JP2018017202A - Valve timing control device of internal combustion engine, and speed reduction mechanism of valve timing control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve timing control device of an internal combustion engine capable of reducing change of spring characteristic of a leaf spring by suppressing generation of local abrasion of the leaf spring.SOLUTION: A valve timing control device of an internal combustion engine includes an eccentric shaft portion 39 to which torque is transmitted from an electric motor, an internal tooth constitution portion 5 having a plurality of internal teeth 5a on an inner periphery, a plurality of rollers 48 disposed between the internal teeth and an outer ring 47b of a ball bearing 47 disposed on an outer periphery of the eccentric shaft portion, and a cage 41 for retaining the rollers. A leaf spring 42 for energizing the rollers in a tooth bottom face direction of the internal teeth through an inner ring 47a of the ball bearing is disposed in a recessed portion 40 cut and formed on an outer peripheral face of the eccentric shaft portion, and the whole surface of the leaf spring is coated with an abrasion proof material 44 of tungsten carbide, to suppress abrasion of a circular arc top portion 42a and both end portions 42b, 42c.SELECTED DRAWING: Figure 7

Description

  The present invention relates to a valve timing control device and a speed reduction mechanism for an internal combustion engine that controls opening and closing timings of intake valves and exhaust valves.

  As this type of conventional valve timing control device for an internal combustion engine, for example, there is one described in Patent Document 1 below.

  In this valve timing control device, fluctuating torque is transmitted from the camshaft to the speed reduction mechanism by the driving reaction force of the intake and exhaust valves that open and close during operation. Due to the transmission of the torque, rattling occurs between the plurality of rollers rotatably held by the cage of the speed reduction mechanism and the internal teeth of the internal gear with which the rollers are in rolling contact. As a result, there is a possibility that abnormal noise may occur due to contact between the roller and the internal teeth.

  Therefore, a leaf spring is interposed between the bottom surface of the arc-shaped recess formed in a part of the outer circumferential surface of the eccentric shaft portion of the speed reduction mechanism and the outer circumferential surface of the inner ring, and the action line of the spring force of this leaf spring is Inclination in the circumferential direction of the outer peripheral surface with respect to the eccentric direction line of the outer peripheral surface of the eccentric shaft portion cancels the fluctuating torque and suppresses the generation of abnormal noise.

  That is, the leaf spring is bent in an arc shape, and both end portions in the longitudinal direction are in elastic contact with the bottom surface of the concave portion inward in the radial direction, and the top portion of the arc located at the center in the longitudinal direction is the inner ring. It is elastically contacted radially outward on the inner peripheral surface.

Japanese Patent Laying-Open No. 2016-17417 (see FIG. 1)

  In such a valve timing control device, during the normal drive rotation, the eccentric shaft portion and the inner ring of the bearing rotate integrally by the urging force of the leaf spring, so that the leaf spring and the bottom surface of the recess and the inner circumference of the inner ring are rotated. There is little sliding between the surfaces.

  However, for example, when the rotation of the motor output shaft is switched from one direction of rotation to the other direction, or when the motor output shaft suddenly stops from one direction of rotation, the bottom surfaces of both ends of the leaf spring and the recesses The sliding occurs by the inertial force in the rotating direction between the bottom surface of the plate and the top outer surface of the leaf spring and the inner peripheral surface of the inner ring. For this reason, the leaf spring is partially worn, and there is a possibility that the influence on the spring load characteristic is increased, and the durability may be lowered.

  An object of the present invention is to provide a valve timing control device and a speed reduction mechanism for an internal combustion engine that can suppress wear of an urging member and reduce the influence of spring load characteristics to improve the durability of the urging member. It is said.

The invention according to claim 1 of the present invention is, in particular, a recess formed on the outer peripheral surface of the eccentric rotating body or the inner peripheral surface of the bearing, and the rolling element is housed in the recess and the rolling element is inserted through the bearing. An urging member for urging the tooth bottom surface direction,
The urging member has a wear-resistant material at least in a portion that contacts the bottom surface of the recess and a portion that contacts the inner peripheral surface of the bearing.

  According to this invention, the influence of the spring load characteristic of the urging member can be suppressed, and the durability of the urging member can be improved.

1 is a longitudinal sectional view showing an embodiment of a valve timing control device for an internal combustion engine according to the present invention. It is a disassembled perspective view which shows the main structural members in this embodiment. It is the sectional view on the AA line of FIG. It is the BB sectional view taken on the line of FIG. It is CC sectional view taken on the line of FIG. It is the D section enlarged view enclosed with the dashed-dotted line of FIG. It is the E section enlarged view enclosed with the dashed-dotted line of FIG. The leaf | plate spring with which this embodiment is provided is shown, A is an overhead view of a leaf | plate spring, B is a side view. FIG. 4 is an enlarged view of a portion F surrounded by a dashed line in FIG. 3. It is an expanded sectional view which shows the expansion-contraction state of the recessed groove formed in the bottom face of the recessed part with which this embodiment is provided, and the one end part of a leaf | plate spring. The leaf | plate spring with which 2nd Embodiment is provided, and the coating area | region of the abrasion-resistant material with respect to this leaf | plate spring are shown, A is a top view of a leaf | plate spring, B is a side view, C is a bottom view.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of a valve timing control device and a speed reduction mechanism for an internal combustion engine according to the present invention will be described with reference to the drawings. In this embodiment, the present invention is applied to the intake valve side of the engine.

  As shown in FIGS. 1 and 2, the valve timing control device is rotatable on a timing sprocket 1 that is a driving rotating body that is rotationally driven by a crankshaft of an internal combustion engine, and a cylinder head 01 via a bearing portion 02. The camshaft 2 that is supported and rotated by the rotational force transmitted from the timing sprocket 1, the cover member 3 disposed at the front position of the timing sprocket 1, and the timing sprocket 1 and the camshaft 2 are disposed, And a phase changing mechanism 4 that changes the relative rotational phases of both 1 and 2 in accordance with the engine operating state.

  The timing sprocket 1 is entirely formed of a ferrous metal in a cylindrical shape, and the inner peripheral surface is integrally provided on the outer periphery of the sprocket main body 1a and the sprocket main body 1a. The gear part 1b which receives the rotational force from a crankshaft via this timing chain, and the internal-tooth structure part 5 provided integrally continuously by the front-end side of the said sprocket main body 1a are comprised.

  In addition, a single large-diameter ball bearing 43 is interposed between the sprocket body 1a of the timing sprocket 1 and a driven member 9 which is a driven rotating body (described later) provided at the front end of the camshaft 2. Yes. The large-diameter ball bearing 43 supports the timing sprocket 1 and the camshaft 2 so as to be relatively rotatable.

  The large-diameter ball bearing 43 includes an outer ring 43a, an inner ring 43b, and a ball 43c interposed between the wheels 43a and 43b. The outer ring 43a is fixed to the inner peripheral side of the sprocket body 1a, while the inner ring 43b is fixed to the outer peripheral side of the driven member 9.

  The sprocket body 1a has an annular groove-shaped outer ring fixing portion 1d opened on the camshaft 2 side on the inner peripheral side. Bolt insertion holes 1c are formed in the outer peripheral portion of the sprocket body 1a (internal tooth constituent portion 5) at substantially equal intervals in the circumferential direction.

  The internal tooth component 5 is integrally provided on the outer peripheral side of the front end portion of the sprocket body 1a, is formed in a cylindrical shape extending forward, and has a plurality of corrugated internal teeth 5a on the inner periphery. Is formed.

  Further, a motor housing 12 to be described later is disposed opposite to the front end side of the internal tooth component 5 from the axial direction. In the motor housing 12, six female screw holes 12e corresponding to the bolt insertion holes 1c are formed at equal intervals in the circumferential direction of the rear end portion on the inner tooth constituent portion 5 side.

  Furthermore, an annular holding plate 61 is disposed at the rear end portion of the sprocket body 1a opposite to the internal tooth constituent portion 5. The holding plate 61 is integrally formed of a metal plate material. As shown in FIG. 1, the outer diameter is set to be substantially the same as the outer diameter of the sprocket body 1 a and the inner diameter is the same as that of the large-diameter ball bearing 43. The diameter is set smaller than the inner diameter of the outer ring 43a. Further, a stopper convex portion 61b protruding inward in the radial direction, that is, in the central axis direction is integrally provided at a predetermined position on the inner peripheral edge of the inner peripheral portion 61a.

  As shown in FIGS. 1 and 4, the stopper convex portion 61b is formed in a substantially fan shape, and the tip edge 61c is formed in an arc shape along an arc-shaped inner peripheral surface of a stopper concave portion 2b described later. Furthermore, six bolt insertion holes 61d are formed at equal circumferential positions at positions corresponding to the bolt insertion holes 1c of the sprocket body 1a on the outer peripheral portion of the holding plate 61.

  The sprocket body 1a, the internal tooth component 5, the holding plate 61, and the motor housing 12 are set to have substantially the same outer diameter, and are inserted through the bolt insertion holes 1c, 61d and the female screw hole 12e. The bolts 7 are screwed together and fixed together.

  The sprocket body 1a and the internal tooth component 5 are configured as a casing for a speed reduction mechanism 15 described later.

  The camshaft 2 has two egg-shaped drive cams per cylinder for opening an intake valve (not shown) on the outer periphery, and a flange portion 2a is integrally provided at the front end.

  As shown in FIG. 1, the flange portion 2a is set to be slightly larger than the outer diameter of the fixed end portion 9a of the driven member 9 which is a driven rotating body to be described later, and after assembling each component, The outer peripheral portion of the front end surface is arranged in contact with the outer end surface in the axial direction of the inner ring 43 b of the large-diameter ball bearing 43. Further, the front end surface of the flange portion 2a is coupled from the axial direction by the cam bolt 10 in a state in which the front end surface is in contact with the driven member 9 from the axial direction.

  Further, as shown in FIG. 4, a stopper recess 2 b into which the stopper protrusion 61 b of the holding plate 61 is engaged is formed on the outer periphery of the flange portion 2 a along the circumferential direction. The stopper recess 2b is formed in an arc shape having a predetermined length in the circumferential direction, and both end edges of the stopper projection 61b rotated within the arc length range abut against the circumferential opposite edges 2c and 2d, respectively. Thus, the relative rotational position of the camshaft 2 on the maximum advance angle side or the maximum retard angle side with respect to the timing sprocket 1 is regulated.

  The stopper convex portion 61b and the stopper concave portion 2b constitute a stopper mechanism.

  As shown in FIGS. 1 and 2, the cover member 3 is integrally formed in a cup shape with, for example, an aluminum alloy material that is a metal material, and is disposed so as to cover the front end portion of the motor housing 12. The cover member 3 includes a bulging cover main body 3a and an annular mounting flange 3b integrally formed on the outer peripheral edge on the opening side of the cover main body 3a. A cylindrical wall 3c is integrally formed along the axial direction on the outer peripheral side of the cover body 3a. The cylindrical wall 3c has a holding hole 3d formed therein, and a part of a holding body 28 to be described later is fitted and held on the inner peripheral surface of the holding hole 3d.

  As shown in FIGS. 1 and 2, the mounting flange 3b is provided with four boss portions 3e at substantially equal intervals in the circumferential direction (approximately 90 ° positions). Each boss portion 3e has bolt insertion holes 3f through which bolts 54 to be screwed into the respective female screw holes 49c in the plurality of boss portions 49b formed at four locations in the circumferential direction of the annular wall 49a of the chain cover 49 are inserted. It is formed through. The cover member 3 is fixed to the chain cover 49 by the bolts 54.

  A large-diameter oil seal 50 is interposed between the inner peripheral surface of the stepped portion on the outer peripheral side of the cover body 3 a and the outer peripheral surface of the motor housing 12. The large-diameter oil seal 50 is formed in a substantially U-shaped cross section, a core metal is embedded in a synthetic rubber base material, and an annular base 50a on the outer peripheral side is formed in the cover member 3. It is fitted and fixed to a stepped annular portion provided on the peripheral surface. Further, the inner peripheral seal portion 50b is slidably elastically contacted with the outer peripheral surface of the motor housing 12 via a backup spring.

  As shown in FIG. 1, the chain cover 49 is disposed and fixed along the vertical direction so as to cover the cylinder head 01 and the chain outside the figure wound around the timing sprocket 1 on the front end side of the cylinder block outside the figure. Has been.

  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 The cylindrical portion 9b protrudes in the axial direction from the inner peripheral front end face of the end portion 9a.

  The fixed end portion 9 a has a rear end surface disposed in contact with a front end surface of the flange portion 2 a of the camshaft 2, and is integrally joined to the flange portion 2 a by axial contact with the flange portion 2 a by the axial force of the cam bolt 10. Yes.

  In addition, a holder 41 described later, which is a cylindrical holding member that holds the plurality of rollers 48, is integrally provided on the outer peripheral portion of the fixed end portion 9a.

  As shown in FIG. 1, the cylindrical portion 9b is formed with a through hole 9c through which the shaft portion 10b of the cam bolt 10 is inserted, and a bearing member (second bearing) on the outer peripheral side. A needle bearing 38 is provided.

  As shown in FIG. 1, the cam bolt 10 has an end surface of the head 10a that abuts and supports the inner ring of the small-diameter ball bearing 37 from the axial direction, and an outer periphery of the shaft portion 10b from the end of the camshaft 2. A male screw portion 10c is formed to be screwed into a female screw hole 2e formed in the inner axial direction.

  Further, between the outer peripheral portion of the fixed end portion 9a and the bottom side coupling portion of the retainer 41, an inner ring fixing portion 63 in which the inner ring 43b of the large-diameter ball bearing 43 is press-fitted and fixed while performing axial positioning. Is notched.

  The phase change mechanism 4 includes the electric motor 8 disposed on the front end side of the cylindrical portion 9b of the driven member 9, and the speed reduction mechanism 15 that reduces the rotational speed of the electric motor 8 and transmits it to the camshaft 2. , Mainly consists of.

  As shown in FIGS. 1 and 2, the electric motor 8 is a brushed DC motor, the motor housing 12 being a yoke that rotates integrally with the timing sprocket 1, and the motor housing 12. A motor output shaft 13 that is rotatably provided, four arc-shaped permanent magnets 14 that are stators fixed to the inner peripheral surface of the motor housing 12, and a sealing plate 11 that seals the front end opening of the motor housing 12. And.

  As shown in FIG. 1, the motor housing 12 includes a cylindrical housing body 12a formed of a ferrous metal material in a bottomed cylindrical shape by press molding, and a partition wall integrally formed on the rear end side of the housing body 12a. 12b.

  The partition wall 12b is formed with a large-diameter shaft insertion hole 12c through which an eccentric shaft portion 39, which will be described later, is inserted at a substantially central position, and in the axial direction of the camshaft 2 at the hole edge of the shaft insertion hole 12c. A protruding cylindrical extending portion 12d is integrally provided.

  The sealing plate 11 is composed of a central metal plate 11a and a non-magnetic material 11b made of synthetic resin on both sides of the metal plate 11a.

  The motor output shaft 13 is formed in a stepped cylindrical shape and functions as an armature, and a large-diameter portion 13a on the camshaft 2 side and a cover member 3 side via a stepped portion 13c formed at a substantially central position in the axial direction. The small-diameter portion 13b. The large-diameter portion 13a has an iron core rotor 17 press-fitted and fixed to the outer periphery, and an eccentric shaft portion 39 that is an eccentric rotating body constituting a part of the speed reduction mechanism 15 is integrally provided on the rear end side. The bearings 37 and 38 are provided on the inner periphery of the large diameter portion 13a.

  On the other hand, the small-diameter portion 13 b has an annular member 20 made of a synthetic resin material fixed to the outer periphery, and a commutator 21 fixed to the outer peripheral surface of the annular member 20 from the axial direction. The annular member 20 and the commutator 21 are positioned in the axial direction by the step portion 13c. The annular member 20 has an outer diameter that is substantially the same as the outer diameter of the large-diameter portion 13a, and an axial length that is slightly shorter than the small-diameter portion 13b.

  A stopper 55 is press-fitted and fixed to the inner periphery of the small diameter portion 13b. The plug body 55 is supplied into the motor output shaft 13 and the eccentric shaft portion 39 so that lubricating oil for lubricating the bearings 37 and 38 is applied to the slip rings 26a and 26b and the power supply brushes 30a and 30b. Regulations are made so that it does not flow.

  The iron core rotor 17 is formed of a magnetic material having a plurality of magnetic poles, and the outer peripheral side is configured as a bobbin having a slot around which the coil wire of the coil 18 is wound.

  On the other hand, the commutator 21 is formed in an annular shape by a conductive material, and the end of the coil wire from which the coil 18 is drawn is electrically connected to each segment divided into the same number as the number of poles of the iron core rotor 17. ing.

  The permanent magnet 14 is formed in a cylindrical shape as a whole and has a plurality of magnetic poles in the circumferential direction, and its axial position is offset from the fixed position of the iron core rotor 17. .

  As shown in FIG. 5, the sealing plate 11 is slidable along the radial direction inside a pair of resin holders 23a and 23b provided on the nonmagnetic material 11b and inside the resin holders 23a and 23b. A pair of first brushes 25a and 212b, which are switching brushes that are accommodated and arranged so that each tip surface elastically contacts the outer peripheral surface of the commutator 21 from the radial direction by the spring force of the coil springs 24a and 24b, and the resin holder 23a, The inner and outer double annular power supply slip rings 26a and 26b, embedded and fixed to the front end surface of the outer end surface of the front end surface 23b, the first brushes 25a and 212b, and the slip rings 26a and 26b. Pigtail harnesses 27a and 27b that are electrically connected to each other.

  The sealing plate 11 is positioned and fixed by caulking the outer peripheral portion of the metal plate 11a to the concave stepped portion formed on the inner periphery of the front end portion of the motor housing 12, and at the center position, one end of the motor output shaft 13 is fixed. A shaft insertion hole 11c through which a portion and the like are inserted is formed through.

  A holding body 28 that is integrally molded with a synthetic resin material is attached to the cover body 3a. As shown in FIGS. 1 and 2, the holding body 28 is formed in a substantially L shape in a side view, and has a substantially cylindrical brush holding portion 28a inserted into the holding hole 3d, and the brush holding portion 28a. A pair of a connector portion 28b at the upper end portion, a bracket portion 28c that is integrally projected on one side surface of the brush holding portion 28a and bolted to the cover body 3a, and a large portion embedded therein. It is mainly composed of power supply terminal pieces 29 and 29.

  The brush holding portion 28a extends in a substantially horizontal direction (axial direction), and is a pair of bottomed cylindrical shapes formed in parallel with the internal vertical position (inner and outer peripheral sides with respect to the axis of the motor housing 12). A pair of rectangular tube-shaped brush holders 31a and 31b are fixed in the fixing holes.

  Also, in each brush holder 31a, 31b, a pair of power supply brushes 30a, 30b whose tip surfaces are in contact with the power supply slip rings 26a, 26b from the axial direction are slidably held in the axial direction. Has been.

  Each of the power supply brushes 30a and 30b is formed in a rectangular tube shape and set to a predetermined axial length, and constitutes a part of the power supply mechanism together with the power supply slip rings 26a and 26b. .

  The bottom wall located on the bottom side of the pair of fixing holes is formed with through holes (not shown) through which pigtail harnesses, which will be described later, are inserted, and on the outside of the bottom walls, A space S where the through hole faces is formed. The space S is liquid-tightly closed by a circular cap 36 whose one end opening in the axial direction is formed of the same synthetic resin material as the holding body 28.

  The pair of power supply terminal pieces 29, 29 are formed in a parallel and crank shape along the vertical direction, and the terminals 29a, 29a on one side (lower end side) are arranged in an exposed state on the outer surface of the bottom wall. On the other hand, the terminals 29b and 29b on the other side (upper end side) protrude from the female fitting grooves 28d of the connector portion 28b. The other side terminals 29b and 29b are connected to a control unit (not shown) via a female terminal (not shown) and a harness.

  As shown in FIGS. 1 and 2, each of the power supply brushes 30 a and 30 b is formed in a substantially rectangular shape, and is formed between each rear end surface and a hole edge of each fixing hole, that is, an inner surface of the bottom wall. It is urged | biased by the direction of each said slip ring 26a, 26b by the spring force of a pair of 2nd coil spring 33a, 33b elastically mounted between, respectively.

  The rear ends of the power supply brushes 30a and 30b and the one side terminals 29a and 29a are electrically connected by a pair of pigtail harnesses (not shown) that can be flexibly deformed.

  A sealing member 34 that seals between the inner peripheral surface of the cylindrical wall 3c and the brush holding portion 28a is held in an annular fitting groove formed on the base side outer periphery of the brush holding portion 28a.

  As shown in FIG. 2, the bracket portion 28 c has a bolt insertion hole 28 e formed at a substantially central position. Bolts to be screwed into female screw holes (not shown) formed in the cover body 3a are inserted into the bolt insertion holes 28e so that the entire holding body 28 is attached to the cover body 3a.

  The motor output shaft 13 and the eccentric shaft portion 39 include a small-diameter ball bearing 37 fixed to the outer peripheral surface of an annular groove formed on the distal end side of the outer peripheral surface of the cylindrical portion 9 b of the driven member 9, and the small-diameter ball bearing 37. And the needle bearing 38 disposed on the side in the axial direction is rotatably supported by the cylindrical portion 9b of the driven member 9.

  As shown in FIG. 6, the needle bearing 38 includes a cylindrical retainer 38a press-fitted into the inner peripheral surface of the eccentric shaft portion 39, and a plurality of needle rollers 38b rotatably held in the retainer 38a. And is composed of. The needle roller 38 b rolls on the outer peripheral surface of the cylindrical portion 9 b of the driven member 9.

  Further, between the outer peripheral surface of the large diameter portion 13 a of the motor output shaft 13 and the inner peripheral surface of the extending portion 12 d of the motor housing 12, the inside of the electric motor 8 (motor housing 12) from the inside of the speed reduction mechanism 15. A small-diameter oil seal 46 is provided to prevent the lubricating oil from flowing into.

  The control unit detects the current engine operating state based on information signals from various sensors such as a crank angle sensor, an air flow meter, a water temperature sensor, and an accelerator opening sensor (not shown), and performs engine control. The coil 18 is energized to control the rotation of the motor output shaft 13, and the relative rotation phase of the camshaft 2 with respect to the timing sprocket 1 is controlled via the speed reduction mechanism 15.

  As shown in FIGS. 1 to 3, the speed reduction mechanism 15 is provided on an outer periphery of the eccentric shaft portion 39 and an eccentric shaft portion 39 that is a cylindrical eccentric rotor that is an eccentric rotor that performs an eccentric rotational motion. A medium-diameter ball bearing 47 which is a bearing, a plurality of rollers 48 which are provided on the outer periphery of the medium-diameter ball bearing 47, and a radial movement while holding the rollers 48 in the rolling direction. The cage 41 is mainly composed of the cage 41 to be allowed and the driven member 9 integrated with the cage 41.

  The eccentric shaft portion 39 is formed of a hardened steel material, and as shown in FIGS. 1 and 3, is integrally extended from the outer end edge of the large-diameter portion 13a of the motor output shaft 13 and has an outer diameter. Is formed to have substantially the same size as the outer diameter of the large-diameter portion 13a of the motor output shaft 13, and an annular groove-shaped cam surface 39a is formed on the outer peripheral surface.

  As shown in FIG. 3, the cam surface 39a has a circumferential thickness that changes so that the shaft center Y of the outer diameter is slightly eccentric from the axis X of the motor output shaft 13 in the radial direction. A recess 40 is formed on the outer surface of the maximum thickness portion on the opposite side in the radial direction from the thickness portion 39c.

  As shown in FIGS. 1 and 3, the medium-diameter ball bearing 47 includes an inner ring 47a, and an outer ring 47b and a ball 47c interposed between the two wheels 47a and 47b. Are disposed so as to substantially overlap each other at the radial position.

  As shown in FIGS. 1 and 6, the inner ring 47a has a clearance of about 0.1 mm on the recess 40 side without the inner peripheral surface 47d being press-fitted into the outer peripheral surface of the cam surface 39a of the eccentric shaft portion 39. Opposing with a certain minute gap C, the spring force of the leaf spring 42 is secured by this. The inner ring 47a has a front end abutting against a step edge 39b between the motor output shaft 13 and the large diameter portion 13a, while a rear end edge is fitted and fixed to the front end side of the cam surface 39a. Abutting on the ring 53, in combination with the step edge 39b, the axial positioning is performed, and the escape from the cam surface 39a is restricted.

  On the other hand, the outer ring 47b is in a free state without being fixed in the axial direction. That is, in the outer ring 47b, one end surface on the side of the electric motor 8 in the axial direction does not come into contact with any part, and the other end surface in the axial direction is between the inner side surface of the retainer 41 facing this. One gap C1 is formed and is in a free state. Further, the outer peripheral surface of each of the rollers 48 is in contact with the outer peripheral surface of the outer ring 47b so as to be able to roll, and on the outer peripheral side of the outer ring 47b, as shown in FIG. C2 is formed, and the entire medium-diameter ball bearing 47 can move in the radial direction along with the eccentric rotation of the eccentric shaft portion 39, that is, can move eccentrically by the second gap C2.

  As shown in FIG. 6, the outer diameter of the outer ring 47b of the ball bearing 47 is set to be substantially the same as the outer diameter of the outer ring of the conventional ordinary ball bearing. The wall thickness t is usually set larger than the wall thickness in the radial direction of the inner ring of a general ball bearing. Accordingly, the inner ring thickness t is set to be larger than the radial thickness t1 of the outer ring 47b.

  Therefore, since the outer diameter of the inner ring 47a is inevitably larger than usual, the number of the balls 47c is larger than the number of balls of the ordinary ball bearing. As a result, the surface pressure with respect to the entire ball 47c is lowered, and the durability can be improved.

  A leaf spring 42 as a biasing member (spring member) is accommodated in the recess 40 of the eccentric shaft portion 39.

  More specifically, as shown in FIGS. 6 and 7, the concave portion 40 is formed by cutting the outer peripheral portion of the maximum thickness portion of the eccentric shaft portion 39 into a rectangular shape along the tangential direction and cutting the longitudinal section D-cut. The bottom surface 40a is formed in a flat shape.

  Further, as shown in FIG. 6, the recess 40 is formed such that the width W in the width direction is smaller than the width W1 of the outer ring 47b of the medium-diameter ball bearing 47, and the width side of the outer ring 47b. In other words, it is formed in a region inside the both end edges of the outer ring 47b.

  As shown in FIGS. 7 and 8A and B, the leaf spring 42 is formed by bending a substantially rectangular stainless steel plate into an arc shape, and has an arc apex portion 42a having a central position in the longitudinal direction, and the arc apex portion 42a. And both end portions 42b and 42c extending in the left-right direction.

  The arcuate top portion 42a protrudes outward in a maximum arcuate shape, and the outer surface is disposed close to the inner circumferential surface 47d of the inner ring 47a in the radially outward direction.

  On the other hand, the both end portions 42b and 42c are bent in a small arc shape that is bent outward, and the lower surfaces thereof are in elastic contact with the bottom surface 40a of the recess 40.

  That is, as shown in FIG. 7, in a state where the leaf spring 42 is set in the recess 40, the lower end edges 42d and 42e of the both end portions 42b and 42c are formed on the both end surfaces 40b and 40c of the bottom surface 40a of the recess 40, respectively. Elastic contact with line contact. On the other hand, the top portion 42 a is in elastic contact with the inner peripheral surface 47 d of the inner ring 47 a of the medium diameter ball bearing 47. That is, in a state where the leaf spring 42 is set in the recess 40, both end portions 42b and 42c are in elastic contact with both end surfaces 40b and 40c of the recess bottom surface 40a, and the top portion 42a is also an inner peripheral surface of the inner ring 47a of the ball bearing 47. The spring load in the opposite direction acts by elastic contact with 47d and a spring load is applied. Due to this spring load, the eccentric shaft portion 39 and the inner ring 47a of the ball bearing 47 are elastically integrated.

  The leaf spring 42 is formed such that the length L in the longitudinal direction is sufficiently smaller than the length of the recess 40, and allows elastic deformation in the recess 40 in a freely extending and contracting direction. When this elastic deformation, that is, when it is freely expanded and contracted in the longitudinal direction, the lower end edges 42d and 42e of both end portions 42b and 42c usually slide to the left and right on the bottom surface 40a of the recess 40 with the top portion 42a as the center. Yes.

  The leaf spring 42 is formed with a width W3 slightly smaller than the width W of the recess 40, and both side edges 42f and 42g of the leaf spring 42 in the width direction of the recess 40 are also elastically deformed in its own expansion / contraction direction. It is formed so as not to interfere with the opposed inner surfaces.

  The plate spring 42 is coated with a wear resistant material 44 on the entire surface. For example, tungsten carbide (tungsten carbide), which is one of cemented carbides, is used as the wear resistant material 44, which is a mixture of tungsten carbide WC and cobalt Co, which is a binder, and sintered. . The wear-resistant material 44 is somewhat flexible while ensuring high hardness, and therefore does not affect the free elastic deformation action of the leaf spring 42.

  Further, the hardness of the wear resistant material 44 is higher than the hardness of the inner ring 47 a and the eccentric shaft portion 39 of the ball bearing 47.

  Further, the plate spring 42 is formed with a small surface roughness by coating the entire surface with the wear resistant material 44. For this reason, as will be described later, the leaf spring 42 is formed between the upper end edge of the top portion 42a and the inner peripheral surface 47d of the inner ring 47a, the lower end edges 42d and 42e of both end portions 42b and 42c, and the bottom surface 40a of the recess 40. The slidability during is improved.

  As shown in FIGS. 1 and 6, the retainer 41 is bent in a substantially L-shaped cross section forward from the front end of the outer peripheral portion of the fixed end portion 9a and protrudes in the same direction as the cylindrical portion 9b. It is formed in a bottom cylindrical shape.

  The cylindrical tip 41a of the retainer 41 extends in the direction of the partition wall 12b of the housing main body 12a through an annular concave storage space S1 formed between the retainer 41 and the partition wall 12b. In addition, as shown in FIGS. 1 to 3, a plurality of substantially rectangular roller holders that hold the plurality of rollers 48 so as to roll freely are provided at substantially equal intervals in the circumferential direction of the cylindrical tip portion 41 a. A plurality of holes 41b are formed at equally spaced positions in the circumferential direction.

  The roller holding holes 41b are configured to restrict the circumferential movement of the rollers 48 while allowing the rollers 48 to move in the radial direction. One less than the total number of teeth of the inner teeth 5a.

  Each of the rollers 48 is formed of an iron-based metal, and is fitted into the inner teeth 5a of the inner tooth component 5 while moving in the radial direction along with the eccentric movement of the medium-diameter ball bearing 47. The roller holding hole 41b is caused to swing in the radial direction while being guided in the circumferential direction by both side edges.

  Further, when each roller 48 is set in the roller holding hole 41b of the retainer 41 and set between each inner tooth 5a of the inner tooth component 5 and the outer ring 47b of the medium-diameter ball bearing 47 As shown in FIG. 9, a minute radial clearance C3 is formed between the outer surface of the roller 48 and the inner surface of the inner tooth 5a, and one of the outer surface of the roller 48 and the roller holding hole 41b facing each other. A small cage clearance C4 is formed between the side surface 41c. These clearances C3 and C4 are necessary for ensuring the operation responsiveness of the roller 48 at the initial rolling when the speed reduction mechanism 15 is converting.

  Further, the radial clearance C3 (backlash) is set smaller than the minute gap C between the cam surface 39a of the eccentric shaft portion 39 and the inner peripheral surface of the inner ring 47a, and is caused by the spring force of the leaf spring 42. The radial clearance C3 (backlash) can be absorbed.

  Inside the casing of the speed reduction mechanism 15 is formed inside the bearing portion 02 of the cylinder head 01, and the camshaft 2 is connected to the camshaft 2 from an oil supply passage (not shown) through which lubricating oil is supplied from a main oil gallery (not shown). Lubricating oil is supplied to the inside from an oil supply hole 51 formed in the inner axial direction and the small diameter oil hole 52 opened in the vicinity of the needle bearing 38 and the medium diameter ball bearing 47 ( 1 and 6).

By this lubricating oil supply means, lubricating oil is supplied and stays in the accommodation space S1, from which the medium diameter ball bearing 47 and each roller 48 are lubricated, and further, the eccentric shaft portion 39 and the motor output shaft 13 It flows into the interior and is used to lubricate movable parts such as the needle bearing 38, the small-diameter ball bearing 37, and the medium-diameter ball bearing 47. The lubricating oil staying in the accommodation space S is prevented from leaking into the motor housing 12 by the small diameter oil seal 46.
[Operation of this embodiment]
First, when the crankshaft of the engine is rotationally driven, the timing sprocket 1 is rotated via the timing chain, and the rotational force is synchronously rotated by the motor housing 12, that is, the electric motor 8, via the internal gear component 5. On the other hand, the rotational force of the internal tooth component 5 is transmitted from each roller 48 to the camshaft 2 via the cage 41 and the driven member 9. As a result, each drive cam of the camshaft 2 opens and closes each intake valve via the spring force of the valve spring.

  When a predetermined engine is operated after the engine is started, the coil 18 of the electric motor 8 is supplied from the control unit through the terminal pieces 29 and 29, the pigtail harness, the power supply brushes 30a and 30b, the slip rings 26a and 26b, and the like. Is energized. As a result, the motor output shaft 13 is rotationally driven, and the rotational force of this rotational force is transmitted to the camshaft 2 via the speed reduction mechanism 15.

  That is, when the eccentric shaft portion 39 rotates eccentrically with the rotation of the motor output shaft 13, each roller 48 is guided in the radial direction by each roller holding hole 41b of the retainer 41 for each rotation of the motor output shaft 13. It moves over one internal tooth 5a of the internal tooth component 5 while rolling to another adjacent internal tooth 5a. Rolling contact is made in the circumferential direction while repeating this in sequence. By the rolling contact of the rollers 48, the rotation of the motor output shaft 13 is decelerated and the rotational force is transmitted to the driven member 9. The reduction ratio at this time can be arbitrarily set according to the number of rollers 48 or the like.

  As a result, the camshaft 2 rotates forward and backward relative to the timing sprocket 1 to convert the relative rotational phase. As a result, the opening / closing timing of each intake valve is controlled to be advanced or retarded.

  The maximum position restriction (angular position restriction) of forward and reverse relative rotation of the camshaft 2 with respect to the timing sprocket 1 is such that each side surface of the stopper convex portion 61b is in contact with one of the opposing edges 2c and 2d of the stopper concave portion 2b. It is done by touching.

  That is, the driven member 9 rotates in the same direction as the rotation direction of the timing sprocket 1 as the eccentric shaft portion 39 rotates eccentrically, so that one side surface of the stopper convex portion 61b is on one side of the stopper concave portion 2b. Further rotation in the same direction is restricted by contacting the opposite edge 2c. As a result, the relative rotation phase of the camshaft 2 with respect to the timing sprocket 1 is changed to the maximum on the advance side.

  On the other hand, when the driven member 9 rotates in the direction opposite to the rotation direction of the timing sprocket 1, the other side surface of the stopper convex portion 61b comes into contact with the opposite surface 2d on the other side of the stopper concave portion 2b and further in the same direction. Rotation is regulated. As a result, the relative rotation phase of the camshaft 2 with respect to the timing sprocket 1 is changed to the maximum on the retard side.

  As a result, the opening / closing timing of the intake valve is converted to the maximum on the advance side or the retard side, and the fuel efficiency and output of the engine can be improved.

  In the present embodiment, when the eccentric shaft portion 39 rotates with the rotation of the motor output shaft 13 of the electric motor 8, the spring force of the leaf spring 42 positioned at the maximum thickness portion via the recess 40. The entire ball bearing 47 is pressed in the radial direction while elastically contacting the inner peripheral surface of the inner ring 47a of the medium diameter ball bearing 47 in the radial direction. As a result, the roller 48 is pushed up in the direction of the thick arrow shown in FIG. 9 to reduce the radial clearance C3 (backlash).

  By reducing the radial clearance C3, it becomes possible to reduce the clearance C4 in the rotational direction, and strong interference between the roller 48 and the inner surface of the inner tooth 5a is suppressed, thereby sufficiently reducing the occurrence of vibration and sound. It becomes possible to make it. As a result, it is possible to suppress deterioration of the quality of the valve timing control device.

  The clearances C3 and C4 are reduced by the spring force of the leaf spring 42. However, the clearances C3 and C4 are not structurally reduced (narrow) but reduced by the elastic force of the leaf spring 42. There is no effect on operating response.

  Since the top portion 42a of the leaf spring 42 elastically contacts the inner peripheral surface 47d of the inner ring 47a, the corresponding contact is automatically aligned to the longest distance portion between the recess 40 and the inner ring 47a.

Further, since the leaf spring 42 can be elastically deformed freely in the direction of expansion and contraction in the recess 40 during elastic deformation, it can slide freely along both flat end surfaces 40b and 40c of the bottom surface 40a of the recess 40. Since it moves, a stable spring load is obtained. In particular, since the surface roughness is reduced by the wear-resistant material 44 formed on the surface of the plate spring 42, the slidability with respect to the bottom surface 40a of both end portions 42b and 42c of the plate spring 42 is improved. As a result, the leaf spring 42, in combination with the flexibility of the wear-resistant material 44, further improves the elastic deformation action in the expansion / contraction direction, and appropriate spring characteristics are obtained.

Since the expansion / contraction deformation action of the leaf spring 42 becomes smooth, a rapid change in the spring load on the leaf spring 42 is suppressed, and a stable spring load can be applied.

  In this way, the plate spring 42 can be easily returned to the normal position by the good expansion and contraction action, so that appropriate spring characteristics can be obtained at all times.

  In addition, since the wear resistant material 44 is formed on the entire surface of the leaf spring 42, the entire length of the leaf spring 42 in the longitudinal direction when it is stretched or deformed, or when the eccentric shaft 39 is suddenly stopped or forward / reversely converted. The occurrence of wear on the lower end edges 42d and 42e of the both end portions 42b and 42c and the upper end edge of the arcuate peak portion 42a can be sufficiently suppressed.

  That is, when the leaf spring 42 expands or contracts or moves relatively, the lower end edges 42d and 42e of the both end portions 42b and 42c slide slightly on the both end surfaces 40b and 42c of the bottom surface 40a, and the arc top portion 42a Although the upper end edge slightly slides on the inner peripheral surface 47d of the inner ring 47a, if these are repeated, partial wear may occur over time, and the spring characteristics may change and the required load may not be satisfied.

  However, since the wear-resistant material 44 is formed on the entire surface of the leaf spring 42 as in this embodiment, partial wear can be effectively suppressed, so that changes in spring characteristics are suppressed over a long period of time. The required load can be satisfied. As a result, the clearances C3 and C4 described above can be reduced, so that the occurrence of vibration and sound during driving can be effectively reduced. Further, the durability of the leaf spring 42 itself is also improved.

  Further, the wear-resistant material 44 has a hardness greater than that of the eccentric shaft portion 39. Therefore, as described above, when the leaf spring 42 is repeatedly expanded and contracted, the both end portions 42b and 42c slide on the both end surfaces 40b and 40c of the recess bottom surface 40a as shown in FIG. In the both end faces 40b, 40c, both end portions 42b, 42c are greatly extended (one-dot chain line), and the portion where the maximum load is applied is worn away to form concave grooves 45, 45 of about 30 μm, for example.

  Therefore, when the leaf spring 42 is extended and deformed, the bent portions of the both end portions 42b and 42c are engaged with the recessed grooves 45 and 45, and further extension and deformation are restricted.

  For this reason, due to excessive extension deformation or movement in the left-right direction of the leaf spring 42, either one of the two end portions 42b, 42c is brought into contact with the outer peripheral surface of the eccentric shaft portion 39 and the inner peripheral surface of the inner ring 47a of the ball bearing 47. It is possible to suppress the problem of being caught in the gap between the two.

  In particular, in the present embodiment, excessive deformation and movement of the leaf spring 42 are restricted by the concave grooves 45, 45, so that the occurrence of stress concentration on the leaf spring 42 can be sufficiently suppressed. That is, when both end portions 42b and 42c are regulated from the outside by a predetermined metal member, for example, stress concentration may occur. However, since this stress concentration is eliminated, the plate is not subjected to repeated elastic deformation. Phenomena such as sag of the spring 42 is suppressed, and durability can be improved.

  Further, the both end portions 42b, 42c of the leaf spring 42 abut against the flat both end surfaces 40b, 40c of the recess 40, whereby the inclination of the leaf spring 42 during elastic deformation is suppressed, and the occurrence of backlash variation is suppressed. be able to.

  Furthermore, in this embodiment, since the said recessed grooves 45 and 45 are formed naturally, it becomes unnecessary to provide a control part separately, Therefore The increase in a number of parts can be suppressed. As a result, the manufacturing operation is facilitated and the cost can be reduced.

  Further, in the medium diameter ball bearing 47, since the thickness t in the radial direction of the inner ring 47a is set larger than the thickness t1 in the radial direction of the outer ring 47b, the number of each ball 47c is set to a normal general ball bearing. Place more than the number of balls.

  For this reason, it is possible to distribute the load generated in the ball bearing 47 during the driving of the device to each ball 47c. As a result, the load on the ball bearing 47 is reduced, so that a decrease in durability can be suppressed.

Moreover, since the entire outer diameter of the ball bearing 47 including the inner ring 47a and the outer ring 47b can be made as small as possible, the size in the radial direction of the device can be made sufficiently small. As a result, the apparatus can be miniaturized.
[Second Embodiment]
FIGS. 11A to 11C show the second embodiment, and the basic structure is the same as that of the first embodiment, except that a wear resistant material 44 is coated on a part of the leaf spring 42.

  That is, the wear resistant material 44 made of tungsten carbide is provided on the left and right sides of the upper surface of the top portion 42a of the leaf spring 42, that is, the portion where the leaf spring 42 is in contact with the inner circumferential surface 47d of the inner ring 47a and both end surfaces 40b and 40c of the recess 40. It is formed in a predetermined region T and predetermined regions T1, T2 on the lower end surfaces of both end portions 42b, 42c.

  As described above, the wear-resistant material 44 is formed only in specific regions of T, T1, and T2 of the leaf spring 42, and is not formed in other portions. Thus, the original spring characteristics of the leaf spring 32 can be extracted. Therefore, the clearances C3 and C4 can be effectively reduced. Further, since the wear resistant material 44 is partially formed, the material cost can be reduced.

  The present invention is not limited to the configuration of the embodiment described above, and the wear-resistant material 44 may be, for example, diamond-like carbon (DLC) instead of tungsten carbide. It may be a material.

  Further, the coating area (formation area) of the wear resistant material 44 can be further reduced if necessary.

  Further, for example, the thickness t in the radial direction of the inner ring 47a of the ball bearing 47 can be further increased depending on the size and specifications of the device, and the number of balls 47c can be increased. Thereby, the load can be further distributed to reduce the load.

  By disposing the oil seal 46 close to one side surface of the inner ring 47a of the ball bearing 47, inadvertent movement of the oil seal 46 in the camshaft 2 direction can be restricted.

  Moreover, the recessed part 40 should just be notched and formed in the rectangular shape along the tangential direction the outer peripheral part of the largest thickness part of the said eccentric shaft part 39, and the said recessed part 40 may be open | released at the axial direction one end side. .

  Further, the recess 40 can be formed not on the eccentric shaft 39 side but on the inner peripheral surface 47d side of the inner ring 47a.

  The present invention is not limited to application to the speed reduction mechanism 15 having the roller 48, and can be applied to any device as long as the eccentric shaft portion and the inner ring are configured to be relatively rotatable. For example, the present invention can also be applied to a planetary gear type speed reducer having a planetary gear capable of planetary movement while meshing with the internal teeth of the internal gear component by rotating the eccentric shaft portion. In this case, a planetary gear is disposed on the outer periphery of the eccentric shaft portion, and a bearing having an inner ring and an outer ring is disposed between the outer periphery of the eccentric shaft portion and the inner periphery of the planetary gear.

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.
That is, the valve timing control device includes a drive rotator to which the rotational force from the crankshaft is transmitted, a driven rotator fixed to the camshaft,
An electric motor having a motor output shaft that can rotate relative to the drive rotator, and an eccentric rotator in which a rotational force is transmitted from the motor output shaft and the shaft rotates eccentrically with respect to the rotation center of the motor output shaft. And a bearing that is arranged on the outer peripheral side of the eccentric rotating body, the inner ring and the outer ring rotate relative to each other, and an inner ring that is provided on the drive rotating body and has a plurality of inner teeth on the inner periphery and that faces the bearing from the outside. A plurality of teeth that are arranged between a tooth component, an outer peripheral surface of the bearing and each of the inner teeth of the inner tooth component, and the meshing locations with the inner teeth move in the circumferential direction due to the eccentric rotation of the eccentric rotor. A rolling member and a holding member that is provided on the driven rotating body and allows radial movement between the bearings and internal teeth of the rolling elements while separating the rolling elements; A recess formed in the outer peripheral surface of the eccentric rotor or the inner peripheral surface of the bearing; Housed in portion, and a biasing member for biasing the rolling elements the tooth bottom direction of the inner teeth via the bearing,
The urging member has a wear-resistant material at least at a portion that contacts the bottom surface of the recess and a portion that contacts the inner peripheral surface of the bearing.

  As another preferred embodiment, the wear resistant material of the urging member has a hardness higher than that of the bottom surface of the recess.

  As another preferred aspect, the urging member is configured by a leaf spring bent in an arc shape protruding outward in the radial direction.

  In another preferred embodiment, the leaf spring has both ends elastically contacted with the bottom surface of the recess, while the longitudinal center portion bent in the arc shape contacts the inner peripheral surface of the inner ring of the bearing. ing.

  As another preferred embodiment, the wear-resistant material is formed by coating the entire surface of the biasing member.

  In another preferred embodiment, the coated wear resistant material is tungsten carbide.

  In another preferred embodiment, the coated wear resistant material is diamond-like carbon.

  As another preferred embodiment, a decelerating mechanism that decelerates the rotation speed of the electric motor is configured by the eccentric rotating body, the bearing, the internal tooth constituent portion, the rolling element, and the holding member.

  As another preferred embodiment, a clearance is formed between the outer peripheral surface of the eccentric rotating body and the inner peripheral surface of the bearing, and the clearance is the outer peripheral surface of the bearing, the inner tooth constituent portion, and the outer periphery of the rolling element. It is set to be larger than the maximum radial clearance formed between the surfaces.

The speed reduction mechanism of the valve timing control device includes an eccentric rotating body in which a rotational force is transmitted from the motor output shaft of the electric motor and the shaft rotates eccentrically with respect to the rotation center of the motor output shaft, and the eccentric rotation A bearing disposed on the outer peripheral side of the body, a housing provided with a clearance on the outer peripheral side of the outer ring of the bearing, and an inner tooth constituent part having a plurality of inner teeth formed on the inner periphery, and the outer ring of the bearing A plurality of rolling elements that are arranged between the outer peripheral surface of the inner teeth and the inner teeth of the inner tooth constituent portion, and that are engaged with the inner teeth in the circumferential direction by the eccentric rotation of the eccentric rotor. A holding member that allows the rolling elements to move in the radial direction while separating the moving bodies; a recess formed on the outer peripheral surface of the eccentric rotating body or the inner peripheral surface of the inner ring of the bearing; The rolling element through the bearing. And a biasing member for biasing the tooth bottom direction of the serial endodontic,
The urging member has a wear-resistant material at least at a portion that contacts the bottom surface of the recess and a portion that contacts the inner peripheral surface of the bearing.

  As another preferred aspect, the urging member is configured by a leaf spring bent in an arc shape protruding outward in the radial direction.

  As another preferred embodiment, the leaf spring has both end portions elastically contacted with the bottom surface of the recess, while the center portion in the longitudinal direction bulging in the arc shape elastically contacts the inner peripheral surface of the inner ring of the bearing. Yes.

1. Timing sprocket (drive rotor)
DESCRIPTION OF SYMBOLS 1a ... Sprocket main body 2 ... Camshaft 4 ... Phase change mechanism 5 ... Internal-tooth component 5a ... Internal-tooth 8 ... Electric motor 9 ... Driven member (driven rotor)
DESCRIPTION OF SYMBOLS 12 ... Motor housing 13 ... Motor output shaft 15 ... Deceleration mechanism 39 ... Eccentric shaft part (eccentric rotating body)
39a ... Cam surface 40 ... Recess 40a ... Bottom surface 40b, 40c ... Both end surfaces 41 ... Cage (holding member)
41a ... tip 41b ... roller holding hole 42 ... leaf spring (biasing member)
42a ... Arc top (central part)
42b, 42c ... Both ends 44 ... Tungsten carbide (tungsten carbide)
47 ... Medium-diameter ball bearing (bearing)
47a ... Inner ring 47b ... Outer ring 47c ... Ball 47d ... Inner ring inner peripheral surface 48 ... Roller (rolling element)
C ... Minute gap C3 ... Radial clearance C4 ... Cage clearance

Claims (12)

A driving rotating body to which the rotational force from the crankshaft is transmitted;
A driven rotor fixed to the camshaft;
An electric motor having a motor output shaft capable of rotating relative to the drive rotor;
An eccentric rotator in which a rotational force is transmitted from the motor output shaft and the shaft rotates eccentrically with respect to the rotation center of the motor output shaft;
A bearing disposed on the outer peripheral side of the eccentric rotating body, the inner ring and the outer ring rotating relative to each other;
An internal gear component provided on the drive rotor, having a plurality of internal teeth on the inner periphery and facing the bearing from the outside in the radial direction;
A plurality of rolling elements that are arranged between the outer peripheral surface of the bearing and each internal tooth of the inner tooth constituent part, and in which the meshing location with the inner teeth moves in the circumferential direction by the eccentric rotation of the eccentric rotating body;
A holding member that is provided on the driven rotating body and that allows the rolling elements to move in a radial direction between the bearings and the internal teeth while separating the rolling elements;
A recess formed on the outer peripheral surface of the eccentric rotor or the inner peripheral surface of the bearing;
A biasing member that is housed in the recess and biases the rolling element toward the bottom surface of the internal teeth via the bearing;
With
The valve timing control device for an internal combustion engine, wherein the urging member has a wear-resistant material at least at a portion that contacts the bottom surface of the recess and a portion that contacts the inner peripheral surface of the bearing. The valve timing control apparatus for an internal combustion engine according to claim 1,
The valve timing control device for an internal combustion engine, wherein the wear resistant material of the urging member has a hardness higher than that of the bottom surface of the recess. The valve timing control apparatus for an internal combustion engine according to claim 1,
The valve timing control device for an internal combustion engine, wherein the urging member is constituted by a leaf spring bent in an arc shape protruding outward in the radial direction. The valve timing control apparatus for an internal combustion engine according to claim 3,
Both ends of the leaf spring are in elastic contact with the bottom surface of the recess, while the longitudinal central portion bent in the arc shape is in contact with the inner peripheral surface of the inner ring of the bearing. 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 the wear resistant material is formed by coating the entire surface of the biasing member. In the internal combustion engine valve timing control device according to claim 5,
The valve timing control device for an internal combustion engine, wherein the coated wear-resistant material is tungsten carbide. In the internal combustion engine valve timing control device according to claim 5,
The valve timing control device for an internal combustion engine, wherein the coated wear-resistant material is diamond-like carbon. The valve timing control apparatus for an internal combustion engine according to claim 1,
A valve timing control device for an internal combustion engine, characterized in that a decelerating mechanism for decelerating the rotational speed of the electric motor is constituted by an eccentric rotator, a bearing, an internal tooth component, a rolling element and a holding member. The valve timing control apparatus for an internal combustion engine according to claim 1,
A clearance is formed between the outer peripheral surface of the eccentric rotating body and the inner peripheral surface of the bearing, and the clearance is formed between the outer peripheral surface of the bearing and the inner tooth constituent portion and the outer peripheral surface of the rolling element. A valve timing control device for an internal combustion engine, wherein the valve timing control device is set to be larger than a maximum radial clearance. An eccentric rotating body in which a rotational force is transmitted from the motor output shaft of the electric motor, and the shaft center rotates eccentrically with respect to the rotation center of the motor output shaft;
A bearing disposed on the outer peripheral side of the eccentric rotating body;
A housing having an inner tooth constituent part provided on the outer peripheral side of the outer ring of the bearing via a clearance and having a plurality of inner teeth formed on the inner periphery;
A plurality of rolling elements arranged between an outer peripheral surface of the outer ring of the bearing and each inner tooth of the inner tooth constituent part, and an engagement portion with the inner teeth is moved in the circumferential direction by the eccentric rotation of the eccentric rotating body; ,
A holding member that allows movement of each rolling element in the radial direction while separating the rolling elements;
A recess formed on the outer peripheral surface of the eccentric rotor or the inner peripheral surface of the inner ring of the bearing;
A biasing member that is housed in the recess and biases the rolling element toward the bottom surface of the internal teeth via the bearing;
With
The reduction mechanism of the valve timing control device for an internal combustion engine, wherein the biasing member has a wear-resistant material at least in a portion contacting the bottom surface of the recess and a portion contacting the inner peripheral surface of the bearing. The speed reduction mechanism according to claim 10,
The said biasing member is comprised by the leaf | plate spring bent in the circular arc shape protruded to radial direction outward, The deceleration mechanism of the valve timing control apparatus of the internal combustion engine characterized by the above-mentioned. In the deceleration mechanism of the valve timing control device for an internal combustion engine according to claim 11,
Both ends of the leaf spring are in elastic contact with the bottom surface of the recess, while the central portion in the longitudinal direction protruding in the arc shape is in contact with the inner peripheral surface of the inner ring of the bearing. Engine valve timing control device.

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