WO2017208530A1 - Dispositif de commande de distribution pour moteur à combustion interne et dispositif d'alimentation pour moteur électrique - Google Patents

Dispositif de commande de distribution pour moteur à combustion interne et dispositif d'alimentation pour moteur électrique Download PDF

Info

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
Authority
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
English (en)
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日立オートモティブシステムズ株式会社 filed Critical 日立オートモティブシステムズ株式会社
Publication of WO2017208530A1 publication Critical patent/WO2017208530A1/fr

Links

Images

Classifications

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

Landscapes

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

Abstract

La présente invention est équipée d'un moteur électrique (12) qui amène un arbre à cames à tourner par rapport à un pignon de synchronisation (5), et de deux bagues collectrices (26)(27) l'un devant et l'autre en arrière de la surface circonférentielle externe d'une partie tubulaire (17a) d'une plaque d'alimentation (17) fixée à la partie d'extrémité avant d'un carter de moteur. Une partie de retenue pour connecteur (28) est disposée sur l'extrémité supérieure de la partie circonférentielle externe d'un élément de couvercle (4) disposé de manière à recouvrir l'extrémité avant de la plaque d'alimentation électrique, et une paire de brosses d'alimentation en énergie, qui sont en contact avec les bagues collectrices à partir de la direction radiale, est prévue sur la partie de retenue pour connecteur Ainsi, en modifiant l'agencement des brosses d'alimentation dans la direction radiale, il est possible de réduire la longueur axiale du dispositif de commande de distribution.
PCT/JP2017/007202 2016-06-01 2017-02-24 Dispositif de commande de distribution pour moteur à combustion interne et dispositif d'alimentation pour moteur électrique WO2017208530A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-109667 2016-06-01
JP2016109667A JP2019132129A (ja) 2016-06-01 2016-06-01 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構造

Publications (1)

Publication Number Publication Date
WO2017208530A1 true WO2017208530A1 (fr) 2017-12-07

Family

ID=60479291

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2017/007202 WO2017208530A1 (fr) 2016-06-01 2017-02-24 Dispositif de commande de distribution pour moteur à combustion interne et dispositif d'alimentation pour moteur électrique

Country Status (2)

Country Link
JP (1) JP2019132129A (fr)
WO (1) WO2017208530A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS473203U (fr) * 1971-02-01 1972-09-04
JPS49149203U (fr) * 1973-04-23 1974-12-24
JPS6216042A (ja) * 1985-07-10 1987-01-24 Toshiba Corp 回転電機の集電環装置
JP2009293576A (ja) * 2008-06-09 2009-12-17 Hitachi Automotive Systems Ltd 内燃機関のバルブタイミング制御装置
JP2011132808A (ja) * 2009-12-22 2011-07-07 Hitachi Automotive Systems Ltd 内燃機関の可変動弁装置
JP2013207928A (ja) * 2012-03-28 2013-10-07 Toyota Central R&D Labs Inc 回転電機
JP2015206308A (ja) * 2014-04-22 2015-11-19 日立オートモティブシステムズ株式会社 内燃機関のバルブタイミング制御装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS473203U (fr) * 1971-02-01 1972-09-04
JPS49149203U (fr) * 1973-04-23 1974-12-24
JPS6216042A (ja) * 1985-07-10 1987-01-24 Toshiba Corp 回転電機の集電環装置
JP2009293576A (ja) * 2008-06-09 2009-12-17 Hitachi Automotive Systems Ltd 内燃機関のバルブタイミング制御装置
JP2011132808A (ja) * 2009-12-22 2011-07-07 Hitachi Automotive Systems Ltd 内燃機関の可変動弁装置
JP2013207928A (ja) * 2012-03-28 2013-10-07 Toyota Central R&D Labs Inc 回転電機
JP2015206308A (ja) * 2014-04-22 2015-11-19 日立オートモティブシステムズ株式会社 内燃機関のバルブタイミング制御装置

Also Published As

Publication number Publication date
JP2019132129A (ja) 2019-08-08

Similar Documents

Publication Publication Date Title
JP5976505B2 (ja) 内燃機関のバルブタイミング制御装置
JP2017106468A (ja) 内燃機関のバルブタイミング制御装置
JP6042233B2 (ja) 内燃機関のバルブタイミング制御システム
JP2012132367A (ja) 内燃機関のバルブタイミング制御装置
JP2013167181A (ja) 内燃機関のバルブタイミング制御装置
JP6174160B2 (ja) 内燃機関のバルブタイミング制御装置
JP6001506B2 (ja) 内燃機関の可変動弁装置
JP5823769B2 (ja) 内燃機関のバルブタイミング制御装置
JP5719008B2 (ja) 内燃機関の可変動弁装置
JP6154521B2 (ja) 内燃機関のバルブタイミング制御システム
JP5873523B2 (ja) 内燃機関のバルブタイミング制御装置
KR101710232B1 (ko) 내연 기관의 밸브 타이밍 제어 장치 및 이 밸브 타이밍 제어 장치에 이용되는 급전 기구
WO2017208530A1 (fr) Dispositif de commande de distribution pour moteur à combustion interne et dispositif d'alimentation pour moteur électrique
JP6030781B2 (ja) 内燃機関のバルブタイミング制御装置
JP6263462B2 (ja) 内燃機関のバルブタイミング制御装置
JP5462380B2 (ja) 内燃機関のバルブタイミング制御装置
JP6311044B2 (ja) 内燃機関の可変動弁装置
JP6274900B2 (ja) 内燃機関のバルブタイミング制御装置
JP5976529B2 (ja) 内燃機関のバルブタイミング制御装置及び該バルブタイミング制御装置に用いられるカバー部材
WO2020039743A1 (fr) Dispositif de commande de réglage de distribution pour moteur à combustion interne
JPWO2016125545A1 (ja) 内燃機関のバルブタイミング制御装置
WO2018055951A1 (fr) Dispositif de commande de réglage de distribution pour moteur à combustion interne et structure d'étanchéité pour dispositif de commande de réglage de distribution
JP2014214723A (ja) 内燃機関の可変動弁装置
JP2018204508A (ja) 内燃機関のバルブタイミング制御装置
JP2019190384A (ja) 内燃機関のバルブタイミング制御装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17806092

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 17806092

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP