduction de performance d'étanchéité peut être empêchée tout en garantissant la concentricité du carter de moteur et du joint d'étanchéité à l'huile.
PCT/JP2017/029261 2016-09-20 2017-08-14 Dispositif de commande de réglage de distribution pour moteur à combustion interne et structure d'étanchéité pour dispositif de commande de réglage de distribution WO2018055951A1 (fr)

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JP2016182834A JP2019203384A (ja) 2016-09-20 2016-09-20 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
JP2016-182834 2016-09-20

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015093423A1 (fr) * 2013-12-19 2015-06-25 日立オートモティブシステムズ株式会社 Dispositif de calage de distribution pour un moteur à combustion interne et dispositif de commande associé
JP2016048053A (ja) * 2014-08-28 2016-04-07 日立オートモティブシステムズ株式会社 内燃機関のバルブタイミング制御装置及びバルブタイミング制御システム

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015093423A1 (fr) * 2013-12-19 2015-06-25 日立オートモティブシステムズ株式会社 Dispositif de calage de distribution pour un moteur à combustion interne et dispositif de commande associé
JP2016048053A (ja) * 2014-08-28 2016-04-07 日立オートモティブシステムズ株式会社 内燃機関のバルブタイミング制御装置及びバルブタイミング制御システム

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