WO2017026240A1 - Valve timing control device for internal combustion engine - Google Patents

Valve timing control device for internal combustion engine Download PDF

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Publication number
WO2017026240A1
WO2017026240A1 PCT/JP2016/071483 JP2016071483W WO2017026240A1 WO 2017026240 A1 WO2017026240 A1 WO 2017026240A1 JP 2016071483 W JP2016071483 W JP 2016071483W WO 2017026240 A1 WO2017026240 A1 WO 2017026240A1
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WO
WIPO (PCT)
Prior art keywords
timing control
valve timing
combustion engine
internal combustion
control device
Prior art date
Application number
PCT/JP2016/071483
Other languages
French (fr)
Japanese (ja)
Inventor
陽輔 岩瀬
幹弘 梶浦
淳史 山中
Original Assignee
日立オートモティブシステムズ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 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
Priority to JP2017534154A priority Critical patent/JPWO2017026240A1/en
Publication of WO2017026240A1 publication Critical patent/WO2017026240A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/352—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
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34483—Phaser return springs

Definitions

  • the present invention relates to a valve timing control device for an internal combustion engine that controls the opening and closing timing of an intake valve and an exhaust valve, for example.
  • a plate-shaped sealing member is fixed to the front end portion of the motor housing of the electric motor, and a cover member is disposed at a front position of the front end portion with a predetermined clearance.
  • the sealing member is provided with an inner / outer double power supply slip ring facing the clearance, while the cover member has a front end slidably contacting each of the power supply slip rings to supply power to the electric motor.
  • a pair of power supply brushes are provided.
  • Each of the power supply brushes is urged toward the top surface of each slip ring by a coil spring elastically mounted on the rear end side of the power supply brush.
  • the current supplied from the external power source to the power supply brush through the power supply connector is supplied to the coil of the electric motor from the switching brush and the commutator through the slip rings, and the motor output shaft is driven to rotate.
  • the valve timing of the intake valve is controlled by changing the relative rotation phase of the camshaft with respect to the crankshaft.
  • each coil spring is provided in series along the axial direction at the axial end portion of each power supply brush.
  • the length of will inevitably become longer.
  • the degree of freedom of layout in the engine room of the vehicle is limited.
  • the present invention has been devised in view of the above-described conventional technical problems, and provides a valve timing control device for an internal combustion engine that can shorten the axial direction of the device and can provide a firmly fixed state of a support member to a cover member. It is intended to provide.
  • the invention according to claim 1 of the present application is, inter alia, an electric motor that is integrally provided on one side of the first member or the second member and changes the relative rotational phase of the second member relative to the first member when energized.
  • a pair of power supply brushes that are provided in contact with each of the corresponding slip rings to supply power, and on the cover member side, a winding portion is provided so as to overlap the power supply brush in the radial direction of the cover member.
  • the axial length of the apparatus can be shortened, and the support member can be firmly fixed to the cover member.
  • 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 rear view of the sealing member provided for this embodiment. It is a top view of the cover main body provided for this embodiment. It is a top view which shows the state with which the torsion coil spring and retainer which are provided to this embodiment were assembled
  • valve timing control device for an internal combustion engine according to the present invention will be described with reference to the drawings.
  • the valve timing control device is applied to the intake valve side.
  • the valve timing control device includes a timing sprocket 1 that is a first member (drive rotating body) that is rotationally driven by a crankshaft of an internal combustion engine, and a bearing 02 on a cylinder head 01.
  • the camshaft 2 is a second member that is rotatably supported and rotated by the rotational force transmitted from the timing sprocket 1, and is disposed between the timing sprocket 1 and the camshaft 2, and depends on the engine operating state.
  • the phase change mechanism 3 that changes the relative rotational phase of the two and 1 and the cover member 4 disposed on the front end side of the phase change mechanism 3 is provided.
  • the timing sprocket 1 is formed integrally with an iron-based metal in an annular shape, and the inner peripheral surface is integrally provided on the outer periphery of the sprocket body 1a with a stepped diameter, and is wound outside the drawing.
  • the gear part 1b which receives the rotational force from a crankshaft via this timing chain, and the internal-tooth structure part 5 integrally provided in the front-end side of the said sprocket main body 1a are comprised.
  • the timing sprocket 1 has a single large-diameter ball bearing 43 interposed between a sprocket body 1a and a driven member 9 (described later) provided at the front end of the camshaft 2.
  • the timing sprocket 1 is supported on the outer periphery of the driven member 9 by a ball bearing 43 so as to be relatively rotatable.
  • the large-diameter ball bearing 43 is a general one and includes an outer ring 43a, an inner ring 43b, and a ball 43c interposed between the two rings, and the outer ring 43a is disposed on the inner peripheral side of the sprocket body 1a.
  • the inner ring 43b is press-fitted and fixed to the annular annular inner ring fixing part 9e of the driven member 9 while being press-fitted and fixed to the formed annular outer ring fixing part 1d.
  • the internal tooth component 5 is integrally formed on the outer peripheral side of the front end portion of the sprocket body 1a, is formed in a cylindrical shape extending forward of the phase change mechanism 3, and has a plurality of wave shapes on the inner periphery.
  • the inner teeth 5a are formed.
  • annular stopper plate 21 is disposed at the rear end portion of the sprocket body 1a opposite to the internal tooth component 5 as shown in FIG.
  • the stopper plate 21 is formed in an annular shape by a metal plate material, and has an outer diameter set to be substantially the same as the outer diameter of the sprocket body 1 a and an inner diameter larger than the inner diameter of the outer ring 43 a of the large-diameter ball bearing 43. It is set to a small diameter.
  • the inner peripheral portion 21a of the stopper plate 21 is disposed in contact with the outer end surface of the outer ring 43a in the axial direction, and protrudes radially inward, that is, toward the central axis direction at a predetermined position of the inner peripheral edge.
  • the stopper convex part 21b is provided integrally.
  • the stopper convex portion 21b is formed in a substantially fan shape, and the tip edge 21c is formed in an arc shape along an arc-shaped inner peripheral surface of a stopper concave groove 22d described later.
  • sprocket main body 1a In the outer peripheral portions of the sprocket main body 1a (internal tooth constituting portion 5) and the stopper plate 21, six insertion holes 1c and 21d through which the bolts 7 are inserted are formed at substantially equal intervals in the circumferential direction.
  • the sprocket body 1a and the internal gear component 5 are configured as a casing for a speed reduction mechanism 12 to be described later.
  • the camshaft 2 has two drive cams per cylinder for opening an intake valve (not shown) on the outer periphery, and a driven rotor through a flange portion 2a at one end in the axial direction via an adapter 22.
  • the driven member 9 is fixed together by a cam bolt 10 from the axial direction.
  • the driven member 9 is integrally formed of an iron-based metal, and as shown in FIG. 1, a disk-like fixed end portion 9a formed on the rear end side (camshaft 2 side), and the fixed end portion 9a.
  • the fixed end portion 9a has a first fitting groove 9d formed on the rear end surface thereof in contact with the front end surface of the flange portion 2a of the camshaft 2 via an adapter 22 which will be described later.
  • the flange portion 2a is pressed against and fixed to the flange portion 2a by an axial force.
  • a cylindrical retainer 41 that holds a plurality of rollers 48 to be described later is integrally provided on the outer peripheral portion of the fixed end portion 9a.
  • the cylindrical portion 9b is provided with a small-diameter ball bearing 37 and a needle bearing 38 on the outer periphery in parallel along the axial direction.
  • the adapter 22 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 22 a and an electric motor. It is comprised from the inner peripheral part 22b of the center side of the bottomed cylindrical shape protruded in the motor 11 direction.
  • the outer peripheral portion 22a 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 11 side serves as the restricting surface 22c after assembling each component. It is configured.
  • the restricting surface 22c is in contact with the other axial end surface of the inner ring 43b of the large-diameter ball bearing 43 so as to restrict movement outward in the axial direction.
  • a stopper concave groove 22d for engaging the stopper convex portion 21b of the stopper plate 21 is formed in an arc shape along the circumferential direction on the outer peripheral surface of the outer peripheral portion 22a.
  • the stopper concave groove 22d is formed in a circular arc shape having a predetermined length in the circumferential direction, and both end edges of the stopper convex portion 21b rotated in this length range come into contact with opposite circumferential edges, respectively.
  • the relative rotational position of the camshaft 2 on the maximum advance angle side or the maximum retard angle side with respect to the timing sprocket 1 is regulated.
  • the inner peripheral portion 22b includes a bottomed cylindrical convex portion protruding toward the electric motor 11, and a disc groove-shaped second fitting groove 22e formed simultaneously when the convex portion is formed by press molding. , Is composed of.
  • an insertion hole 22f through which the shaft portion 10b of the cam bolt 10 is inserted is formed at the center position of the convex portion of the inner peripheral portion 22b, and the flange of the camshaft 2 is inserted into the second fitting groove 22e.
  • An annular projection 2d protruding from the end face of the portion 2a is fitted.
  • an oil passage hole (not shown) that constitutes a part of a later-described lubricating oil passage is formed through the inner peripheral portion 22b.
  • the convex portion is fitted into the first fitting groove 9d of the driven member 9 by press-fitting from the axial direction, and in this fitted state, the tip wall of the convex portion is connected to the camshaft 2 by the cam bolt 10.
  • the projecting portion 2d and the fixed end portion 9a of the driven member 9 are coupled in a sandwiched state.
  • the cam bolt 10 has an axial end surface of the head portion 10a supporting the inner ring of the small-diameter ball bearing 37 from the axial direction, and an outer periphery of the shaft portion 10b from one end portion of the camshaft 2.
  • a male screw 10c is formed to be screwed onto the female screw 2c formed in the internal axis direction.
  • the phase changing mechanism 3 includes an electric motor 11 disposed on the front end side of the cylindrical portion 9 b of the driven member 9, and a speed reducing mechanism 12 that reduces the rotational speed of the electric motor 11 and transmits it to the camshaft 2. It is mainly composed.
  • the electric motor 11 is a brushed DC motor, a motor housing 13 that is a yoke that rotates integrally with the timing sprocket 1, and rotates inside the motor housing 13.
  • a cylindrical motor output shaft 14 provided freely, four semicircular arc-shaped permanent magnets 15 fixed to the inner peripheral surface of the motor housing 13, and a sealing member fixed by caulking to the front end portion of the motor housing 13 16.
  • the motor housing 13 is formed by pressing a ferrous metal material into a bottomed cylindrical shape, and has a disk-shaped partition wall 13a on the rear end side, and is substantially at the center of the partition wall 13a. Is formed with a large-diameter shaft insertion hole 13b into which an eccentric shaft portion 39, which will be described later, is inserted, and a cylindrical extension portion 13c protruding in the axial direction of the camshaft 2 at the hole edge of the shaft insertion hole 13b. Are provided integrally. A female screw hole 13d is formed along the axial direction inside the outer peripheral portion of the partition wall 13a.
  • the female screw hole 13d is formed at a position corresponding to each of the bolt insertion holes 1c and 21d, and the timing sprocket 1, the stopper plate 21 and the motor housing 13 are shared in the axial direction by the six bolts 7 inserted through these holes. Tightened and fixed. Note that the inner tooth constituent portion 5 is in contact with the rear end surface of the partition wall 13a of the motor housing 13 from the axial direction.
  • the motor output shaft 14 has one end portion on the camshaft 2 side through a step wall 14c formed in a substantially central position in the axial direction. And an insertion hole 14d into which the cam bolt 10 can be inserted penetrates in the internal axial direction. Is formed.
  • the large-diameter portion 14a has an iron core rotor 17 fixed to the outer periphery, and an eccentric shaft portion 39, which will be described later, constituting a part of the speed reduction mechanism 12 on the rear end side, is integrally provided along the axial direction. .
  • the commutator 20 is press-fitted and fixed to the outer periphery, and a detected portion 50 of an angle sensor 35 described later is inserted and fixed to the inner periphery.
  • the iron core rotor 17 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 18 is wound.
  • the motor output shaft 14 is fixed to the outer periphery of the stepped wall 14c while being axially positioned.
  • the commutator 20 includes an annular member 20a on the inner peripheral side, and an annular electrode portion 20b provided on the outer periphery of the annular member 20a.
  • the annular member 20a has an outer diameter set to be substantially the same as the outer diameter of the large-diameter portion 14a, and is disposed at a substantially central position in the axial direction of the small-diameter portion 14b.
  • the electrode portion 20b is formed in an annular shape with a conductive material, and the ends of the coil wires led out of the coil 18 are electrically connected to the segments divided into the same number as the number of poles of the iron core rotor 17. Yes.
  • Each of the permanent magnets 15 is formed in a cylindrical shape and has a plurality of magnetic poles in the circumferential direction, and its axial position is the axial direction of the iron core rotor 17 as shown in FIG.
  • the offset member is offset from the center of the sealing member 16 side.
  • the sealing member 16 includes a disk-shaped plate portion 16a made of an iron-based metal material, and a disk-shaped resin portion 16b obtained by molding almost the entire plate portion 16a.
  • the shaft insertion hole 16c is formed through the central portion and through which the small diameter portion 14b of the motor output shaft 14 is inserted.
  • the outer peripheral portion of the plate portion 16a that is not covered with the resin portion 16b is positioned and fixed by caulking in an annular groove formed on the inner peripheral surface of the front end portion of the motor housing 13.
  • the sealing member 16 is disposed inside a plurality of opening holes formed in the plate portion 16a and fixed to the front end portion of the resin portion 16b by a plurality of rivets 40.
  • a pair of brush holders 23a, 23b made of copper, and accommodated in the brush holders 23a, 23b so as to be slidable along the radial direction.
  • a pair of switching brushes 25a and 25b which are commutators whose tip surfaces elastically contact the outer peripheral surface of the commutator 20 from the radial direction, and the front end surface side of the resin portion 16b are molded and fixed with their respective outer surfaces exposed.
  • Double inner and outer power supply slip rings 26a, 26b, harnesses 27a for electrically connecting the switching brushes 25a, 25b and the slip rings 26a, 26b, And 7b, are provided.
  • the inner peripheral small-diameter feeding slip ring 26a and the outer peripheral large-diameter feeding slip ring 26b are formed by punching a thin plate made of a copper material into an annular shape by pressing.
  • the cover member 4 is formed in a substantially disk shape and is disposed to face the front end side of the sealing member 16.
  • the cover main body 28 is arranged so as to cover the portion, and the synthetic resin cap portion 29 covers a part of the outer side surface 28b of the cover main body 28.
  • the cover main body 28 has an outer diameter larger than the outer diameter of the motor housing 13, and a metal reinforcing plate 28a is molded and fixed inside an outer layer portion formed with a predetermined thickness by a synthetic resin material. ing.
  • the cover main body 28 is made of metal in which a bolt insertion hole 28d into which a bolt fixed to the chain case 36 is inserted is molded into a resin material in an arc-shaped boss portion 28c projecting at four locations on the outer peripheral portion.
  • the two left and right boss portions 28c in FIG. 6 have two pin insertion holes 28f through which positioning pins are inserted when the cover member 4 is attached to the chain case 36, respectively. 28f is formed through.
  • the reinforcing plate 28a is formed in a substantially disk shape smaller than the outer diameter of the cover body 28, and a synthetic resin material is filled in a through hole formed at the center position.
  • a circular hole 28k is formed, and an elongated notch-shaped notch portion in which a conductive material of a signal connector 34 to be described later is disposed is formed along the radial direction on the lower side.
  • the cover main body 28 has a pair of rectangular holder holes 28g and 28g penetratingly formed by a synthetic resin material filled in a window hole formed substantially above the reinforcing plate 28a in FIG.
  • an accommodation groove 56 that is a recess for accommodating a pair of torsion coil springs 32 and 32, which will be described later, is formed at an obliquely upper position of the holder holes 28g and 28g.
  • rectangular tube-shaped brush holders 30a and 30b are mold-fixed along the axial direction.
  • a deformed circular locking wall 28 h to which the cap portion 29 is fitted and fixed is integrally provided on the outer surface 28 b of the cover main body 28.
  • the cap portion 29 is formed in a disk plate shape, and an annular locking projection 29a formed integrally with the outer peripheral edge is locked and fixed to the locking wall 28h of the cover body 28 by press-fitting from the axial direction. Has been.
  • the cover main body 28 includes a pair of square rectangular brush holders 30 a made of copper at positions facing the slip rings 26 a and 26 b in the axial direction in the holder holes 28 g and 28 g. 30b is fixed along the axial direction, and a pair of power supply brushes 31a and 31b whose tip end surfaces are in sliding contact with the slip rings 26a and 26b are axially arranged in the brush holders 30a and 30b. Is slidably held in the head.
  • the brush holders 30a and 30b and the power feeding brushes 31a and 31b are arranged in parallel on the inner side and the outer side on the radial inner side of the cover main body 28, and the rear ends of the brush holders 30a and 30b and the power supply brushes 31a and 31b are on the outer side surface 28b of the cover main body 28. I'm here.
  • the circular hole 28k formed at substantially the center position of the inner surface of the cover main body 28 on the electric motor 11 side is formed so that the inner diameter is larger than the outer diameter of the distal end portion of the detected portion 50 described later, and the depth thereof.
  • the cover body 28 is formed slightly smaller than the axial width of the cover body 28 and has a thin bottom wall.
  • a pair of torsion coil springs 32 and 32 for urging the power supply brushes 31a and 31b in the direction of the slip rings 26a and 26b are accommodated on the outer surface 28b of the cover body 28 via a retainer 55 as a support member.
  • a rectangular accommodation groove 56 is formed.
  • the housing groove 56 is formed by cutting a synthetic resin material filled in the window portion of the reinforcing plate 28 a into a rectangular shape substantially along the radial direction of the cover body 28.
  • the power supply brushes 31a and 31b are disposed substantially in parallel with each other. That is, the formation position of the accommodation groove 56 is provided at a radial position on the opposite side to the power supply connector 33 described later with the power supply brushes 31a and 31b interposed therebetween.
  • the housing groove 56 includes a holding groove portion 57 that houses the pair of torsion coil springs 32 and 32 while being supported by the retainer 55, and both opposing sides of the holding groove portion 57.
  • a pair of fixing shelves 58, 58 formed at substantially the center position in the longitudinal direction of the surfaces 57a, 57b, and both ends in the longitudinal direction of one side surface 57a of the holding groove 57 (both sides of one shelf 58) It is comprised from a pair of support groove part 59, 59 formed in this.
  • the holding groove portion 57 is formed in a rectangular shape as viewed from above, and has the deepest depth from the upper end opening to the bottom surface, and its width is larger than the outer diameter of each of the torsion coil springs 32 and 32.
  • the length L is slightly larger than the axial length of the retainer 55.
  • each upper surface 58a is formed one step lower than the outer surface 28b of the cover body 28, and each upper surface 58a is formed as a concave portion 58b.
  • the protrusions 60, 60 having a conical tip are provided upright at a substantially central position of each upper surface 58a.
  • the support groove portions 59, 59 extend from both end portions of one side surface 57a of the holding groove portion 57 in the direction perpendicular to the axis, and the widths of the support groove portions 59, 59 are relatively small.
  • the pair of torsion coil springs 32 and 32 are arranged in parallel and linearly with respect to the power feeding brushes 31a and 31b, and are cylindrical, which generate spring force.
  • the arm-shaped one end portions 32b and 32b elastically contacting the bottom of 31d and the one end portions 32b and 32b extend in the opposite direction from the other axial end side of the winding portions 32a and 32a.
  • Arm-like other end portions 32c and 32c that elastically contact the upper surfaces of the respective support groove portions 59 and 59 are provided.
  • the winding portions 32a and 32a are set so that the winding directions are opposite to each other and generate a desired spring force in the opening direction with a predetermined winding dose.
  • Each of the winding portions 32a and 32a is formed so that the outer diameter is smaller than the width dimension of the holding groove portion 57, and the whole can be accommodated in the holding groove portion 57 with a predetermined gap, as shown in FIG.
  • a part of each is arranged in an axially overlapping state with a through portion 28 i formed at a predetermined position of the reinforcing plate 28 a. That is, it is located on the inner diameter side of the penetrating portion 28i.
  • Each of the one end portions 32b and 32b is formed such that each tip end is bent in an arc shape, and each bent top portion is elastically contacted with the bottom portion of each of the V-shaped grooves 31c and 31d of each of the power feeding brushes 31a and 31b.
  • the one end portions 32b and 32b are in elastic contact with the bottoms of the V-shaped grooves 31c and 31c of the power feeding brushes 31a and 31b and are pressed toward the slip rings 26a and 26b.
  • the winding directions of the winding portions 32a and 32a are opposite to each other, the one end portions 32b and 32b are positioned close to each other in the axial direction, that is, a partition wall of a retainer 55 described later. 62 are located close to each other on both side surfaces, and extend along the both side surfaces in parallel to the rear end surface direction of each of the power supply brushes 31a and 31b.
  • each of the other end portions 32c and 32c has a substantially straight end portion, and each lower end edge is elastically contacted with each upper surface of the support groove portions 59 and 59 of the cover member 4 in a line contact state. Yes. Further, the other end portions 32c and 32c are spaced apart from each other in the axial direction because the winding directions of the winding portions 32a and 32a are opposite to each other.
  • the torsion coil springs 32 and 32 urge the power supply brushes 31a and 31b by a spring force acting in a direction in which the respective one end portions 32b and 32b and the other end portions 32c and 32c open.
  • the retainer 55 is integrally formed of a synthetic resin material, and is provided integrally with a support shaft 61 formed in a single shaft shape and in the axial center position of the support shaft 61. And a partition wall 62 that is a locking portion.
  • the support shaft 61 is formed in a solid cylindrical shape, and its axial length is slightly shorter than the length in the longitudinal direction of the receiving groove 56, and both axial end surfaces thereof are the receiving grooves 56.
  • the torsion coil springs 32, 32 are opposed to the left and right end portions 61a, 61b from the opposite sides in the axial direction through the winding portions 32a, 32a. It is designed to be inserted.
  • the partition wall 62 has a bottom wall portion 62a integrally formed on the center bottom portion side of the support shaft 61, and a pair of fixed projections protruding in the horizontal direction from both side surfaces in the radial direction of the support shaft 61 located above the bottom wall portion 62a. Projecting walls 62b, 62b.
  • the bottom wall portion 62a is formed in a substantially rectangular parallelepiped shape and is fitted and held in the holding groove portion 57 of the receiving groove 56.
  • Each of the fixing protruding walls 62b and 62b is formed in a thick and substantially rectangular plate shape and is fitted into the concave portions 58b and 58b of the shelf portions 58 and 58, and the lower surfaces thereof are the upper surfaces of the shelf portions 58 and 58.
  • the fixing holes 62c and 62c into which the projections 60 and 60 are inserted are vertically formed in the center position.
  • the upper ends of the protrusions 60 and 60 are as shown by the one-dot chain lines in FIGS.
  • the fixing projecting walls 62b and 62b are fixed on the shelves 58 and 58 while being positioned.
  • Each of the brush holders 30a and 30b has openings at the front and rear ends, and the front ends of the power supply brushes 31a and 31b can be moved forward and backward from the opening on the front end side, as shown in FIG.
  • one end portions of the pair of pigtail harnesses 64 and 64 are connected to the rear end side portions of the power feeding brushes 31a and 31a through slits 63 and 63 formed in the longitudinal direction of the respective one side walls.
  • Each of the pigtail harnesses 64 and 64 has the other end connected to one end 33a and 33a of a pair of terminal pieces of a power supply connector 33 described later by soldering, and the power supply brushes 31a and 31b are connected to the power supply brushes 31a and 31b.
  • the torsion coil springs 32, 32, etc. When sliding via the spring force of the torsion coil springs 32, 32, etc., it moves in the slits 63, 63 and moves together with the brush holders 30a, 30b.
  • Each of the power supply brushes 31a and 31b is formed in a prismatic shape and is set to a predetermined axial length, and each flat tip surface is formed by the spring force of each of the torsion coil springs 32 and 32 described above.
  • Each slip ring 26a, 26b comes into contact with the slip ring 26a, 26b from the axial direction.
  • 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 provided at the lower end of the cover body 28.
  • a signal connector 34 for outputting the rotation angle signal detected by the detection unit 51 to the control unit is provided in parallel with the power supply connector 33 and projecting in the radial direction.
  • the power feeding connector 33 has an opening projecting substantially radially along the lower end on the outer peripheral side of the cover member 4 and a pair of terminal pieces partially embedded in the cover main body 28.
  • the one end portions 33a, 33a are connected to the pigtail harnesses 64, 64, while the other end portion (not shown) disposed inside the opening and exposed to the outside is connected to a female connector terminal on the control unit side. It has become so.
  • the signal connector 34 has an opening formed substantially along the radial direction at the lower end on the outer peripheral side of the cover member 4. While being formed in parallel, the entire width is substantially the same as the width of the cover member 4. Further, as shown in FIG. 1, the signal connector 34 has a plurality of terminal pieces made of a conductive material partially embedded in the cover main body 28, and one end 34a of each terminal piece will be described later. In addition to being connected to the integrated circuit 66 of the printed circuit board 65, the other end 34b is connected to a female connector terminal (not shown) on the control unit side.
  • the rotational angular position of the motor output shaft 14 is detected between the small diameter portion 14b of the motor output shaft 14 and the central portion sandwiching the bottom wall of the circular hole 28k of the cover body 28.
  • the angle sensor 35 is provided.
  • the angle sensor 35 is of an electromagnetic induction type, and is fixed to the detected portion 50 fixed in the small diameter portion 14b of the motor output shaft 14 and the substantially central position of the cover body 28, so that the detected portion And a detection unit 51 that receives a detection signal from 50.
  • the detected portion 50 is formed in a substantially bottomed cylindrical shape made of a synthetic resin material, and has a cylindrical insertion portion 52 inserted and fixed in the small diameter portion 14b, and a bottom wall of the distal end portion of the insertion portion 52. It is mainly composed of a three-leaf thin rotor to be detected 53 fixed to the outer surface.
  • the detected portion 50 is inserted and arranged at the tip end in the circular hole 28k, and the detected rotor 53 is inserted into the bottom surface of the thin bottom wall of the circular hole 28k via a minute clearance C. Are opposed to each other.
  • the detection unit 51 includes a substantially rectangular printed board 65 extending in a radial direction from a substantially central position of the cover body 28, and a plurality of integrated circuits provided on the outer surface of one end of the printed board 65 in the longitudinal direction. (ASIC) 66 and a receiving circuit and an oscillating circuit (not shown) provided on the other end side of the same outer surface as the integrated circuit 66.
  • ASIC application-specific integrated circuit
  • the printed circuit board 65 has a positioning small hole formed in the center of the reception and oscillation circuit (not shown), and the positioning small hole protrudes from the center of the tip of the detected portion 50.
  • the center of the detected rotor 53 and the center of the receiving and oscillating circuit are positioned by press-fitting to the portion 28j.
  • the printed circuit board 65 is fixed to the outer side surface 18b of the cover body 28 by a predetermined fixing means such as a screw. Therefore, the reception and oscillation circuit is connected via the fixed printed circuit board 65.
  • the rotor 53 is opposed to the detected rotor 53 from the axial direction through the bottom wall of the circular hole 28k and a minute clearance C.
  • a circuit 66 detects the rotation angle of the motor output shaft 14 and outputs this detection signal to the control unit.
  • the motor output shaft 14 and the eccentric shaft portion 39 are rotatable by a small-diameter ball bearing 37 provided on the outer peripheral surface of the cylindrical portion 9 b of the driven member 9 and a needle bearing 38 disposed on a side portion of the small-diameter ball bearing 37. It is supported by.
  • the needle bearing 38 includes a cylindrical bearing retainer that is press-fitted into the inner peripheral surface of the eccentric shaft portion 39, and needle rollers that are a plurality of rolling elements that are rotatably held inside the bearing retainer. ing.
  • 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 the like, and engine control based on this And the rotation of the motor output shaft 14 is controlled by energizing the coil 18 through 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. 12 controls the relative rotational phase of the camshaft 2 with respect to the timing sprocket 1.
  • the speed reduction mechanism 12 includes the eccentric shaft portion 39 that performs an eccentric rotational motion, a medium-diameter ball bearing 47 provided on the outer periphery of the eccentric shaft portion 39, and the medium-diameter ball.
  • the roller 48 provided on the outer periphery of the bearing 47; the retainer 41 that allows the roller 48 to move in the radial direction while retaining the roller 48 in the rolling direction; and the driven member 9 that is integral with the retainer 41; Is mainly composed of
  • the shaft center Y of the cam surface 39a formed on the outer peripheral surface is slightly eccentric from the shaft center X of the motor output shaft 14 in the radial direction.
  • the medium-diameter ball bearing 47 is disposed so as to be substantially overlapped at the radial position of the needle bearing 38, and includes an inner ring 47a, an outer ring 47b, and a ball interposed between the two wheels 47a and 47b. It is configured.
  • the inner ring 47a is press-fitted and fixed to the outer peripheral surface of the eccentric shaft portion 39, whereas the outer ring 47b is in a free state without being fixed in the axial direction.
  • the outer ring 47b has a small first end surface on the side of the electric motor 11 in the axial direction that does not come into contact with any part, and the other end surface in the axial direction is between the inner side surface of the retainer 41 facing it.
  • One gap C1 is formed and is in a free state. Further, the outer peripheral surface of the outer ring 47b is in contact with the outer peripheral surface of each roller 48 in a freely rolling manner, and an annular second gap C2 is formed on the outer peripheral side of the outer ring 47b. Due to the second gap C2, the entire medium-diameter ball bearing 47 can move in the radial direction along with the eccentric rotation of the eccentric shaft portion 39, that is, can move eccentrically.
  • the retainer 41 is formed in a bottomed cylindrical shape which 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 protrudes in the same direction as the cylindrical portion 9b.
  • the cylindrical tip portion 41a of the retainer 41 extends in the direction of the partition wall 13a of the motor housing 13 through an annular concave storage space defined by the internal tooth component 5 and the partition wall 13a.
  • a plurality of substantially rectangular roller holding holes 41b for holding the plurality of rollers 48 in a freely rollable manner are formed at substantially equal intervals in the circumferential direction at substantially equal intervals in the circumferential direction of the cylindrical tip portion 41a. Has been.
  • the roller holding hole 41b is formed in a rectangular shape elongated in the front-rear direction with the tip end side closed, and the total number (the number of rollers 48) is the total number of teeth of the internal teeth 5a of the internal tooth component 5. Thus, the reduction ratio is obtained.
  • Each of the rollers 48 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 along with the eccentric movement of the medium-diameter ball bearing 47.
  • the roller holding hole 41b is caused to swing in the radial direction while being guided in the circumferential direction by both side edges.
  • Lubricating oil is supplied into the speed reduction mechanism 12 by lubricating oil supply means.
  • This lubricating oil supply means is formed inside the bearing 02 of the cylinder head 01, and is formed in the oil supply passage through which the lubricating oil is supplied from a main oil gallery (not shown) and in the direction of the internal axis of the camshaft 2.
  • An oil supply hole 67 communicating with the oil supply passage through a groove groove 67a, and an inner axial direction of the driven member 9, and one end opened to the oil supply hole 67 through an annular groove 67b.
  • the timing sprocket 1 rotates through the timing chain in accordance with the rotational drive of the crankshaft of the engine, and the rotational force is transmitted to the motor housing 13 through the internal gear component 5.
  • the motor housing 13 rotates synchronously.
  • the rotational force of the internal tooth component 5 is transmitted from each roller 48 to the camshaft 2 via the cage 41 and the driven member 9.
  • the plurality of drive cams provided on the camshaft 2 opens and closes the intake valves of the respective cylinders.
  • the one end portions 33a and 33a of the pair of terminal pieces, the pigtail harnesses 64 and 64, the power supply brushes 31a and 31b, the slip rings 26a and 26b, etc. are connected from the control unit. Then, the coil 18 of the electric motor 11 is energized. As a result, the motor output shaft 14 is rotationally driven, and the rotational force of this rotational force is transmitted to the camshaft 2 via the speed reduction mechanism 12.
  • the rollers 48 are guided in the radial direction by the roller holding holes 41b of the retainer 41 for each rotation of the motor output shaft 14. It moves while rolling over one internal tooth 5a of the internal tooth constituent part 5 and moving to another adjacent internal tooth 5a, and rolling in the circumferential direction while repeating this in sequence.
  • the rotational force of the motor output shaft 14 is transmitted to the driven member 9 while the rotation of the motor output shaft 14 is decelerated by the rolling contact of the rollers 48.
  • the camshaft 2 rotates relative to the timing sprocket 1 in the forward and reverse directions and the relative rotational phase is converted, and 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 each side surface of the stopper convex portion 21b abuts one of the opposing surfaces of the stopper concave groove 22d. Done. Therefore, 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 control unit outputs a rotational drive signal to the electric motor 11 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 receiving groove 56 provided in the cover main body 28 is located at the side position close to the brush holders 30a and 30b (power supply brushes 31a and 31b) in the radial direction. Since the winding portions 32a and 32a are formed in a parallel state (a state where the winding portions 32a and 32a overlap with the power supply brushes 31a and 31b in the radial direction of the cover member 4), the arrangement of the torsion coil springs 32 and 32 with respect to the power supply brushes 31a and 31b. The configuration is a radial arrangement rather than an axial direction of the apparatus. For this reason, the entire cover member 4 can be flattened, and the axial length of the entire apparatus can be sufficiently shortened.
  • the torsion coil springs 32 and 32 and the retainer 55 are all housed in the housing groove 56 without projecting from the outer surface 28 b of the cover body 28, and the amount of projection from the outer surface 28 b of the cover body 28 is reduced. Can be lowered.
  • the winding portions 32a and 32a and the support shaft 61 of the retainer 55 are almost entirely accommodated in the holding groove portion 57 of the accommodation groove 56, and the other end portions 32c and 32c of the winding portions 32a and 32a.
  • the respective support groove portions 59, 59, and the projecting walls 62b, 62b of the retainer 55 are also accommodated in the concave portions 58b, 58b, and none of them protrudes from the outer surface 28b.
  • the axial length can be further shortened.
  • the one end portions 32b and 32b can be arranged close to each other on both axial sides of the partition wall 62, and Since the other end portions 32c and 32c can be arranged at positions separated from each other, the winding dose and the flexibility of layout of the winding portions 32a and 32a are improved.
  • the axial positions of both end portions 32b, 32b of the torsion coil springs 32, 32 are constant, that is, the distance between the both ends 32b, 32b is the winding of the winding portions 32a, 32a. Regardless of the dose, it is always constant through the partition wall 62, so that the winding dose of each of the winding portions 32a and 32a and the degree of freedom of layout are improved.
  • the width W of the partition wall 62 can be formed relatively thick in accordance with the separation width of the power supply brushes 31a and 31b, so that the rigidity of the partition wall 62 itself is also increased. Can do.
  • the rigidity of the retainer 55 as a whole can be increased.
  • the torsion coil springs 32 and 32 can be supported stably and reliably, and the durability can be improved.
  • the partition wall 62 is used for fixing the retainer 55, the length of the retainer 55 in the axial direction of the support shaft 61 can be shortened. For this reason, the radial layout of the cover body 28 can be made compact.
  • the position between the one end portions 32b, 32b of the torsion coil springs 32, 32 can be set constant irrespective of the winding dose of the winding portions 32a, 32a, each power supply brush 31a,
  • the degree of freedom in layout of the distance between 31b is improved.
  • the layout freedom of the distance between the two slip rings 26a, 26b is also improved. In other words, the space between the two slip rings 26a and 26b can be narrowed, and the radial layout can be made compact.
  • the projecting walls 62b and 62b are integrally fixed to the upper surfaces of the shelves 58 and 58 by welding the tips of the projecting parts 60 and 60. A fixed state can be obtained.
  • each projection 60, 60 can be made shorter than the radial thickness of the partition wall 62. . As a result, it is possible to reduce the influence of the moment applied to each projection 60, 60 during assembly or after welding, and to suppress breakage such as breakage of each projection 60, 60.
  • the winding portions 32a and 32a in addition to the one end portions 32b and 32b, also extend the other end portions 32c and 32c in the radial direction so that the upper surfaces of the support groove portions 59 and 59 are provided. Since the torsion coil springs 32 and 32 are slightly in contact with each other, the torsion coil springs 32 and 32 are slightly lifted by their respective rotational moments so that part of the inner surfaces of the winding portions 32 a and 32 a are end portions 61 a and 61 b of the support shafts 61. However, the winding portions 32a and 32a are less likely to fall down.
  • the present invention is not limited to the configuration of the above embodiment, and for example, the coil diameter of each of the torsion coil springs 32 and 32 and the winding dose of the winding portions 32a and 32a can be arbitrarily set. .
  • the retainer 55 is not limited to the one fixed to the cover main body 28 by the partition wall 62.
  • the retainer 55 may be held by fixing the end portions 61a and 61b of the support shafts 61 to the cover member by welding or welding. good.
  • the fixing protrusion walls 62b and 62b can be divided at the tip ends of the protrusions 60 and 60. It is also possible to insert and fix a pin.
  • the first member may be a timing pulley in addition to the timing sprocket.
  • valve timing control device for an internal combustion engine based on the embodiment described above, for example, the following modes can be considered.
  • the valve timing control device for an internal combustion engine is a valve timing control device for an internal combustion engine that varies the operating characteristics of the engine valve by changing the relative rotational phase of the second member with respect to the first member.
  • An electric motor that is integrally provided on one side of the first member or the second member and that changes the relative rotational phase of the second member with respect to the first member when energized; and a front end portion of the electric motor
  • a cover member arranged and fixed so as to cover, a pair of power supply slip rings provided on the electric motor side and provided on the inner and outer sides, and each corresponding slip ring provided on the cover member side
  • a pair of torsion coil springs that urge each of the power supply brushes in the direction of each slip ring, a support shaft that is inserted in the direction of the internal axis of each of the torsion coil
  • the fixing hole is provided in the partition wall of the support member.
  • a recess is formed on the outer surface of the cover member, and the support member and each torsion coil spring are fixed to the protrusion. It is accommodated and fixed in the recess through the use hole.
  • valve timing control device of the internal combustion engine in a state where the protrusion is inserted into the fixing hole, a tip of the protrusion is welded, and the partition wall is It is fixed to the wall of the recess.
  • two fixing holes for the partition wall are provided at positions in a direction intersecting the support shaft.
  • the concave portion includes a holding groove portion formed in a long groove shape, and a longitudinal direction on both long sides facing the holding groove portion.
  • a pair of shelves projecting inward between both ends, and the protrusions are provided on the upper surfaces of the shelves, respectively, while the partition walls of the support member are Provided integrally with the lower portion, the bottom wall portion accommodated in the holding groove portion together with the support shaft, and projecting from both radial sides of the support shaft, and placed on the upper surface of each shelf portion
  • a pair of fixing protrusion walls in which the fixing holes through which the protrusions are inserted are formed.
  • the partition wall of the retainer can make the length of each protrusion shorter than the radial thickness of the partition wall. As a result, it is possible to reduce the influence of the moment applied to each projection during assembly or after welding, and to suppress breakage such as breakage of each projection.
  • the axis of the support shaft of the support member is located in the holding groove portion.
  • the cover member in any one of the aspects of the valve timing control device of the internal combustion engine, includes an outer layer portion formed of a resin material, and a metal core molded inside the outer layer portion. And a through portion filled with the resin material at a predetermined position of the core material, and the concave portion is formed by the resin material at a formation position of the through portion.
  • one winding portion of each torsion coil spring is accommodated and fixed in the recess through the support member.
  • the portion is provided so as to overlap the penetrating portion of the core member in the radial direction.
  • the concave groove in which one end portions of the pair of torsion coil springs are fitted into and contact with rear end surfaces of the pair of power supply brushes. Is formed.
  • the pair of torsion coil springs are formed so that winding directions are opposite to each other, and the pair of power supply brushes The distance between the respective one end portions that respectively press the rear end surfaces is close, whereas the distance between the respective other end portions that are in elastic contact with the cover member is separated.
  • the pair of torsion coil springs are configured such that each one end portion that presses the pair of power supply brushes is relative to each other end portion. Therefore, a spring force acts in the direction of opening from the closed side.
  • the valve timing control device for an internal combustion engine includes a drive rotator to which the rotational force from the crankshaft is transmitted and a driven rotator that rotates integrally with the camshaft, and the drive rotation
  • a valve timing control device for an internal combustion engine that converts a relative rotational phase of a driven rotor relative to a body, an electric motor provided integrally with the drive rotor, and a front end portion of the electric motor opposite to the camshaft And a pair of power feedings provided on the cover member and in contact with the slip rings, respectively, and a cover member disposed oppositely from the axial direction, a power feeding slip ring provided on the front end of the electric motor.
  • a support member having a brush, a cylindrical support shaft, and a locking portion provided at a substantially central position in the axial direction of the support shaft; and the support shaft sandwiching the locking portion
  • a spring and the cover member are formed so as to overlap with each of the power supply brushes in the radial direction of the cover member, and each torsion coil spring is accommodated in the state attached to the support shaft of the support member.
  • the cover member includes a resin portion and a metal plate-like core material fixed to the inside of the resin portion, and the core material is notched.
  • the concave portion is formed by the resin portion filled in a predetermined portion, and a part of the locking portion of the support member disposed in the concave portion has a diameter with respect to the core member through the concave portion. It is arranged to overlap in the direction.
  • the cover member in any one of the aspects of the valve timing control device of the internal combustion engine, includes an outer layer portion in which a cover body is formed of a resin material, and a metal core molded on the outer layer portion.
  • the core material has a penetrating portion at a predetermined position, and the concave portion of the cover body is separated from the penetrating portion of the core material by the resin material.
  • the thickness of the entire cover body including the torsion coil springs can be made as small as possible by forming the recesses for accommodating the torsion coil springs at the positions where the through portions are formed.
  • the axial length can be shortened.
  • the rigidity of the entire cover body can be increased by the metal core material.
  • the fixing means includes a protrusion provided on an outer surface side of the cover member on which the torsion coil spring is disposed, A fixing hole that is formed through the support member and is fitted into the protrusion.

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

Abstract

A pair of shelf parts 58 having protruding parts 60 in the top surfaces are provided in opposing side surfaces of an accommodating groove 56 provided in an outer-side surface 28b of a cover body 28 of a cover member 4, winding wire sections 32a of a pair of torsion coil springs 32 supported at the end parts 61a, 61b of a support shaft 61 of a retainer are accommodated in the accommodating groove, securing protruding walls 62b are provided in positions in the center of the support shaft 61, and, with the protruding parts of the shelf parts inserted through securing holes 62c bored in the centers of the securing protruding walls, the leading ends of the protruding parts are welded, whereby the retainer is secured to the shelf parts 58. The device can thereby be reduced in axial length, and the support member can be firmly secured to the cover member.

Description

内燃機関のバルブタイミング制御装置Valve timing control device for internal combustion engine
　本発明は、例えば吸気弁や排気弁の開閉タイミングを制御する内燃機関のバルブタイミング制御装置に関する。 The present invention relates to a valve timing control device for an internal combustion engine that controls the opening and closing timing of an intake valve and an exhaust valve, for example.
　内燃機関のバルブタイミング制御装置としては、本出願人が先に出願した以下の特許文献１に記載されているものが知られている。 2. Description of the Related Art As a valve timing control device for an internal combustion engine, one described in the following Patent Document 1 previously filed by the present applicant 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部にプレート状の封止部材が固定されていると共に、前記前端部の前方位置には、所定のクリアランスをもってカバー部材が配置されている。前記封止部材には、前記クリアランスに臨む内外二重の給電用スリップリングが設けられている一方、前記カバー部材には、先端部が前記各給電用スリップリングに摺接して前記電動モータへ給電を行う一対の給電用ブラシが設けられている。 In this valve timing control device, a plate-shaped sealing member is fixed to the front end portion of the motor housing of the electric motor, and a cover member is disposed at a front position of the front end portion with a predetermined clearance. The sealing member is provided with an inner / outer double power supply slip ring facing the clearance, while the cover member has a front end slidably contacting each of the power supply slip rings to supply power to the electric motor. A pair of power supply brushes are provided.
　前記各給電用ブラシは、この給電用ブラシの後端側に弾装されたコイルスプリングによって、各先端部が前記各スリップリングの上面方向へ付勢されている。 Each of the power supply brushes is urged toward the top surface of each slip ring by a coil spring elastically mounted on the rear end side of the power supply brush.
　そして、外部電源から給電用コネクタを介して給電用ブラシに供給された電流は、前記各スリップリングを介して切り換え用ブラシやコミュテータから電動モータのコイルに通電されて、モータ出力軸が回転駆動されることにより、クランクシャフトに対するカムシャフトの相対回転位相を変更して吸気弁のバルブタイミングを制御するようになっている。 Then, the current supplied from the external power source to the power supply brush through the power supply connector is supplied to the coil of the electric motor from the switching brush and the commutator through the slip rings, and the motor output shaft is driven to rotate. Thus, the valve timing of the intake valve is controlled by changing the relative rotation phase of the camshaft with respect to the crankshaft.
　しかしながら、前記公報記載のバルブタイミング制御装置にあっては、前記各コイルスプリングが、各給電用ブラシの軸方向端部に軸方向に沿って直列状態に設けられていることから、装置の軸方向の長さが必然的に長くなってしまう。この結果、車両のエンジンルーム内でのレイアウトの自由度が制約されてしまう。 However, in the valve timing control device described in the publication, each coil spring is provided in series along the axial direction at the axial end portion of each power supply brush. The length of will inevitably become longer. As a result, the degree of freedom of layout in the engine room of the vehicle is limited.
特開２０１４－０９８３７６号公報JP 2014-098376 A
　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、装置の軸方向の短尺化と、カバー部材に対する支持部材の強固な固定状態が得られ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目的としている。 The present invention has been devised in view of the above-described conventional technical problems, and provides a valve timing control device for an internal combustion engine that can shorten the axial direction of the device and can provide a firmly fixed state of a support member to a cover member. It is intended to provide.
　本願請求項１に記載の発明は、とりわけ、第１部材または第２部材の一方側に一体的に設けられ、通電されることによって前記第１部材に対する第２部材の相対回転位相を変更する電動モータと、該電動モータの前端部を覆うように配置固定されたカバー部材と、前記電動モータ側に設けられ、内外二重に設けられた一対の給電用のスリップリングと、前記カバー部材側に設けられ、対応する前記各スリップリングに接触して給電する一対の給電用ブラシと、前記カバー部材側に、巻き線部が前記カバー部材の径方向において前記各給電用ブラシと重なるように設けられて、前記各給電用ブラシを前記各スリップリング方向へ付勢する一対の捩りコイルばねと、前記各捩りコイルばねの内部軸方向に挿通する支持軸と、該支持軸に設けられて、前記２つの捩りコイルばねを軸方向で隔成しつつ前記カバー部材に固定される隔壁とを有する支持部材と、前記カバー部材の前記捩りコイルばねが配置される外側面側に設けられた突起部と、前記支持部材に貫通形成されて、前記突起部に嵌入されることにより前記支持部材をカバー部材に固定する固定用孔と、を備えたことを特徴としている。 The invention according to claim 1 of the present application is, inter alia, an electric motor that is integrally provided on one side of the first member or the second member and changes the relative rotational phase of the second member relative to the first member when energized. A motor, a cover member arranged and fixed so as to cover the front end of the electric motor, a pair of power supply slip rings provided on the electric motor side and provided on the inner and outer sides, and on the cover member side A pair of power supply brushes that are provided in contact with each of the corresponding slip rings to supply power, and on the cover member side, a winding portion is provided so as to overlap the power supply brush in the radial direction of the cover member. A pair of torsion coil springs for urging each of the power supply brushes in the direction of each slip ring, a support shaft inserted in the direction of the internal axis of each of the torsion coil springs, and the support shaft. A support member having a partition wall that is fixed to the cover member while separating the two torsion coil springs in the axial direction, and a protrusion provided on an outer surface side of the cover member on which the torsion coil spring is disposed And a fixing hole for fixing the support member to the cover member by being inserted into the protrusion and penetratingly formed in the support member.
　この発明によれば、装置の軸方向の長さの短尺化が図れると共に、支持部材をカバー部材に対して強固に固定することができる。 According to the present invention, the axial length of the apparatus can be shortened, and the support member can be firmly fixed to the cover member.
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品を示す分解斜視図である。It is a disassembled perspective view which shows the main components 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. 本実施形態に供される封止部材の背面図である。It is a rear view of the sealing member provided for this embodiment. 本実施形態に供されるカバー本体の平面図である。It is a top view of the cover main body provided for this embodiment. 本実施形態に供される捩りコイルばねとリテーナがカバー本体に組み付けられた状態を示す平面図である。It is a top view which shows the state with which the torsion coil spring and retainer which are provided to this embodiment were assembled | attached to the cover main body. 本実施形態に供される捩りコイルばねとリテーナを示す分解斜視図である。It is a disassembled perspective view which shows the torsion coil spring and retainer which are provided to this embodiment. カバー本体に組み込まれた捩りコイルばねとリテーナを示す斜視図である。It is a perspective view which shows the torsion coil spring and the retainer integrated in the cover main body. 図７のＣ－Ｃ線断面図である。It is CC sectional view taken on the line of FIG.
　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、バルブタイミング制御装置を吸気弁側に適用したものを示している。 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. In this embodiment, the valve timing control device is applied to the intake valve side.
　この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第１部材（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、前記タイミングスプロケット１から伝達された回転力によって回転する第２部材であるカムシャフト２と、前記タイミングスプロケット１とカムシャフト２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の前端側に配置されたカバー部材４と、を備えている。 As shown in FIGS. 1 and 2, the valve timing control device includes a timing sprocket 1 that is a first member (drive rotating body) that is rotationally driven by a crankshaft of an internal combustion engine, and a bearing 02 on a cylinder head 01. The camshaft 2 is a second member that is rotatably supported and rotated by the rotational force transmitted from the timing sprocket 1, and is disposed between the timing sprocket 1 and the camshaft 2, and depends on the engine operating state. The phase change mechanism 3 that changes the relative rotational phase of the two and 1 and the cover member 4 disposed on the front end side of the phase change mechanism 3 is provided.
　前記タイミングスプロケット１は、全体が鉄系金属によって環状一体に形成され、内周面が段差径状のスプロケット本体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ギア部１ｂと、前記スプロケット本体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 is formed integrally with an iron-based metal in an annular shape, and the inner peripheral surface is integrally provided on the outer periphery of the sprocket body 1a with a stepped diameter, and is wound outside the drawing. The gear part 1b which receives the rotational force from a crankshaft via this timing chain, and the internal-tooth structure part 5 integrally provided in the front-end side of the said sprocket main body 1a are comprised.
　また、このタイミングスプロケット１は、スプロケット本体１ａと前記カムシャフト２の前端部に設けられた後述する従動部材９との間に、１つの大径ボールベアリング４３が介装されており、この大径ボールベアリング４３によって、タイミングスプロケット１が前記従動部材９の外周に相対回転自在に軸受されている。 The timing sprocket 1 has a single large-diameter ball bearing 43 interposed between a sprocket body 1a and a driven member 9 (described later) provided at the front end of the camshaft 2. The timing sprocket 1 is supported on the outer periphery of the driven member 9 by a ball bearing 43 so as to be relatively rotatable.
　前記大径ボールベアリング４３は、一般的なもので、外輪４３ａと、内輪４３ｂ及び該両輪の間に介装されたボール４３ｃと、から構成され、前記外輪４３ａがスプロケット本体１ａの内周側に形成された円環状の外輪固定部１ｄに圧入固定されているのに対して内輪４３ｂが従動部材９の段差円環状の内輪固定部９ｅに圧入固定されている。 The large-diameter ball bearing 43 is a general one and includes an outer ring 43a, an inner ring 43b, and a ball 43c interposed between the two rings, and the outer ring 43a is disposed on the inner peripheral side of the sprocket body 1a. The inner ring 43b is press-fitted and fixed to the annular annular inner ring fixing part 9e of the driven member 9 while being press-fitted and fixed to the formed annular outer ring fixing part 1d.
　前記内歯構成部５は、前記スプロケット本体１ａの前端部外周側に一体に設けられ、位相変更機構３の前方へ延出した円筒状に形成されていると共に、内周には波形状の複数の内歯５ａが形成されている。 The internal tooth component 5 is integrally formed on the outer peripheral side of the front end portion of the sprocket body 1a, is formed in a cylindrical shape extending forward of the phase change mechanism 3, and has a plurality of wave shapes on the inner periphery. The inner teeth 5a are formed.
　さらに、スプロケット本体１ａの内歯構成部５と反対側の後端部には、図４にも示すように、円環状のストッパプレート２１が配置されている。このストッパプレート２１は、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設定されていると共に、内径が前記大径ボールベアリング４３の外輪４３ａの内径よりも小径に設定されている。 Furthermore, an annular stopper plate 21 is disposed at the rear end portion of the sprocket body 1a opposite to the internal tooth component 5 as shown in FIG. The stopper plate 21 is formed in an annular shape by a metal plate material, and has an outer diameter set to be substantially the same as the outer diameter of the sprocket body 1 a and an inner diameter larger than the inner diameter of the outer ring 43 a of the large-diameter ball bearing 43. It is set to a small diameter.
　前記ストッパプレート２１の内周部２１ａは、前記外輪４３ａの軸方向の外端面に当接配置されていると共に、内周縁の所定位置には、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２１ｂが一体に設けられている。このストッパ凸部２１ｂは、ほぼ扇状に形成されて、先端縁２１ｃが後述するストッパ凹溝２２ｄの円弧状内周面に沿った円弧状に形成されている。 The inner peripheral portion 21a of the stopper plate 21 is disposed in contact with the outer end surface of the outer ring 43a in the axial direction, and protrudes radially inward, that is, toward the central axis direction at a predetermined position of the inner peripheral edge. The stopper convex part 21b is provided integrally. The stopper convex portion 21b is formed in a substantially fan shape, and the tip edge 21c is formed in an arc shape along an arc-shaped inner peripheral surface of a stopper concave groove 22d described later.
　前記スプロケット本体１ａ（内歯構成部５）及びストッパプレート２１の各外周部には、それぞれボルト７が挿通する挿通孔１ｃ、２１ｄが周方向のほぼ等間隔位置に６つ貫通形成されている。なお、前記スプロケット本体１ａと内歯構成部５は、後述する減速機構１２のケーシングとして構成されている。 In the outer peripheral portions of the sprocket main body 1a (internal tooth constituting portion 5) and the stopper plate 21, six insertion holes 1c and 21d through which the bolts 7 are inserted are formed at substantially equal intervals in the circumferential direction. The sprocket body 1a and the internal gear component 5 are configured as a casing for a speed reduction mechanism 12 to be described later.
　前記カムシャフト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と共に、軸方向の一端部に有するフランジ部２ａにアダプタ２２を介して従動回転体である従動部材９がカムボルト１０によって軸方向から共締め固定されている。 The camshaft 2 has two drive cams per cylinder for opening an intake valve (not shown) on the outer periphery, and a driven rotor through a flange portion 2a at one end in the axial direction via an adapter 22. The driven member 9 is fixed together by a cam bolt 10 from the axial direction.
　前記従動部材９は、鉄系金属によって一体に形成され、図１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の前端面中央位置から軸方向へ突出した円筒部９ｂと、内部軸方向に貫通形成されて、カムボルト１０を挿通させるボルト挿通孔９ｃと、を備えている。 The driven member 9 is integrally formed of an iron-based metal, and as shown in FIG. 1, a disk-like fixed end portion 9a formed on the rear end side (camshaft 2 side), and the fixed end portion 9a. A cylindrical portion 9b that protrudes in the axial direction from the center position of the front end surface thereof, and a bolt insertion hole 9c that is formed to penetrate the cam bolt 10 through the inner axial direction.
　また、固定端部９ａは、後端面に形成された第１嵌合溝９ｄが前記カムシャフト２のフランジ部２ａの前端面に後述するアダプタ２２を介して当接配置されて、前記カムボルト１０の軸力によってフランジ部２ａに軸方向から圧接固定されている。固定端部９ａの外周部には、後述する複数のローラ４８を保持する円筒状の保持器４１が一体に設けられている。 Further, the fixed end portion 9a has a first fitting groove 9d formed on the rear end surface thereof in contact with the front end surface of the flange portion 2a of the camshaft 2 via an adapter 22 which will be described later. The flange portion 2a is pressed against and fixed to the flange portion 2a by an axial force. A cylindrical retainer 41 that holds a plurality of rollers 48 to be described later is integrally provided on the outer peripheral portion of the fixed end portion 9a.
　前記円筒部９ｂは、外周に小径ボールベアリング３７とニードルベアリング３８が軸方向に沿って並列に設けられている。 The cylindrical portion 9b is provided with a small-diameter ball bearing 37 and a needle bearing 38 on the outer periphery in parallel along the axial direction.
　前記アダプタ２２は、図１及び図２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２２ａと、電動モータ１１方向へ突出した有底円筒状の中央側の内周部２２ｂと、から構成されている。 As shown in FIGS. 1 and 2, the adapter 22 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 22 a and an electric motor. It is comprised from the inner peripheral part 22b of the center side of the bottomed cylindrical shape protruded in the motor 11 direction.
　前記外周部２２ａ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、各構成部品の組立て後に、電動モータ１１側の内側面の外周側が規制面２２ｃとして構成されている。この規制面２２ｃは、前記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 22a 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 11 side serves as the restricting surface 22c after assembling each component. It is configured. The restricting surface 22c is in contact with the other axial end surface of the inner ring 43b of the large-diameter ball bearing 43 so as to restrict movement outward in the axial direction.
　また、前記外周部２２ａの外周面には、図４に示すように、前記ストッパプレート２１のストッパ凸部２１ｂが係入するストッパ凹溝２２ｄが円周方向に沿って円弧状に形成されている。このストッパ凹溝２２ｄは、円周方向へ所定長さの円弧状に形成されて、この長さ範囲で回動したストッパ凸部２１ｂの両端縁が周方向の対向縁にそれぞれ当接することによって、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規制するようになっている。 Further, as shown in FIG. 4, a stopper concave groove 22d for engaging the stopper convex portion 21b of the stopper plate 21 is formed in an arc shape along the circumferential direction on the outer peripheral surface of the outer peripheral portion 22a. . The stopper concave groove 22d is formed in a circular arc shape having a predetermined length in the circumferential direction, and both end edges of the stopper convex portion 21b rotated in this length range come into contact with opposite circumferential edges, respectively. The relative rotational position of the camshaft 2 on the maximum advance angle side or the maximum retard angle side with respect to the timing sprocket 1 is regulated.
　前記内周部２２ｂは、電動モータ１１側に突出した有底円筒状の凸部と、該凸部をプレス成形によって成形した際に、同時に形成された円盤溝状の第２嵌合溝２２ｅと、から構成されている。 The inner peripheral portion 22b includes a bottomed cylindrical convex portion protruding toward the electric motor 11, and a disc groove-shaped second fitting groove 22e formed simultaneously when the convex portion is formed by press molding. , Is composed of.
　また、内周部２２ｂの凸部の中央位置には、前記カムボルト１０の軸部１０ｂが挿通する挿通孔２２ｆが貫通形成されていると共に、前記第２嵌合溝２２ｅにはカムシャフト２のフランジ部２ａの端面から突出した円環状の突部２ｄが嵌合するようになっている。また、内周部２２ｂには、後述する潤滑油通路の一部を構成する図外の油通路孔が貫通形成されている。 Further, an insertion hole 22f through which the shaft portion 10b of the cam bolt 10 is inserted is formed at the center position of the convex portion of the inner peripheral portion 22b, and the flange of the camshaft 2 is inserted into the second fitting groove 22e. An annular projection 2d protruding from the end face of the portion 2a is fitted. In addition, an oil passage hole (not shown) that constitutes a part of a later-described lubricating oil passage is formed through the inner peripheral portion 22b.
　前記凸部は、前記従動部材９の第１嵌合溝９ｄ内に軸方向から圧入によって嵌合しており、この嵌合した状態で、前記凸部の先端壁を、カムボルト１０によってカムシャフト２の突部２ｄと従動部材９の固定端部９ａとの間に挟持状態に結合されている。 The convex portion is fitted into the first fitting groove 9d of the driven member 9 by press-fitting from the axial direction, and in this fitted state, the tip wall of the convex portion is connected to the camshaft 2 by the cam bolt 10. The projecting portion 2d and the fixed end portion 9a of the driven member 9 are coupled in a sandwiched state.
　前記カムボルト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３７の内輪を軸方向から支持していると共に、軸部１０ｂの外周に前記カムシャフト２の一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。 As shown in FIG. 1, the cam bolt 10 has an axial end surface of the head portion 10a supporting the inner ring of the small-diameter ball bearing 37 from the axial direction, and an outer periphery of the shaft portion 10b from one end portion of the camshaft 2. A male screw 10c is formed to be screwed onto the female screw 2c formed in the internal axis direction.
　前記位相変更機構３は、前記従動部材９の円筒部９ｂの前端側に配置された電動モータ１１と、該電動モータ１１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１２と、から主として構成されている。 The phase changing mechanism 3 includes an electric motor 11 disposed on the front end side of the cylindrical portion 9 b of the driven member 9, and a speed reducing mechanism 12 that reduces the rotational speed of the electric motor 11 and transmits it to the camshaft 2. It is mainly composed.
　前記電動モータ１１は、図１及び図２に示すように、ブラシ付きのＤＣモータであって、前記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１３と、該モータハウジング１３の内部に回転自在に設けられた円筒状のモータ出力軸１４と、モータハウジング１３の内周面に固定された半円弧状の４つの永久磁石１５と、モータハウジング１３の前端部にかしめ固定された封止部材１６と、を備えている。 As shown in FIGS. 1 and 2, the electric motor 11 is a brushed DC motor, a motor housing 13 that is a yoke that rotates integrally with the timing sprocket 1, and rotates inside the motor housing 13. A cylindrical motor output shaft 14 provided freely, four semicircular arc-shaped permanent magnets 15 fixed to the inner peripheral surface of the motor housing 13, and a sealing member fixed by caulking to the front end portion of the motor housing 13 16.
　前記モータハウジング１３は、図１に示すように、鉄系金属材をプレス成形によって有底筒状に形成されて、後端側に円板状の隔壁１３ａを有し、該隔壁１３ａのほぼ中央に後述する偏心軸部３９が挿通される大径な軸挿通孔１３ｂが形成されていると共に、該軸挿通孔１３ｂの孔縁にカムシャフト２の軸方向へ突出した円筒状の延出部１３ｃが一体に設けられている。また、前記隔壁１３ａの外周部の内部には、雌ねじ孔１３ｄが軸方向に沿って形成されている。 As shown in FIG. 1, the motor housing 13 is formed by pressing a ferrous metal material into a bottomed cylindrical shape, and has a disk-shaped partition wall 13a on the rear end side, and is substantially at the center of the partition wall 13a. Is formed with a large-diameter shaft insertion hole 13b into which an eccentric shaft portion 39, which will be described later, is inserted, and a cylindrical extension portion 13c protruding in the axial direction of the camshaft 2 at the hole edge of the shaft insertion hole 13b. Are provided integrally. A female screw hole 13d is formed along the axial direction inside the outer peripheral portion of the partition wall 13a.
　前記雌ねじ孔１３ｄは、各ボルト挿通孔１ｃ、２１ｄと対応した位置に形成されており、これらに挿通した６本のボルト７によって前記タイミングスプロケット１とストッパプレート２１及びモータハウジング１３が軸方向から共締め固定されている。なお、モータハウジング１３の隔壁１３ａの後端面に、前記内歯構成部５が軸方向から当接している。 The female screw hole 13d is formed at a position corresponding to each of the bolt insertion holes 1c and 21d, and the timing sprocket 1, the stopper plate 21 and the motor housing 13 are shared in the axial direction by the six bolts 7 inserted through these holes. Tightened and fixed. Note that the inner tooth constituent portion 5 is in contact with the rear end surface of the partition wall 13a of the motor housing 13 from the axial direction.
　前記モータ出力軸１４は、図１及び図２に示すように、周壁が段差径状に形成されて、軸方向のほぼ中央位置に形成された段差壁１４ｃを介してカムシャフト２側の一端部に形成された大径部１４ａと、その軸方向反対側の他端部に形成された小径部１４ｂと、を有し、内部軸方向には、前記カムボルト１０が挿入可能な挿入孔１４ｄが貫通形成されている。 As shown in FIGS. 1 and 2, the motor output shaft 14 has one end portion on the camshaft 2 side through a step wall 14c formed in a substantially central position in the axial direction. And an insertion hole 14d into which the cam bolt 10 can be inserted penetrates in the internal axial direction. Is formed.
　前記大径部１４ａは、外周に鉄心ロータ１７が固定されていると共に、後端側に減速機構１２の一部を構成する後述の偏心軸部３９が軸方向に沿って一体に設けられている。 The large-diameter portion 14a has an iron core rotor 17 fixed to the outer periphery, and an eccentric shaft portion 39, which will be described later, constituting a part of the speed reduction mechanism 12 on the rear end side, is integrally provided along the axial direction. .
　一方、前記小径部１４ｂは、外周にコミュテータ２０が圧入固定されていると共に、内周に後述する角度センサ３５の被検出部５０が挿入固定されている。 On the other hand, in the small diameter portion 14b, the commutator 20 is press-fitted and fixed to the outer periphery, and a detected portion 50 of an angle sensor 35 described later is inserted and fixed to the inner periphery.
　前記鉄心ロータ１７は、図１及び図２に示すように、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１８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、内周部が前記モータ出力軸１４の段差壁１４ｃの外周に軸方向の位置決めされつつ固定されている。 As shown in FIGS. 1 and 2, the iron core rotor 17 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 18 is wound. The motor output shaft 14 is fixed to the outer periphery of the stepped wall 14c while being axially positioned.
　一方、前記コミュテータ２０は、内周側の円環部材２０ａと、該円環部材２０ａの外周に設けられた環状の電極部２０ｂと、から構成されている。前記円環部材２０ａは、その外径が前記大径部１４ａの外径とほぼ同一に設定されていると共に、小径部１４ｂの軸方向のほぼ中央位置に配置されている。前記電極部２０ｂは、導電材によって円環状に形成されて、前記鉄心ロータ１７の極数と同数に分割された各セグメントに前記コイル１８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 includes an annular member 20a on the inner peripheral side, and an annular electrode portion 20b provided on the outer periphery of the annular member 20a. The annular member 20a has an outer diameter set to be substantially the same as the outer diameter of the large-diameter portion 14a, and is disposed at a substantially central position in the axial direction of the small-diameter portion 14b. The electrode portion 20b is formed in an annular shape with a conductive material, and the ends of the coil wires led out of the coil 18 are electrically connected to the segments divided into the same number as the number of poles of the iron core rotor 17. Yes.
　前記各永久磁石１５は、全体が円筒状に形成されて円周方向に複数の磁極を有していると共に、その軸方向の位置が、図１に示すように、前記鉄心ロータ１７の軸方向の中心に対して前記封止部材１６側にオフセット配置されている。 Each of the permanent magnets 15 is formed in a cylindrical shape and has a plurality of magnetic poles in the circumferential direction, and its axial position is the axial direction of the iron core rotor 17 as shown in FIG. The offset member is offset from the center of the sealing member 16 side.
　前記封止部材１６は、図１及び図５に示すように、鉄系金属材からなる円盤状のプレート部１６ａと、該プレート部１６ａのほぼ全体をモールドした円板状の樹脂部１６ｂと、中央部に貫通形成されて、モータ出力軸１４の小径部１４ｂが挿通される軸挿通孔１６ｃと、から構成されている。 As shown in FIGS. 1 and 5, the sealing member 16 includes a disk-shaped plate portion 16a made of an iron-based metal material, and a disk-shaped resin portion 16b obtained by molding almost the entire plate portion 16a. The shaft insertion hole 16c is formed through the central portion and through which the small diameter portion 14b of the motor output shaft 14 is inserted.
　前記プレート部１６ａは、前記樹脂部１６ｂに覆われていない外周部が前記モータハウジング１３の前端部内周面に形成された円環溝にかしめによって位置決め固定されている。 The outer peripheral portion of the plate portion 16a that is not covered with the resin portion 16b is positioned and fixed by caulking in an annular groove formed on the inner peripheral surface of the front end portion of the motor housing 13.
　また、前記封止部材１６には、図５に示すように、前記プレート部１６ａに形成された複数の開口孔の内側に配置されて、前記樹脂部１６ｂの前端部に複数のリベット４０により固定された銅製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て、コイルスプリング２４ａ、２４ｂのばね力で円弧状の各先端面が前記コミュテータ２０の外周面に径方向から弾接する整流子である一対の切換用ブラシ２５ａ、２５ｂと、樹脂部１６ｂの前端面側に、それぞれの外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スリップリング２６ａ，２６ｂと、前記各切換用ブラシ２５ａ、２５ｂと各スリップリング２６ａ，２６ｂを電気的に接続するハーネス２７ａ、２７ｂと、が設けられている。前記内周側の小径な給電用スリップリング２６ａと、外周側の大径な給電用スリップリング２６ｂは、銅材からなる薄板をプレスによって円環状に打ち抜き形成されている。 Further, as shown in FIG. 5, the sealing member 16 is disposed inside a plurality of opening holes formed in the plate portion 16a and fixed to the front end portion of the resin portion 16b by a plurality of rivets 40. A pair of brush holders 23a, 23b made of copper, and accommodated in the brush holders 23a, 23b so as to be slidable along the radial direction. A pair of switching brushes 25a and 25b, which are commutators whose tip surfaces elastically contact the outer peripheral surface of the commutator 20 from the radial direction, and the front end surface side of the resin portion 16b are molded and fixed with their respective outer surfaces exposed. Double inner and outer power supply slip rings 26a, 26b, harnesses 27a for electrically connecting the switching brushes 25a, 25b and the slip rings 26a, 26b, And 7b, are provided. The inner peripheral small-diameter feeding slip ring 26a and the outer peripheral large-diameter feeding slip ring 26b are formed by punching a thin plate made of a copper material into an annular shape by pressing.
　前記カバー部材４は、図１、図２及び図６、図７に示すように、ほぼ円盤状に形成されて、封止部材１６の前端側に対向配置されており、前記モータハウジング１３の前端部を覆う形で配置されたカバー本体２８と、該カバー本体２８の外側面２８ｂの一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, 2, 6, and 7, the cover member 4 is formed in a substantially disk shape and is disposed to face the front end side of the sealing member 16. The cover main body 28 is arranged so as to cover the portion, and the synthetic resin cap portion 29 covers a part of the outer side surface 28b of the cover main body 28.
　前記カバー本体２８は、外径が前記モータハウジング１３の外径より大きく形成されて、合成樹脂材によって所定の肉厚に形成された外層部の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 has an outer diameter larger than the outer diameter of the motor housing 13, and a metal reinforcing plate 28a is molded and fixed inside an outer layer portion formed with a predetermined thickness by a synthetic resin material. ing.
　また、カバー本体２８は、外周部の４箇所に突設された円弧状のボス部２８ｃに、チェーンケース３６に固定されるボルトが挿通されるボルト挿通孔２８ｄが樹脂材にモールドされた金属製のスリーブ２８ｅによってそれぞれ形成されていると共に、図６中、下側の左右２つのボス部２８ｃには、カバー部材４をチェーンケース３６に取り付ける際に位置決めピンを挿通する２つのピン挿通孔２８ｆ、２８ｆが貫通形成されている。 The cover main body 28 is made of metal in which a bolt insertion hole 28d into which a bolt fixed to the chain case 36 is inserted is molded into a resin material in an arc-shaped boss portion 28c projecting at four locations on the outer peripheral portion. The two left and right boss portions 28c in FIG. 6 have two pin insertion holes 28f through which positioning pins are inserted when the cover member 4 is attached to the chain case 36, respectively. 28f is formed through.
　前記補強プレート２８ａは、カバー本体２８の外径よりも小さなほぼ円盤状に形成され、中央位置に形成された貫通孔に合成樹脂材が充填されており、この樹脂材によって凹溝である後述の円形穴２８ｋを形成すると共に、下部側には後述する信号用コネクタ３４の導電材が配置される細長い長方形状の図外の切欠部が径方向に沿って形成されている。 The reinforcing plate 28a is formed in a substantially disk shape smaller than the outer diameter of the cover body 28, and a synthetic resin material is filled in a through hole formed at the center position. A circular hole 28k is formed, and an elongated notch-shaped notch portion in which a conductive material of a signal connector 34 to be described later is disposed is formed along the radial direction on the lower side.
　また、カバー本体２８は、前記補強プレート２８ａの図６中のほぼ上方位置に形成された窓孔内に充填された合成樹脂材によって一対の矩形状のホルダ孔２８ｇ、２８ｇが貫通形成されていると共に、該ホルダ孔２８ｇ、２８ｇの斜め上方位置には、後述する一対の捩りコイルばね３２、３２を収容する凹部である収容溝５６が形成されている。 Further, the cover main body 28 has a pair of rectangular holder holes 28g and 28g penetratingly formed by a synthetic resin material filled in a window hole formed substantially above the reinforcing plate 28a in FIG. In addition, an accommodation groove 56 that is a recess for accommodating a pair of torsion coil springs 32 and 32, which will be described later, is formed at an obliquely upper position of the holder holes 28g and 28g.
　前記各ホルダ孔２８ｇ、２８ｇに、角筒状のブラシホルダ３０ａ、３０ｂが軸方向に沿ってモールド固定されている。 In each of the holder holes 28g and 28g, rectangular tube-shaped brush holders 30a and 30b are mold-fixed along the axial direction.
　また、カバー本体２８の外側面２８ｂには、図１及び図６に示すように、前記キャップ部２９が嵌着固定される異形円形状の係止壁２８ｈが一体に設けられている。一方、前記キャップ部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円環状の係止凸部２９ａがカバー本体２８の係止壁２８ｈに軸方向から圧入によって係止固定されている。 Further, as shown in FIGS. 1 and 6, a deformed circular locking wall 28 h to which the cap portion 29 is fitted and fixed is integrally provided on the outer surface 28 b of the cover main body 28. On the other hand, the cap portion 29 is formed in a disk plate shape, and an annular locking projection 29a formed integrally with the outer peripheral edge is locked and fixed to the locking wall 28h of the cover body 28 by press-fitting from the axial direction. Has been.
　また、カバー本体２８は、図７に示すように、前記各ホルダ孔２８ｇ、２８ｇ内に、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製の一対の角筒状ブラシホルダ３０ａ、３０ｂが軸方向に沿って固定されていると共に、該各ブラシホルダ３０ａ、３０ｂの内部には、各先端面が前記各スリップリング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。 Further, as shown in FIG. 7, the cover main body 28 includes a pair of square rectangular brush holders 30 a made of copper at positions facing the slip rings 26 a and 26 b in the axial direction in the holder holes 28 g and 28 g. 30b is fixed along the axial direction, and a pair of power supply brushes 31a and 31b whose tip end surfaces are in sliding contact with the slip rings 26a and 26b are axially arranged in the brush holders 30a and 30b. Is slidably held in the head.
　前記ブラシホルダ３０ａ、３０ｂ及び給電用ブラシ３１ａ、３１ｂは、前記カバー本体２８の径方向内側で内側と外側に並設されていると共に、それぞれの後端部が前記カバー本体２８の外側面２８ｂに臨んでいる。 The brush holders 30a and 30b and the power feeding brushes 31a and 31b are arranged in parallel on the inner side and the outer side on the radial inner side of the cover main body 28, and the rear ends of the brush holders 30a and 30b and the power supply brushes 31a and 31b are on the outer side surface 28b of the cover main body 28. I'm here.
　前記カバー本体２８の電動モータ１１側の内面のほぼ中央位置に形成された前記円形穴２８ｋは、内径が後述する被検出部５０の先端部の外径よりも大きく形成されていると共に、その深さは前記カバー本体２８の軸方向の幅長さよりも僅かに小さく形成されて、薄肉な底壁を有している。 The circular hole 28k formed at substantially the center position of the inner surface of the cover main body 28 on the electric motor 11 side is formed so that the inner diameter is larger than the outer diameter of the distal end portion of the detected portion 50 described later, and the depth thereof. The cover body 28 is formed slightly smaller than the axial width of the cover body 28 and has a thin bottom wall.
　前記カバー本体２８の外側面２８ｂには、前記各給電用ブラシ３１ａ、３１ｂを前記スリップリング２６ａ、２６ｂ方向へ付勢する一対の捩りコイルばね３２、３２を支持部材であるリテーナ５５を介して収容する矩形状の収容溝５６が形成されている。 A pair of torsion coil springs 32 and 32 for urging the power supply brushes 31a and 31b in the direction of the slip rings 26a and 26b are accommodated on the outer surface 28b of the cover body 28 via a retainer 55 as a support member. A rectangular accommodation groove 56 is formed.
　この収容溝５６は、図６及び図７に示すように、前記補強プレート２８ａの窓部内に充填された合成樹脂材を、カバー本体２８のほぼ径方向に沿って長方形状に切り欠いて形成され、前記両給電用ブラシ３１ａ、３１ｂの上方位置にほぼ並行状態に配置されている。つまり、この収容溝５６の形成位置は、各給電用ブラシ３１ａ、３１ｂを挟んで後述する給電用コネクタ３３と反対側の径方向位置に設けられている。 As shown in FIGS. 6 and 7, the housing groove 56 is formed by cutting a synthetic resin material filled in the window portion of the reinforcing plate 28 a into a rectangular shape substantially along the radial direction of the cover body 28. The power supply brushes 31a and 31b are disposed substantially in parallel with each other. That is, the formation position of the accommodation groove 56 is provided at a radial position on the opposite side to the power supply connector 33 described later with the power supply brushes 31a and 31b interposed therebetween.
　この収容溝５６は、図６、図７、図９に示すように、リテーナ５５に支持された状態で一対の捩りコイルばね３２，３２を収容する保持溝部５７と、該保持溝部５７の対向両側面５７ａ、５７ｂの長手方向のほぼ中央位置に形成された一対の固定用の棚部５８、５８と、前記保持溝部５７の一側面５７ａの長手方向の両端部（一方の棚部５８の両側）に形成された一対の支持溝部５９、５９と、から構成されている。 As shown in FIGS. 6, 7, and 9, the housing groove 56 includes a holding groove portion 57 that houses the pair of torsion coil springs 32 and 32 while being supported by the retainer 55, and both opposing sides of the holding groove portion 57. A pair of fixing shelves 58, 58 formed at substantially the center position in the longitudinal direction of the surfaces 57a, 57b, and both ends in the longitudinal direction of one side surface 57a of the holding groove 57 (both sides of one shelf 58) It is comprised from a pair of support groove part 59, 59 formed in this.
　前記保持溝部５７は、平面から視て長方形状に形成されて、上端開口から底面までの深さが最も深く形成されていると共に、その巾は前記各捩りコイルばね３２，３２の外径よりも大きく、かつ、その長さＬは前記リテーナ５５の軸方向長さよりも僅かに大きく形成されている。 The holding groove portion 57 is formed in a rectangular shape as viewed from above, and has the deepest depth from the upper end opening to the bottom surface, and its width is larger than the outer diameter of each of the torsion coil springs 32 and 32. The length L is slightly larger than the axial length of the retainer 55.
　前記一対の棚部５８、５８は、それぞれほぼ立方形状に形成されて、各上面５８ａがカバー本体２８の外側面２８ｂより一段低く形成されて各上面５８ａ上が凹状部５８ｂに形成されていると共に、前記各上面５８ａのほぼ中央位置に先端が円錐状の突起部６０、６０が立設されている。 The pair of shelves 58, 58 are formed in a substantially cubic shape, each upper surface 58a is formed one step lower than the outer surface 28b of the cover body 28, and each upper surface 58a is formed as a concave portion 58b. The protrusions 60, 60 having a conical tip are provided upright at a substantially central position of each upper surface 58a.
　前記各支持溝部５９，５９は、保持溝部５７の一側面５７ａの両端部から軸直角方向へ延出していると共に、それぞれの巾長さは比較的小さく形成されている。 The support groove portions 59, 59 extend from both end portions of one side surface 57a of the holding groove portion 57 in the direction perpendicular to the axis, and the widths of the support groove portions 59, 59 are relatively small.
　前記一対の捩りコイルばね３２、３２は、図７～図９に示すように、前記両給電用ブラシ３１ａ、３１ｂに対して平行かつ直線状に配置されており、ばね力を発生する円筒状の巻き線部３２ａ、３２ａと、該巻き線部３２ａ、３２ａの軸方向一端側から接線方向に沿って延出して、前記各給電用ブラシ３１ａ、３１ｂの後端面に形成されたＶ字溝３１ｃ、３１ｄの底部に弾接したアーム状の一端部３２ｂ、３２ｂと、巻き線部３２ａ、３２ａの軸方向他端側から前記一端部３２ｂ、３２ｂとは逆方向へ延出して、前記カバー部材４の各支持溝部５９、５９の上面に弾接するアーム状の他端部３２ｃ、３２ｃと、を備えている。 As shown in FIGS. 7 to 9, the pair of torsion coil springs 32 and 32 are arranged in parallel and linearly with respect to the power feeding brushes 31a and 31b, and are cylindrical, which generate spring force. Winding portions 32a, 32a, and V-shaped grooves 31c formed on the rear end surfaces of the power feeding brushes 31a, 31b, extending along the tangential direction from one axial end side of the winding portions 32a, 32a, The arm-shaped one end portions 32b and 32b elastically contacting the bottom of 31d and the one end portions 32b and 32b extend in the opposite direction from the other axial end side of the winding portions 32a and 32a. Arm-like other end portions 32c and 32c that elastically contact the upper surfaces of the respective support groove portions 59 and 59 are provided.
　前記各巻き線部３２ａ、３２ａは、巻線方向が互いに逆方向に設定されていると共に、所定の巻き線量によって開き方向へ所望のばね力を発生させるようになっている。また、各巻き線部３２ａ、３２ａは、外径が前記保持溝部５７の巾寸法よりも小さく形成されて全体が保持溝部５７の内部に所定隙間をもって収容可能になっていると共に、図１０に示すようにそれぞれの一部が、前記補強プレート２８ａの所定位置に形成された貫通部２８ｉと軸方向でオーバーラップ状態に配置されている。つまり、貫通部２８ｉの内径側に位置している。 The winding portions 32a and 32a are set so that the winding directions are opposite to each other and generate a desired spring force in the opening direction with a predetermined winding dose. Each of the winding portions 32a and 32a is formed so that the outer diameter is smaller than the width dimension of the holding groove portion 57, and the whole can be accommodated in the holding groove portion 57 with a predetermined gap, as shown in FIG. As described above, a part of each is arranged in an axially overlapping state with a through portion 28 i formed at a predetermined position of the reinforcing plate 28 a. That is, it is located on the inner diameter side of the penetrating portion 28i.
　前記各一端部３２ｂ、３２ｂは、各先端部が円弧状に折曲形成されて、その各屈曲頂部が前記各給電用ブラシ３１ａ、３１ｂのＶ字溝３１ｃ、３１ｄの底部に点接触状態で弾接している、つまり、一端部３２ｂ、３２ｂは、前記各給電用ブラシ３１ａ、３１ｂのＶ字溝３１ｃ、３１ｃ底部に弾接してスリップリング２６ａ、２６ｂ方向へ押圧するようになっている。また、この各一端部３２ｂ、３２ｂは、前記各巻き線部３２ａ、３２ａの巻線方向が互いに逆方向になっていることから、互いに軸方向へ近接した位置、つまり、後述するリテーナ５５の隔壁６２の両側面側へ互いに近接した位置になっていると共に、前記両側面に沿って各給電用ブラシ３１ａ、３１ｂの後端面方向に並行に延出している。 Each of the one end portions 32b and 32b is formed such that each tip end is bent in an arc shape, and each bent top portion is elastically contacted with the bottom portion of each of the V-shaped grooves 31c and 31d of each of the power feeding brushes 31a and 31b. In other words, the one end portions 32b and 32b are in elastic contact with the bottoms of the V-shaped grooves 31c and 31c of the power feeding brushes 31a and 31b and are pressed toward the slip rings 26a and 26b. Further, since the winding directions of the winding portions 32a and 32a are opposite to each other, the one end portions 32b and 32b are positioned close to each other in the axial direction, that is, a partition wall of a retainer 55 described later. 62 are located close to each other on both side surfaces, and extend along the both side surfaces in parallel to the rear end surface direction of each of the power supply brushes 31a and 31b.
　一方、前記各他端部３２ｃ、３２ｃは、各先端部がほぼ直線状に形成されて、それぞれの下端縁が前記カバー部材４の支持溝部５９，５９の各上面に線接触状態で弾接している。また、この各他端部３２ｃ、３２ｃは、前記各巻き線部３２ａ、３２ａの巻線方向が互いに逆方向になっていることから、互いに軸方向へ離間した位置になっている。 On the other hand, each of the other end portions 32c and 32c has a substantially straight end portion, and each lower end edge is elastically contacted with each upper surface of the support groove portions 59 and 59 of the cover member 4 in a line contact state. Yes. Further, the other end portions 32c and 32c are spaced apart from each other in the axial direction because the winding directions of the winding portions 32a and 32a are opposite to each other.
　各捩りコイルばね３２，３２は、それぞれの一端部３２ｂ、３２ｂと他端部３２ｃ、３２ｃが互いに開く方向へ作用するばね力によって各給電用ブラシ３１ａ、３１ｂを付勢している。 The torsion coil springs 32 and 32 urge the power supply brushes 31a and 31b by a spring force acting in a direction in which the respective one end portions 32b and 32b and the other end portions 32c and 32c open.
　前記リテーナ５５は、図７～図１０に示すように、合成樹脂材によって一体に形成され、一本軸状に形成された支持軸６１と、該支持軸６１の軸方向中央位置に一体に設けられた係止部である隔壁６２と、から構成されている。 As shown in FIGS. 7 to 10, the retainer 55 is integrally formed of a synthetic resin material, and is provided integrally with a support shaft 61 formed in a single shaft shape and in the axial center position of the support shaft 61. And a partition wall 62 that is a locking portion.
　前記支持軸６１は、中実な円柱状に形成されて、その軸方向の長さが前記収容溝５６の長手方向の長さよりも僅かに短く形成されて軸方向の両端面が前記収容溝５６の長手方向の対向面に微小なクリアランスをもって対峙していると共に、左右の両端部６１ａ、６１ｂに各捩りコイルばね３２，３２が各巻き線部３２ａ、３２ａを介して互いに軸方向の反対側から嵌挿されるようになっている。 The support shaft 61 is formed in a solid cylindrical shape, and its axial length is slightly shorter than the length in the longitudinal direction of the receiving groove 56, and both axial end surfaces thereof are the receiving grooves 56. The torsion coil springs 32, 32 are opposed to the left and right end portions 61a, 61b from the opposite sides in the axial direction through the winding portions 32a, 32a. It is designed to be inserted.
　前記隔壁６２は、支持軸６１の中央底部側に一体に有する底壁部６２ａと、該底壁部６２ａの上方位置にある支持軸６１の径方向の両側面から水平方向へ突出した一対の固定用突壁６２ｂ、６２ｂと、を備えている。 The partition wall 62 has a bottom wall portion 62a integrally formed on the center bottom portion side of the support shaft 61, and a pair of fixed projections protruding in the horizontal direction from both side surfaces in the radial direction of the support shaft 61 located above the bottom wall portion 62a. Projecting walls 62b, 62b.
　前記底壁部６２ａは、ほぼ直方体に形成されて前記収容溝５６の保持溝部５７に嵌合保持されている。 The bottom wall portion 62a is formed in a substantially rectangular parallelepiped shape and is fitted and held in the holding groove portion 57 of the receiving groove 56.
　各固定用突壁６２ｂ、６２ｂは、肉厚なほぼ矩形板状に形成されて前記棚部５８、５８の凹状部５８ｂ、５８ｂに嵌合しつつ各下面が前記各棚部５８、５８の上面５８ａ、５８ａに載置されていると共に、中央位置に前記各突起部６０、６０が挿入される固定用孔６２ｃ、６２ｃが上下方向に貫通形成されている。 Each of the fixing protruding walls 62b and 62b is formed in a thick and substantially rectangular plate shape and is fitted into the concave portions 58b and 58b of the shelf portions 58 and 58, and the lower surfaces thereof are the upper surfaces of the shelf portions 58 and 58. The fixing holes 62c and 62c into which the projections 60 and 60 are inserted are vertically formed in the center position.
　また、前記各突起部６０、６０は、前記固定用孔６２ｃ、６２ｃに挿入された後は、上端部が図７及び図９の一点鎖線で示すように、所定の加熱治具によって茸の傘状に溶着されて、各固定用突壁６２ｂ、６２ｂを各棚部５８，５８上に位置決めしつつ固定するようになっている。 In addition, after the protrusions 60 and 60 are inserted into the fixing holes 62c and 62c, the upper ends of the protrusions 60 and 60 are as shown by the one-dot chain lines in FIGS. The fixing projecting walls 62b and 62b are fixed on the shelves 58 and 58 while being positioned.
　前記各ブラシホルダ３０ａ、３０ｂは、前後端に開口部が形成されて、前端側の開口部から前記各給電用ブラシ３１ａ、３１ｂの先端部が進退自在になっていると共に、図９に示すように、各一側壁の長手方向に形成されたスリット６３、６３を介して各給電用ブラシ３１ａ、３１ａの後端側部に一対のピグテールハーネス６４、６４のそれぞれの一端部が接続されている。 Each of the brush holders 30a and 30b has openings at the front and rear ends, and the front ends of the power supply brushes 31a and 31b can be moved forward and backward from the opening on the front end side, as shown in FIG. In addition, one end portions of the pair of pigtail harnesses 64 and 64 are connected to the rear end side portions of the power feeding brushes 31a and 31a through slits 63 and 63 formed in the longitudinal direction of the respective one side walls.
　前記各ピグテールハーネス６４，６４は、各他端部が後述する給電用コネクタ３３の一対の端子片の各一端部３３ａ、３３ａに半田付けによって接続されており、前記給電用ブラシ３１ａ、３１ｂが前記捩りコイルばね３２、３２のばね力など介して摺動すると、前記各スリット６３，６３内を移動してブラシホルダ３０ａ、３０ｂと一緒に移動するようになっている。 Each of the pigtail harnesses 64 and 64 has the other end connected to one end 33a and 33a of a pair of terminal pieces of a power supply connector 33 described later by soldering, and the power supply brushes 31a and 31b are connected to the power supply brushes 31a and 31b. When sliding via the spring force of the torsion coil springs 32, 32, etc., it moves in the slits 63, 63 and moves together with the brush holders 30a, 30b.
　前記各給電用ブラシ３１ａ、３１ｂは、角柱状に形成されて所定の軸方向長さに設定されていると共に、前述した各捩りコイルばね３２，３２のばね力によって、平坦な各先端面が前記各スリップリング２６ａ，２６ｂに軸方向からそれぞれ当接するようになっている。 Each of the power supply brushes 31a and 31b is formed in a prismatic shape and is set to a predetermined axial length, and each flat tip surface is formed by the spring force of each of the torsion coil springs 32 and 32 described above. Each slip ring 26a, 26b comes into contact with the slip ring 26a, 26b from the axial direction.
　また、前記カバー本体２８の下端部には、図６及び図７に示すように、前記各給電用ブラシ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と共に、前記検出部５１で検出された回転角度信号を前記コントロールユニットに出力する信号用コネクタ３４が前記給電用コネクタ３３と並行かつ径方向に沿って突設されている。 Further, as shown in FIGS. 6 and 7, 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 provided at the lower end of the cover body 28. Are integrally provided, and a signal connector 34 for outputting the rotation angle signal detected by the detection unit 51 to the control unit is provided in parallel with the power supply connector 33 and projecting in the radial direction. .
　前記給電用コネクタ３３は、その開口部がカバー部材４の外周側下端部にほぼ径方向に沿って突設されていると共に、カバー本体２８の内部に部分的に埋設された一対の端子片の前記各一端部３３ａ、３３ａが前記ピグテールハーネス６４，６４に接続されている一方、開口部の内部に配置されて外部に露出した図外の他端部がコントロールユニット側の雌コネクタ端子に接続されるようになっている。 The power feeding connector 33 has an opening projecting substantially radially along the lower end on the outer peripheral side of the cover member 4 and a pair of terminal pieces partially embedded in the cover main body 28. The one end portions 33a, 33a are connected to the pigtail harnesses 64, 64, while the other end portion (not shown) disposed inside the opening and exposed to the outside is connected to a female connector terminal on the control unit side. It has become so.
　一方、前記信号用コネクタ３４は、図１及び図６に示すように、開口部がカバー部材４の外周側下端部にほぼ径方向に沿って形成されて、前記給電用コネクタ３３の開口部と並行に形成されていると共に、全体の巾長さがカバー部材４の巾長さとほぼ同じ長さになっている。また、この信号用コネクタ３４は、図１に示すように、カバー本体２８内に部分的に埋設された導電材である複数の端子片を有し、該各端子片の一端部３４ａが後述するプリント基板６５の集積回路６６に接続されていると共に、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。 On the other hand, as shown in FIGS. 1 and 6, the signal connector 34 has an opening formed substantially along the radial direction at the lower end on the outer peripheral side of the cover member 4. While being formed in parallel, the entire width is substantially the same as the width of the cover member 4. Further, as shown in FIG. 1, the signal connector 34 has a plurality of terminal pieces made of a conductive material partially embedded in the cover main body 28, and one end 34a of each terminal piece will be described later. In addition to being connected to the integrated circuit 66 of the printed circuit board 65, the other end 34b is connected to a female connector terminal (not shown) on the control unit side.
　前記モータ出力軸１４の小径部１４ｂと、前記カバー本体２８の円形穴２８ｋの底壁を挟んだ中央部との間には、図１に示すように、モータ出力軸１４の回転角度位置を検出する前記角度センサ３５が設けられている。 As shown in FIG. 1, the rotational angular position of the motor output shaft 14 is detected between the small diameter portion 14b of the motor output shaft 14 and the central portion sandwiching the bottom wall of the circular hole 28k of the cover body 28. The angle sensor 35 is provided.
　この角度センサ３５は、電磁誘導型であって、前記モータ出力軸１４の小径部１４ｂ内に固定された被検出部５０と、前記カバー本体２８のほぼ中央位置に固定されて、前記被検出部５０からの検出信号を受信する検出部５１と、から構成されている。 The angle sensor 35 is of an electromagnetic induction type, and is fixed to the detected portion 50 fixed in the small diameter portion 14b of the motor output shaft 14 and the substantially central position of the cover body 28, so that the detected portion And a detection unit 51 that receives a detection signal from 50.
　前記被検出部５０は、合成樹脂材からなるほぼ有底円筒状に形成されて、前記小径部１４ｂ内に挿入固定される円筒状の挿入部５２と、該挿入部５２の先端部の底壁外面に固定された３葉形状の薄板な被検出ロータ５３と、から主として構成されている。 The detected portion 50 is formed in a substantially bottomed cylindrical shape made of a synthetic resin material, and has a cylindrical insertion portion 52 inserted and fixed in the small diameter portion 14b, and a bottom wall of the distal end portion of the insertion portion 52. It is mainly composed of a three-leaf thin rotor to be detected 53 fixed to the outer surface.
　また、前記被検出部５０は、先端部が前記円形穴２８ｋ内に挿入配置されると共に、挿入された状態で被検出ロータ５３が円形穴２８ｋの薄肉な底壁の底面に微少クリアランスＣを介して対向配置されている。 In addition, the detected portion 50 is inserted and arranged at the tip end in the circular hole 28k, and the detected rotor 53 is inserted into the bottom surface of the thin bottom wall of the circular hole 28k via a minute clearance C. Are opposed to each other.
　前記検出部５１は、前記カバー本体２８のほぼ中央位置から径方向に延設されたほぼ長方形状のプリント基板６５と、該プリント基板６５の長手方向の一端部外面に設けられた複数の集積回路（ＡＳＩＣ）６６と、該集積回路６６と同じ外面の他端部側に設けられた図外の受信回路及び発振回路と、を備えている。 The detection unit 51 includes a substantially rectangular printed board 65 extending in a radial direction from a substantially central position of the cover body 28, and a plurality of integrated circuits provided on the outer surface of one end of the printed board 65 in the longitudinal direction. (ASIC) 66 and a receiving circuit and an oscillating circuit (not shown) provided on the other end side of the same outer surface as the integrated circuit 66.
　前記プリント基板６５は、図外の前記受信、発振回路の中央に位置決め用小孔が形成されており、この位置決め用小孔が前記被検出部５０の先端部中央に突設された位置決め用凸部２８ｊに圧入嵌合して前記被検出ロータ５３の中心と受信、発振回路の中心が位置決めされるようになっている。 The printed circuit board 65 has a positioning small hole formed in the center of the reception and oscillation circuit (not shown), and the positioning small hole protrudes from the center of the tip of the detected portion 50. The center of the detected rotor 53 and the center of the receiving and oscillating circuit are positioned by press-fitting to the portion 28j.
　また、このプリント基板６５は、前記カバー本体２８の外側面１８ｂに対してビスなどの所定の固定手段によって固定されており、したがって、前記受信、発振回路は、固定されたプリント基板６５を介して前記円形穴２８ｋの底壁と微少クリアランスＣを介して前記被検出ロータ５３に軸方向から対峙している。 The printed circuit board 65 is fixed to the outer side surface 18b of the cover body 28 by a predetermined fixing means such as a screw. Therefore, the reception and oscillation circuit is connected via the fixed printed circuit board 65. The rotor 53 is opposed to the detected rotor 53 from the axial direction through the bottom wall of the circular hole 28k and a minute clearance C.
　よって、前記モータ出力軸１４の回転に伴って前記被検出ロータ５３が回転することにより、前記受信、発信回路と被検出ロータ５３との間に誘導電流が流れて、この電磁誘導作用によって前記集積回路６６がモータ出力軸１４の回転角度を検出し、この検出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。 Therefore, as the rotor 53 to be detected rotates with the rotation of the motor output shaft 14, an induced current flows between the receiving and transmitting circuit and the rotor 53 to be detected. A circuit 66 detects the rotation angle of the motor output shaft 14 and outputs this detection signal to the control unit.
　前記モータ出力軸１４と偏心軸部３９は、従動部材９の円筒部９ｂの外周面に設けられた小径ボールベアリング３７と該小径ボールベアリング３７の側部に配置されたニードルベアリング３８とによって回転自在に支持されている。 The motor output shaft 14 and the eccentric shaft portion 39 are rotatable by a small-diameter ball bearing 37 provided on the outer peripheral surface of the cylindrical portion 9 b of the driven member 9 and a needle bearing 38 disposed on a side portion of the small-diameter ball bearing 37. It is supported by.
　前記ニードルベアリング３８は、偏心軸部３９の内周面に圧入された円筒状のベアリングリテーナと、該ベアリングリテーナの内部に回転自在に保持された複数の転動体であるニードルローラと、から構成されている。 The needle bearing 38 includes a cylindrical bearing retainer that is press-fitted into the inner peripheral surface of the eccentric shaft portion 39, and needle rollers that are a plurality of rolling elements that are rotatably held inside the bearing retainer. ing.
　前記小径ボールベアリング３７は、内輪が従動部材９の円筒部９ｂの前端縁とカムボルト１０の頭部１０ａとの間に挟持状態に固定されている一方、外輪が前記偏心軸部３９の段差拡径状の内周面に圧入固定されていると共に、前記内周面に形成された段差縁に当接して軸方向の位置決めがなされている。 In the small-diameter ball bearing 37, the inner ring is fixed in a sandwiched state between the front end edge of the cylindrical portion 9 b of the driven member 9 and the head 10 a of the cam bolt 10, while the outer ring has a step enlarged diameter of the eccentric shaft portion 39. The inner circumferential surface is press-fitted and fixed, and is positioned in the axial direction by contacting a step edge formed on the inner circumferential surface.
　また、前記モータ出力軸１４（偏心軸部３９）の外周面と前記モータハウジング１３の延出部１３ｃの内周面との間には、減速機構１２の内部から電動モータ１１内への潤滑油のリークを阻止する小径なオイルシール４６が設けられている。 Further, between the outer peripheral surface of the motor output shaft 14 (eccentric shaft portion 39) and the inner peripheral surface of the extending portion 13c of the motor housing 13, lubricating oil from the inside of the speed reduction mechanism 12 to the electric motor 11 is provided. A small-diameter oil seal 46 is provided to prevent this leakage.
　前記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、これに基づいて機関制御を行うと共に、前記給電用ブラシ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などを介してコイル１８に通電してモータ出力軸１４の回転制御を行い、減速機構１２によってカムシャフト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 the like, and engine control based on this And the rotation of the motor output shaft 14 is controlled by energizing the coil 18 through 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. 12 controls the relative rotational phase of the camshaft 2 with respect to the timing sprocket 1.
　前記減速機構１２は、図１～図３に示すように、偏心回転運動を行う前記偏心軸部３９と、該偏心軸部３９の外周に設けられた中径ボールベアリング４７と、該中径ボールベアリング４７の外周に設けられた前記ローラ４８と、該ローラ４８を転動方向に保持しつつ径方向の移動を許容する前記保持器４１と、該保持器４１と一体の前記従動部材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 12 includes the eccentric shaft portion 39 that performs an eccentric rotational motion, a medium-diameter ball bearing 47 provided on the outer periphery of the eccentric shaft portion 39, and the medium-diameter ball. The roller 48 provided on the outer periphery of the bearing 47; the retainer 41 that allows the roller 48 to move in the radial direction while retaining the roller 48 in the rolling direction; and the driven member 9 that is integral with the retainer 41; Is mainly composed of
　前記偏心軸部３９は、図１に示すように、外周面に形成されたカム面３９ａの軸心Ｙがモータ出力軸１４の軸心Ｘから径方向へ僅かに偏心している。 In the eccentric shaft portion 39, as shown in FIG. 1, the shaft center Y of the cam surface 39a formed on the outer peripheral surface is slightly eccentric from the shaft center X of the motor output shaft 14 in the radial direction.
　前記中径ボールベアリング４７は、前記ニードルベアリング３８の径方向位置で全体がほぼオーバーラップする状態に配置され、内輪４７ａと外輪４７ｂ及び該両輪４７ａ、４７ｂとの間に介装されたボールとから構成されている。前記内輪４７ａは、前記偏心軸部３９の外周面に圧入固定されているのに対して、前記外輪４７ｂ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４７ｂは、軸方向の電動モータ１１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の内側面との間に微小な第１隙間Ｃ１が形成されてフリーな状態になっている。また、この外輪４７ｂの外周面には、前記各ローラ４８の外周面が転動自在に当接していると共に、この外輪４７ｂの外周側には、円環状の第２隙間Ｃ２が形成されて、この第２隙間Ｃ２によって中径ボールベアリング４７全体が前記偏心軸部３９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。 The medium-diameter ball bearing 47 is disposed so as to be substantially overlapped at the radial position of the needle bearing 38, and includes an inner ring 47a, an outer ring 47b, and a ball interposed between the two wheels 47a and 47b. It is configured. The inner ring 47a is press-fitted and fixed to the outer peripheral surface of the eccentric shaft portion 39, whereas the outer ring 47b is in a free state without being fixed in the axial direction. In other words, the outer ring 47b has a small first end surface on the side of the electric motor 11 in the axial direction that does not come into contact with any part, and the other end surface in the axial direction is between the inner side surface of the retainer 41 facing it. One gap C1 is formed and is in a free state. Further, the outer peripheral surface of the outer ring 47b is in contact with the outer peripheral surface of each roller 48 in a freely rolling manner, and an annular second gap C2 is formed on the outer peripheral side of the outer ring 47b. Due to the second gap C2, the entire medium-diameter ball bearing 47 can move in the radial direction along with the eccentric rotation of the eccentric shaft portion 39, that is, can move eccentrically.
　前記保持器４１は、前記固定端部９ａの外周部前端から前方へ断面ほぼＬ字形状に折曲されて、前記円筒部９ｂと同方向へ突出した有底円筒状に形成されている。この保持器４１の筒状先端部４１ａは、前記内歯構成部５や隔壁１３ａなどによって隔成された円環凹状の収容空間を介してモータハウジング１３の隔壁１３ａ方向へ延出している。また、前記筒状先端部４１ａの周方向のほぼ等間隔位置には、複数のローラ４８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４１ｂ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４１ｂ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て、その全体の数（ローラ４８の数）が前記内歯構成部５の内歯５ａの全体の歯数よりも少なくなっており、これによって、減速比を得るようになっている。 The retainer 41 is formed in a bottomed cylindrical shape which 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 protrudes in the same direction as the cylindrical portion 9b. The cylindrical tip portion 41a of the retainer 41 extends in the direction of the partition wall 13a of the motor housing 13 through an annular concave storage space defined by the internal tooth component 5 and the partition wall 13a. Further, a plurality of substantially rectangular roller holding holes 41b for holding the plurality of rollers 48 in a freely rollable manner are formed at substantially equal intervals in the circumferential direction at substantially equal intervals in the circumferential direction of the cylindrical tip portion 41a. Has been. The roller holding hole 41b is formed in a rectangular shape elongated in the front-rear direction with the tip end side closed, and the total number (the number of rollers 48) is the total number of teeth of the internal teeth 5a of the internal tooth component 5. Thus, the reduction ratio is obtained.
　前記各ローラ４８は、鉄系金属によって形成され、前記中径ボールベアリング４７の偏心動に伴って径方向へ移動しつつ前記内歯構成部５の内歯５ａに嵌入すると共に、保持器４１のローラ保持孔４１ｂ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させるようになっている。 Each of the rollers 48 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 along with the eccentric movement of the medium-diameter ball bearing 47. The roller holding hole 41b is caused to swing in the radial direction while being guided in the circumferential direction by both side edges.
　前記減速機構１２の内部には、潤滑油供給手段によって潤滑油が供給されるようになっている。この潤滑油供給手段は、前記シリンダヘッド０１の軸受０２の内部に形成されて、図外のメインオイルギャラリーから潤滑油が供給される油供給通路と、前記カムシャフト２の内部軸方向に形成されて、前記油供給通路にグルーブ溝６７ａを介して連通した油供給孔６７と、前記従動部材９の内部軸方向に貫通形成されて、一端が前記油供給孔６７に環状溝６７ｂを介して開口し、他端が前記ニードルベアリング３８と中径ボールベアリング４７の付近に開口した図外のオイル孔と、前記大径ボールベアリング４３の内部を介して潤滑油を外部に排出する図外のオイル排出孔と、から構成されている。
〔本実施形態の作動〕
　以下、本実施形態の作動について説明すると、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が回転し、その回転力が内歯構成部５を介してモータハウジング１３に伝達されて、該モータハウジング１３が同期回転する。一方、前記内歯構成部５の回転力が、各ローラ４８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に設けられた複数の駆動カムが各気筒の吸気弁を開閉作動させる。 Lubricating oil is supplied into the speed reduction mechanism 12 by lubricating oil supply means. This lubricating oil supply means is formed inside the bearing 02 of the cylinder head 01, and is formed in the oil supply passage through which the lubricating oil is supplied from a main oil gallery (not shown) and in the direction of the internal axis of the camshaft 2. An oil supply hole 67 communicating with the oil supply passage through a groove groove 67a, and an inner axial direction of the driven member 9, and one end opened to the oil supply hole 67 through an annular groove 67b. The other end opens near the needle bearing 38 and the medium-diameter ball bearing 47, and an unillustrated oil drain that drains the lubricating oil to the outside through the inside of the large-diameter ball bearing 43. And a hole.
[Operation of this embodiment]
Hereinafter, the operation of the present embodiment will be described. First, the timing sprocket 1 rotates through the timing chain in accordance with the rotational drive of the crankshaft of the engine, and the rotational force is transmitted to the motor housing 13 through the internal gear component 5. The motor housing 13 rotates synchronously. On the other hand, the rotational force of the internal tooth component 5 is transmitted from each roller 48 to the camshaft 2 via the cage 41 and the driven member 9. As a result, the plurality of drive cams provided on the camshaft 2 opens and closes the intake valves of the respective cylinders.
　そして、機関始動後の所定の機関運転時には、前記コントロールユニットから一対の端子片の各一端部３３ａ、３３ａや各ピグテールハーネス６４，６４及び給電用ブラシ３１ａ、３１ｂ、各スリップリング２６ａ，２６ｂなどを介して電動モータ１１のコイル１８に通電される。これによって、モータ出力軸１４が回転駆動され、この回転力が減速機構１２を介してカムシャフト２に減速された回転力が伝達される。 When a predetermined engine is operated after the engine is started, the one end portions 33a and 33a of the pair of terminal pieces, the pigtail harnesses 64 and 64, the power supply brushes 31a and 31b, the slip rings 26a and 26b, etc. are connected from the control unit. Then, the coil 18 of the electric motor 11 is energized. As a result, the motor output shaft 14 is rotationally driven, and the rotational force of this rotational force is transmitted to the camshaft 2 via the speed reduction mechanism 12.
　すなわち、前記モータ出力軸１４の回転に伴い偏心軸部３９が偏心回転すると、各ローラ４８がモータ出力軸１４の１回転毎に保持器４１の各ローラ保持孔４１ｂで径方向へガイドされながら前記内歯構成部５の一つの内歯５ａを乗り越えて隣接する他の内歯５ａに転動しながら移動し、これを順次繰り返しながら円周方向へ転接する。この各ローラ４８の転接によって前記モータ出力軸１４の回転が減速されつつ前記従動部材９に回転力が伝達される。 That is, when the eccentric shaft portion 39 rotates eccentrically with the rotation of the motor output shaft 14, the rollers 48 are guided in the radial direction by the roller holding holes 41b of the retainer 41 for each rotation of the motor output shaft 14. It moves while rolling over one internal tooth 5a of the internal tooth constituent part 5 and moving to another adjacent internal tooth 5a, and rolling in the circumferential direction while repeating this in sequence. The rotational force of the motor output shaft 14 is transmitted to the driven member 9 while the rotation of the motor output shaft 14 is decelerated by the rolling contact of the rollers 48.
　これにより、カムシャフト２が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 rotates relative to the timing sprocket 1 in the forward and reverse directions and the relative rotational phase is converted, and the opening / closing timing of the intake valve is controlled to be advanced or retarded.
　前記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、前記ストッパ凸部２１ｂの各側面がストッパ凹溝２２ｄの各対向面のいずれか一方に当接することによって行われる。したがって、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 each side surface of the stopper convex portion 21b abuts one of the opposing surfaces of the stopper concave groove 22d. Done. Therefore, 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、前記電動モータ１１のモータ出力軸１４の回転に伴って前記角度センサ３５の被検出部５０が回転すると、検出部５１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６６がモータ出力軸１４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１４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１１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 50 of the angle sensor 35 rotates with the rotation of the motor output shaft 14 of the electric motor 11, an induced current flows between the angle sensor 35 and the integrated circuit 66 due to this electromagnetic induction action. The rotation angle of the motor output shaft 14 is detected, and the current rotation angle position of the motor output shaft 14 is detected by the control unit based on this detection signal. The control unit outputs a rotational drive signal to the electric motor 11 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、前述したように、カバー本体２８に設けられた収容溝５６を、各ブラシホルダ３０ａ、３０ｂ（給電用ブラシ３１ａ、３１ｂ）に対して径方向の近接した側部位置に並列状態（巻き線部３２ａ、３２ａがカバー部材４の径方向において給電用ブラシ３１ａ、３１ｂと重なる状態）に形成したことから、給電用ブラシ３１ａ、３１ｂに対する各捩りコイルばね３２，３２との配置構成が装置の軸方向ではなく径方向の配置となる。このため、前記カバー部材４全体を扁平化することが可能になって、装置全体の軸方向の長さを十分に短くすることが可能になる。 In the present embodiment, as described above, the receiving groove 56 provided in the cover main body 28 is located at the side position close to the brush holders 30a and 30b (power supply brushes 31a and 31b) in the radial direction. Since the winding portions 32a and 32a are formed in a parallel state (a state where the winding portions 32a and 32a overlap with the power supply brushes 31a and 31b in the radial direction of the cover member 4), the arrangement of the torsion coil springs 32 and 32 with respect to the power supply brushes 31a and 31b. The configuration is a radial arrangement rather than an axial direction of the apparatus. For this reason, the entire cover member 4 can be flattened, and the axial length of the entire apparatus can be sufficiently shortened.
　この結果、このバルブタイミング制御装置を搭載した内燃機関のエンジンルーム内でのレイアウトの自由度が向上する。 As a result, the degree of freedom of layout in the engine room of the internal combustion engine equipped with this valve timing control device is improved.
　特に、前記各捩りコイルばね３２，３２やリテーナ５５は、全体がカバー本体２８の外側面２８ｂから突出することなく、収容溝５６内に収容されてカバー本体２８の外側面２８ｂからの突出量を低くできる。 In particular, the torsion coil springs 32 and 32 and the retainer 55 are all housed in the housing groove 56 without projecting from the outer surface 28 b of the cover body 28, and the amount of projection from the outer surface 28 b of the cover body 28 is reduced. Can be lowered.
　つまり、前記各巻き線部３２ａ、３２ａやリテーナ５５の支持軸６１は、ほぼ全体が前記収容溝５６の保持溝部５７内に収容され、各巻き線部３２ａ、３２ａの各他端部３２ｃ、３２ｃは各支持溝部５９，５９内に収容され、さらに、リテーナ５５の各突壁６２ｂ、６２ｂも凹状部５８ｂ、５８ｂ内に収容されて、いずれもが外側面２８ｂから突出することがないことから、軸方向の長さをさらに短くすることが可能になる。また、各突壁６２ｂ、６２ｂが凹状部５８ｂ、５８ｂ内に収容されていることから、リテーナ５５の位置ずれが抑えられるため、組み付け精度と組み付け後の耐久性が向上する。 That is, the winding portions 32a and 32a and the support shaft 61 of the retainer 55 are almost entirely accommodated in the holding groove portion 57 of the accommodation groove 56, and the other end portions 32c and 32c of the winding portions 32a and 32a. Are accommodated in the respective support groove portions 59, 59, and the projecting walls 62b, 62b of the retainer 55 are also accommodated in the concave portions 58b, 58b, and none of them protrudes from the outer surface 28b. The axial length can be further shortened. Moreover, since each protrusion wall 62b and 62b is accommodated in the recessed part 58b and 58b, since the position shift of the retainer 55 is suppressed, the assembly | attachment precision and the durability after an assembly | attachment improve.
　また、前記各巻き線部３２ａ、３２ａの巻き線方向を互いに逆方向に設定したことによって、前記各一端部３２ｂ、３２ｂを前記隔壁６２の軸方向両側面側へ互いに近接して配置できると共に、各他端部３２ｃ、３２ｃを互いに離間した位置に配置できることから、前記巻き線部３２ａ、３２ａの巻き線量やレイアウトの自由度が向上する。 In addition, by setting the winding direction of each of the winding portions 32a and 32a to be opposite to each other, the one end portions 32b and 32b can be arranged close to each other on both axial sides of the partition wall 62, and Since the other end portions 32c and 32c can be arranged at positions separated from each other, the winding dose and the flexibility of layout of the winding portions 32a and 32a are improved.
　すなわち、本実施形態では、前記両捩りコイルばね３２，３２の両一端部３２ｂ、３２ｂの軸方向の位置が一定になる、つまり、両者３２ｂ、３２ｂ間の距離が巻き線部３２ａ、３２ａの巻き線量に拘わらず前記隔壁６２を介して常に一定になることから、各巻き線部３２ａ、３２ａの巻き線量やレイアウトの自由度が向上するのである。 That is, in the present embodiment, the axial positions of both end portions 32b, 32b of the torsion coil springs 32, 32 are constant, that is, the distance between the both ends 32b, 32b is the winding of the winding portions 32a, 32a. Regardless of the dose, it is always constant through the partition wall 62, so that the winding dose of each of the winding portions 32a and 32a and the degree of freedom of layout are improved.
　また、本実施形態では、前記隔壁６２の巾厚さＷを、両給電用ブラシ３１ａ、３１ｂの離間巾に合わせて比較的肉厚に形成することができるので、隔壁６２自体の剛性も高めることができる。 Further, in this embodiment, the width W of the partition wall 62 can be formed relatively thick in accordance with the separation width of the power supply brushes 31a and 31b, so that the rigidity of the partition wall 62 itself is also increased. Can do.
　これにより、前記リテーナ５５全体の剛性を高くすることができ、この結果、前記各捩りコイルばね３２、３２を安定かつ確実に支持することが可能になると共に、耐久性の向上が図れる。 Thereby, the rigidity of the retainer 55 as a whole can be increased. As a result, the torsion coil springs 32 and 32 can be supported stably and reliably, and the durability can be improved.
　また、前記隔壁６２をリテーナ５５の固定用に用いたことから、リテーナ５５の支持軸６１の軸方向における長さを短くすることができる。このため、カバー本体２８の径方向レイアウトのコンパクト化が可能になる。 Further, since the partition wall 62 is used for fixing the retainer 55, the length of the retainer 55 in the axial direction of the support shaft 61 can be shortened. For this reason, the radial layout of the cover body 28 can be made compact.
　また、前述のように、前記両捩りコイルばね３２，３２の両一端部３２ｂ、３２ｂ間の位置を巻き線部３２ａ、３２ａの巻き線量に拘わらず一定に設定できることから、各給電用ブラシ３１ａ、３１ｂの間の距離のレイアウトの自由度が向上する。これにより、前記２つのスリップリング２６ａ、２６ｂの間の距離のレイアウト自由度も向上する。つまり、２つのスリップリング２６ａ、２６ｂの間を狭く構成することが可能となり、径方向レイアウトのコンパクト化が可能となる。 Further, as described above, since the position between the one end portions 32b, 32b of the torsion coil springs 32, 32 can be set constant irrespective of the winding dose of the winding portions 32a, 32a, each power supply brush 31a, The degree of freedom in layout of the distance between 31b is improved. Thereby, the layout freedom of the distance between the two slip rings 26a, 26b is also improved. In other words, the space between the two slip rings 26a and 26b can be narrowed, and the radial layout can be made compact.
　しかも、この実施形態では、前記各突壁６２ｂ、６２ｂは、各突起部６０，６０の先端部の溶着によって各棚部５８，５８の上面に一体的に固定されることから、強固かつ確実な固定状態を得ることができる。 In addition, in this embodiment, the projecting walls 62b and 62b are integrally fixed to the upper surfaces of the shelves 58 and 58 by welding the tips of the projecting parts 60 and 60. A fixed state can be obtained.
　また、リテーナ５５の隔壁６２は、底壁部６２ａと突壁６２ｂ、６２ｂによって段差状に形成されていることから、各突起部６０，６０の長さを隔壁６２の径方向厚さよりも短くできる。この結果、組み付け時や溶着後に各突起部６０，６０にかかるモーメントの影響を低減し、各突起部６０，６０の折れなどの破損を抑制することができる。 Further, since the partition wall 62 of the retainer 55 is formed in a stepped shape by the bottom wall portion 62 a and the projecting walls 62 b and 62 b, the length of each projection 60, 60 can be made shorter than the radial thickness of the partition wall 62. . As a result, it is possible to reduce the influence of the moment applied to each projection 60, 60 during assembly or after welding, and to suppress breakage such as breakage of each projection 60, 60.
　また、本実施形態では、それぞれの巻き線部３２ａ、３２ａは、各一端部３２ｂ、３２ｂの他に、前記各他端部３２ｃ、３２ｃも径方向へ延出して各支持溝部５９、５９の上面に弾接していることから、各捩りコイルばね３２，３２の各自の回転モーメントによって僅かに上昇して各巻き線部３２ａ、３２ａの内面の一部が各支持軸６１の各端部６１ａ、６１ｂの外周面に軽く当接するものの、該各巻き線部３２ａ、３２ａの倒れの発生が少なくなる。 Further, in the present embodiment, the winding portions 32a and 32a, in addition to the one end portions 32b and 32b, also extend the other end portions 32c and 32c in the radial direction so that the upper surfaces of the support groove portions 59 and 59 are provided. Since the torsion coil springs 32 and 32 are slightly in contact with each other, the torsion coil springs 32 and 32 are slightly lifted by their respective rotational moments so that part of the inner surfaces of the winding portions 32 a and 32 a are end portions 61 a and 61 b of the support shafts 61. However, the winding portions 32a and 32a are less likely to fall down.
　したがって、各巻き線部３２ａ、３２ａの内面と各支持軸６１の各端部６１ａ、６１ｂの外周面との間でのフリクションを低減させることができ、各捩りコイルばね３２，３２のばね荷重の変化を抑制することができる。この結果、各給電用ブラシ３１ａ、３１ｂに対して常時安定した付勢力を付与することが可能になる。 Therefore, the friction between the inner surface of each winding part 32a, 32a and the outer peripheral surface of each end part 61a, 61b of each support shaft 61 can be reduced, and the spring load of each torsion coil spring 32, 32 can be reduced. Change can be suppressed. As a result, it is possible to always apply a stable urging force to each of the power supply brushes 31a and 31b.
　本発明は、前記実施形態の構成に限定されるものではなく、例えば、前記各捩りコイルばね３２，３２のコイル径や巻き線部３２ａ、３２ａの巻き線量を任意に設定することも可能である。 The present invention is not limited to the configuration of the above embodiment, and for example, the coil diameter of each of the torsion coil springs 32 and 32 and the winding dose of the winding portions 32a and 32a can be arbitrarily set. .
　また、リテーナ５５は、隔壁６２によってカバー本体２８に固定されるものに限らず、例えば各支持軸６１の端部６１ａ、６１ｂを前記カバー部材に嵌着や溶接によって固定することで保持されても良い。 The retainer 55 is not limited to the one fixed to the cover main body 28 by the partition wall 62. For example, the retainer 55 may be held by fixing the end portions 61a and 61b of the support shafts 61 to the cover member by welding or welding. good.
　さらに、リテーナ５５をカバー本体２８に固定する方法としては、前記カバー本体２８側にネジ孔を切り、前記固定用孔６２ｃ、６２ｃにネジを挿通して固定することも可能である。また、前記各突起部６０，６０によって各固定用突壁６２ｂ、６２ｂを固定する方法としては、前記各突起部６０，６０を溶着する他に、前記各突起部６０，６０の先端部に割りピンを挿入して固定することも可能である。 Furthermore, as a method of fixing the retainer 55 to the cover main body 28, it is also possible to cut a screw hole on the cover main body 28 side and insert and fix the screw into the fixing holes 62c and 62c. In addition, as a method of fixing the fixing protruding walls 62b and 62b by the protrusions 60 and 60, in addition to welding the protrusions 60 and 60, the fixing protrusion walls 62b and 62b can be divided at the tip ends of the protrusions 60 and 60. It is also possible to insert and fix a pin.
　前記第１部材としては、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 first member may be a timing pulley in addition to the timing sprocket.
　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.
　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、第１部材に対する第２部材の相対回転位相を変更することによって、機関弁の作動特性を可変にする内燃機関のバルブタイミング制御装置であって、前記第１部材または第２部材の一方側に一体的に設けられ、通電されることによって前記第１部材に対する第２部材の相対回転位相を変更する電動モータと、該電動モータの前端部を覆うように配置固定されたカバー部材と、前記電動モータ側に設けられ、内外二重に設けられた一対の給電用のスリップリングと、前記カバー部材側に設けられ、対応する前記各スリップリングに接触して給電する一対の給電用ブラシと、前記カバー部材側に、巻き線部が前記カバー部材の径方向において前記各給電用ブラシと重なるように設けられ、前記各給電用ブラシを前記各スリップリング方向へ付勢する一対の捩りコイルばねと、前記各捩りコイルばねの内部軸方向に挿通する支持軸と、該支持軸に設けられて、前記２つの捩りコイルばねを軸方向で隔成しつつ前記カバー部材に固定される隔壁とを有する支持部材と、前記カバー部材の前記捩りコイルばねが配置される外側面側に設けられた突起部と、前記支持部材に貫通形成されて、前記突起部に嵌入される固定用孔と、を備えている。 In one aspect, the valve timing control device for an internal combustion engine is a valve timing control device for an internal combustion engine that varies the operating characteristics of the engine valve by changing the relative rotational phase of the second member with respect to the first member. An electric motor that is integrally provided on one side of the first member or the second member and that changes the relative rotational phase of the second member with respect to the first member when energized; and a front end portion of the electric motor A cover member arranged and fixed so as to cover, a pair of power supply slip rings provided on the electric motor side and provided on the inner and outer sides, and each corresponding slip ring provided on the cover member side A pair of power supply brushes for supplying power in contact with the cover member, and on the cover member side, the winding portion overlaps each of the power supply brushes in the radial direction of the cover member A pair of torsion coil springs that urge each of the power supply brushes in the direction of each slip ring, a support shaft that is inserted in the direction of the internal axis of each of the torsion coil springs, and provided on the support shaft, A support member having a partition wall which is fixed to the cover member while separating two torsion coil springs in the axial direction; and a protrusion provided on an outer surface side of the cover member where the torsion coil spring is disposed; And a fixing hole that is formed through the support member and is fitted into the protrusion.
　前記内燃機関のバルブタイミング制御装置の好ましい態様において、前記固定用孔は前記支持部材の前記隔壁に設けられている。 In a preferred aspect of the valve timing control device for the internal combustion engine, the fixing hole is provided in the partition wall of the support member.
　別の好ましい態様では、前記内燃機関のバルブタイミング制御装置の態様のいずれかにおいて、前記カバー部材の外側面に凹部が形成されていると共に、前記支持部材と各捩りコイルばねが前記突起部と固定用孔を介して前記凹部内に収容固定される。 In another preferred aspect, in any one of the aspects of the valve timing control device of the internal combustion engine, a recess is formed on the outer surface of the cover member, and the support member and each torsion coil spring are fixed to the protrusion. It is accommodated and fixed in the recess through the use hole.
　さらに別の好ましい態様では、前記内燃機関のバルブタイミング制御装置の態様のいずれかにおいて、前記突起部を前記固定用孔に挿入した状態で、前記突起部の先端が溶着されて、前記隔壁が前記凹部の壁部に固定されている。 In still another preferred aspect, in any one of aspects of the valve timing control device of the internal combustion engine, in a state where the protrusion is inserted into the fixing hole, a tip of the protrusion is welded, and the partition wall is It is fixed to the wall of the recess.
　さらに別の好ましい態様では、前記内燃機関のバルブタイミング制御装置の態様のいずれかにおいて、前記隔壁の固定用孔は、前記支持軸に対して交差する方向の位置に２つ設けられている。 In still another preferred aspect, in any of the aspects of the valve timing control device of the internal combustion engine, two fixing holes for the partition wall are provided at positions in a direction intersecting the support shaft.
　さらに別の好ましい態様では、前記内燃機関のバルブタイミング制御装置の態様のいずれかにおいて、前記凹部は、長溝状に形成された保持溝部と、該保持溝部の対向する両長辺側の長手方向の両端の間に内方へ突設された一対の棚部と、を有し、該両棚部の上面に前記突起部がそれぞれ設けられている一方、前記支持部材の隔壁は、前記支持軸の下部に一体に設けられて、前記支持軸と一緒に前記保持溝部に収容される底壁部と、前記支持軸の径方向の両側から突設されて、前記各棚部の上面に載置されると共に、前記各突起部が挿通する前記固定用孔が穿設された一対の固定用突壁と、を有する。 In still another preferred aspect, in any one of the aspects of the valve timing control device of the internal combustion engine, the concave portion includes a holding groove portion formed in a long groove shape, and a longitudinal direction on both long sides facing the holding groove portion. A pair of shelves projecting inward between both ends, and the protrusions are provided on the upper surfaces of the shelves, respectively, while the partition walls of the support member are Provided integrally with the lower portion, the bottom wall portion accommodated in the holding groove portion together with the support shaft, and projecting from both radial sides of the support shaft, and placed on the upper surface of each shelf portion And a pair of fixing protrusion walls in which the fixing holes through which the protrusions are inserted are formed.
　この態様によれば、リテーナの隔壁は、各突起部の長さを隔壁の径方向厚さよりも短くできる。この結果、組み付け時や溶着後に各突起部にかかるモーメントの影響を低減し、各突起部の折れなどの破損を抑制することができる。 According to this aspect, the partition wall of the retainer can make the length of each protrusion shorter than the radial thickness of the partition wall. As a result, it is possible to reduce the influence of the moment applied to each projection during assembly or after welding, and to suppress breakage such as breakage of each projection.
　さらに別の好ましい態様では、前記内燃機関のバルブタイミング制御装置の態様のいずれかにおいて、前記支持部材の支持軸の軸心が前記保持溝部内に位置する。 In still another preferred aspect, in any of the aspects of the valve timing control device of the internal combustion engine, the axis of the support shaft of the support member is located in the holding groove portion.
　さらに別の好ましい態様では、前記内燃機関のバルブタイミング制御装置の態様のいずれかにおいて、前記カバー部材は、樹脂材によって形成された外層部と、該外層部の内部にモールドされた金属製の芯材とからなり、前記芯材の所定位置に、前記樹脂材が充填された貫通部を有すると共に、該貫通部の形成位置に前記樹脂材によって前記凹部が形成されている。 In still another preferred aspect, in any one of the aspects of the valve timing control device of the internal combustion engine, the cover member includes an outer layer portion formed of a resin material, and a metal core molded inside the outer layer portion. And a through portion filled with the resin material at a predetermined position of the core material, and the concave portion is formed by the resin material at a formation position of the through portion.
　さらに別の好ましい態様では、前記内燃機関のバルブタイミング制御装置の態様のいずれかにおいて、前記凹部内に前記支持部材を介して収容固定された状態で、前記各捩りコイルばねの巻き線部の一部が前記芯材の貫通部と径方向で重なるように設けられている。 In yet another preferred aspect, in any one of the aspects of the valve timing control device of the internal combustion engine, one winding portion of each torsion coil spring is accommodated and fixed in the recess through the support member. The portion is provided so as to overlap the penetrating portion of the core member in the radial direction.
　さらに別の好ましい態様では、前記内燃機関のバルブタイミング制御装置の態様のいずれかにおいて、前記一対の給電用ブラシの後端面に、前記一対の捩りコイルばねの一端部が嵌入して当接する凹溝が形成されている。 In still another preferred aspect, in any one of the aspects of the valve timing control device of the internal combustion engine, the concave groove in which one end portions of the pair of torsion coil springs are fitted into and contact with rear end surfaces of the pair of power supply brushes. Is formed.
　さらに別の好ましい態様では、前記内燃機関のバルブタイミング制御装置の態様のいずれかにおいて、前記一対の捩りコイルばねは、巻き線方向が互いに逆方向に形成されていると共に、前記一対の給電用ブラシの後端面をそれぞれ押圧する各一端部間の距離が近接しているのに対して、前記カバー部材に弾接する各他端部間の距離が離間している。 In still another preferred aspect, in any one of aspects of the valve timing control device of the internal combustion engine, the pair of torsion coil springs are formed so that winding directions are opposite to each other, and the pair of power supply brushes The distance between the respective one end portions that respectively press the rear end surfaces is close, whereas the distance between the respective other end portions that are in elastic contact with the cover member is separated.
　さらに別の好ましい態様では、前記内燃機関のバルブタイミング制御装置の態様のいずれかにおいて、前記一対の捩りコイルばねは、前記一対の給電用ブラシを押圧する各一端部が各他端部との相対関係で互いに閉じ側から開く方向にばね力が作用する。 In yet another preferred aspect, in any one of the aspects of the valve timing control device of the internal combustion engine, the pair of torsion coil springs are configured such that each one end portion that presses the pair of power supply brushes is relative to each other end portion. Therefore, a spring force acts in the direction of opening from the closed side.
　また、内燃機関のバルブタイミング制御装置は、別の観点から、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、カムシャフトと一体に回転する従動回転体と、を有し、前記駆動回転体に対して従動回転体の相対回転位相を変換する内燃機関のバルブタイミング制御装置において、前記駆動回転体に一体に設けられた電動モータと、該電動モータの前記カムシャフトと反対側の前端部に軸方向から対向配置されたカバー部材と、前記電動モータの前端部に内外二重に設けられた給電用スリップリングと、前記カバー部材に設けられ、前記各スリップリングにそれぞれ当接する一対の給電用ブラシと、円柱状の支持軸と該支持軸の軸方向のほぼ中央位置に設けられた係止部と、を有する支持部材と、前記係止部を挟んだ前記支持軸の両端部に巻き線部がそれぞれ嵌挿され、各一端部が前記各給電用ブラシを前記各スリップリング方向へ付勢する一方、各他端部が前記カバー部材に係止された一対の捩りコイルばねと、前記カバー部材に、前記カバー部材の径方向において前記各給電用ブラシと重なるように形成されて、各捩りコイルばねが前記支持部材の支持軸に取り付けられた状態で内部に収容される凹部と、前記支持部材の係止部を前記カバー部材の前記凹部内に固定する固定手段と、を備えている。 In another aspect, the valve timing control device for an internal combustion engine includes a drive rotator to which the rotational force from the crankshaft is transmitted and a driven rotator that rotates integrally with the camshaft, and the drive rotation In a valve timing control device for an internal combustion engine that converts a relative rotational phase of a driven rotor relative to a body, an electric motor provided integrally with the drive rotor, and a front end portion of the electric motor opposite to the camshaft And a pair of power feedings provided on the cover member and in contact with the slip rings, respectively, and a cover member disposed oppositely from the axial direction, a power feeding slip ring provided on the front end of the electric motor. A support member having a brush, a cylindrical support shaft, and a locking portion provided at a substantially central position in the axial direction of the support shaft; and the support shaft sandwiching the locking portion A pair of torsion coils in which winding portions are respectively inserted into both end portions, each one end portion urges each power supply brush in each slip ring direction, and each other end portion is locked to the cover member. A spring and the cover member are formed so as to overlap with each of the power supply brushes in the radial direction of the cover member, and each torsion coil spring is accommodated in the state attached to the support shaft of the support member. A recess, and a fixing means for fixing the locking portion of the support member in the recess of the cover member.
　前記内燃機関のバルブタイミング制御装置の好ましい態様において、前記カバー部材は、樹脂部と、該樹脂部の内部にモールド固定された金属板状の芯材とからなり、前記芯材の切り欠かれた所定部位に充填された前記樹脂部によって前記凹部が形成されていると共に、該凹部内に配置された前記支持部材の係止部の一部が、前記凹部を介して前記芯材に対して径方向でオーバーラップするように配置されている。 In a preferred aspect of the valve timing control device for the internal combustion engine, the cover member includes a resin portion and a metal plate-like core material fixed to the inside of the resin portion, and the core material is notched. The concave portion is formed by the resin portion filled in a predetermined portion, and a part of the locking portion of the support member disposed in the concave portion has a diameter with respect to the core member through the concave portion. It is arranged to overlap in the direction.
　別の好ましい態様では、前記内燃機関のバルブタイミング制御装置の態様のいずれかにおいて、前記カバー部材は、カバー本体が樹脂材で形成された外層部と、該外層部にモールドされた金属製の芯材とを有し、前記芯材は、所定位置に貫通部を有すると共に、前記カバー本体の凹部が前記芯材の貫通部に前記樹脂材によって隔成されている。 In another preferred aspect, in any one of the aspects of the valve timing control device of the internal combustion engine, the cover member includes an outer layer portion in which a cover body is formed of a resin material, and a metal core molded on the outer layer portion. The core material has a penetrating portion at a predetermined position, and the concave portion of the cover body is separated from the penetrating portion of the core material by the resin material.
　この態様によれば、各捩りコイルばねを収容する凹部を貫通部の形成位置に形成することによって、前記各捩りコイルばねを含めたカバー本体全体の肉厚を可及的に小さくできるので、装置の軸方向の長さを短くすることができる。また、金属製の芯材によってカバー本体全体の剛性を高められる。 According to this aspect, the thickness of the entire cover body including the torsion coil springs can be made as small as possible by forming the recesses for accommodating the torsion coil springs at the positions where the through portions are formed. The axial length can be shortened. Further, the rigidity of the entire cover body can be increased by the metal core material.
　さらに別の好ましい態様では、前記内燃機関のバルブタイミング制御装置の態様のいずれかにおいて、前記固定手段は、前記カバー部材の前記捩りコイルばねが配置される外側面側に設けられた突起部と、前記支持部材に貫通形成されて、前記突起部に嵌入される固定用孔と、を含む。 In still another preferred aspect, in any one of the aspects of the valve timing control device of the internal combustion engine, the fixing means includes a protrusion provided on an outer surface side of the cover member on which the torsion coil spring is disposed, A fixing hole that is formed through the support member and is fitted into the protrusion.

Claims (16)

  1. 　第１部材に対する第２部材の相対回転位相を変更することによって、機関弁の作動特性を可変にする内燃機関のバルブタイミング制御装置であって、
    　前記第１部材または第２部材の一方側に一体的に設けられ、通電されることによって前記第１部材に対する第２部材の相対回転位相を変更する電動モータと、
    　該電動モータの前端部を覆うように配置固定されたカバー部材と、
    　前記電動モータ側に設けられ、内外二重に設けられた一対の給電用のスリップリングと、
    　前記カバー部材側に設けられ、対応する前記各スリップリングに接触して給電する一対の給電用ブラシと、
    　前記カバー部材側に、巻き線部が前記カバー部材の径方向において前記各給電用ブラシと重なるように設けられ、前記各給電用ブラシを前記各スリップリング方向へ付勢する一対の捩りコイルばねと、
    　前記各捩りコイルばねの内部軸方向に挿通する支持軸と、該支持軸に設けられて、前記２つの捩りコイルばねを軸方向で隔成しつつ前記カバー部材に固定される隔壁とを有する支持部材と、
    　前記カバー部材の前記捩りコイルばねが配置される外側面側に設けられた突起部と、
    　前記支持部材に貫通形成されて、前記突起部に嵌入される固定用孔と、
    　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 valve timing control device for an internal combustion engine that changes an operation characteristic of an engine valve by changing a relative rotational phase of a second member with respect to a first member,
    An electric motor that is integrally provided on one side of the first member or the second member and changes a relative rotation phase of the second member with respect to the first member by being energized;
    A cover member arranged and fixed so as to cover the front end of the electric motor;
    A pair of power supply slip rings provided on the electric motor side and provided inside and outside double;
    A pair of power supply brushes that are provided on the cover member side and that supply power in contact with the corresponding slip rings;
    A pair of torsion coil springs provided on the cover member side so that a winding portion overlaps each of the power supply brushes in the radial direction of the cover member, and biases each of the power supply brushes in the direction of each slip ring. ,
    A support shaft having a support shaft inserted through the torsion coil springs in the internal axial direction and a partition wall provided on the support shaft and fixed to the cover member while separating the two torsion coil springs in the axial direction. Members,
    A protrusion provided on the outer surface side where the torsion coil spring of the cover member is disposed;
    A fixing hole formed through the support member and fitted into the protrusion;
    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、
    　前記固定用孔は前記支持部材の前記隔壁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。     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 fixing hole is provided in the partition wall of the support member.
  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、
    　前記カバー部材の外側面に凹部が形成されていると共に、前記支持部材と各捩りコイルばねが前記突起部と固定用孔を介して前記凹部内に収容固定され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,
    A concave portion is formed on an outer surface of the cover member, and the support member and each torsion coil spring are housed and fixed in the concave portion through the protrusion and a fixing hole. Valve timing control device.
  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、
    　前記突起部を前記固定用孔に挿入した状態で、前記突起部の先端が溶着されて、前記隔壁が前記凹部の壁部に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,
    A valve timing control device for an internal combustion engine, wherein a tip of the projection is welded in a state where the projection is inserted into the fixing hole, and the partition is fixed to a wall of the recess.
  5. 　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、
    　前記隔壁の固定用孔は、前記支持軸に対して交差する方向の位置に２つ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 two fixing holes for the partition wall are provided at positions intersecting with the support shaft.
  6. 　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、
    　前記凹部は、長溝状に形成された保持溝部と、該保持溝部の対向する両長辺側の長手方向の両端の間に内方へ突設された一対の棚部と、を有し、該両棚部の上面に前記突起部がそれぞれ設けられている一方、
    　前記支持部材の隔壁は、前記支持軸の下部に一体に設けられて、前記支持軸と一緒に前記保持溝部に収容される底壁部と、前記支持軸の径方向の両側から突設されて、前記各棚部の上面に載置されると共に、前記各突起部が挿通する前記固定用孔が穿設された一対の固定用突壁と、
    　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 concave portion has a holding groove portion formed in a long groove shape, and a pair of shelf portions projecting inwardly between both ends in the longitudinal direction on both long sides facing the holding groove portion, While the protrusions are provided on the upper surfaces of both shelves,
    The partition wall of the support member is provided integrally with a lower portion of the support shaft, and protrudes from both sides of the support shaft in the radial direction of the support shaft and the bottom wall portion accommodated in the holding groove portion. A pair of fixing projecting walls that are placed on the upper surface of each shelf and in which the fixing holes through which the protrusions are inserted are formed;
    A valve timing control device for an internal combustion engine, comprising:
  7. 　請求項６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、
    　前記支持部材の支持軸の軸心が前記保持溝部内に位置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 6,
    The valve timing control device for an internal combustion engine, wherein an axis of a support shaft of the support member is located in the holding groove.
  8. 　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、
    　前記カバー部材は、樹脂材によって形成された外層部と、該外層部の内部にモールドされた金属製の芯材とからなり、
    　前記芯材の所定位置に、前記樹脂材が充填された貫通部を有すると共に、該貫通部の形成位置に前記樹脂材によって前記凹部が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 3,
    The cover member comprises an outer layer portion formed of a resin material, and a metal core material molded inside the outer layer portion,
    A valve timing control for an internal combustion engine having a through portion filled with the resin material at a predetermined position of the core material, and the concave portion being formed by the resin material at a formation position of the through portion. apparatus.
  9. 　請求項８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、
    　前記凹部内に前記支持部材を介して収容固定された状態で、前記各捩りコイルばねの巻き線部の一部が前記芯材の貫通部と径方向で重なるよう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。     The valve timing control device for an internal combustion engine according to claim 8,
    A portion of the winding portion of each torsion coil spring is provided so as to overlap with the through portion of the core member in a radial direction in a state of being housed and fixed in the recess through the support member. A valve timing control device for an internal combustion engine.
  10. 　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、
    　前記一対の給電用ブラシの後端面に、前記一対の捩りコイルばねの一端部が嵌入して当接する凹溝が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 3,
    A valve timing control device for an internal combustion engine, wherein a concave groove is formed on the rear end face of the pair of power supply brushes, into which one end portions of the pair of torsion coil springs are fitted and abutted.
  11. 　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、
    　前記一対の捩りコイルばねは、巻き線方向が互いに逆方向に形成されていると共に、前記一対の給電用ブラシの後端面をそれぞれ押圧する各一端部間の距離が近接しているのに対して、前記カバー部材に弾接する各他端部間の距離が離間し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 pair of torsion coil springs are formed so that the winding directions are opposite to each other, and the distances between the one end portions that respectively press the rear end surfaces of the pair of power supply brushes are close to each other. A valve timing control device for an internal combustion engine, characterized in that the distance between the other end portions elastically contacting the cover member is separated.
  12. 　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、
    　前記一対の捩りコイルばねは、前記一対の給電用ブラシを押圧する各一端部が各他端部との相対関係で互いに閉じ側から開く方向にばね力が作用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,
    In the internal combustion engine, the pair of torsion coil springs are configured such that each one end portion that presses the pair of power supply brushes has a spring force acting in a direction opening from the closed side relative to each other end portion. Valve timing control device.
  13. 　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、カムシャフトと一体に回転する従動回転体と、を有し、前記駆動回転体に対して従動回転体の相対回転位相を変換する内燃機関のバルブタイミング制御装置において、
    　前記駆動回転体に一体に設けられた電動モータと、
    　該電動モータの前記カムシャフトと反対側の前端部に軸方向から対向配置されたカバー部材と、
    　前記電動モータの前端部に内外二重に設けられた給電用スリップリングと、
    　前記カバー部材に設けられ、前記各スリップリングにそれぞれ当接する一対の給電用ブラシと、
    　円柱状の支持軸と該支持軸の軸方向のほぼ中央位置に設けられた係止部と、を有する支持部材と、
    　前記係止部を挟んだ前記支持軸の両端部に巻き線部がそれぞれ嵌挿され、各一端部が前記各給電用ブラシを前記各スリップリング方向へ付勢する一方、各他端部が前記カバー部材に係止された一対の捩りコイルばねと、
    　前記カバー部材に、前記カバー部材の径方向において前記各給電用ブラシと重なるように形成されて、各捩りコイルばねが前記支持部材の支持軸に取り付けられた状態で内部に収容される凹部と、
    　前記支持部材の係止部を前記カバー部材の前記凹部内に固定する固定手段と、
    　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。     An internal combustion engine having a drive rotator to which the rotational force from the crankshaft is transmitted and a driven rotator that rotates integrally with the camshaft, and that converts a relative rotational phase of the driven rotator with respect to the drive rotator. In the valve timing control device of
    An electric motor provided integrally with the drive rotor;
    A cover member disposed to face the front end of the electric motor opposite to the camshaft from the axial direction;
    A slip ring for power feeding provided in an inner and outer double at the front end of the electric motor;
    A pair of power supply brushes provided on the cover member and in contact with the slip rings;
    A support member having a cylindrical support shaft and a locking portion provided at a substantially central position in the axial direction of the support shaft;
    Winding portions are respectively inserted into both end portions of the support shaft across the locking portion, and each one end portion urges each power supply brush in each slip ring direction, while each other end portion A pair of torsion coil springs locked to the cover member;
    A concave portion that is formed in the cover member so as to overlap with each of the power supply brushes in the radial direction of the cover member, and each of the torsion coil springs is housed inside the support shaft of the support member;
    Fixing means for fixing the locking portion of the support member in the recess of the cover member;
    A valve timing control apparatus for an internal combustion engine, comprising:
  14. 　請求項１３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、
    　前記カバー部材は、樹脂部と、該樹脂部の内部にモールド固定された金属板状の芯材とからなり、
    　前記芯材の切り欠かれた所定部位に充填された前記樹脂部によって前記凹部が形成されていると共に、該凹部内に配置された前記支持部材の係止部の一部が、前記凹部を介して前記芯材に対して径方向でオーバーラップするように配置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 13,
    The cover member is composed of a resin portion and a metal plate-like core material fixed to the inside of the resin portion,
    The recess is formed by the resin portion filled in a predetermined part of the core material, and a part of the locking portion of the support member disposed in the recess is interposed through the recess. A valve timing control device for an internal combustion engine, wherein the valve timing control device is disposed so as to overlap the core material in a radial direction.
  15. 　請求項１４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、
    　前記カバー部材は、カバー本体が樹脂材で形成された外層部と、該外層部にモールドされた金属製の芯材とを有し、
    　前記芯材は、所定位置に貫通部を有すると共に、前記カバー本体の凹部が前記芯材の貫通部に前記樹脂材によって隔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 14,
    The cover member has an outer layer portion in which a cover main body is formed of a resin material, and a metal core material molded on the outer layer portion,
    The valve timing control device for an internal combustion engine, wherein the core member has a through portion at a predetermined position, and a concave portion of the cover body is separated from the through portion of the core material by the resin material.
  16. 　請求項１３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、
    　前記固定手段は、前記カバー部材の前記捩りコイルばねが配置される外側面側に設けられた突起部と、前記支持部材に貫通形成されて、前記突起部に嵌入される固定用孔と、を含む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 13,
    The fixing means includes: a protrusion provided on an outer surface side of the cover member where the torsion coil spring is disposed; and a fixing hole formed through the support member and fitted into the protrusion. A valve timing control apparatus for an internal combustion engine, comprising:
PCT/JP2016/071483 2015-08-10 2016-07-22 Valve timing control device for internal combustion engine WO2017026240A1 (en)

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JP2019019698A (en) * 2017-07-13 2019-02-07 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 manufacturing method of the valve timing control device
EP3578769A1 (en) 2018-06-01 2019-12-11 Ovalo GmbH Adjusting device, in particular camshaft adjuster

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Publication number Priority date Publication date Assignee Title
JP2019019698A (en) * 2017-07-13 2019-02-07 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 manufacturing method of the valve timing control device
EP3578769A1 (en) 2018-06-01 2019-12-11 Ovalo GmbH Adjusting device, in particular camshaft adjuster

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