JP2019132129A - Valve timing control device of internal combustion engine and power supply structure of electric motor - Google Patents

Abstract

To provide a valve timing control device of an internal combustion engine which changes arrangement of a power supply brush in a radial direction to reduce an axial length of the valve timing control device.SOLUTION: A valve timing control device of an internal combustion engine includes: an electric motor 12 which rotates a cam shaft relative to a timing sprocket; and two front and rear slip rings 26, 27 formed on an outer peripheral surface of a cylinder part 17a of a power supply plate 17 fixed to a front end part of a motor housing. A connector holding part 28 is provided at an outer periphery part upper end part of a cover member 4 which is provided so as to cover a front end of the power supply plate. A pair of power supply brushes 39, 40 which contacts with the respective snap rings from a radial direction is provided at the connector holding part.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a valve timing control device for an internal combustion engine that controls opening and closing timings of, for example, an intake valve and an exhaust valve, and an electric motor feeding structure.

  As a valve timing control device for an internal combustion engine, one described in Patent Document 1 below is known.

  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.

  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.

Japanese Patent Laid-Open No. 2015-151983

  As described above, the pair of power supply brushes provided on the cover member is in 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.

  As a result, for example, in the case of an in-line type internal combustion engine, the axial length of the entire 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.

  The present invention has been devised in view of the above-described conventional technical problems, and an object of the present invention 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.

  According to the present invention, the axial length of the apparatus can be sufficiently shortened, and the mountability of the internal combustion engine in the engine room and the freedom of layout are improved.

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 | attached the timing sprocket provided to this embodiment, and a motor housing. It is a front view of the electric power feeding plate provided to this embodiment. It is a rear view of the same electric power feeding plate. It is a side view of the electric power feeding plate. It is the front view which looked at the cover member provided to this embodiment from the arrow A direction of FIG. 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. 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. It is a principal part expanded sectional view of 4th Embodiment of this invention.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of a valve timing control device for an internal combustion engine and an electric motor feeding structure 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.

  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.

  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).

  Further, an internal gear 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.

  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.

  Further, a holding plate 8 is fixed to the rear end surface of the sprocket body 1a on the side opposite to the internal tooth component 5. 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.

  A substantially inverted trapezoidal stopper convex portion 8b protruding toward the central axis direction is integrally provided at a predetermined position on the inner peripheral edge of the central hole 8a of the holding plate 8.

  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.

  The camshaft 2 has two drive cams per cylinder for opening an intake valve (not shown) on the outer periphery, and an axial end portion 2a and a flange integrally provided on the outer periphery of the end portion 2a. The driven member 9 is fastened together by a cam bolt 10 from the axial direction via the portion 2b. 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 determined. Are now regulated.

  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 member It is mainly composed of a cylindrical portion 9b protruding in the axial direction from the inner peripheral front end face of the end 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 one end portion 2a of the camshaft 2 is fitted from the axial direction at a substantially central position of the outer surface. A joint groove 9d is formed.

  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 small-diameter ball bearing 35 and a needle bearing 36 are juxtaposed in the axial direction.

  As shown in FIG. 1, the cam bolt 10 has an end face in the axial direction 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 includes the electric motor 12 disposed on the front end side of the cylindrical portion 9b of the driven member 9, a speed reducing mechanism 13 that reduces the rotational speed of the electric motor 12 and transmits the speed to the camshaft 2. Is mainly composed of

  As shown in FIG. 1, the electric motor 12 is a brushed DC motor, which is a yoke that rotates integrally with the timing sprocket 1, and a cylindrical housing body of the motor housing 14. A motor output shaft 15 rotatably provided inside 14a, 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 the power feeding plate 17 which is a holding member fixed to the head.

  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 a ferrous metal material, and has an outer diameter that is relatively small like the outer diameter of the sprocket main body 1a. In addition, a disk-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.

  In the partition wall 14b, a large-diameter shaft insertion hole 14c through which the motor output shaft 15 and the eccentric shaft portion 37 are inserted is formed on the inner periphery of a cylindrical extending 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 portions of the respective bolts 7 are screwed at positions corresponding to the respective bolt insertion holes 1c and 8c are formed at equal intervals in the circumferential direction. Yes. The timing sprocket 1 (internal gear 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 is formed on the cover member 4 side with a large diameter portion 15a formed on the camshaft 2 side through a stepped portion at a substantially central position in the axial direction. And a small-diameter portion 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 which 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 into the outer peripheral surface of the small diameter portion 15b, and a coil 19 described later is divided into each segment divided into the same number as the number of poles of the iron core rotor 18. The terminal of the drawn coil wire is 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 of the permanent magnets 16 is disposed with a predetermined gap in the circumferential direction, is formed in a cylindrical shape as a whole, and has a plurality of magnetic poles in the circumferential direction.

  As shown in FIGS. 1 to 4, the power feeding plate 17 is basically formed in a bottomed cylindrical shape by a synthetic resin material, and has a cylindrical portion 17 a on the outer peripheral side and an axial front end side of the cylindrical portion 17 a. A bottom wall portion 17b that is integrally formed with the cylindrical portion, and an annular support portion that is fixed to the inner side of the connecting portion between the cylindrical portion 17a and the bottom wall portion 17b, and the iron-based metal material is bent into a substantially U-shaped cross section. 17c.

  The cylindrical portion 17a has a rear end portion that is press-fitted and fixed to the outer peripheral surface of the cylindrical fixing portion 14e of the motor housing 14 via the annular support portion 17c, and two slips arranged in the axial direction on the outer periphery. Rings 26 and 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. The mold is fixed to the cylindrical portion 17a via the. The slip rings 26 and 27 are provided so that the formation positions thereof overlap in the radial direction of the motor output shaft 15 with respect to the commutator 20 and a commutator brush 23 which will be in contact with the commutator 20. .

  The bottom wall portion 17b is formed with a relatively large-diameter working hole 17d formed in the center of FIGS. 1 and 5 to 7, and a rectangular copper tube 4 on the inner surface side of the camshaft 2 side. Each of the two brush holders 23 is fixed by four rivets 32. Each of the brush holders 23 is a set of two, and each set arranged in the circumferential direction is opposed to each other in the radial direction, and each arcuate tip surface is provided inside the commutator. A commutator brush 25 that is in contact with the outer peripheral surface 20 is housed and arranged so as to be slidable along the radial direction. Each commutator brush portion 25 is biased in the direction of the outer peripheral surface of the commutator 20 by the spring force of the coil spring 24. Further, as shown in FIGS. 1 and 5, the slip rings 26, 27 and the two brush holders 23 (two commutator brushes 25) of each set are provided inside the cylindrical portion 17 a and the bottom wall portion 17 b. Wiring boards 26a, 27a are electrically molded through the pair of pigtail harnesses 26b, 27b.

  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, while being integrated with the outer peripheral edge of the inner peripheral portion 17a. A cylindrical outer peripheral portion 17f coupled to the outer peripheral portion is fixed in a state of being exposed from the inner peripheral surface of the cylindrical portion 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 cylindrical portion 9b of the driven member 9 and the small diameter ball bearing 35 provided on the outer peripheral surface of the shaft portion 10b of the cam bolt 10. It is rotatably supported by the needle bearing 36 disposed on the axial direction side portion of 35.

  Further, 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 body 14a, electric power is supplied from the inside of the speed reduction mechanism 13. A small-diameter oil seal 38 that prevents leakage of lubricating oil into the motor 12 is provided.

  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 portion of the outer wall portion 4 a. It is mainly composed of a mounting flange 4b integrally formed on the periphery via an inclined peripheral wall 4c and a connector holding portion 28 protruding in the vertical direction from the upper end portion of the outer wall portion 4a.

  Further, the cover member 4 is disposed close to each other so that the entire outer diameter including the mounting flange 4b is larger than the outer diameter of the power feeding plate 17 and substantially covers the power feeding plate 17 and the entire front end of the housing body 14a. Has been.

  The mounting flange 4b has four bosses 4d integrally projecting at substantially equal intervals in the circumferential direction, and each boss 4d has four bolts 29 attached to a chain case 60 described later. A bolt insertion hole 4e to be inserted is formed through. The mounting flange 4b is formed with an annular seal groove 4f on the rear end surface of the motor housing 17 side. In this seal groove 4f, a seal member 33 made of synthetic rubber that seals between the opposing surfaces of the chain case 60 is fitted and fixed.

  As shown in FIGS. 1 to 3, the connector holding portion 28 is formed in a rectangular cross-sectional shape along the vertical direction in the figure, and a holding hole 28 a for holding the power supply connector 34 in the internal axial direction. Is formed penetrating along the vertical direction. Further, on both side portions of the connector holding portion 28, female screw constituent portions 28b, 28b each having a female screw (not shown) formed therein are integrally provided.

  The holding hole 28a is formed in a substantially rectangular shape in cross section, and the lower end opening is disposed above 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.

  The power feeding connector 34 is integrally formed of a synthetic resin material in a rectangular tube shape. As shown in FIGS. 1 and 3, a rectangular tube-like lower end portion 34a is inserted into the holding hole 28a and is held. The terminal 35 is exposed inside an upper end 34b having an elliptic cylindrical shape protruding upward from the hole 28a. A pair of shoulder portions 34c and 34c extending in the left and right directions contacting the upper surface of the connector holding portion 28 are integrally projected on the outer periphery between the lower end portion 34a and the upper end portion 34b. A pair of boss portions 34d and 34d that are in contact with the upper surfaces of the female screw structures 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 constituting portions 28b and 28b are inserted. The power supply connector 34 is fixed to the connector holding portion 28 by the bolts 61, 61.

  The power feeding connector 34 is formed with a pair of holder holes 34e, 34e in the inner axial direction from the lower end surface of the lower end 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.

  Each of the brush holders 36 and 37 is formed in a substantially square shape in cross section by a copper material, and the axial length is slightly longer than the axial length of the holder holes 34e and 34e. The tip portions 36a and 37a slightly protrude from the tip openings of the holder holes 34e and 34e. Also. 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 across the both.

  Further, as shown in FIG. 8, both the brush holders 36 and 37 are disposed so as to be shifted from each other by a predetermined amount in the circumferential direction, and are inclined in the radial direction in the center P direction of the cover member 4. Is arranged.

  For this reason, power supply brushes 39 and 40, which will be described later, slidably held by the brush holders 36 and 37, respectively, are inclined along the radial direction toward the center P direction of the cover member 4 as shown in the figure. The two end portions 36b and 37b are arranged in a substantially V-shape.

  Inside 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.

  The power supply connector 34, the brush holders 36 and 37, and the power supply brushes 39 and 40 constitute a power supply mechanism.

  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 tip end surface 39a and 40a is formed by the spring force of the spring members 41 and 42 to form the slip rings 26 and 27. The outer surface is elastically contacted from the radial direction of the motor housing 14, and one end portion of the pigtail harness 43, 44 inserted through the inside of each coil spring 41, 42 is coupled to each rear end surface. Each of the power supply brushes 39 and 40 is disposed at an upper position in the vertical direction of the motor housing 14 through the holding hole 28a.

  The pigtail harnesses 43 and 44 are formed on a wiring board (not shown) which is molded inside the power feeding connector 34 through a pair of through holes in the retainer 38 on the other end side which is extended in a bent state. They are coupled by soldering or the like and connected to the terminals 35.

  A seal ring 45 is held between the lower surface of the protrusion 34 c of the power supply connector 34 and the upper surface of the connector holding portion 28.

  Further, the cover member 4 is fixed via a bolt 29 having a mounting flange 4b screwed to a female screw 60a of the chain case 60, and an annular surface of the motor housing 14 and an inner peripheral surface of the mounting flange 4b. An oil seal 46, which is a seal member, is interposed between the outer peripheral surface of the protrusion 14f.

  The oil seal 46 is a general one having a substantially U-shaped transverse cross section, and the whole is basically formed of a rubber material, and an inner peripheral portion 46a is formed on the outer peripheral surface of the annular protrusion 14f by a backup spring. While being in elastic contact, the outer peripheral portion is press-fitted and fixed to the inner peripheral surface of the mounting flange 4b via an L-shaped metal retainer 46b. The oil seal 46 adheres to the brushes 39 and 40 and the slip rings 26 and 27 in the direction of the lubricating oil scattered by the rotational drive of the timing chain wound around the gear portion 1 b of the timing sprocket 1. It is designed to suppress this.

  A control current is supplied to the power supply connector 34 from a control unit that controls an engine (not shown). This control unit detects the engine operating state based on information from various sensors such as a crank angle sensor, air flow meter, throttle valve opening sensor, water temperature sensor, oil temperature sensor, cam angle sensor, etc. The fuel injection amount and the like are controlled, and the rotation of the electric motor 12 is controlled by a control current to the power feeding connector 34.

  As shown in FIGS. 1 to 3, the speed reduction mechanism 13 includes the 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. The roller 48 provided on the outer periphery of the bearing 47 and rotatably held in each of the internal teeth 5a of the internal tooth component 5, and allowing radial movement while holding the roller 48 in the rolling direction The retainer 49 and the driven member 9 integrated with the retainer 49 are mainly configured.

  The eccentric shaft portion 37 is formed in a cylindrical shape integrally provided in the large diameter portion 15a of the motor output shaft 15 from the axial direction, and the rotation shaft center of the cam surface 37a formed on the outer peripheral surface is the motor output shaft 15. Is slightly eccentric in the radial direction from the rotational axis.

  The medium-diameter ball bearing 47 is disposed so as to be substantially overlapped at the radial position of the needle bearing 36, and holds a ball interposed between the inner ring, the outer ring, and the two rings, and the ball. And a cage.

  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.

  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 with the eccentric rotation of the eccentric shaft portion 37 through the clearance.

  The retainer 49 is provided integrally with the outer peripheral portion of the fixed end portion 9a, and is bent and formed in a substantially L-shaped cross section from the front end of the outer peripheral portion of the fixed end portion 9a to the front of the fixed end portion 9a. A cylindrical roller holding 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 is provided on the front end side of the outer peripheral portion.

  The roller holding portion 49a extends in the direction of the partition wall 14b through an annular recess-shaped receiving space that is separated by the inner tooth component 5 and the partition wall 14b of the motor housing 14 and the like. A plurality of substantially rectangular roller holding holes for holding the plurality of rollers 48 in a freely rollable manner are formed at substantially equal intervals in the direction. The 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 larger than the total number of teeth of the internal teeth 5a of the internal tooth component 5. Thus, a predetermined reduction ratio is obtained.

Each of the rollers 48 is formed of an iron-based metal, and is fitted into the inner teeth 5a of the inner tooth component 5 while moving in the radial direction along with the eccentric movement of the medium-diameter ball bearing 47. The roller holding hole 41c is oscillated in the radial direction while being guided in the circumferential direction by both side edges.
[Operation of this embodiment]
Hereinafter, the operation of the valve timing control device according to the present embodiment will be briefly described. First, the timing sprocket 1 is rotated through the timing chain in accordance with the rotational drive of the crankshaft of the engine, and the rotational force is the internal tooth component. 5 is transmitted to the motor housing 14 via 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.

  During a predetermined engine operation after the engine is started, the control current from the control unit is energized to the coil 19 of the electric motor 12 via the power supply brushes 39 and 40, the slip rings 26 and 27, and the motor output shaft 15 is turned on. The rotational force is rotationally driven, and the rotational force reduced by the rotational force is transmitted to the camshaft 2 via the speed reduction mechanism 13.

  Thereby, 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 converted to the advance side or the retard side. 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.

  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. Since the slip rings 26 and 27 are elastically contacted from the radial direction of the housing main body 14a, the axial length of the entire apparatus as compared with the case of being provided along the axial direction as in the prior art. Can be made sufficiently short.

  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 to the outer peripheral surface of the cylindrical portion 17a, not the front end surface of the power supply plate 17, and are arranged so as to overlap the straightening brushes 25 (brush holders 23) in the radial direction. Therefore, the axial length of the entire apparatus can be shortened from this point as well.

  Further, since each of the rectifying brushes 25 and each of the slip rings 26 and 27 are electrically connected by using wiring boards 26a and 27a molded inside the power feeding plate 17, wiring is simplified. Manufacturing process becomes easy.

  Further, the 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). In addition, since the metal annular support portion 17c is used for press-fitting and fixing, a strong fixed state can be obtained.

  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. Therefore, the overall weight can be reduced.

  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 17a of the power feeding plate 17, the length of the slip rings 26 and 27 in the circumferential direction is increased. Lengthens. For this reason, it is necessary to increase the axial length of the power supply brushes 39 and 40 in consideration of an increase in the amount of wear between the power supply brushes 39 and 40.

  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.

  Accordingly, since the spring constant of each of the coil springs 41 and 42 can be lowered, the spring load can be lowered. As a result, the sliding resistance is lowered and the occurrence of the wear is sufficiently suppressed. Can be used over a long period of 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, and the slip rings 26 and 27 and the front end surfaces 39a of the power supply brushes 39 and 40, It is arranged at a position one step higher than the sliding position 40a. 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. In addition, since the clearance C between each of 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 moves toward the oil seal 46. It becomes difficult to flow in.

In addition, as shown in FIG. 8, the power supply brushes 39 and 40 are spaced apart from each other at a predetermined distance in the circumferential direction, so that the abrasion powders that are generated and spread with each sliding are spread. There is no contact. 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.

  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.

  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.

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.

  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. Further, the lower end opening of the fixing hole 54 is closed by a plug 57 made of a synthetic resin material, and one end of the brush holder 55 is elastically contacted with the plug 57 so that the power supply brush 40 is attached. A coil spring 56 that biases toward the slip ring 27 is elastically 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 or a pigtail harness (not shown). ing.

  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.

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. As a result, the clearance C between the outer peripheral portion of the annular protrusion 14f and the blocking wall 28b can be further reduced while securing the arrangement of the oil seal 46.

  As described above, by reducing the clearance C and exerting the labyrinth effect, the wear powder generated by the sliding of the slip rings 26 and 27 and the power supply brushes 39 and 40 is reduced by the oil seal 46. Inflow in the direction can be prevented.

  For this reason, since the adhesion of the wear powder to the oil seal 46 can be avoided, 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.

  The present invention is not limited to the configuration of the above-described embodiment. For example, the device can be provided on the exhaust valve side. Further, as the driving rotating body, in addition to the timing sprocket, a timing pulley, etc. It 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.

  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.

  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.

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.

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.

  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.

  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 from the axial direction to the outer peripheral surface of the front end portion of the housing main body.

  As another preferred embodiment, the permanent magnet is fixed to the inner peripheral surface of the housing body.

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.

  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.

  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.

  As another preferable aspect, 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 rotation axis of the drive rotating body.

  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.

  As another preferred aspect, 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.

  As another preferred aspect, the two power supply brushes are displaced from each other by a predetermined angle in the circumferential direction of the motor housing.

  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.

  As another preferred embodiment, the four power supply brushes are displaced from each other by a predetermined angle in the circumferential direction of the motor housing.

  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 rotation axis of the drive rotator.

  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.

Yet another preferred embodiment is an electric motor feeding structure,
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.

1. Timing sprocket (drive rotor)
DESCRIPTION OF SYMBOLS 1a ... Sprocket body 2 ... Camshaft 3 ... Phase change mechanism 4 ... Cover member 4b ... Mounting flange 5 ... Internal tooth component 5a ... Internal tooth 9 ... Drive member (driven rotor)
DESCRIPTION OF SYMBOLS 12 ... Electric motor 13 ... Deceleration mechanism 14 ... Motor housing 14a ... Housing main body 14b ... Partition 14c ... Shaft insertion hole 14d ... Female screw hole 14e ... Cylindrical fixing part 14f ... Annular protrusion 15 ... Motor output shaft 16 ... Permanent magnet 17 ... Power feeding plate (holding member)
17a ... cylindrical portion 17b ... bottom wall 26, 27 ... slip ring 28, 53 ... connector holding portion 28a ... holding hole 28b ... blocking wall 34 ... power feeding connector (power feeding mechanism)
36, 37 ... Brush holder (power feeding mechanism)
39, 40, 50, 51 ... brush for power supply (power supply mechanism)
41, 42 ... coil spring 46 ... oil seal (seal member)

Claims (18)

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: 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. 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.
A valve timing control device for an internal combustion engine, wherein the holding member is provided at a front end portion of the housing body. The valve timing control apparatus for an internal combustion engine according to claim 3,
The holding member includes a cylindrical portion fixed to the housing body from the axial direction, a bottom wall portion integrally provided on the axial front end side of the cylindrical portion, and the commutator brush provided on the inner peripheral side; A valve timing control device for an internal combustion engine, characterized in that a rear end portion of the cylindrical portion is fixed to the housing body. In the valve timing control device for an internal combustion engine according to the item 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. 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. 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. 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. 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 is interposed in a gap between the annular protrusion and the connector and blocks communication between the power supply brush and the seal member. A valve timing control device for an internal combustion engine. 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. 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. 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. 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. The valve timing control apparatus for an internal combustion engine according to claim 1,
The slip rings are arranged in parallel in the axial direction on the outer periphery of the motor housing, while the power supply brushes are provided in a total of four in contact with 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. In the valve timing control device for an internal combustion engine described in the commutator 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. 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 the vertical direction than the rotation shaft of the drive rotator. 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. An electric motor feeding structure,
An electric motor having a motor housing integrally fixed to the drive rotator and rotating 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;
An electric motor feeding structure characterized by comprising: