WO2017026240A1 - Dispositif de commande de calage de distribution destiné à un moteur à combustion interne - Google Patents

Dispositif de commande de calage de distribution destiné à un moteur à combustion interne 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
English (en)
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/ja
Publication of WO2017026240A1 publication Critical patent/WO2017026240A1/fr

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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

Selon la présente invention, une paire de parties de plate-forme (58) ayant des parties saillantes (60) dans les surfaces supérieures est prévue dans des surfaces latérales opposées d'une rainure de réception (56) prévue dans une surface côté externe (28b) d'un corps de couvercle (28) d'un élément couvercle (4), des sections de fil d'enroulement (32a) d'une paire de ressorts hélicoïdaux de torsion (32) soutenus à des parties d'extrémité (61a, 61b) d'un arbre de support (61) d'un organe de retenue sont reçues dans la rainure de réception, des parois de fixation saillantes (62b) sont prévues dans des positions au centre de l'arbre de support (61), et, avec les parties saillantes des parties de plate-forme introduites à travers des trous de fixation (62c) percés dans les centres des parois de fixation saillantes, les extrémités avant des parties saillantes sont soudées, ce par quoi l'organe de retenue est fixé aux parties de plate-forme (58). Le dispositif peut ainsi être réduit en longueur axiale, et l'élément de support peut être fixé solidement à l'élément couvercle.
PCT/JP2016/071483 2015-08-10 2016-07-22 Dispositif de commande de calage de distribution destiné à un moteur à combustion interne WO2017026240A1 (fr)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019019698A (ja) * 2017-07-13 2019-02-07 日立オートモティブシステムズ株式会社 内燃機関のバルブタイミング制御装置と該バルブタイミング制御装置の製造方法
EP3578769A1 (fr) 2018-06-01 2019-12-11 Ovalo GmbH Dispositif de réglage, en particulier régulateur d'arbre à cames

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0660275U (ja) * 1993-01-14 1994-08-19 ジェコー株式会社 モータにおけるブラシ保持構造
JP2003023746A (ja) * 2001-07-04 2003-01-24 Mitsuba Corp ブラシホルダユニット
JP2008005689A (ja) * 2006-05-24 2008-01-10 Denso Corp 燃料ポンプ
WO2015087648A1 (fr) * 2013-12-11 2015-06-18 日立オートモティブシステムズ株式会社 Dispositif de commande de réglage de soupapes pour moteur à combustion interne
WO2016009790A1 (fr) * 2014-07-15 2016-01-21 日立オートモティブシステムズ株式会社 Dispositif de soupape variable pour moteur à combustion interne

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0660275U (ja) * 1993-01-14 1994-08-19 ジェコー株式会社 モータにおけるブラシ保持構造
JP2003023746A (ja) * 2001-07-04 2003-01-24 Mitsuba Corp ブラシホルダユニット
JP2008005689A (ja) * 2006-05-24 2008-01-10 Denso Corp 燃料ポンプ
WO2015087648A1 (fr) * 2013-12-11 2015-06-18 日立オートモティブシステムズ株式会社 Dispositif de commande de réglage de soupapes pour moteur à combustion interne
WO2016009790A1 (fr) * 2014-07-15 2016-01-21 日立オートモティブシステムズ株式会社 Dispositif de soupape variable pour moteur à combustion interne

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019019698A (ja) * 2017-07-13 2019-02-07 日立オートモティブシステムズ株式会社 内燃機関のバルブタイミング制御装置と該バルブタイミング制御装置の製造方法
EP3578769A1 (fr) 2018-06-01 2019-12-11 Ovalo GmbH Dispositif de réglage, en particulier régulateur d'arbre à cames

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