WO2017208530A1 - Valve timing control device for internal combustion engine and power supply device for electric motor - Google Patents

Valve timing control device for internal combustion engine and power supply device for electric motor Download PDF

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Publication number
WO2017208530A1
WO2017208530A1 PCT/JP2017/007202 JP2017007202W WO2017208530A1 WO 2017208530 A1 WO2017208530 A1 WO 2017208530A1 JP 2017007202 W JP2017007202 W JP 2017007202W WO 2017208530 A1 WO2017208530 A1 WO 2017208530A1
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WO
WIPO (PCT)
Prior art keywords
combustion engine
internal combustion
timing control
valve timing
power supply
Prior art date
Application number
PCT/JP2017/007202
Other languages
French (fr)
Japanese (ja)
Inventor
亮 田所
山田　吉彦
Original Assignee
日立オートモティブシステムズ株式会社
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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
Publication of WO2017208530A1 publication Critical patent/WO2017208530A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K13/00—Structural associations of current collectors with motors or generators, e.g. brush mounting plates or connections to windings; Disposition of current collectors in motors or generators; Arrangements for improving commutation

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, and a power supply device for an electric motor.
  • Patent Document 1 As a valve timing control device for an internal combustion engine, a device described in Patent Document 1 below is known.
  • a cylindrical motor housing of an electric motor is bolted to the front end portion of the sprocket body of the timing sprocket, and a disk-shaped power feeding plate is fixed to the front end portion of the motor housing.
  • the plate is provided with a pair of slip rings on the front end face for energizing the coil of the electric motor via a commutator.
  • a cover member is provided at a front position of the motor housing so as to cover the power feeding plate.
  • a pair of power supply brushes are provided at the rear end of the cover member so as to contact the slip rings of the power supply plate from the axial direction of the motor housing.
  • the pair of power supply brushes provided on the cover member come into contact with each slip ring from the axial direction of the motor housing. For this reason, the axial length of the apparatus is inevitably long.
  • the present invention has been devised in view of the above-described conventional technical problems, and an object thereof is to provide a valve timing control device for an internal combustion engine capable of shortening the axial length of the device.
  • the invention of the present application is characterized in that a power supply brush that abuts against a slip ring formed on the outer periphery of the motor housing is abutted from the radial direction of the motor housing.
  • the length of the apparatus in the axial direction can be sufficiently shortened, and the ease of mounting the internal combustion engine in the engine room and the layout are improved.
  • FIG. 1st embodiment of a valve timing control device It is a longitudinal section showing a 1st embodiment of a valve timing control device concerning the present invention. It is a disassembled perspective view which shows the main structural members in this embodiment. It is a principal part enlarged view of this embodiment shown in FIG. It is a perspective view which shows the state which assembled
  • valve timing control device for an internal combustion engine and a power feeding device for an electric motor 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 of an in-line four-cylinder internal combustion engine.
  • the valve timing control device is provided on a timing sprocket 1 which is a driving rotating body to which the rotational driving force of a crankshaft of an internal combustion engine is transmitted via a timing chain, and on a cylinder head 01.
  • the camshaft 2 is rotatably supported via a bearing 02, and is disposed between the timing sprocket 1 and the camshaft 2, and is disposed between the timing sprocket 1 and the camshaft 2.
  • the phase change mechanism 3 that changes the relative rotational phases of the two and 1 and the cover member 4 that is a fixed member disposed at the front end of the phase change mechanism 3 is provided.
  • the timing sprocket 1 is formed integrally with an iron-based metal in an annular shape.
  • the sprocket body 1a has a relatively small outer diameter and is integrally provided on the outer periphery of the sprocket body 1a.
  • a gear portion 1b that receives the rotational force from the crankshaft via a rotated timing chain (not shown).
  • an internal tooth component 5 is integrally provided on the front end side of the sprocket body 1a.
  • 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.
  • a motor housing 14 of an electric motor 12 described later is coupled to the outer end surface in the axial direction of the internal tooth component 5 from the axial direction via the bolts 7.
  • the timing sprocket 1 has a single large-diameter ball bearing 6 interposed between a sprocket body 1a and a driven member 9 which is a driven rotating body, which will be described later, fixed to one axial end portion 2a of the camshaft 2.
  • a large diameter ball bearing 6 By this large diameter ball bearing 6, the timing sprocket 1 is supported by the driven member 9 (cam shaft 2) so as to be relatively rotatable.
  • a holding plate 8 is fixed to the rear end surface of the sprocket body 1a on the side opposite to the internal teeth constituting portion 5.
  • the holding plate 8 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 1a.
  • the inner diameter of the central hole 8a at the center is formed smaller than the inner diameter of the outer ring 6a of the large-diameter ball bearing 6, and the inner side surface of the inner peripheral portion has a small gap on the other end surface in the axial direction of the outer ring 6a. Facing each other in the axial direction.
  • a substantially inverted trapezoidal stopper convex portion 8b protruding in the direction of the central axis is integrally provided at a predetermined position on the inner peripheral edge of the central hole 8a of the holding plate 8.
  • eight bolt insertion holes 1c through which eight bolts 7 are inserted are formed in the outer peripheral portions of the sprocket main body 1a including the internal gear component 5 and the holding plate 8 at substantially equal intervals in the circumferential direction. ing.
  • the camshaft 2 has two drive cams per cylinder for opening an intake valve (not shown) on the outer periphery.
  • the camshaft 2 has a driven member 9 fixed together by a cam bolt 10 from the axial direction via an axial end portion 2a and a flange portion 2b integrally provided on the outer periphery of the end portion 2a.
  • An arcuate stopper groove 11 into which the stopper convex portion 8c is inserted is formed in the flange portion 2b. Both side surfaces of the stopper projection 8c are in contact with the circumferential surface of the stopper groove 11 as appropriate, and the relative rotational position of the camshaft 2 with respect to the timing sprocket 1, that is, the maximum advance angle position and the maximum delay angle position are mechanically determined. It has come to regulate.
  • the driven member 9 is integrally formed of iron-based metal, and as shown in FIGS. 1 and 2, a disk-like fixed end portion 9a formed on the rear end side (camshaft 2 side), and the fixed end It is mainly composed of a cylindrical portion 9b protruding in the axial direction from the inner peripheral front end face of the portion 9a.
  • the fixed end portion 9a has an outer surface opposed to the front end surface side of the one end portion 2a of the camshaft 2, and the end portion 2a of the camshaft 2 is fitted from the axial direction at a substantially central position of the outer surface.
  • a groove 9d is formed.
  • the cylindrical portion 9b has a bolt insertion hole 9c through which the shaft portion 10b of the cam bolt 10 is inserted in the inner axial direction including the fixed end portion 9a.
  • a bearing 35 and a needle bearing 36 are juxtaposed in the axial direction.
  • the cam bolt 10 has an axial end face of the head 10a supporting the inner ring of the small-diameter ball bearing 35 from the axial direction, and is formed inside the camshaft 2 on the outer periphery of the shaft portion 10b.
  • a male screw 10c that is screwed onto the female screw 2c is formed.
  • the phase changing mechanism 3 is mainly composed of an electric motor 12 disposed on the front end side of the cylindrical portion 9b of the driven member 9, and a speed reducing mechanism 13 that reduces the rotational speed of the electric motor 12 and transmits it to the camshaft 2. Has been.
  • the electric motor 12 is a brushed DC motor, and includes a motor housing 14 that is a yoke that rotates integrally with the timing sprocket 1, and a cylindrical housing body 14 a of the motor housing 14.
  • Fixed to the motor output shaft 15 provided rotatably inside, six arc-shaped permanent magnets 16 fixed to the inner peripheral surface of the housing body 14a, and the cover member 4 side which is the front end of the housing body 14a.
  • a power feeding plate 17 as a holding member.
  • the housing main body 14a of the motor housing 14 is formed into a bottomed cylindrical shape with an iron-based metal material, and has an outer diameter that is relatively small like the outer diameter of the sprocket main body 1a.
  • a disc-shaped partition wall 14b is integrally formed on the rear end side.
  • the housing main body 14a has a cylindrical fixing portion 14e having a small stepped diameter formed at the front end portion on the cover member 4 side, and a large-diameter annular protrusion 14f on the outer periphery of the rear end side of the cylindrical fixing portion 14e. Are integrally formed.
  • the partition wall 14b is formed with a large-diameter shaft insertion hole 14c through which the motor output shaft 15 and the eccentric shaft portion 37 are inserted, on the inner periphery of a cylindrical extension portion at substantially the center. Further, on the outer peripheral portion of the partition wall 14b, six female screw holes 14d into which the tip end portions of the respective bolts 7 are screwed at positions corresponding to the respective bolt insertion holes 1c and 8c are formed at equally spaced positions in the circumferential direction. .
  • the timing sprocket 1 (internal tooth component 5), the holding plate 8, and the housing main body 14a are fastened and fixed together in the axial direction by the bolts 7 inserted and screwed into these.
  • the motor output shaft 15 is formed in a stepped cylindrical shape, and has a large diameter portion 15a formed on the camshaft 2 side through a step portion at a substantially central position in the axial direction, and a small diameter formed on the cover member 4 side. Part 15b.
  • the large-diameter portion 15a has an iron core rotor 18 fixed to the outer periphery thereof, and an eccentric shaft portion 37 (described later) constituting a part of the speed reduction mechanism 13 is integrally coupled to a rear end surface in the axial direction.
  • a commutator 20 that is a commutator formed in an annular shape by a conductive material is fixed to the outer periphery of the small diameter portion 15b.
  • This commutator 20 is provided on the outer periphery of a non-conductive annular member press-fitted on the outer peripheral surface of the small-diameter portion 15b, and a coil 19 described later is drawn into each segment divided into the same number as the number of poles of the iron core rotor 18.
  • the coil wire ends are electrically connected.
  • the iron core rotor 18 is formed of a magnetic material having a plurality of magnetic poles, and the outer peripheral side is configured as a bobbin having a slot around which the coil wire of the coil 19 is wound.
  • the iron core rotor 18 is fixed while the inner peripheral portion thereof is positioned in the axial direction on the outer periphery of the stepped portion of the motor output shaft 15.
  • Each permanent magnet 16 is disposed with a predetermined gap in the circumferential direction and is formed in a cylindrical shape as a whole, and has a plurality of magnetic poles in the circumferential direction.
  • the power feeding plate 17 is basically formed of a synthetic resin material into a bottomed cylindrical shape, and has a cylindrical portion 17a on the outer peripheral side and an axially front end side of the cylindrical portion 17a.
  • Mainly consists of.
  • the cylindrical portion 17a is press-fitted and fixed to the outer peripheral surface of the cylindrical fixing portion 14e of the motor housing 14 via an annular support portion 17c, and has two slip rings 26 aligned in the axial direction on the outer periphery. , 27 are provided.
  • the slip rings 26 and 27 are each formed in an annular shape from a copper alloy material, are spaced apart from each other in the axial direction with a predetermined gap, and are provided with a plurality of unillustrated claws integrally formed on both side edges. It is fixed to the cylinder portion 17a through a mold. Further, the slip rings 26 and 27 are provided so that the formation positions thereof overlap the commutator 20 and a commutator brush 23 which will be in contact with the commutator 20 in the radial direction of the motor output shaft 15.
  • the bottom wall portion 17b is formed with a relatively large diameter working hole 17d formed in the center of FIGS. 1 and 5-7, and on the inner surface side on the camshaft 2 side, there are four rectangular copper tubes.
  • Each brush holder 23 is fixed by four rivets 32.
  • Each of the brush holders 23 is a set of two, and each set disposed adjacent to each other in the circumferential direction is opposed to each other from the radial direction, and each arcuate tip surface is provided inside the commutator 20.
  • a commutator brush 25 that is in contact with the outer peripheral surface is accommodated in a slidable manner along the radial direction.
  • Each of the commutator brush portions 25 is biased in the direction of the outer peripheral surface of the commutator 20 by the spring force of the coil spring 24.
  • each slip ring 26,27 and each set of two brush holders 23 are provided in the inside of the cylinder part 17a and the bottom wall part 17b.
  • the wiring boards 26a and 27a that are electrically connected through the pair of pigtail harnesses 26b and 27b are molded.
  • the annular support portion 17c has a substantially L-shaped cross section, and a disc-shaped inner peripheral portion 17e is disposed on the inner surface side of the bottom wall portion 17b.
  • the cylindrical outer peripheral part 17f integrally joined to the outer peripheral edge of the inner peripheral part 17a is fixed in a state of being exposed from the inner peripheral surface of the cylindrical part 17a.
  • the outer peripheral portion 17f is press-fitted and fixed to the outer peripheral surface of the cylindrical fixing portion 14e of the motor housing 14 from the axial direction.
  • the motor output shaft 15 and the eccentric shaft portion 37 are provided on the outer peripheral surface of the small diameter ball bearing 35 on the outer peripheral surface of the shaft portion 10 b of the cam bolt 10 and on the outer peripheral surface of the cylindrical portion 9 b of the driven member 9. It is rotatably supported by a needle bearing 36 disposed on the direction side portion.
  • An electric motor is provided between the outer peripheral surface of the large diameter portion 15a of the motor output shaft 15 and the inner peripheral surface of the extending portion formed on the inner periphery of the partition wall 14b of the housing main body 14a from the inside of the speed reduction mechanism 13.
  • a small-diameter oil seal 38 that prevents leakage of lubricating oil into the inside 12 is provided.
  • the cover member 4 is integrally formed of an aluminum alloy material in a deep dish shape, and has a flat outer wall portion 4 a serving as a bottom wall, and an outer peripheral edge of the outer wall portion 4 a.
  • the mounting flange 4b is integrally formed via the inclined peripheral wall 4c, and the connector holding portion 28 protrudes in the vertical direction from the upper end portion of the outer wall portion 4a.
  • cover member 4 is formed so that the entire outer diameter including the mounting flange 4b is larger than the outer diameter of the power feeding plate 17 so as to substantially cover the power feeding plate 17 and the entire front end portion of the housing body 14a. ing.
  • the mounting flange 4b has four boss portions 4d integrally projecting at substantially equal intervals in the circumferential direction. Each boss 4d is formed with a bolt insertion hole 4e through which four bolts 29 attached to a chain case 60 described later are inserted.
  • the mounting flange 4b is formed with an annular seal groove 4f on the rear end surface of the motor housing 17 side.
  • a sealing member 33 made of synthetic rubber that seals between the opposing surfaces of the chain case 60 is fitted and fixed in the sealing groove 4f.
  • the connector holding portion 28 is formed in a rectangular cross section along the vertical direction in the figure.
  • a holding hole 28a for holding the power feeding connector 34 is formed through the connector holding portion 28 in the vertical direction.
  • female screw constituent portions 28b, 28b having internal female screws are integrally provided on both side portions of the connector holding portion 28.
  • the holding hole 28a is formed in a substantially rectangular cross section, and the lower end opening is disposed above both the slip rings 26 and 27. That is, the holding hole 28a is formed at an upper position in the vertical direction with respect to the housing body 14a.
  • a blocking wall 28b that is opposed to the oil seal 46 in the axial direction is provided integrally with a part of the peripheral wall that forms the holding hole 28a.
  • the power feeding connector 34 is integrally formed of a synthetic resin material in a rectangular tube shape, and as shown in FIGS. 1 and 3, a rectangular tube-like lower end portion 34a is inserted into the holding hole 28a.
  • the power supply connector 34 has a terminal 35 exposed inside an elliptical cylindrical upper end 34b protruding upward from the holding hole 28a.
  • a pair of left and right shoulder portions 34 c and 34 c that abut on the upper surface of the connector holding portion 28 are integrally projected.
  • a pair of boss portions 34d and 34d that are in contact with the upper surfaces of the female screw constituting portions 28b and 28b are integrally provided on the left and right outer sides of the shoulder portions 34c and 34c. Both boss portions 34d and 34d are formed with through-holes for female screws through which two bolts 61 and 61 that are screwed into the respective female screws of the female screw constituent portions 28b and 28b are inserted.
  • the power supply connector 34 is fixed to the connector holding portion 28 by the respective bolts 61 and 61.
  • the power feeding connector 34 has a pair of holder holes 34e, 34e formed in the inner axial direction from the lower end surface of the lower end portion 34a. Both the holder holes 34e and 34e are separated and formed via a central partition wall 34f, and a pair of brush holders 36 and 37 are inserted and fixed to each of the holder holes 34e and 34e, and the axial length is the lower end opening of the lower end portion 34a. To the formation position of the protrusion 34c.
  • the brush holders 36 and 37 are each formed in a substantially square shape in cross section by a copper material, and the length in the axial direction is slightly longer than the length in the axial direction of the holder holes 34e and 34e. Thereby, each front-end
  • a plate-like retainer 38 made of an insulating material is disposed and fixed on the upper end portions of the brush holders 36 and 37 so as to straddle both.
  • both the brush holders 36 and 37 are arranged so as to be shifted from each other by a predetermined amount in the circumferential direction, and are arranged in an inclined manner along the radial direction in the center P direction of the cover member 4. Has been.
  • each of the power supply brushes 39 and 40 which will be described later, slidably held by the brush holders 36 and 37, is inclined along the radial direction toward the center P direction of the cover member 4 as shown in the figure.
  • the two tip portions 36b and 37b are arranged in a substantially V shape.
  • each of the brush holders 36 and 37 power supply brushes 39 and 40 having a substantially rectangular cross section are slidably provided. Between the rear end face of each of the power supply brushes 39, 40 and the retainer 38, a spring member 41 that biases each of the power supply brushes 39, 40 downward in the figure, that is, toward the slip rings 26, 27. 42 are mounted.
  • a power feeding mechanism is configured by the power feeding connector 34, the brush holders 36 and 37, and the power feeding brushes 39 and 40.
  • Each of the power supply brushes 39 and 40 is a carbon brush and is formed to be relatively long in the axial direction, and each of the front end surfaces 39a and 40a is applied to the outer surface of each slip ring 26 and 27 by the spring force of the spring members 41 and 42.
  • the motor housing 14 is elastically contacted from the radial direction. Further, one end portions of pigtail harnesses 43 and 44 inserted through the insides of the coil springs 41 and 42 are coupled to the rear end surfaces of the power supply brushes 39 and 40, respectively.
  • Each of the power supply brushes 39 and 40 is disposed at an upper position in the vertical direction of the motor housing 14 via the holding hole 28a.
  • the pigtail harnesses 43 and 44 are soldered to a wiring board (not shown) molded inside the power supply connector 34 through a pair of through holes provided in the retainer 38 on the other end side which is extended in a bent state. Are connected to each of the terminals 35.
  • seal ring 45 is held in a sandwiched state between the lower surface of the protrusion 34 c of the power feeding connector 34 and the upper surface of the connector holding portion 28.
  • cover member 4 is fixed through bolts 29 in which the mounting flange 4b is screwed to the female screw 60a of the chain case 60, and the outer peripheral surface of the annular flange 14f of the motor housing 14 and the inner peripheral surface of the mounting flange 4b.
  • An oil seal 46 as a seal member is interposed between the surface and the surface.
  • the oil seal 46 is a general one having a substantially U-shaped cross section, and the whole is basically formed of a rubber material.
  • the oil seal 46 has an inner peripheral portion 46a elastically contacting the outer peripheral surface of the annular protrusion 14f by a backup spring, while the outer peripheral portion has an L-shaped metal retainer 46b through an inner peripheral surface of the mounting flange 4b. It is press-fitted and fixed to.
  • the lubricating oil scattered by the rotational drive of the timing chain wound around the gear portion 1b of the timing sprocket 1 enters and adheres to the brushes 39, 40 and the slip rings 26, 27. Is supposed to suppress.
  • a control current is supplied to the power supply connector 34 from a control unit that controls the engine (not shown).
  • This control unit detects the engine operating state based on information from various sensors such as a crank angle sensor, an air flow meter, a throttle valve opening sensor, a water temperature sensor, an oil temperature sensor, and a cam angle sensor.
  • the control unit controls the ignition timing, the fuel injection amount, and the like, and controls the rotation of the electric motor 12 by a control current to the power supply connector 34.
  • the speed reduction mechanism 13 includes an eccentric shaft portion 37 that performs an eccentric rotational motion, a medium-diameter ball bearing 47 provided on the outer periphery of the eccentric shaft portion 37, and the medium-diameter ball bearing 47.
  • the roller 48 provided on the outer periphery of the inner tooth 5a and rotatably held in the inner teeth 5a of the inner tooth component 5, and the holding allowing the radial movement while holding the roller 48 in the rolling direction. It is mainly comprised from the container 49 and the driven member 9 integral with this holder
  • the eccentric shaft portion 37 is formed in a cylindrical shape integrally provided from the axial direction on the large diameter portion 15 a of the motor output shaft 15, and the rotation shaft center of the cam surface 37 a formed on the outer peripheral surface is the motor output shaft 15. It is slightly eccentric in the radial direction from the rotational axis.
  • the medium-diameter ball bearing 47 is disposed so as to substantially overlap at the radial position of the needle bearing 36, and a ball interposed between the inner ring, the outer ring and the both wheels, and a cage for holding the ball, , Is composed of.
  • the inner ring is press-fitted and fixed to the outer peripheral surface of the eccentric shaft portion 37, whereas the outer ring is in a free state without being fixed in the axial direction.
  • the outer ring has a minute end formed between the end surface on the electric motor 12 side in the axial direction and no part, and the other end surface in the axial direction is opposed to the rear surface of the cage 49 facing the outer ring. It is free through clearance.
  • the outer ring is in contact with the outer peripheral surface of the roller 48 so that the outer ring can roll, and an annular ring is formed between the outer peripheral surface and the inner surface of the roller holding portion 49 a of the retainer 49.
  • a clearance is formed, and the entire medium-diameter ball bearing 47 can be eccentrically moved in the radial direction along with the eccentric rotation of the eccentric shaft portion 37 through the clearance.
  • the retainer 49 is integrally provided on the outer peripheral portion of the fixed end portion 9a, and 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. Further, the retainer 49 includes a cylindrical roller retaining portion 49a extending in a direction substantially perpendicular to the axis from the outer end of the annular base portion extending in the radial direction toward the front end side of the outer peripheral portion of the fixed end portion 9a. Have.
  • the roller holding portion 49a extends in the direction of the partition wall 14b through an annular concave storage space whose tip is partitioned by the internal tooth component 5 and the partition wall 14b of the motor housing 14 and the like.
  • the roller holding portion 49a is formed with a plurality of substantially rectangular roller holding holes that hold the plurality of rollers 48 so as to roll freely at substantially equal intervals in the circumferential direction.
  • This roller holding hole is formed in a rectangular shape elongated in the front-rear direction with the tip end side closed, and the total number thereof (number of rollers 48) is smaller than the total number of teeth of the inner teeth 5a of the inner tooth component 5. It has become. As a result, a predetermined reduction ratio is obtained.
  • Each roller 48 is formed of an iron-based metal, and is fitted into the inner teeth 5 a of the inner tooth constituent portion 5 while moving in the radial direction along with the eccentric movement of the medium diameter ball bearing 47. Each roller 48 swings in the radial direction while being guided in the circumferential direction by both side edges of the roller holding hole 41 c of the cage 49.
  • the timing sprocket 1 rotates through the timing chain in accordance with the rotational drive of the crankshaft of the engine. This rotational force is transmitted to the motor housing 14 via the internal tooth component 5, and the motor housing 14 rotates synchronously.
  • the rotational force of the internal tooth component 5 is transmitted from each roller 48 to the camshaft 2 via the retainer 49 and the driven member 9. As a result, the cam of the camshaft 2 opens and closes the intake valve.
  • a control current from the control unit is energized to the coil 19 of the electric motor 12 through the power supply brushes 39 and 40, the slip rings 26 and 27, and the motor output shaft 15 rotates.
  • the rotational force of the motor output shaft 15 that is driven is reduced and transmitted to the camshaft 2 via the speed reduction mechanism 13.
  • the relative rotational phase of the camshaft 2 and the timing sprocket 1 is converted, and the opening / closing timing of the intake valve is controlled to be advanced or retarded.
  • the opening / closing timing of the intake valve is converted to the advance side or the retard side, and as a result, the fuel efficiency and output of the engine can be improved.
  • the power supply brushes 39 and 40 provided on the power supply connector 34 of the cover member 4 via the brush holders 36 and 37 are provided on the outer peripheral surface of the power supply plate 17.
  • the slip rings 26 and 27 are elastically contacted from the radial direction of the housing main body 14a. For this reason, compared with the case where it provides along an axial direction like a prior art, the axial length of the whole apparatus can be fully shortened. As a result, the internal combustion engine including the device can be reduced in size in the axial direction, and the ease of mounting in the engine room and the degree of layout are improved.
  • the slip rings 26 and 27 are fixed not to the front end face of the power supply plate 17 but to the outer peripheral face of the cylindrical portion 17a, and are arranged so as to overlap each rectifying brush 25 (brush holder 23) from the radial direction. Yes. From this point as well, the axial length of the entire apparatus can be shortened.
  • each rectifying brush 25 and each slip ring 26, 27 are electrically connected by using wiring boards 26a, 27a molded inside the power feeding plate 17, wiring is simplified. As a result, the manufacturing operation becomes easy.
  • the power feeding plate 17 is press-fitted and fixed from the axial direction to the cylindrical fixing portion 14e of the housing main body 14a using the cylindrical portion 17a (annular support portion 17c). For this reason, this fixing work is facilitated and, in particular, a strong fixed state can be obtained by press-fitting and fixing using the metal annular support portion 17c.
  • the power supply plate 17 is formed of only a synthetic resin material except for the annular support portion 17c without molding a metal core material or the like inside, and a relatively large working hole 17d is formed at the center. ing. As a result, the overall weight can be reduced.
  • the slip rings 26 and 27 are provided on the outer peripheral surface of the motor housing 14, that is, the outer peripheral surface of the cylindrical portion 17 a of the power feeding plate 17, the lengths of the slip rings 26 and 27 in the circumferential direction are provided. Becomes longer. Therefore, it is necessary to increase the axial length of the power supply brushes 39 and 40 in consideration of the increased amount of wear between the power supply brushes 39 and 40.
  • the power supply brushes 39 and 40 are provided at the upper positions in the vertical direction, so that they can be pressed against the slip rings 26 and 27 by their own weights.
  • each coil spring 41, 42 can be lowered, the spring load can be lowered. As a result, the sliding resistance can be reduced and the occurrence of wear can be sufficiently suppressed, so that it can be used for a long time.
  • the oil seal 46 is interposed between the outer peripheral surface of the annular protrusion 14f and the inner peripheral surface of the mounting flange 4b, so that the slip rings 26, 27 and the tip surfaces 39a, 40a of the power supply brushes 39, 40 are provided. It is arranged at a position one step higher than the sliding position. For this reason, wear powder generated during sliding between the slip rings 26 and 27 and the tip surfaces 39a and 40a of the power supply brushes 39 and 40 is less likely to flow in the direction of the oil seal 46. can do.
  • FIG. 9 shows the second embodiment.
  • a pair of second power supply brushes 50 and 51 are further provided on the lower side in the vertical direction. is there.
  • the second power supply brushes 50 and 51 are slid into a brush holder (not shown) inside a second power supply connector 53 provided through a holding hole at the lower end of the cover member 4 as in the first embodiment. It is provided so as to be movable, and is arranged at a position symmetrical to the upper first power supply brushes 39, 40.
  • the tip surfaces 50a and 51a are elastically contacted with the slip rings 26 and 27 by coil springs (not shown), and are spaced apart from each other by a predetermined distance in the circumferential direction.
  • the conductivity to the slip rings 26 and 27 is further improved. Since the other configuration is the same as that of the first embodiment, the same operation and effect can be obtained.
  • FIG. 10 shows a third embodiment, in which the cover member 4 is integrally formed of a synthetic resin material, and a pair of power supply brushes 39 and 40 that elastically contact with the slip rings 26 and 27, respectively, One is provided at each lower 180 ° symmetrical position.
  • one upper power supply brush 39 is provided on the power supply connector 34 provided at the upper end of the cover member 4 as in the first embodiment.
  • the lower power supply brush 40 is not a power supply connector, but is simply a press fit-fixed in a fixing hole 54 formed in the lower end portion of the cover member 4 along the radial direction. It is slidably held inside a cylindrical brush holder 55. The lower end opening of the fixing hole 54 is closed by a synthetic resin plug 57, and one end of the brush holder 55 is elastically contacted with the plug 57 to slip the power supply brush 40.
  • a coil spring 56 urging in the 27 direction is mounted.
  • the lower power supply brush 40 is connected to the terminal of the power supply connector 34 in the same manner as the upper power supply brush through a conductive plate molded inside the cover member 4 and a pigtail harness (not shown).
  • the cover member 4 is integrally formed of a synthetic resin material, the weight of the entire apparatus can be reduced.
  • FIG. 11 shows the fourth embodiment, and the basic configuration is the same as that of the first embodiment, except that the height of the annular protrusion 14f of the housing body 14a, that is, the size in the radial direction is further increased. At the same time, the inner diameter of the mounting flange 4b of the cover member 4 is made larger by the increased amount. Accordingly, the clearance C between the outer peripheral portion of the annular protrusion 14f and the blocking wall 28b can be further reduced while ensuring the arrangement of the oil seal 46.
  • the present invention is not limited to the configuration of each of the above-described embodiments.
  • the apparatus can be provided on the exhaust valve side.
  • the driving rotating body in addition to the timing sprocket, a timing pulley or the like can be used. There may be.
  • the cover member 4 can also be formed of a synthetic resin material in the first, second, and fourth embodiments, thereby reducing the weight of the device.
  • valve timing control device for an internal combustion engine based on the embodiment described above, for example, the following modes can be considered.
  • the electric motor includes a plurality of coils provided on a motor output shaft, a permanent magnet provided on an inner peripheral surface of the motor housing, and a plurality of coils connected to the slip ring. And a commutator brush whose tip is in sliding contact with the commutator, The slip ring is provided such that its formation position overlaps the commutator and the commutator brush in the radial direction of the motor output shaft.
  • the motor housing includes a cylindrical housing body provided with the permanent magnet, and a bottomed cylindrical holding member that holds the slip ring and the commutator brush.
  • the holding member is provided at a front end portion of the housing body.
  • the holding member has a cylindrical portion fixed to the housing body from the axial direction, and is integrally provided on the axial front end side of the cylindrical portion, and the commutator brush is provided on the inner peripheral side. And a rear end portion of the cylindrical portion is fixed to the housing body.
  • the housing main body is formed in a cylindrical shape, and the cylindrical portion of the holding member is press-fitted and fixed in the axial direction on the outer peripheral surface of the front end portion of the housing main body.
  • the permanent magnet is fixed to the inner peripheral surface of the housing body.
  • the power supply mechanism includes a connector connected to a power source, and the power supply brush provided integrally with the connector, A cover member that holds the connector of the power feeding mechanism is attached to the front end side of the holding member.
  • the housing main body has a cylindrical fixing portion having a small-diameter step in which the cylindrical portion of the holding member is press-fitted and fixed at a front end portion, and an axially inner end of the cylindrical fixing portion.
  • a large-diameter annular protrusion is integrally provided at the edge, and a seal member that seals between the motor housing and the cover member is provided on the outer periphery of the annular protrusion.
  • a blocking wall is provided on the inner periphery of the outer peripheral portion of the cover member so as to block communication between the power supply brush and the seal member interposed in a gap between the annular protrusion and the connector. It has been.
  • the contact surface of the power supply brush with the slip ring is disposed on the upper side in the vertical direction with respect to the rotational axis of the drive rotator.
  • two slip rings are arranged in parallel in the axial direction on the outer periphery of the motor housing, while two power supply brushes are provided corresponding to the slip rings, and the 2 At least one of the two power supply brushes is disposed on the upper side in the vertical direction with respect to the rotation shaft of the drive rotator.
  • both of the two power supply brushes are arranged on the upper side in the vertical direction with respect to the rotation axis of the drive rotating body.
  • the two power supply brushes are displaced from each other by a predetermined angle in the circumferential direction of the motor housing.
  • two slip rings are arranged in parallel in the axial direction on the outer periphery of the motor housing, while the power supply brushes are in contact with the one slip ring two by four in total.
  • the two power supply brushes are arranged on the upper side in the vertical direction with respect to the rotation shaft of the drive rotator.
  • the four power supply brushes are displaced from each other by a predetermined angle in the circumferential direction of the motor housing.
  • At least one of the two power supply brushes is disposed on the lower side in the vertical direction with respect to the rotational axis of the drive rotator.
  • the cover member is formed in a substantially circular shape, and a holding hole extending in the radial direction is formed through the upper side in the vertical direction of the outer peripheral portion. It is inserted into the hole from the radial direction and held together with the power supply brush.
  • Yet another preferred embodiment is a power supply device for an electric motor
  • a motor housing is integrally fixed to the drive rotator, and is provided on the outer periphery of the motor housing that rotates synchronously with the drive rotator.
  • a power feeding mechanism having a power feeding brush that contacts the slip ring from the outside in the radial direction of the motor housing.

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

Abstract

The present invention is equipped with an electric motor 12 that causes a camshaft to rotate relative to a timing sprocket, and two slip rings 26, 27 formed one in front and one in back on the outer circumferential surface of a tubular part 17a of power supply plate 17 affixed to the front-end part of a motor housing. A connector retaining part 28 is provided on the upper end of the outer circumferential part of a cover member 4 provided so as to cover the front end of the power supply plate, and a pair of power supply brushes 39 and 40, which contact the slip rings from the radial direction, are provided on the connector retaining part. Thus, by changing the arrangement of the power supply brushes in the radial direction it is possible to reduce the axial length of the valve timing control device.

Description

内燃機関のバルブタイミング制御装置及び電動モータの給電装置Valve timing control device for internal combustion engine and power supply device for electric motor
　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及び電動モータの給電装置に関する。 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, and a power supply device for an electric motor.
　内燃機関のバルブタイミング制御装置としては、以下の特許文献１に記載されているものが知られている。 As a valve timing control device for an internal combustion engine, a device described in Patent Document 1 below is known.
　この装置は、タイミングスプロケットのスプロケット本体の前端部に、電動モータの円筒状のモータハウジングがボルト固定されていると共に、該モータハウジングの前端部には、円盤状の給電プレートが固定され、この給電プレートは、前端面に整流子を介して電動モータのコイルに通電する一対のスリップリングが設けられている。 In this device, a cylindrical motor housing of an electric motor is bolted to the front end portion of the sprocket body of the timing sprocket, and a disk-shaped power feeding plate is fixed to the front end portion of the motor housing. The plate is provided with a pair of slip rings on the front end face for energizing the coil of the electric motor via a commutator.
　また、モータハウジングの前方位置には、前記給電プレートを覆う形で配設されたカバー部材が設けられている。このカバー部材の後端部には、前記給電プレートの各スリップリングにモータハウジングの軸方向から当接する一対の給電用ブラシが設けられている。 In addition, a cover member is provided at a front position of the motor housing so as to cover the power feeding plate. A pair of power supply brushes are provided at the rear end of the cover member so as to contact the slip rings of the power supply plate from the axial direction of the motor housing.
特開２０１５－１５１９８３号公報Japanese Patent Laid-Open No. 2015-151983
　前記カバー部材に設けられた一対の給電用ブラシは、前述のように、各スリップリングに対してモータハウジングの軸方向から当接するようになっている。このため、装置の軸方向の長さが必然的に長くなってしまう。 As described above, the pair of power supply brushes provided on the cover member come into contact with each slip ring from the axial direction of the motor housing. For this reason, the axial length of the apparatus is inevitably long.
　この結果、例えば直列型の内燃機関である場合には、機関全体の軸方向の長さが長くなってエンジンルーム内への搭載性の悪化やレイアウトの自由度が制約されるおそれがある。 As a result, for example, in the case of an in-line type internal combustion engine, the axial length of the whole engine becomes long, and there is a possibility that the mounting property in the engine room is deteriorated and the freedom of layout is restricted.
　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、装置の軸方向の長さを短尺化することのでき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 an object thereof is to provide a valve timing control device for an internal combustion engine capable of shortening the axial length of the device.
　本願発明は、モータハウジングの外周に形成されたスリップリングに当接する給電用ブラシを、前記モータハウジングの径方向から当接させたことを特徴としている。 The invention of the present application is characterized in that a power supply brush that abuts against a slip ring formed on the outer periphery of the motor housing is abutted from the radial direction of the motor housing.
　この発明によれば、装置の軸方向の長さを十分に短くすることができ、内燃機関のエンジンルーム内への搭載性とレイアウトの自由度が向上する。 According to the present invention, the length of the apparatus in the axial direction can be sufficiently shortened, and the ease of mounting the internal combustion engine in the engine room and the layout are improved.
本発明に係るバルブタイミング制御装置の第１実施形態を示す縦断面図である。It is a longitudinal section showing a 1st embodiment of a valve timing control device concerning the present invention. 本実施形態における主要な構成部材を示す分解斜視図である。It is a disassembled perspective view which shows the main structural members in this embodiment. 図１に示す本実施形態の要部拡大図である。It is a principal part enlarged view of this embodiment shown in FIG. 本実施形態に供されるタイミングスプロケットとモータハウジングを組み付けた状態を示す斜視図である。It is a perspective view which shows the state which assembled | attached the timing sprocket provided to this embodiment, and a motor housing. 本実施形態に供される給電プレートの正面図である。It is a front view of the electric power feeding plate provided to this embodiment. 同給電プレートの背面図である。It is a rear view of the same electric power feeding plate. 同給電プレートの側面図である。It is a side view of the electric power feeding plate. 本実施形態に供されるカバー部材を図２の矢印Ａ方向からみた正面図である。It is the front view which looked at the cover member provided to this embodiment from the arrow A direction of FIG. 本願発明の第２実施形態に供されるカバー部材を図２の矢印Ａ方向からみた正面図である。It is the front view which looked at the cover member provided to 2nd Embodiment of this invention from the arrow A direction of FIG. 本願発明の第３実施形態に供されるカバー部材を図２の矢印Ａ方向からみた正面図である。It is the front view which looked at the cover member provided to 3rd Embodiment of this invention from the arrow A direction of FIG. 本発明の第４実施形態の要部拡大断面図である。It is a principal part expanded sectional view of 4th Embodiment of this invention.
　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と電動モータの給電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直列４気筒の内燃機関の吸気弁側に適用したものを示している。 Hereinafter, embodiments of a valve timing control device for an internal combustion engine and a power feeding device for an electric motor 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 of an in-line four-cylinder internal combustion engine.
　前記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の回転駆動力がタイミングチェーンを介して伝達される駆動回転体であるタイミングスプロケット１と、シリンダヘッド０１上に軸受０２を介して回転自在に支持されていると共に、前記タイミングスプロケット１に相対回転自在に設けられたカムシャフト２と、前記タイミングスプロケット１とカムシャフト２との間に配置されて、機関運転状態に応じて両者１，２の相対回転位相を変更する位相変更機構３と、該位相変更機構３の前端に配置された固定部材であるカバー部材４と、を備えている。 As shown in FIG. 1 and FIG. 2, the valve timing control device is provided on a timing sprocket 1 which is a driving rotating body to which the rotational driving force of a crankshaft of an internal combustion engine is transmitted via a timing chain, and on a cylinder head 01. The camshaft 2 is rotatably supported via a bearing 02, and is disposed between the timing sprocket 1 and the camshaft 2, and is disposed between the timing sprocket 1 and the camshaft 2. The phase change mechanism 3 that changes the relative rotational phases of the two and 1 and the cover member 4 that is a fixed member disposed at the front end 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ており、外径が比較的小径状に形成されたスプロケット本体１ａと、該スプロケット本体１ａの外周に一体に設けられて、巻回された図外のタイミングチェーンを介してクランクシャフトからの回転力を受ける歯車部１ｂと、を備えている。 The timing sprocket 1 is formed integrally with an iron-based metal in an annular shape. The sprocket body 1a has a relatively small outer diameter and is integrally provided on the outer periphery of the sprocket body 1a. A gear portion 1b that receives the rotational force from the crankshaft via a rotated timing chain (not shown).
　また、前記スプロケット本体１ａの前端側には、内歯構成部５が一体に設けられている。この内歯構成部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。また、この内歯構成部５の軸方向の外端面には、後述する電動モータ１２のモータハウジング１４が前記各ボルト７を介して軸方向から結合されている。 Also, an internal tooth component 5 is integrally provided on the front end side of the sprocket body 1a. 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. Further, a motor housing 14 of an electric motor 12 described later is coupled to the outer end surface in the axial direction of the internal tooth component 5 from the axial direction via the bolts 7.
　前記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の軸方向の一端部２ａに固定された後述する従動回転体である従動部材９との間に、１つの大径ボールベアリング６が介装されており、この大径ボールベアリング６によって、タイミングスプロケット１が前記従動部材９(カムシャフト２)に相対回転自在に軸受けされている。 The timing sprocket 1 has a single large-diameter ball bearing 6 interposed between a sprocket body 1a and a driven member 9 which is a driven rotating body, which will be described later, fixed to one axial end portion 2a of the camshaft 2. By this large diameter ball bearing 6, the timing sprocket 1 is supported by the driven member 9 (cam shaft 2) so as to be relatively rotatable.
　さらに、前記スプロケット本体１ａの内歯構成部５と反対側の後端面には、保持プレート８が固定されている。この保持プレート８は、図１及び図２に示すように、金属板材によって円環状に形成され、外径が前記スプロケット本体１ａの外径とほぼ同一に設定されている。また、中央に有する中央孔８ａの内径が前記大径ボールベアリング６の外輪６ａの内径よりも小さく形成されて、内周部の内側面が前記外輪６ａの軸方向の他端面に微小隙間を介して軸方向から対峙している。 Furthermore, a holding plate 8 is fixed to the rear end surface of the sprocket body 1a on the side opposite to the internal teeth constituting portion 5. As shown in FIGS. 1 and 2, the holding plate 8 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 1a. In addition, the inner diameter of the central hole 8a at the center is formed smaller than the inner diameter of the outer ring 6a of the large-diameter ball bearing 6, and the inner side surface of the inner peripheral portion has a small gap on the other end surface in the axial direction of the outer ring 6a. Facing each other in the axial direction.
　前記保持プレート８の中央孔８ａの内周縁所定位置には、中心軸方向に向かって突出したほぼ逆台形状のストッパ凸部８ｂが一体に設けられている。 A substantially inverted trapezoidal stopper convex portion 8b protruding in the direction of the central axis is integrally provided at a predetermined position on the inner peripheral edge of the central hole 8a of the holding plate 8.
　また、前記内歯構成部５を含むスプロケット本体１ａ及び保持プレート８の各外周部には、８本のボルト７が挿通する８つのボルト挿通孔１ｃが周方向のほぼ等間隔位置に貫通形成されている。 In addition, eight bolt insertion holes 1c through which eight bolts 7 are inserted are formed in the outer peripheral portions of the sprocket main body 1a including the internal gear component 5 and the holding plate 8 at substantially equal intervals in the circumferential direction. ing.
　カムシャフト２は、外周に図外の吸気弁を開作動させる一気筒当たり２つの駆動カムを有している。また、このカムシャフト２は、軸方向の一端部２ａと該一端部２ａ外周に一体に設けられたフランジ部２ｂを介して従動部材９がカムボルト１０によって軸方向から共締め固定されている。フランジ部２ｂには、ストッパ凸部８ｃが嵌入される円弧状のストッパ溝１１が形成されている。このストッパ溝１１の周方向の対向面に、ストッパ凸部８ｃの両側面が適宜当接して、タイミングスプロケット１に対するカムシャフト２の相対回転位置、つまり最大進角位置と最大遅角位置を機械的に規制するようになっている。 The camshaft 2 has two drive cams per cylinder for opening an intake valve (not shown) on the outer periphery. The camshaft 2 has a driven member 9 fixed together by a cam bolt 10 from the axial direction via an axial end portion 2a and a flange portion 2b integrally provided on the outer periphery of the end portion 2a. An arcuate stopper groove 11 into which the stopper convex portion 8c is inserted is formed in the flange portion 2b. Both side surfaces of the stopper projection 8c are in contact with the circumferential surface of the stopper groove 11 as appropriate, and the relative rotational position of the camshaft 2 with respect to the timing sprocket 1, that is, the maximum advance angle position and the maximum delay angle position are mechanically determined. It has come to regulate.
　従動部材９は、鉄系金属によって一体に形成され、図１及び図２に示すように、後端側(カムシャフト２側)に形成された円板状の固定端部９ａと、該固定端部９ａの内周前端面から軸方向へ突出した円筒部９ｂと、から主として構成されている。 The driven member 9 is integrally formed of iron-based metal, and as shown in FIGS. 1 and 2, a disk-like fixed end portion 9a formed on the rear end side (camshaft 2 side), and the fixed end It is mainly composed of a cylindrical portion 9b protruding in the axial direction from the inner peripheral front end face of the portion 9a.
　固定端部９ａは、外側面がカムシャフト２の一端部２ａの前端面側に対向配置され、この外側面のほぼ中央位置に前記カムシャフト２の一端部２ａが軸方向から嵌合する嵌合溝９ｄが形成されている。 The fixed end portion 9a has an outer surface opposed to the front end surface side of the one end portion 2a of the camshaft 2, and the end portion 2a of the camshaft 2 is fitted from the axial direction at a substantially central position of the outer surface. A groove 9d is formed.
　円筒部９ｂは、図１に示すように、固定端部９ａを含む内部軸心方向に前記カムボルト１０の軸部１０ｂが挿通されるボルト挿通孔９ｃを有し、外周側には後述する小径ボールベアリング３５とニードルベアリング３６が軸方向に並設されている。 As shown in FIG. 1, the cylindrical portion 9b has a bolt insertion hole 9c through which the shaft portion 10b of the cam bolt 10 is inserted in the inner axial direction including the fixed end portion 9a. A bearing 35 and a needle bearing 36 are juxtaposed in the axial direction.
　カムボルト１０は、図１に示すように、頭部１０ａの軸方向端面が小径ボールベアリング３５の内輪を軸方向から支持していると共に、軸部１０ｂの外周に前記カムシャフト２の内部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 face of the head 10a supporting the inner ring of the small-diameter ball bearing 35 from the axial direction, and is formed inside the camshaft 2 on the outer periphery of the shaft portion 10b. A male screw 10c that is screwed onto the female screw 2c is formed.
　位相変更機構３は、従動部材９の円筒部９ｂの前端側に配置された電動モータ１２と、該電動モータ１２の回転速度を減速してカムシャフト２に伝達する減速機構１３と、から主として構成されている。 The phase changing mechanism 3 is mainly composed of an electric motor 12 disposed on the front end side of the cylindrical portion 9b of the driven member 9, and a speed reducing mechanism 13 that reduces the rotational speed of the electric motor 12 and transmits it to the camshaft 2. Has been.
　電動モータ１２は、図１に示すように、ブラシ付きのＤＣモータであって、タイミングスプロケット１と一体に回転するヨークである前記モータハウジング１４と、該モータハウジング１４の円筒状のハウジング本体１４ａの内部に回転自在に設けられたモータ出力軸１５と、ハウジング本体１４ａの内周面に固着されたそれぞれ円弧状の６つの永久磁石１６と、ハウジング本体１４ａの前端部であるカバー部材４側に固定された保持部材である給電プレート１７と、を備えている。 As shown in FIG. 1, the electric motor 12 is a brushed DC motor, and includes a motor housing 14 that is a yoke that rotates integrally with the timing sprocket 1, and a cylindrical housing body 14 a of the motor housing 14. Fixed to the motor output shaft 15 provided rotatably inside, six arc-shaped permanent magnets 16 fixed to the inner peripheral surface of the housing body 14a, and the cover member 4 side which is the front end of the housing body 14a. And a power feeding plate 17 as a holding member.
　モータハウジング１４のハウジング本体１４ａは、図１及び図２に示すように、鉄系金属材によって有底円筒状に形成され、外径が前記スプロケット本体１ａの外径と同じく比較的小径に形成されていると共に、後端側に円板状の仕切壁１４ｂが一体に形成されている。 As shown in FIGS. 1 and 2, the housing main body 14a of the motor housing 14 is formed into a bottomed cylindrical shape with an iron-based metal material, and has an outer diameter that is relatively small like the outer diameter of the sprocket main body 1a. In addition, a disc-shaped partition wall 14b is integrally formed on the rear end side.
　また、ハウジング本体１４ａは、カバー部材４側の前端部に段差小径状の筒状固定部１４ｅが形成されていると共に、該筒状固定部１４ｅの後端側外周に大径な環状突部１４ｆが一体に形成されている。 The housing main body 14a has a cylindrical fixing portion 14e having a small stepped diameter formed at the front end portion on the cover member 4 side, and a large-diameter annular protrusion 14f on the outer periphery of the rear end side of the cylindrical fixing portion 14e. Are integrally formed.
　仕切壁１４ｂは、ほぼ中央に有する円筒状の延出部の内周に、モータ出力軸１５及び偏心軸部３７が挿通される大径な軸挿通孔１４ｃが形成されている。また、仕切壁１４ｂの外周部には、各ボルト挿通孔１ｃ、８ｃと対応した位置に各ボルト７の先端部が螺着する６つの雌ねじ孔１４ｄが周方向の等間隔位置に形成されている。これらに挿通、螺着した各ボルト７によってタイミングスプロケット１(内歯構成部５)と保持プレート８及びハウジング本体１４ａが軸方向から共締め固定されている。 The partition wall 14b is formed with a large-diameter shaft insertion hole 14c through which the motor output shaft 15 and the eccentric shaft portion 37 are inserted, on the inner periphery of a cylindrical extension portion at substantially the center. Further, on the outer peripheral portion of the partition wall 14b, six female screw holes 14d into which the tip end portions of the respective bolts 7 are screwed at positions corresponding to the respective bolt insertion holes 1c and 8c are formed at equally spaced positions in the circumferential direction. . The timing sprocket 1 (internal tooth component 5), the holding plate 8, and the housing main body 14a are fastened and fixed together in the axial direction by the bolts 7 inserted and screwed into these.
　モータ出力軸１５は、段差円筒状に形成されており、軸方向のほぼ中央位置の段差部を介してカムシャフト２側に形成された大径部１５ａと、カバー部材４側に形成された小径部１５ｂと、から構成されている。大径部１５ａは、外周に鉄心ロータ１８が固定されていると共に、軸方向の後端面に減速機構１３の一部を構成する後述の偏心軸部３７が一体に結合されている。一方、小径部１５ｂの外周には、導電材によって円環状に形成された整流子であるコミュテータ２０が固定されている。 The motor output shaft 15 is formed in a stepped cylindrical shape, and has a large diameter portion 15a formed on the camshaft 2 side through a step portion at a substantially central position in the axial direction, and a small diameter formed on the cover member 4 side. Part 15b. The large-diameter portion 15a has an iron core rotor 18 fixed to the outer periphery thereof, and an eccentric shaft portion 37 (described later) constituting a part of the speed reduction mechanism 13 is integrally coupled to a rear end surface in the axial direction. On the other hand, a commutator 20 that is a commutator formed in an annular shape by a conductive material is fixed to the outer periphery of the small diameter portion 15b.
　このコミュテータ２０は、小径部１５ｂの外周面に圧入された非導電性の円環部材の外周に設けられ、鉄心ロータ１８の極数と同数に分割された各セグメントに後述のコイル１９の引き出されたコイル線の端末が電気的に接続されている。 This commutator 20 is provided on the outer periphery of a non-conductive annular member press-fitted on the outer peripheral surface of the small-diameter portion 15b, and a coil 19 described later is drawn into each segment divided into the same number as the number of poles of the iron core rotor 18. The coil wire ends are electrically connected.
　鉄心ロータ１８は、複数の磁極を持つ磁性材によって形成され、外周側がコイル１９のコイル線を巻回させるスロットを有するボビンとして構成されている。この鉄心ロータ１８は、内周部が前記モータ出力軸１５の段差部外周に軸方向へ位置決めされつつ固定されている。 The iron core rotor 18 is formed of a magnetic material having a plurality of magnetic poles, and the outer peripheral side is configured as a bobbin having a slot around which the coil wire of the coil 19 is wound. The iron core rotor 18 is fixed while the inner peripheral portion thereof is positioned in the axial direction on the outer periphery of the stepped portion of the motor output shaft 15.
　各永久磁石１６は、円周方向に所定隙間をもって配設されて全体が円筒状に形成されて、円周方向に複数の磁極を有している。 Each permanent magnet 16 is disposed with a predetermined gap in the circumferential direction and is formed in a cylindrical shape as a whole, and has a plurality of magnetic poles in the circumferential direction.
　給電プレート１７は、図１～図４に示すように、基本的に全体が合成樹脂材によって有底円筒状に形成され、外周側の筒部１７ａと、該筒部１７ａの軸方向前端側に一体に有する底壁部１７ｂと、筒部１７ａと底壁部１７ｂとの連結箇所の内側にモールド固定されて、鉄系金属材を横断面ほぼコ字形状に折曲された環状支持部１７ｃと、から主として構成されている。 As shown in FIGS. 1 to 4, the power feeding plate 17 is basically formed of a synthetic resin material into a bottomed cylindrical shape, and has a cylindrical portion 17a on the outer peripheral side and an axially front end side of the cylindrical portion 17a. A bottom wall portion 17b integrally formed, and an annular support portion 17c which is molded and fixed inside a connecting portion between the cylindrical portion 17a and the bottom wall portion 17b, and a ferrous metal material is bent into a substantially U-shaped cross section. , Mainly consists of.
　筒部１７ａは、後端部が前記モータハウジング１４の筒状固定部１４ｅの外周面に環状支持部１７ｃを介して圧入固定されていると共に、外周には軸方向に並んだ２つのスリップリング２６，２７が設けられている。 The cylindrical portion 17a is press-fitted and fixed to the outer peripheral surface of the cylindrical fixing portion 14e of the motor housing 14 via an annular support portion 17c, and has two slip rings 26 aligned in the axial direction on the outer periphery. , 27 are provided.
　この両スリップリング２６，２７は、それぞれ銅合金材によって円環状に形成されて、所定隙間をもって互いに軸方向に離間していると共に、それぞれの両側縁に一体に設けられた図外の複数の爪を介して筒部１７ａにモールド固定されている。また、スリップリング２６，２７は、その形成位置が前記コミュテータ２０と該コミュテータ２０に当接する後述の整流子ブラシ２３に対してモータ出力軸１５の径方向でオーバーラップして設けられている。 The slip rings 26 and 27 are each formed in an annular shape from a copper alloy material, are spaced apart from each other in the axial direction with a predetermined gap, and are provided with a plurality of unillustrated claws integrally formed on both side edges. It is fixed to the cylinder portion 17a through a mold. Further, the slip rings 26 and 27 are provided so that the formation positions thereof overlap the commutator 20 and a commutator brush 23 which will be in contact with the commutator 20 in the radial direction of the motor output shaft 15.
　底壁部１７ｂは、図１及び図５～図７中央に比較的大径な作業用孔１７ｄが貫通形成されていると共に、カムシャフト２側の内面側には銅製の角筒状の４つのブラシホルダ２３がそれぞれ４つのリベット３２によって固定されている。 The bottom wall portion 17b is formed with a relatively large diameter working hole 17d formed in the center of FIGS. 1 and 5-7, and on the inner surface side on the camshaft 2 side, there are four rectangular copper tubes. Each brush holder 23 is fixed by four rivets 32.
　この各ブラシホルダ２３は、２つで一組になっており、円周方向で近接配置された各組が径方向から対向配置されている共に、内部には円弧状の各先端面がコミュテータ２０の外周面に当接する整流子ブラシ２５が径方向に沿って摺動自在に収容配置されている。 Each of the brush holders 23 is a set of two, and each set disposed adjacent to each other in the circumferential direction is opposed to each other from the radial direction, and each arcuate tip surface is provided inside the commutator 20. A commutator brush 25 that is in contact with the outer peripheral surface is accommodated in a slidable manner along the radial direction.
　この各整流子ブラシ部２５は、それぞれコイルスプリング２４のばね力で各先端面が前記コミュテータ２０の外周面方向の付勢されている。 Each of the commutator brush portions 25 is biased in the direction of the outer peripheral surface of the commutator 20 by the spring force of the coil spring 24.
　また、筒部１７ａと底壁部１７ｂの内部には、図１及び図５に示すように、各スリップリング２６，２７と各組の２つのブラシホルダ２３（２つの整流子ブラシ２５）とを、各一対のピグテールハーネス２６ｂ、２７ｂを介して電気的に導通させる配線板２６ａ、２７ａがモールドされている。 Moreover, as shown in FIG.1 and FIG.5, each slip ring 26,27 and each set of two brush holders 23 (two commutator brushes 25) are provided in the inside of the cylinder part 17a and the bottom wall part 17b. The wiring boards 26a and 27a that are electrically connected through the pair of pigtail harnesses 26b and 27b are molded.
　環状支持部１７ｃは、横断面ほぼＬ字形状に形成されて、円盤状の内周部１７ｅが底壁部１７ｂの内面側に配置されている。一方、該内周部１７ａの外周縁に一体に結合された円筒状の外周部１７ｆは、筒部１７ａの内周面から露出した状態で固定されている。この外周部１７ｆが、モータハウジング１４の筒状固定部１４ｅの外周面に軸方向から圧入固定されている。 The annular support portion 17c has a substantially L-shaped cross section, and a disc-shaped inner peripheral portion 17e is disposed on the inner surface side of the bottom wall portion 17b. On the other hand, the cylindrical outer peripheral part 17f integrally joined to the outer peripheral edge of the inner peripheral part 17a is fixed in a state of being exposed from the inner peripheral surface of the cylindrical part 17a. The outer peripheral portion 17f is press-fitted and fixed to the outer peripheral surface of the cylindrical fixing portion 14e of the motor housing 14 from the axial direction.
　モータ出力軸１５と偏心軸部３７は、カムボルト１０の軸部１０ｂの外周面に設けられた小径ボールベアリング３５と、従動部材９の円筒部９ｂの外周面に設けられて小径ボールベアリング３５の軸方向側部に配置されたニードルベアリング３６とによって回転自在に支持されている。 The motor output shaft 15 and the eccentric shaft portion 37 are provided on the outer peripheral surface of the small diameter ball bearing 35 on the outer peripheral surface of the shaft portion 10 b of the cam bolt 10 and on the outer peripheral surface of the cylindrical portion 9 b of the driven member 9. It is rotatably supported by a needle bearing 36 disposed on the direction side portion.
　また、モータ出力軸１５の大径部１５ａの外周面とハウジング本体１４ａの仕切壁１４ｂの内周に形成された延出部の内周面との間には、減速機構１３の内部から電動モータ１２内への潤滑油のリークを阻止する小径なオイルシール３８が設けられている。 An electric motor is provided between the outer peripheral surface of the large diameter portion 15a of the motor output shaft 15 and the inner peripheral surface of the extending portion formed on the inner periphery of the partition wall 14b of the housing main body 14a from the inside of the speed reduction mechanism 13. A small-diameter oil seal 38 that prevents leakage of lubricating oil into the inside 12 is provided.
　カバー部材４は、図１及び図２、図８に示すように、アルミニウム合金材によって深皿状一体に形成されて、底壁となる平坦状の外壁部４ａと、該外壁部４ａの外周縁に傾斜状の周壁４ｃを介して一体に形成された取付フランジ４ｂと、外壁部４ａの上端部から鉛直方向へ突出したコネクタ保持部２８と、から主として構成されている。 As shown in FIGS. 1, 2, and 8, the cover member 4 is integrally formed of an aluminum alloy material in a deep dish shape, and has a flat outer wall portion 4 a serving as a bottom wall, and an outer peripheral edge of the outer wall portion 4 a. The mounting flange 4b is integrally formed via the inclined peripheral wall 4c, and the connector holding portion 28 protrudes in the vertical direction from the upper end portion of the outer wall portion 4a.
　また、このカバー部材４は、取付フランジ４ｂを含めた全体の外径が給電プレート１７の外径より大きく形成されて、給電プレート１７とハウジング本体１４ａの前端部全体をほぼ覆うように近接配置されている。 Further, the cover member 4 is formed so that the entire outer diameter including the mounting flange 4b is larger than the outer diameter of the power feeding plate 17 so as to substantially cover the power feeding plate 17 and the entire front end portion of the housing body 14a. ing.
　取付フランジ４ｂは、円周方向ほぼ等間隔位置に４つのボス部４ｄが一体に突設されている。この各ボス部４ｄには、後述するチェーンケース６０に取り付けられる４本のボルト２９が挿通するボルト挿通孔４ｅが貫通形成されている。また、取付フランジ４ｂは、モータハウジング１７側の後端面に円環状のシール溝４ｆが形成されている。このシール溝４ｆには、チェーンケース６０の対向面との間をシールする合成ゴムからなるシール部材３３が嵌着固定されている。 The mounting flange 4b has four boss portions 4d integrally projecting at substantially equal intervals in the circumferential direction. Each boss 4d is formed with a bolt insertion hole 4e through which four bolts 29 attached to a chain case 60 described later are inserted. The mounting flange 4b is formed with an annular seal groove 4f on the rear end surface of the motor housing 17 side. A sealing member 33 made of synthetic rubber that seals between the opposing surfaces of the chain case 60 is fitted and fixed in the sealing groove 4f.
　コネクタ保持部２８は、図１～図３に示すように、図中上下方向に沿った横断面矩形状に形成されている。また、コネクタ保持部２８の内部軸方向には、給電用コネクタ３４が保持される保持孔２８ａが上下方向に沿って貫通形成されている。コネクタ保持部２８の両側部には、内部に図外の雌ねじが形成された雌ねじ構成部２８ｂ、２８ｂが一体に設けられている。 As shown in FIGS. 1 to 3, the connector holding portion 28 is formed in a rectangular cross section along the vertical direction in the figure. A holding hole 28a for holding the power feeding connector 34 is formed through the connector holding portion 28 in the vertical direction. On both side portions of the connector holding portion 28, female screw constituent portions 28b, 28b having internal female screws (not shown) are integrally provided.
　保持孔２８ａは、横断面ほぼ矩形状に形成されて、下端開口が前記両スリップリング２６，２７の上方に配置されている。つまり、この保持孔２８ａはハウジング本体１４ａに対して鉛直方向の上方位置に形成されている。また、保持孔２８ａを構成する周壁の一部に、オイルシール４６と軸方向から対峙する遮断壁２８ｂが一体に設けられている。 The holding hole 28a is formed in a substantially rectangular cross section, and the lower end opening is disposed above both the slip rings 26 and 27. That is, the holding hole 28a is formed at an upper position in the vertical direction with respect to the housing body 14a. In addition, a blocking wall 28b that is opposed to the oil seal 46 in the axial direction is provided integrally with a part of the peripheral wall that forms the holding hole 28a.
　給電用コネクタ３４は、合成樹脂材によって角筒状一体に形成され、図１、図３に示すように、角筒状の下端部３４ａが前記保持孔２８ａ内に挿入されている。また、この給電用コネクタ３４は、保持孔２８ａから上方へ突出した楕円筒状の上端部３４ｂの内部に端子３５が露出している。給電用コネクタ３４の下端部３４ａと上端部３４ｂとの間の外周には、コネクタ保持部２８の上面に当接する左右に伸びた一対の肩部３４ｃ、３４ｃが一体に突設されている。この両肩部３４ｃ、３４ｃの左右外側には、雌ねじ構成部２８ｂ、２８ｂの上面に当接する一対のボス部３４ｄ、３４ｄが一体に設けられている。この両ボス部３４ｄ、３４ｄには、雌ねじ構成部２８ｂ、２８ｂの各雌ねじにそれぞれ螺着する２つのボルト６１、６１が挿通する雌ねじ挿通孔が貫通形成されている。各ボルト６１、６１によって給電用コネクタ３４がコネクタ保持部２８に固定されるようになっている。 The power feeding connector 34 is integrally formed of a synthetic resin material in a rectangular tube shape, and as shown in FIGS. 1 and 3, a rectangular tube-like lower end portion 34a is inserted into the holding hole 28a. In addition, the power supply connector 34 has a terminal 35 exposed inside an elliptical cylindrical upper end 34b protruding upward from the holding hole 28a. On the outer periphery between the lower end 34 a and the upper end 34 b of the power supply connector 34, a pair of left and right shoulder portions 34 c and 34 c that abut on the upper surface of the connector holding portion 28 are integrally projected. A pair of boss portions 34d and 34d that are in contact with the upper surfaces of the female screw constituting portions 28b and 28b are integrally provided on the left and right outer sides of the shoulder portions 34c and 34c. Both boss portions 34d and 34d are formed with through-holes for female screws through which two bolts 61 and 61 that are screwed into the respective female screws of the female screw constituent portions 28b and 28b are inserted. The power supply connector 34 is fixed to the connector holding portion 28 by the respective bolts 61 and 61.
　また、給電用コネクタ３４は、下端部３４ａの下端面から内部軸方向に一対のホルダ孔３４ｅ、３４ｅが形成されている。この両ホルダ孔３４ｅ、３４ｅは、中央隔壁３４ｆを介して分離形成されて、それぞれに一対のブラシホルダ３６、３７が挿通固定されていると共に、軸方向の長さが前記下端部３４ａの下端開口から前記突起部３４ｃの形成位置まで延びている。 Further, the power feeding connector 34 has a pair of holder holes 34e, 34e formed in the inner axial direction from the lower end surface of the lower end portion 34a. Both the holder holes 34e and 34e are separated and formed via a central partition wall 34f, and a pair of brush holders 36 and 37 are inserted and fixed to each of the holder holes 34e and 34e, and the axial length is the lower end opening of the lower end portion 34a. To the formation position of the protrusion 34c.
　各ブラシホルダ３６、３７は、銅材によってそれぞれ横断面ほぼ四角形状に形成され、軸方向の長さが前記各ホルダ孔３４ｅ、３４ｅの軸方向の長さよりも僅かに長く形成されている。これによって、各先端部３６ａ、３７ａが、各ホルダ孔３４ｅ、３４ｅの先端開口から僅かに突出している。また、各ブラシホルダ３６，３７の上端部には、絶縁材からなるプレート状のリテーナ３８が両者に跨って配置固定されている。 The brush holders 36 and 37 are each formed in a substantially square shape in cross section by a copper material, and the length in the axial direction is slightly longer than the length in the axial direction of the holder holes 34e and 34e. Thereby, each front-end | tip part 36a, 37a protrudes slightly from the front-end | tip opening of each holder hole 34e, 34e. A plate-like retainer 38 made of an insulating material is disposed and fixed on the upper end portions of the brush holders 36 and 37 so as to straddle both.
　この両方のブラシホルダ３６，３７は、図８に示すように、互いに円周方向に所定量だけずれて配置されていると共に、カバー部材４の中心Ｐ方向へ径方向に沿って傾斜状に配置されている。 As shown in FIG. 8, both the brush holders 36 and 37 are arranged so as to be shifted from each other by a predetermined amount in the circumferential direction, and are arranged in an inclined manner along the radial direction in the center P direction of the cover member 4. Has been.
　このため、各ブラシホルダ３６、３７に摺動自在に保持される後述する各給電用ブラシ３９，４０は、図示のように、カバー部材４の中心Ｐ方向に向かって径方向に沿って傾斜所に配置されて両先端部３６ｂ、３７ｂがほぼＶ字形状に交差するようになっている。 Therefore, each of the power supply brushes 39 and 40, which will be described later, slidably held by the brush holders 36 and 37, is inclined along the radial direction toward the center P direction of the cover member 4 as shown in the figure. The two tip portions 36b and 37b are arranged in a substantially V shape.
　各ブラシホルダ３６，３７の内部には、横断面ほぼ四角形状の給電用ブラシ３９，４０がそれぞれ摺動自在に設けられている。この各給電用ブラシ３９、４０の後端面と前記リテーナ３８との間には、前記各給電用ブラシ３９、４０を図中下方向、つまり各スリップリング２６，２７方向へ付勢するばね部材４１，４２が弾装されている。 In each of the brush holders 36 and 37, power supply brushes 39 and 40 having a substantially rectangular cross section are slidably provided. Between the rear end face of each of the power supply brushes 39, 40 and the retainer 38, a spring member 41 that biases each of the power supply brushes 39, 40 downward in the figure, that is, toward the slip rings 26, 27. 42 are mounted.
　なお、給電用コネクタ３４や各ブラシホルダ３６，３７、各給電用ブラシ３９、４０によって給電機構が構成されている。 Note that a power feeding mechanism is configured by the power feeding connector 34, the brush holders 36 and 37, and the power feeding brushes 39 and 40.
　各給電用ブラシ３９、４０は、カーボンブラシであって、軸方向に比較的長く形成されて、各先端面３９ａ、４０ａがばね部材４１、４２のばね力によって各スリップリング２６，２７の外面にモータハウジング１４の径方向から弾接している。また、各給電用ブラシ３９，４０の各後端面には、各コイルばね４１、４２の内部を挿通したピグテールハーネス４３，４４の一端部が結合されている。なお、各給電用ブラシ３９，４０は、保持孔２８ａを介してモータハウジング１４の鉛直方向の上方位置に配置されている。 Each of the power supply brushes 39 and 40 is a carbon brush and is formed to be relatively long in the axial direction, and each of the front end surfaces 39a and 40a is applied to the outer surface of each slip ring 26 and 27 by the spring force of the spring members 41 and 42. The motor housing 14 is elastically contacted from the radial direction. Further, one end portions of pigtail harnesses 43 and 44 inserted through the insides of the coil springs 41 and 42 are coupled to the rear end surfaces of the power supply brushes 39 and 40, respectively. Each of the power supply brushes 39 and 40 is disposed at an upper position in the vertical direction of the motor housing 14 via the holding hole 28a.
　ピグテールハーネス４３，４４は、撓んだ状態で長く延ばされた他端部側がリテーナ３８に有する一対の貫通孔を通って給電用コネクタ３４の内部にモールドされた図外の配線板に半田付けなどによって結合されて、前記各端子３５に接続されるようになっている。 The pigtail harnesses 43 and 44 are soldered to a wiring board (not shown) molded inside the power supply connector 34 through a pair of through holes provided in the retainer 38 on the other end side which is extended in a bent state. Are connected to each of the terminals 35.
　また、給電用コネクタ３４の突起部３４ｃの下面とコネクタ保持部２８の上面との間には、シールリング４５が挟持状態に保持されている。 Further, the seal ring 45 is held in a sandwiched state between the lower surface of the protrusion 34 c of the power feeding connector 34 and the upper surface of the connector holding portion 28.
　さらに、カバー部材４は、取付フランジ４ｂがチェーンケース６０の雌ねじ６０ａに螺着したボルト２９を介して固定されていると共に、取付フランジ４ｂの内周面とモータハウジング１４の環状突部１４ｆの外周面との間にシール部材であるオイルシール４６が介装されている。 Further, the cover member 4 is fixed through bolts 29 in which the mounting flange 4b is screwed to the female screw 60a of the chain case 60, and the outer peripheral surface of the annular flange 14f of the motor housing 14 and the inner peripheral surface of the mounting flange 4b. An oil seal 46 as a seal member is interposed between the surface and the surface.
　このオイルシール４６は、横断面ほぼ横Ｕ字形状の一般的なものであって、全体が基本的にゴム材によって形成されている。また、オイルシール４６は、内周部４６ａがバックアップスプリングによって環状突部１４ｆの外周面に弾接している一方、外周部がＬ字形状の金属リテーナ４６ｂを介して前記取付フランジ４ｂの内周面に圧入固定されている。このオイルシール４６は、タイミングスプロケット１の歯車部１ｂに巻回されたタイミングチェーンの回転駆動などによって飛散した潤滑油が各ブラシ３９，４０や各スリップリング２６，２７方向へ侵入して付着するのを抑制するようになっている。 The oil seal 46 is a general one having a substantially U-shaped cross section, and the whole is basically formed of a rubber material. The oil seal 46 has an inner peripheral portion 46a elastically contacting the outer peripheral surface of the annular protrusion 14f by a backup spring, while the outer peripheral portion has an L-shaped metal retainer 46b through an inner peripheral surface of the mounting flange 4b. It is press-fitted and fixed to. On the oil seal 46, the lubricating oil scattered by the rotational drive of the timing chain wound around the gear portion 1b of the timing sprocket 1 enters and adheres to the brushes 39, 40 and the slip rings 26, 27. Is supposed to suppress.
　給電用コネクタ３４には、図外の機関を制御するコントロールユニットから制御電流が供給されるようになっている。 A control current is supplied to the power supply connector 34 from a control unit that controls the engine (not shown).
　このコントロールユニットは、クランク角センサやエアーフローメータ、スロットルバルブ開度センサ、水温センサ、油温センサ、カム角度センサなど各種のセンサ類からの情報に基づいて機関運転状態を検出している。また、コントロールユニットは、点火時期や燃料噴射量などを制御するようになっていると共に、給電用コネクタ３４への制御電流によって電動モータ１２の回転を制御するようになっている。 This control unit detects the engine operating state based on information from various sensors such as a crank angle sensor, an air flow meter, a throttle valve opening sensor, a water temperature sensor, an oil temperature sensor, and a cam angle sensor. The control unit controls the ignition timing, the fuel injection amount, and the like, and controls the rotation of the electric motor 12 by a control current to the power supply connector 34.
　減速機構１３は、図１～図３に示すように、偏心回転運動を行う偏心軸部３７と、該偏心軸部３７の外周に設けられた中径ボールベアリング４７と、該中径ボールベアリング４７の外周に設けられ、内歯構成部５の各内歯５ａ内に転動自在に保持された前記ローラ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４９と、該保持器４９と一体の従動部材９と、から主として構成されている。 As shown in FIGS. 1 to 3, the speed reduction mechanism 13 includes an eccentric shaft portion 37 that performs an eccentric rotational motion, a medium-diameter ball bearing 47 provided on the outer periphery of the eccentric shaft portion 37, and the medium-diameter ball bearing 47. The roller 48 provided on the outer periphery of the inner tooth 5a and rotatably held in the inner teeth 5a of the inner tooth component 5, and the holding allowing the radial movement while holding the roller 48 in the rolling direction. It is mainly comprised from the container 49 and the driven member 9 integral with this holder | retainer 49. FIG.
　偏心軸部３７は、モータ出力軸１５の大径部１５ａに軸方向から一体に設けられた円筒状に形成されて、外周面に形成されたカム面３７ａの回転軸心がモータ出力軸１５の回転軸心から径方向へ僅かに偏心している。 The eccentric shaft portion 37 is formed in a cylindrical shape integrally provided from the axial direction on the large diameter portion 15 a of the motor output shaft 15, and the rotation shaft center of the cam surface 37 a formed on the outer peripheral surface is the motor output shaft 15. It is slightly eccentric in the radial direction from the rotational axis.
　中径ボールベアリング４７は、ニードルベアリング３６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、内輪と外輪及び該両輪との間に介装されたボールと、該ボールを保持するケージと、から構成されている。 The medium-diameter ball bearing 47 is disposed so as to substantially overlap at the radial position of the needle bearing 36, and a ball interposed between the inner ring, the outer ring and the both wheels, and a cage for holding the ball, , Is composed of.
　内輪は、偏心軸部３７の外周面に圧入固定されているのに対して、外輪は、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、この外輪は、軸方向の電動モータ１２側の一端面がどの部位にも接触せず、また軸方向の他端面がこれに対向する保持器４９の背面との間に形成された微小なクリアランスを介してフリーな状態になっている。 The inner ring is press-fitted and fixed to the outer peripheral surface of the eccentric shaft portion 37, whereas the outer ring is in a free state without being fixed in the axial direction. In other words, the outer ring has a minute end formed between the end surface on the electric motor 12 side in the axial direction and no part, and the other end surface in the axial direction is opposed to the rear surface of the cage 49 facing the outer ring. It is free through clearance.
　また、外輪は、その外周面に前記各ローラ４８の外周面が転動自在に当接していると共に、この外周面と前記保持器４９のローラ保持部４９ａの内面との間に、円環状のクリアランスが形成されて、このクリアランスを介して中径ボールベアリング４７全体が偏心軸部３７の偏心回転に伴って径方向へ偏心移動可能になっている。 In addition, the outer ring is in contact with the outer peripheral surface of the roller 48 so that the outer ring can roll, and an annular ring is formed between the outer peripheral surface and the inner surface of the roller holding portion 49 a of the retainer 49. A clearance is formed, and the entire medium-diameter ball bearing 47 can be eccentrically moved in the radial direction along with the eccentric rotation of the eccentric shaft portion 37 through the clearance.
　保持器４９は、固定端部９ａの外周部に一体に設けられて該固定端部９ａの外周部前端から前方へ断面ほぼＬ字形状に折曲形成されている。また、この保持器４９は、固定端部９ａの外周部前端側に径方向に沿って延出した円環状の基部の外端からほぼ軸直角方向へ延出した円筒状のローラ保持部４９ａを有している。 The retainer 49 is integrally provided on the outer peripheral portion of the fixed end portion 9a, and 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. Further, the retainer 49 includes a cylindrical roller retaining portion 49a extending in a direction substantially perpendicular to the axis from the outer end of the annular base portion extending in the radial direction toward the front end side of the outer peripheral portion of the fixed end portion 9a. Have.
　ローラ保持部４９ａは、先端部が前記内歯構成部５やモータハウジング１４の仕切壁１４ｂなどによって仕切られた円環凹状の収容空間を介して仕切壁１４ｂ方向へ延出している。また、ローラ保持部４９ａは、周方向のほぼ等間隔位置に複数のローラ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が形成されている。このローラ保持孔は、先端部側が閉塞されて前後方向に細長い長方形状に形成され、その全体の数(ローラ４８の数)が内歯構成部５の内歯５ａの全体の歯数よりも少なくなっている。これによって、所定の減速比を得るようになっている。 The roller holding portion 49a extends in the direction of the partition wall 14b through an annular concave storage space whose tip is partitioned by the internal tooth component 5 and the partition wall 14b of the motor housing 14 and the like. In addition, the roller holding portion 49a is formed with a plurality of substantially rectangular roller holding holes that hold the plurality of rollers 48 so as to roll freely at substantially equal intervals in the circumferential direction. This roller holding hole is formed in a rectangular shape elongated in the front-rear direction with the tip end side closed, and the total number thereof (number of rollers 48) is smaller than the total number of teeth of the inner teeth 5a of the inner tooth component 5. It has become. As a result, a predetermined reduction ratio is obtained.
　各ローラ４８は、鉄系金属によって形成され、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内歯構成部５の内歯５ａに嵌入している。また各ローラ４８は、保持器４９のローラ保持孔４１ｃの両側縁によって周方向にガイドされつつ径方向へ揺動運動するようになっている。
〔本実施形態の作動〕
　以下、本実施形態におけるバルブタイミング制御装置の作動について簡単に説明すると、まず、機関のクランクシャフトの回転駆動に伴ってタイミングチェーンを介してタイミングスプロケット１が回転する。この回転力が内歯構成部５を介してモータハウジング１４に伝達されて、該モータハウジング１４が同期回転する。一方、内歯構成部５の回転力が、各ローラ４８から保持器４９及び従動部材９を経由してカムシャフト２に伝達される。これによって、カムシャフト２のカムが吸気弁を開閉作動させる。 Each roller 48 is formed of an iron-based metal, and is fitted into the inner teeth 5 a of the inner tooth constituent portion 5 while moving in the radial direction along with the eccentric movement of the medium diameter ball bearing 47. Each roller 48 swings in the radial direction while being guided in the circumferential direction by both side edges of the roller holding hole 41 c of the cage 49.
[Operation of this embodiment]
Hereinafter, the operation of the valve timing control device in the present embodiment will be briefly described. First, the timing sprocket 1 rotates through the timing chain in accordance with the rotational drive of the crankshaft of the engine. This rotational force is transmitted to the motor housing 14 via the internal tooth component 5, and the motor housing 14 rotates synchronously. On the other hand, the rotational force of the internal tooth component 5 is transmitted from each roller 48 to the camshaft 2 via the retainer 49 and the driven member 9. As a result, the cam of the camshaft 2 opens and closes the intake valve.
　機関始動後の所定の機関運転時には、コントロールユニットからの制御電流が給電用ブラシ３９、４０や各スリップリング２６，２７などを介して電動モータ１２のコイル１９に通電されてモータ出力軸１５が回転駆動される、このモータ出力軸１５の回転力が減速機構１３を介してカムシャフト２に対し減速された回転力が伝達される。 During a predetermined engine operation after the engine is started, a control current from the control unit is energized to the coil 19 of the electric motor 12 through the power supply brushes 39 and 40, the slip rings 26 and 27, and the motor output shaft 15 rotates. The rotational force of the motor output shaft 15 that is driven is reduced and transmitted to the camshaft 2 via the speed reduction mechanism 13.
　これにより、カムシャフト２とタイミングスプロケット１の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。このように、吸気弁の開閉タイミングが、進角側あるいは遅角側へ変換され、この結果、機関の燃費や出力の向上が図れる。 Thus, the relative rotational phase of the camshaft 2 and the timing sprocket 1 is converted, and the opening / closing timing of the intake valve is controlled to be advanced or retarded. Thus, the opening / closing timing of the intake valve is converted to the advance side or the retard side, and as a result, the fuel efficiency and output of the engine can be improved.
　そして、本実施形態では、カバー部材４の給電用コネクタ３４に各ブラシホルダ３６，３７を介して設けられた各給電用ブラシ３９、４０が、前記給電プレート１７の外周面に設けられた前記各スリップリング２６，２７に対してハウジング本体１４ａの径方向から弾接させるようにした。このため、従来技術のような軸方向に沿って設けた場合に比較して、装置全体の軸方向の長さを十分に短くすることができる。この結果、装置を含む内燃機関全体の軸方向の小型化が図れ、エンジンルーム内への搭載性やレイアウトの自由度が向上する。 In the present embodiment, the power supply brushes 39 and 40 provided on the power supply connector 34 of the cover member 4 via the brush holders 36 and 37 are provided on the outer peripheral surface of the power supply plate 17. The slip rings 26 and 27 are elastically contacted from the radial direction of the housing main body 14a. For this reason, compared with the case where it provides along an axial direction like a prior art, the axial length of the whole apparatus can be fully shortened. As a result, the internal combustion engine including the device can be reduced in size in the axial direction, and the ease of mounting in the engine room and the degree of layout are improved.
　各スリップリング２６，２７は、給電プレート１７の前端面ではなく、筒部１７ａの外周面に固定されて、各整流用ブラシ２５(ブラシホルダ２３)と径方向からオーバーラップするように配置されている。この点からも装置全体の軸方向の長さを短くすることが可能になる。 The slip rings 26 and 27 are fixed not to the front end face of the power supply plate 17 but to the outer peripheral face of the cylindrical portion 17a, and are arranged so as to overlap each rectifying brush 25 (brush holder 23) from the radial direction. Yes. From this point as well, the axial length of the entire apparatus can be shortened.
　また、各整流用ブラシ２５と各スリップリング２６，２７は、給電プレート１７の内部にモールドされた配線板２６ａ、２７ａを利用して電気的に接続されていることから、配線の取り回しが簡素化されて製造作業が容易になる。 Further, since each rectifying brush 25 and each slip ring 26, 27 are electrically connected by using wiring boards 26a, 27a molded inside the power feeding plate 17, wiring is simplified. As a result, the manufacturing operation becomes easy.
　さらに、給電プレート１７は、筒部１７ａ(環状支持部１７ｃ)を利用してハウジング本体１４ａの筒状固定部１４ｅに軸方向から圧入固定するようになっている。このため、この固定作業が容易になると共に、特に金属製の環状支持部１７ｃを利用して圧入固定することから強固な固定状態が得られる。 Furthermore, the power feeding plate 17 is press-fitted and fixed from the axial direction to the cylindrical fixing portion 14e of the housing main body 14a using the cylindrical portion 17a (annular support portion 17c). For this reason, this fixing work is facilitated and, in particular, a strong fixed state can be obtained by press-fitting and fixing using the metal annular support portion 17c.
　また、給電プレート１７は、内部に金属製の芯材などをモールドすることなく、環状支持部１７ｃ以外は合成樹脂材のみによって形成されていると共に、中央に比較的大きな作業用孔１７ｄが形成されている。これによって、全体の軽量化が図れる。 Further, the power supply plate 17 is formed of only a synthetic resin material except for the annular support portion 17c without molding a metal core material or the like inside, and a relatively large working hole 17d is formed at the center. ing. As a result, the overall weight can be reduced.
　さらに、各スリップリング２６，２７が、モータハウジング１４の外周面、つまり、給電プレート１７の筒部１７ａの外周面に設けられていることから、各スリップリング２６，２７の円周方向の長さが長くなる。したがって、各給電用ブラシ３９，４０との間の摩耗量が大きくなることを考慮して、該給電用ブラシ３９，４０の軸方向長さを長く形成する必要がある。 Further, since the slip rings 26 and 27 are provided on the outer peripheral surface of the motor housing 14, that is, the outer peripheral surface of the cylindrical portion 17 a of the power feeding plate 17, the lengths of the slip rings 26 and 27 in the circumferential direction are provided. Becomes longer. Therefore, it is necessary to increase the axial length of the power supply brushes 39 and 40 in consideration of the increased amount of wear between the power supply brushes 39 and 40.
　そこで、本実施形態では、各給電用ブラシ３９，４０を、鉛直方向の上方位置に設けたことにより、それぞれの自重によって各スリップリング２６、２７に押し付けることが可能になる。 Therefore, in the present embodiment, the power supply brushes 39 and 40 are provided at the upper positions in the vertical direction, so that they can be pressed against the slip rings 26 and 27 by their own weights.
　よって、各コイルばね４１、４２のばね定数を低くすることができることから、スプリング荷重を低くすることが可能になる。この結果、摺動抵抗を低下させて摩耗の発生を十分に抑制することができるので、長期に渡り使用することが可能になる。 Therefore, since the spring constant of each coil spring 41, 42 can be lowered, the spring load can be lowered. As a result, the sliding resistance can be reduced and the occurrence of wear can be sufficiently suppressed, so that it can be used for a long time.
　オイルシール４６は、環状突部１４ｆの外周面と取付フランジ４ｂの内周面との間に介装されて、各スリップリング２６，２７と各給電用ブラシ３９、４０の先端面３９ａ、４０ａの摺動位置よりも一段高い位置に配置されている。このため、各スリップリング２６，２７と給電用ブラシ３９，４０の先端面３９ａ、４０ａとの摺動時に発生する摩耗粉がオイルシール４６方向へ流入しにくくなることから、シール性能の低下を抑制することができる。 The oil seal 46 is interposed between the outer peripheral surface of the annular protrusion 14f and the inner peripheral surface of the mounting flange 4b, so that the slip rings 26, 27 and the tip surfaces 39a, 40a of the power supply brushes 39, 40 are provided. It is arranged at a position one step higher than the sliding position. For this reason, wear powder generated during sliding between the slip rings 26 and 27 and the tip surfaces 39a and 40a of the power supply brushes 39 and 40 is less likely to flow in the direction of the oil seal 46. can do.
　また、取付フランジ４ｂの内周側に設けられた遮断壁２８ｂによって、各スリップリング２６，２７とオイルシール４６との間のクリアランスＣを小さくできるので、摩耗粉がオイルシール４６方向へさらに流入しにくくなる。 Further, since the clearance C between the slip rings 26 and 27 and the oil seal 46 can be reduced by the blocking wall 28b provided on the inner peripheral side of the mounting flange 4b, the wear powder further flows in the direction of the oil seal 46. It becomes difficult.
　しかも、両給電用ブラシ３９，４０は、図８に示すように、円周方向へ所定の距離をもって離間していることから、摺動に伴ってそれぞれ発生して広がった摩耗粉同士が接触することがない。したがって、電気的な短絡の発生を抑制することができる。
〔第２実施形態〕
　図９は第２実施形態を示し、第１実施形態の一対の給電用ブラシ３９，４０の他に、鉛直方向の下側にさらに一対の第２の給電用ブラシ５０、５１を設けたものである。 In addition, as shown in FIG. 8, the power supply brushes 39 and 40 are spaced apart from each other by a predetermined distance in the circumferential direction, so that the abrasion powders that are generated and spread as they slide are brought into contact with each other. There is nothing. Therefore, generation | occurrence | production of an electrical short circuit can be suppressed.
[Second Embodiment]
FIG. 9 shows the second embodiment. In addition to the pair of power supply brushes 39 and 40 of the first embodiment, a pair of second power supply brushes 50 and 51 are further provided on the lower side in the vertical direction. is there.
　この第２の給電用ブラシ５０、５１は、第１実施形態と同じくカバー部材４の下端部の保持孔を介して設けられた第２給電用コネクタ５３の内部に図外のブラシホルダ内に摺動自在に設けられていると共に、上側の第１給電用ブラシ３９，４０と対称位置に配置されている。また、これらは、図外のコイルばねによって各先端面５０ａ、５１ａが前記各スリップリング２６，２７に弾接していると共に、互いに円周方向で所定の距離をもって離間している。 The second power supply brushes 50 and 51 are slid into a brush holder (not shown) inside a second power supply connector 53 provided through a holding hole at the lower end of the cover member 4 as in the first embodiment. It is provided so as to be movable, and is arranged at a position symmetrical to the upper first power supply brushes 39, 40. In addition, the tip surfaces 50a and 51a are elastically contacted with the slip rings 26 and 27 by coil springs (not shown), and are spaced apart from each other by a predetermined distance in the circumferential direction.
　この実施形態によれば、第１の他に第２の給電用ブラシ５０，５１を設けたことによって、各スリップリング２６，２７への通電性がさらに良好になる。他の構成は第１実施形態と同じであるから、同様な作用効果が得られる。 According to this embodiment, by providing the second power supply brushes 50 and 51 in addition to the first, the conductivity to the slip rings 26 and 27 is further improved. Since the other configuration is the same as that of the first embodiment, the same operation and effect can be obtained.
　なお、第１の給電用ブラシ３９，４０は、前述のように、自重を利用して各スリップリング２６，に当接させることができるのに対して、第２の給電用ブラシ５０，５１は、ハウジング本体１４ａの鉛直方向下側に位置するので、各スリップリング２６，２７に対して自重を利用した当接ができないが、コイルばねのばね力を介して安定かつ確実な通電性が得られる。
〔第３実施形態〕
　図１０は第３実施形態を示し、カバー部材４が合成樹脂材によって一体に形成されていると共に、各スリップリング２６，２７にそれぞれ弾接する一対の給電用ブラシ３９，４０が図中、上側と下側の１８０°の対称位置に一つずつ設けられている。 As described above, the first power supply brushes 39 and 40 can be brought into contact with the slip rings 26 by using their own weights, whereas the second power supply brushes 50 and 51 are used. Since it is located on the lower side of the housing main body 14a in the vertical direction, it cannot contact the slip rings 26, 27 using its own weight, but stable and reliable energization is obtained through the spring force of the coil spring. .
[Third Embodiment]
FIG. 10 shows a third embodiment, in which the cover member 4 is integrally formed of a synthetic resin material, and a pair of power supply brushes 39 and 40 that elastically contact with the slip rings 26 and 27, respectively, One is provided at each lower 180 ° symmetrical position.
　すなわち、上側の一つの給電用ブラシ３９は、第１実施形態と同じくカバー部材４の上端部に有する給電用コネクタ３４に設けられている。これに対して、下側の一つの給電用ブラシ４０は、給電用コネクタではなく、単にカバー部材４の下端部内に径方向に沿って貫通形成された固定用孔５４内に圧入固定された角筒状のブラシホルダ５５の内部に摺動自在に保持されている。また、固定用孔５４の下端開口は、合成樹脂材のプラグ５７によって閉塞され、ブラシホルダ５５の内部後端側には、一端が前記プラグ５７に弾接されて、給電用ブラシ４０をスリップリング２７方向へ付勢するコイルばね５６が弾装されている。 That is, one upper power supply brush 39 is provided on the power supply connector 34 provided at the upper end of the cover member 4 as in the first embodiment. On the other hand, the lower power supply brush 40 is not a power supply connector, but is simply a press fit-fixed in a fixing hole 54 formed in the lower end portion of the cover member 4 along the radial direction. It is slidably held inside a cylindrical brush holder 55. The lower end opening of the fixing hole 54 is closed by a synthetic resin plug 57, and one end of the brush holder 55 is elastically contacted with the plug 57 to slip the power supply brush 40. A coil spring 56 urging in the 27 direction is mounted.
　また、下側の給電用ブラシ４０は、カバー部材４の内部にモールドされた導電プレートや図外のピグテールハーネスを介して上側の給電用ブラシと同じく給電用コネクタ３４の端子に接続されている。 The lower power supply brush 40 is connected to the terminal of the power supply connector 34 in the same manner as the upper power supply brush through a conductive plate molded inside the cover member 4 and a pigtail harness (not shown).
　この実施形態によれば、カバー部材４を合成樹脂材によって一体に形成したことから装置全体の軽量化を図ることができる。 According to this embodiment, since the cover member 4 is integrally formed of a synthetic resin material, the weight of the entire apparatus can be reduced.
　また、本実施形態では、各給電用ブラシ３９，４０が、円周方向の１８０°位置に大きく離間して配置されていることから、前述したような、各スリップリング２６，２７との摺動に伴う摩耗粉の付着による互いの短絡の発生を十分に抑制できる。
〔第４実施形態〕
　図１１は第４実施形態を示し、基本構成は第１実施形態と同じであるが、異なるところは、前記ハウジング本体１４ａの環状突部１４ｆの高さ、つまり径方向の大きさをさらに大きくすると共に、この大きくなった分だけカバー部材４の取付フランジ４ｂの内径を大きく形成した。これによって、オイルシール４６の配置を確保しつつ環状突部１４ｆの外周部と遮断壁２８ｂとの間のクリアランスＣをさらに小さくすることができる。 Further, in the present embodiment, since the power supply brushes 39 and 40 are arranged at a large distance of 180 ° in the circumferential direction, they slide with the slip rings 26 and 27 as described above. It is possible to sufficiently suppress the occurrence of short-circuiting due to the adhesion of wear powder accompanying the.
[Fourth Embodiment]
FIG. 11 shows the fourth embodiment, and the basic configuration is the same as that of the first embodiment, except that the height of the annular protrusion 14f of the housing body 14a, that is, the size in the radial direction is further increased. At the same time, the inner diameter of the mounting flange 4b of the cover member 4 is made larger by the increased amount. Accordingly, the clearance C between the outer peripheral portion of the annular protrusion 14f and the blocking wall 28b can be further reduced while ensuring the arrangement of the oil seal 46.
　このように、クリアランスＣを小さくしてラビリンス効果を発揮させることにより、各スリップリング２６，２７と各給電用ブラシ３９，４０との摺動に伴って発生した摩耗粉が前記オイルシール４６方向へ流入するのを阻止することができる。 As described above, by reducing the clearance C and exerting the labyrinth effect, the wear powder generated by the sliding between the slip rings 26 and 27 and the power supply brushes 39 and 40 is directed toward the oil seal 46. Inflow can be prevented.
　このため、オイルシール４６への摩耗粉の付着を回避できるので、シール性能の低下をさらに抑制できる。この結果、長期に渡る使用が可能になって耐久性の向上が図れる。 For this reason, since it is possible to avoid the adhesion of wear powder to the oil seal 46, the deterioration of the sealing performance can be further suppressed. As a result, it can be used over a long period of time, and durability can be improved.
　本発明は、前記各実施形態の構成に限定されるものではなく、例えば、装置を排気弁側に設けることも可能であり、さらに駆動回転体としては、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 present invention is not limited to the configuration of each of the above-described embodiments. For example, the apparatus can be provided on the exhaust valve side. Further, as the driving rotating body, in addition to the timing sprocket, a timing pulley or the like can be used. There may be.
　また、カバー部材４を、第１、第２、第４実施形態においても合成樹脂材によって形成することも可能であり、これによって、装置の軽量化が図れる。 The cover member 4 can also be formed of a synthetic resin material in the first, second, and fourth embodiments, thereby reducing the weight of the device.
　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.
　クランクシャフトから回転力が伝達される駆動回転体と、カムシャフトに固定された従動回転体と、前記駆動回転体にモータハウジングが固定され、回転駆動することによって前記駆動回転体に対して従動回転体を相対回転させる電動モータと、前記モータハウジングの外周側に設けられ、前記電動モータに通電するスリップリングと、前記スリップリングに、前記モータハウジングの径方向から当接して給電する給電用ブラシを有する給電機構と、を備えている。 A drive rotator to which a rotational force is transmitted from the crankshaft, a driven rotator fixed to the camshaft, and a motor housing fixed to the drive rotator and driven to rotate relative to the drive rotator An electric motor that relatively rotates the body, a slip ring that is provided on the outer peripheral side of the motor housing and energizes the electric motor, and a power supply brush that abuts the slip ring from the radial direction of the motor housing to supply power And a power supply mechanism.
　別の好ましい態様として、前記電動モータは、モータ出力軸に設けられた複数のコイルと、前記モータハウジングの内周面に設けられた永久磁石と、前記スリップリングと導通して前記複数のコイルへの通電する整流子と、先端部が前記整流子に摺接する整流子ブラシと、を備え、
　前記スリップリングは、その形成位置が前記整流子と整流子ブラシに対して前記モータ出力軸の径方向でオーバーラップして設けられている。 As another preferred aspect, the electric motor includes a plurality of coils provided on a motor output shaft, a permanent magnet provided on an inner peripheral surface of the motor housing, and a plurality of coils connected to the slip ring. And a commutator brush whose tip is in sliding contact with the commutator,
The slip ring is provided such that its formation position overlaps the commutator and the commutator brush in the radial direction of the motor output shaft.
　さらに別の好ましい態様として、前記モータハウジングは、前記永久磁石が設けられた筒状のハウジング本体と、前記スリップリングと前記整流子ブラシを保持する有底円筒状の保持部材と、を備え、
　前記ハウジング本体の前端部に前記保持部材が設けられている。 As still another preferred aspect, the motor housing includes a cylindrical housing body provided with the permanent magnet, and a bottomed cylindrical holding member that holds the slip ring and the commutator brush.
The holding member is provided at a front end portion of the housing body.
　別の好ましい態様として、前記保持部材は、前記ハウジング本体に軸方向から固定される筒部と、該筒部の軸方向前端側に一体に有し、内周側に前記整流子ブラシが設けられた底壁部と、を有し、前記筒部の後端部が前記ハウジング本体に固定されている。 As another preferable aspect, the holding member has a cylindrical portion fixed to the housing body from the axial direction, and is integrally provided on the axial front end side of the cylindrical portion, and the commutator brush is provided on the inner peripheral side. And a rear end portion of the cylindrical portion is fixed to the housing body.
　別の好ましい態様として、前記ハウジング本体は筒状に形成され、該ハウジング本体の前端部の外周面に、前記保持部材の筒部が軸方向から圧入固定されている。 As another preferred embodiment, the housing main body is formed in a cylindrical shape, and the cylindrical portion of the holding member is press-fitted and fixed in the axial direction on the outer peripheral surface of the front end portion of the housing main body.
　別の好ましい態様として、前記永久磁石は、ハウジング本体の内周面に固定されている。 As another preferred embodiment, the permanent magnet is fixed to the inner peripheral surface of the housing body.
　別の好ましい態様として、前記給電機構は、電源に接続されるコネクタと、該コネクタに一体に設けられた前記給電用ブラシとを有し、
　前記保持部材の前端側に、前記給電機構のコネクタを保持するカバー部材が取り付けられている。 As another preferred aspect, the power supply mechanism includes a connector connected to a power source, and the power supply brush provided integrally with the connector,
A cover member that holds the connector of the power feeding mechanism is attached to the front end side of the holding member.
　別の好ましい態様として、前記ハウジング本体は、前端部に前記保持部材の筒部が圧入固定される段差小径状の筒状固定部が形成されていると共に、該筒状固定部の軸方向内端縁に大径な環状突部が一体に設けられ、該環状突部の外周に、前記モータハウジングと前記カバー部材との間をシールするシール部材が設けられている。 As another preferred aspect, the housing main body has a cylindrical fixing portion having a small-diameter step in which the cylindrical portion of the holding member is press-fitted and fixed at a front end portion, and an axially inner end of the cylindrical fixing portion. A large-diameter annular protrusion is integrally provided at the edge, and a seal member that seals between the motor housing and the cover member is provided on the outer periphery of the annular protrusion.
　さらに別の好ましい態様として、前記カバー部材の外周部の内周に、前記環状突部とコネクタとの間の隙間に介在して給電用ブラシと前記シール部材との連通を遮断する遮断壁が設けられている。 As yet another preferred embodiment, a blocking wall is provided on the inner periphery of the outer peripheral portion of the cover member so as to block communication between the power supply brush and the seal member interposed in a gap between the annular protrusion and the connector. It has been.
　別の好ましい態様として、前記給電用ブラシの前記スリップリングとの当接面は、前記駆動回転体の回転軸よりも鉛直方向の上側に配置されている。 As another preferred embodiment, the contact surface of the power supply brush with the slip ring is disposed on the upper side in the vertical direction with respect to the rotational axis of the drive rotator.
　別の好ましい態様として、前記スリップリングは、前記モータハウジングの外周に軸方向に２つ並設されている一方、前記給電用ブラシも、前記各スリップリングに対応して２つ設けられ、前記２つの給電用ブラシのうち、少なくとも一方は前記駆動回転体の回転軸よりも鉛直方向の上側に配置されている。 As another preferred embodiment, two slip rings are arranged in parallel in the axial direction on the outer periphery of the motor housing, while two power supply brushes are provided corresponding to the slip rings, and the 2 At least one of the two power supply brushes is disposed on the upper side in the vertical direction with respect to the rotation shaft of the drive rotator.
　別の好ましい態様として、前記２つの給電用ブラシの両方が前記駆動回転体の回転軸よりも鉛直方向の上側に配置されている。 As another preferred embodiment, both of the two power supply brushes are arranged on the upper side in the vertical direction with respect to the rotation axis of the drive rotating body.
　別の好ましい態様として、前記２つの給電用ブラシは、互いの配置が前記モータハウジングの円周方向に所定角度だけずれている。 As another preferred embodiment, the two power supply brushes are displaced from each other by a predetermined angle in the circumferential direction of the motor housing.
　別の好ましい態様として、前記スリップリングは、前記モータハウジングの外周に軸方向に２つ並設されている一方、前記給電用ブラシは、前記一つのスリップリングに対して二つずつ当接する合計４つ設けられ、前記２つの給電用ブラシは、前記駆動回転体の回転軸よりも鉛直方向の上側に配置されている。 In another preferred embodiment, two slip rings are arranged in parallel in the axial direction on the outer periphery of the motor housing, while the power supply brushes are in contact with the one slip ring two by four in total. The two power supply brushes are arranged on the upper side in the vertical direction with respect to the rotation shaft of the drive rotator.
　別の好ましい態様として、前記４つの給電用ブラシは、互いの配置が前記モータハウジングの円周方向に所定角度だけずれている。 As another preferred mode, the four power supply brushes are displaced from each other by a predetermined angle in the circumferential direction of the motor housing.
　別の好ましい態様として、２つの給電用ブラシのうち、少なくとも１つの給電用ブラシは駆動回転体の回転軸よりも鉛直方向の下側に配置されている。 As another preferred embodiment, at least one of the two power supply brushes is disposed on the lower side in the vertical direction with respect to the rotational axis of the drive rotator.
　別の好ましい態様として、前記カバー部材は、ほぼ円形状に形成され、外周部の鉛直方向上側に径方向に沿った保持孔が貫通形成されていると共に、前記給電機構は、前記コネクタが前記保持孔に径方向から挿入されて前記給電用ブラシと一緒に保持されている。 As another preferred embodiment, the cover member is formed in a substantially circular shape, and a holding hole extending in the radial direction is formed through the upper side in the vertical direction of the outer peripheral portion. It is inserted into the hole from the radial direction and held together with the power supply brush.
　さらに別の好ましい態様として、電動モータの給電装置であって、
　駆動回転体にモータハウジングが一体的に固定されて、前記駆動回転体と同期回転する電動モータと、前記モータハウジングの外周部に設けられて、給電用ブラシが当接することによって前記電動モータに給電するスリップリングと、該スリップリングに前記モータハウジングの径方向外側から当接する給電用ブラシを有する給電機構と、を備えている。 Yet another preferred embodiment is a power supply device for an electric motor,
A motor housing is integrally fixed to the drive rotator, and is provided on the outer periphery of the motor housing that rotates synchronously with the drive rotator. And a power feeding mechanism having a power feeding brush that contacts the slip ring from the outside in the radial direction of the motor housing.

Claims (18)

  1. 　クランクシャフトから回転力が伝達される駆動回転体と、
    　カムシャフトに固定された従動回転体と、
    　前記駆動回転体にモータハウジングが固定され、回転駆動することによって前記駆動回転体に対して従動回転体を相対回転させる電動モータと、
    　前記モータハウジングの外周側に設けられたスリップリングと、
    　前記スリップリングに、前記モータハウジングの径方向外側から当接して給電する給電用ブラシを有する給電機構と、
    　を備えたことを特徴とする内燃機関のバルブタイミング制御装置。     A driving rotating body to which rotational force is transmitted from the crankshaft;
    A driven rotating body fixed to the camshaft;
    An electric motor having a motor housing fixed to the drive rotator and rotating the driven rotator relative to the drive rotator by rotationally driving;
    A slip ring provided on the outer peripheral side of the motor housing;
    A power feeding mechanism having a power feeding brush that feeds power by contacting the slip ring from the radially outer side of the motor housing;
    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、
    　前記電動モータは、モータ出力軸に設けられた複数のコイルと、前記モータハウジングの内周面に設けられた永久磁石と、前記スリップリングと導通して前記複数のコイルへの通電する整流子と、先端部が前記整流子に摺接する整流子ブラシと、を備え、
    　前記スリップリングは、その形成位置が前記整流子と整流子ブラシに対して前記モータ出力軸の径方向でオーバーラップ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 1,
    The electric motor includes a plurality of coils provided on a motor output shaft, a permanent magnet provided on an inner peripheral surface of the motor housing, and a commutator that conducts the slip ring and energizes the plurality of coils. A commutator brush whose tip is in sliding contact with the commutator, and
    The valve timing control device for an internal combustion engine, wherein a formation position of the slip ring overlaps with the commutator and the commutator brush in a radial direction of the motor output shaft.
  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、
    　前記モータハウジングは、前記永久磁石が設けられた筒状のハウジング本体と、前記スリップリングと前記整流子ブラシを保持する有底円筒状の保持部材と、を備え、
    　前記ハウジング本体の前記カムシャフトと反対側に位置する軸方向前端部に前記保持部材が設けられていることを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control device for an internal combustion engine according to claim 2,
    The motor housing includes a cylindrical housing body provided with the permanent magnets, and a bottomed cylindrical holding member that holds the slip ring and the commutator brush.
    The valve timing control device for an internal combustion engine, wherein the holding member is provided at an axially front end located on the opposite side of the housing body from the camshaft.
  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、
    　前記保持部材は、前記ハウジング本体の前端部に軸方向から固定される筒部と、該筒部の軸方向前端側に一体に有し、内周側に前記整流子ブラシが設けられた底壁部と、を備え、前記筒部の後端部が前記ハウジング本体の前端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,
    The holding member has a cylindrical portion fixed to the front end portion of the housing body from the axial direction, and a bottom wall integrally provided on the axial front end side of the cylindrical portion, and the commutator brush is provided on the inner peripheral side. A valve timing control device for an internal combustion engine, wherein a rear end portion of the cylindrical portion is fixed to a front end portion of the housing body.
  5. 　請求項４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、
    　前記ハウジング本体は筒状に形成され、該ハウジング本体の前端部の外周面に、前記保持部材の筒部が軸方向から圧入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 4,
    The valve timing control device for an internal combustion engine, wherein the housing main body is formed in a cylindrical shape, and the cylindrical portion of the holding member is press-fitted and fixed in an axial direction on an outer peripheral surface of a front end portion of the housing main body.
  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、
    　前記永久磁石は、ハウジング本体の内周面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,
    The valve timing control device for an internal combustion engine, wherein the permanent magnet is fixed to an inner peripheral surface of a housing body.
  7. 　請求項５に記載の内燃機関のバルブタイミング制御装置において、
    　前記給電機構は、電源に接続されるコネクタと、該コネクタに一体に設けられた前記給電用ブラシとを有し、
    　前記保持部材の前端側に、前記給電機構のコネクタを保持するカバー部材が取り付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。     In the internal combustion engine valve timing control device according to claim 5,
    The power supply mechanism has a connector connected to a power source, and the power supply brush provided integrally with the connector,
    A valve timing control device for an internal combustion engine, wherein a cover member that holds a connector of the power feeding mechanism is attached to a front end side of the holding member.
  8. 　請求項７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、
    　前記ハウジング本体は、前端部に前記保持部材の筒部が圧入固定される段差小径状の筒状固定部が形成されていると共に、該筒状固定部の軸方向内端縁に大径な環状突部が一体に設けられ、該環状突部の外周に、前記モータハウジングと前記カバー部材との間をシールするシール部材が設けられていることを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control apparatus for an internal combustion engine according to claim 7,
    The housing body is formed with a stepped small-diameter cylindrical fixing portion in which the cylindrical portion of the holding member is press-fitted and fixed at a front end portion, and a large-diameter annular shape at an axial inner end edge of the cylindrical fixing portion. A valve timing control device for an internal combustion engine, wherein a protrusion is provided integrally, and a seal member for sealing between the motor housing and the cover member is provided on an outer periphery of the annular protrusion.
  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、
    　前記カバー部材の外周部の内周に、前記環状突部とコネクタとの間の隙間に介在して前記給電用ブラシと前記シール部材との連通を遮断する遮断壁が設けられていることを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control device for an internal combustion engine according to claim 8,
    The inner periphery of the outer peripheral portion of the cover member is provided with a blocking wall that blocks communication between the power supply brush and the seal member, interposed in a gap between the annular protrusion and the connector. A valve timing control device for an internal combustion engine.
  10. 　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、
    　前記給電用ブラシの前記スリップリングとの当接面は、前記駆動回転体の回転軸よりも鉛直方向の上側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 apparatus for an internal combustion engine according to claim 1,
    The valve timing control device for an internal combustion engine, wherein a contact surface of the power supply brush with the slip ring is disposed above a rotation axis of the drive rotating body in a vertical direction.
  11. 　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、
    　前記スリップリングは、前記モータハウジングの外周に軸方向に２つ並設されている一方、前記給電用ブラシも、前記各スリップリングに対応して２つ設けられ、
    　前記２つの給電用ブラシのうち、少なくとも一方は前記駆動回転体の回転軸よりも鉛直方向の上側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 apparatus for an internal combustion engine according to claim 1,
    Two slip rings are provided in parallel in the axial direction on the outer periphery of the motor housing, while two brushes for power feeding are provided corresponding to each slip ring,
    The valve timing control device for an internal combustion engine, wherein at least one of the two power supply brushes is disposed above a rotation axis of the drive rotating body in a vertical direction.
  12. 　請求項１１に記載の内燃機関のバルブタイミング制御装置において、
    　前記２つの給電用ブラシの両方が前記駆動回転体の回転軸よりも鉛直方向の上側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 apparatus for an internal combustion engine according to claim 11,
    The valve timing control device for an internal combustion engine, characterized in that both of the two power supply brushes are arranged on the upper side in the vertical direction with respect to the rotation shaft of the drive rotating body.
  13. 　請求項１１に記載の内燃機関のバルブタイミング制御装置において、
    　前記２つの給電用ブラシは、互いの配置が前記モータハウジングの円周方向に所定角度だけずれていることを特徴とする内燃機関のバルブタイミング制御装置。     The valve timing control apparatus for an internal combustion engine according to claim 11,
    The valve timing control device for an internal combustion engine, wherein the two power supply brushes are displaced from each other by a predetermined angle in a circumferential direction of the motor housing.
  14. 　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、
    　前記スリップリングは、前記モータハウジングの外周に軸方向に２つ並設されている一方、
    　前記給電用ブラシは、前記一つのスリップリングに対して二つずつ当接する合計４つ設けられ、
    　前記２つの給電用ブラシは、前記駆動回転体の回転軸よりも鉛直方向の上側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 apparatus for an internal combustion engine according to claim 1,
    While two slip rings are arranged in parallel in the axial direction on the outer periphery of the motor housing,
    A total of four power supply brushes are provided that abut against the one slip ring two by two,
    The valve timing control device for an internal combustion engine, wherein the two power supply brushes are arranged on the upper side in a vertical direction with respect to a rotation shaft of the drive rotating body.
  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４つの給電用ブラシは、互いの配置が前記モータハウジングの円周方向で所定角度だけず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 valve timing control device for an internal combustion engine, wherein the four power supply brushes are displaced from each other by a predetermined angle in a circumferential direction of the motor housing.
  16. 　請求項１１に記載の内燃機関のバルブタイミング制御装置において、
    　前記２つの給電用ブラシのうち、少なくとも１つの給電用ブラシは駆動回転体の回転軸よりも鉛直方向の下側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 apparatus for an internal combustion engine according to claim 11,
    The valve timing control device for an internal combustion engine, wherein at least one of the two power supply brushes is disposed on a lower side in a vertical direction than the rotation shaft of the drive rotating body.
  17. 　請求項７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、ほぼ円形状に形成され、外周部の鉛直方向上側に径方向に沿った保持孔が貫通形成されていると共に、
    　前記給電機構は、前記コネクタが前記保持孔に径方向から挿入されて前記給電用ブラシと一緒に保持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 7,
    The cover member is formed in a substantially circular shape, and a holding hole along the radial direction is formed on the upper side in the vertical direction of the outer peripheral portion.
    The valve timing control device for an internal combustion engine, wherein the power feeding mechanism is configured such that the connector is inserted into the holding hole from a radial direction and held together with the power feeding brush.
  18. 　電動モータの給電装置であって、
    　駆動回転体にモータハウジングが一体的に固定されて、該モータハウジングが前記駆動回転体と同期回転する電動モータと、
    　前記モータハウジングの外周部に設けられて、前記モータハウジングの径方向外側から当接する給電用ブラシによって前記電動モータへの給電に用いられるスリップリングと、
    　を備えたことを特徴とする電動モータの給電装置。     A power supply device for an electric motor,
    An electric motor in which a motor housing is integrally fixed to a drive rotator, and the motor housing rotates synchronously with the drive rotator;
    A slip ring provided on the outer periphery of the motor housing and used for power feeding to the electric motor by a power feeding brush that comes into contact with the motor housing from the outside in the radial direction;
    A power supply device for an electric motor, comprising:
PCT/JP2017/007202 2016-06-01 2017-02-24 Valve timing control device for internal combustion engine and power supply device for electric motor WO2017208530A1 (en)

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS473203U (en) * 1971-02-01 1972-09-04
JPS49149203U (en) * 1973-04-23 1974-12-24
JPS6216042A (en) * 1985-07-10 1987-01-24 Toshiba Corp Collector ring device for rotary electric machine
JP2009293576A (en) * 2008-06-09 2009-12-17 Hitachi Automotive Systems Ltd Valve timing control device of internal combustion engine
JP2011132808A (en) * 2009-12-22 2011-07-07 Hitachi Automotive Systems Ltd Variable valve gear of internal combustion engine
JP2013207928A (en) * 2012-03-28 2013-10-07 Toyota Central R&D Labs Inc Rotary electric machine
JP2015206308A (en) * 2014-04-22 2015-11-19 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

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS473203U (en) * 1971-02-01 1972-09-04
JPS49149203U (en) * 1973-04-23 1974-12-24
JPS6216042A (en) * 1985-07-10 1987-01-24 Toshiba Corp Collector ring device for rotary electric machine
JP2009293576A (en) * 2008-06-09 2009-12-17 Hitachi Automotive Systems Ltd Valve timing control device of internal combustion engine
JP2011132808A (en) * 2009-12-22 2011-07-07 Hitachi Automotive Systems Ltd Variable valve gear of internal combustion engine
JP2013207928A (en) * 2012-03-28 2013-10-07 Toyota Central R&D Labs Inc Rotary electric machine
JP2015206308A (en) * 2014-04-22 2015-11-19 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

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