JP2019148168A - Valve timing control device of internal combustion engine - Google Patents

Abstract

To solve a problem that the attachment work of a detected member of a rotation detection mechanism to a motor output shaft has been difficult.SOLUTION: A detected member 50 of an angle sensor has: a support part 52 which is inserted into and held in a small-diameter part 14b of a motor output shaft 14; a flange part 54 arranged at an external peripheral face of a tip part of the support member at a cover member side; a protrusion 52b protruded frontward from the flange part of the support part; and a detected rotor 53 arranged at a tip face of the protrusion. A fixing member 60 has a circular plate part 61 having a through-hole 63 at a center, and a cylinder part 62 arranged at an external peripheral edge of the circular plate part so as to be protrusive in a motor output shaft direction. The fixing member also has an engagement groove 56 formed at an external peripheral face of the protrusion, and an extension part 64 arranged at a hole edge of the through-hole integrally therewith, and regulating the movement of the detected member in an axial direction in a state of being engaged with the engagement groove.SELECTED DRAWING: Figure 9

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.

  As a valve timing control device for an internal combustion engine, a device described in the following Patent Document 1 previously filed by the present applicant is known.

  This device includes an electromagnetic induction type rotation angle detection mechanism for detecting a rotation angle of a motor output shaft of an electric motor between a front end portion of a motor housing of the electric motor and a cover member covering the front end portion of the motor housing. Is provided.

  The rotation angle detection mechanism includes a member to be detected provided in a front end portion of the motor output shaft formed in the cylindrical shape, and a motor provided by the induction current provided in the cover member and output from the member to be detected. And a detection mechanism for detecting the rotational position of the output shaft.

  The detected member is formed in a substantially cylindrical shape by a synthetic resin material, and a double-leaf-shaped detected rotor disposed opposite to the receiving circuit and the excitation circuit of the detection mechanism is integrally fixed to the front end surface, and The end is press-fitted and fixed in the tip of the motor output shaft.

Japanese Patent Laid-Open No. 2016-11628

  In the conventional valve timing control device, the member to be detected of the rotation angle detection mechanism is press-fitted and fixed from the outside in the axial direction into the tip portion of the motor output shaft, as described above. Since this press-fitting work requires a relatively large pushing force, the worker performs the work individually using a predetermined press-fitting jig. For this reason, this press-fitting work becomes complicated, and the work efficiency of attaching the detected member is reduced.

  The present invention has been devised in view of the above-described conventional technical problems, and provides a valve timing control device for an internal combustion engine capable of improving the work efficiency of attaching a detected member of a rotation detection mechanism to a motor output shaft. .

  The invention according to claim 1 of the present application is, inter alia, provided on the outer periphery of the insertion portion that is inserted and held in the distal end portion of the motor output shaft of the electric motor, and the distal end portion of the insertion portion on the cover member side. A flange portion that restricts further insertion of the insertion portion in an axially contacted state with the distal end surface, and a detected rotor provided on a protrusion portion protruding forward from the flange portion of the insertion portion; A member to be detected, a disk portion having a through hole through which the protruding portion is inserted, and abutting against an outer surface of the flange portion on the cover member side, and the motor on the outer peripheral edge of the disk portion A fixing member that protrudes in the direction of the output shaft and that is fitted and fixed to the outer periphery of the front end of the motor output shaft via the outer peripheral surface of the flange portion; The motor output shaft through the detected member A rotation detection mechanism for detecting a rotation angle; an engagement portion formed on an outer peripheral surface of the protruding portion; and a hole edge of a through hole of the disc portion, and by engaging with the engagement portion, A locking mechanism that limits the movement of the fixing member relative to the detected member in the axial direction; and a locking mechanism that is formed between the engaging portion and the locking portion in an engaged state. And a gap that allows the detection member to move in the radial direction.

  According to this invention, it is possible to improve the work efficiency of attaching the member to be detected of the rotation detection mechanism into the motor output shaft.

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. FIG. 2 is a view as seen from an arrow A in FIG. It is the BB sectional view taken on the line of FIG. It is a rear view of the electric power feeding plate provided to this embodiment. It is a perspective view which shows the state by which the to-be-detected member was attached to the motor output shaft via the fixing member provided for this embodiment. It is CC sectional view taken on the line of FIG. It is a disassembled perspective view of the to-be-detected member and fixing member which are provided to this embodiment. It is a principal part enlarged view of FIG. It is a disassembled perspective view of the to-be-detected member and fixing member which are provided to 2nd Embodiment of this invention. It is a bottom view of the member for fixation provided for 3rd Embodiment. It is a disassembled perspective view of the to-be-detected member and fixing member which are provided to 3rd Embodiment. It is a disassembled perspective view of the to-be-detected member and fixing member which are provided to 4th Embodiment. It is a disassembled perspective view of the to-be-detected member and fixing member which are provided to 5th Embodiment. It is a longitudinal cross-section which shows the state by which the to-be-detected member was attached to the motor output shaft via the fixing member provided for this embodiment. It is a principal part enlarged view of FIG. It is a disassembled perspective view of the to-be-detected member and fixing member which are provided to 6th Embodiment. It is a principal part expanded sectional view which shows the state by which the fixing member was attached to the to-be-detected member in this embodiment by the elastic member. It is a disassembled perspective view of the to-be-detected member and fixing member which are provided to 7th Embodiment. It is a principal part expanded sectional view which shows the state by which the fixing member was attached to the to-be-detected member in this embodiment by the elastic member. It is a disassembled perspective view of the to-be-detected member provided for embodiment of 2nd invention, the member for fixing, and a ring nut. It is a principal part expanded sectional view which shows the state by which the fixing member was attached to the to-be-detected member in this embodiment with the ring nut.

DESCRIPTION OF EMBODIMENTS Hereinafter, an embodiment of a valve timing control device for an internal combustion engine 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.
[First Embodiment]
As shown in FIGS. 1 and 2, the valve timing control device is rotatably supported 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 02. The camshaft 2 is rotated by the rotational force transmitted from the timing sprocket 1 and is disposed between the timing sprocket 1 and the camshaft 2 so that the relative rotational phases of the both 1 and 2 are changed according to the engine operating state. The phase change mechanism 3 to change and the cover member 4 arrange | positioned at the front-end side of this phase change mechanism 3 are provided.

  The timing sprocket 1 is formed integrally with an iron-based metal in an annular shape, and the inner peripheral surface is integrally provided on the outer periphery of the sprocket body 1a with a stepped diameter, and is wound outside the drawing. The gear part 1b which receives the rotational force from a crankshaft via this timing chain, and the internal-tooth structure part 5 integrally provided in the front-end side of the said sprocket main body 1a are comprised.

  The timing sprocket 1 has a single large-diameter ball bearing 6 interposed between a sprocket body 1a and a driven member 9 (described later) provided at the front end of the camshaft 2. The timing sprocket 1 is supported by the ball bearing 6 on the outer periphery of the driven member 9 so as to be relatively rotatable.

  The large-diameter ball bearing 6 is a general one and includes an outer ring 6a, an inner ring 6b, and a ball 6c interposed between the two rings. The outer ring 6a is disposed on the inner peripheral side of the sprocket body 1a. While being fixed, the inner ring 6b is press-fitted and fixed to the outer peripheral side of the driven member 9.

  The internal tooth constituting part 5 constitutes a part of a speed reducing mechanism 12 (to be described later) of the phase changing mechanism 3, and is integrally provided on the outer peripheral side of the front end portion of the sprocket body 1 a and forward of the phase changing mechanism 3. In addition to being formed in an extended cylindrical shape, a plurality of corrugated internal teeth 5a are formed on the inner periphery.

  Further, an annular stopper plate 7 is arranged at the rear end portion of the sprocket body 1a opposite to the internal tooth constituent portion 5. The stopper plate 7 is formed in an annular shape by a metal plate material, has an outer diameter set substantially the same as the outer diameter of the sprocket body 1a, and an inner diameter larger than the inner diameter of the outer ring 6a of the large-diameter ball bearing 6. It is set to a small diameter.

  At a predetermined position on the inner peripheral edge of the inner peripheral portion 7a of the stopper plate 7, a stopper convex portion 7b protruding inward in the radial direction, that is, toward the central axis is integrally provided. The stopper convex portion 7b is formed in a substantially fan shape, and the tip edge 7c is formed in an arc shape along an arcuate inner peripheral surface of a stopper groove 2b described later.

  Six insertion holes 1c and 7d through which bolts 19 are inserted are formed in the outer peripheral portions of the sprocket main body 1a (internal tooth constituent portion 5) and the stopper plate 7 so as to penetrate at substantially equal intervals in the circumferential direction.

  The camshaft 2 has two drive cams per cylinder for opening an intake valve (not shown) on the outer periphery, and is driven by a flange portion 2a at one end in the axial direction via an adapter 8 described later. A driven member 9 that is a rotating body is fastened together by a cam bolt 10 from the axial direction.

  The driven member 9 is integrally formed of iron-based metal, and as shown in FIG. 1, a disk-shaped fixed end portion 9a formed on the rear end side (camshaft 2 side), and the fixed end portion 9a. The cylindrical portion 9b protrudes in the axial direction from the center position of the front end surface of the main body. A cylindrical retainer 49 that holds a plurality of rollers 48 that are part of the speed reduction mechanism 12 is integrally formed on the outer peripheral portion of the fixed end portion 9a.

  The fixed end portion 9a has a first fitting groove 9d formed on the rear end surface thereof in contact with the front end surface of the flange portion 2a of the camshaft 2 via an adapter 8 so that the axial force of the cam bolt 10 The flange portion 2a is fixed in pressure contact from the axial direction.

  As shown in FIG. 1, the cylindrical portion 9b has a through hole 9d through which the shaft 10b of the cam bolt 10 is inserted, and a small-diameter ball bearing 37 and a needle bearing 38 on the outer peripheral side. It is provided in parallel along the axial direction.

  As shown in FIGS. 1 and 2, the adapter 8 is formed by bending a disk-shaped metal plate having a constant thickness into a substantially crank shape by press molding, and has a flange-shaped outer peripheral portion 8a and an electric motor. A bottomed cylindrical inner peripheral portion 8b protruding in the direction of the motor 11.

  The outer peripheral portion 8 a is formed with an outer diameter slightly larger than the outer diameter of the fixed end portion 9 a of the driven member 9, and the outer peripheral side on the electric motor 11 side is the other end surface in the axial direction of the inner ring 6 b of the large-diameter ball bearing 6. To move outward in the axial direction.

  Further, as shown in FIG. 3, a stopper concave groove 8d into which the protrusion 7b of the stopper plate 7 is engaged is formed in an arc shape along the circumferential direction on the outer peripheral surface of the outer peripheral portion 8a. The stopper concave groove 8d is formed in a circular arc shape having a predetermined length in the circumferential direction, and both end edges of the protruding portion 7b rotated within this length range are brought into contact with the opposing edges in the circumferential direction. The relative rotational position of the camshaft 2 on the maximum advance angle side or the maximum retard angle side with respect to the sprocket 1 is regulated.

  The inner peripheral portion 8b is formed by press molding into a bottomed cylindrical shape protruding toward the electric motor 11, has a disk groove-like second fitting groove 8e on the camshaft 2, and the second An insertion hole 8f through which the shaft portion 10b of the cam bolt 10 is inserted is formed in the center of the fitting groove 8e. An annular projection 2d protruding from the end surface of the flange portion 2a of the camshaft 2 is fitted into the second fitting groove 8e. Further, an oil passage hole (not shown) that constitutes a part of a lubricating oil passage described later is formed through the inner peripheral portion 8b.

  The inner peripheral portion 8b is fitted into the first fitting groove 9d of the driven member 9 by press-fitting from the axial direction, and in this fitted state, the cam bolt 10 and the protruding portion 2d of the cam shaft 2 are driven. The member 9 is coupled to the fixed end portion 9a in a sandwiched state.

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

  The phase changing mechanism 3 includes the electric motor 11 disposed on the front end side of the cylindrical portion 9b of the driven member 9, a speed reducing mechanism 12 that reduces the rotational speed of the electric motor 11 and transmits the speed to the camshaft 2. Is mainly composed of

  As shown in FIGS. 1 and 2, the electric motor 11 is a brushed DC motor, a motor housing 13 that is a yoke that rotates integrally with the timing sprocket 1, and rotates inside the motor housing 13. A cylindrical motor output shaft 14 provided freely, four semicircular arc-shaped permanent magnets 15 fixed to the inner peripheral surface of the motor housing 13, and a power feeding plate 16 fixed by caulking to the front end portion of the motor housing 13. And.

  As shown in FIG. 1, the motor housing 13 is formed into a bottomed cylindrical shape with an iron-based metal material, has a disk-shaped partition wall 13a on the rear end side, and has a motor output substantially at the center of the partition wall 13a. A relatively large diameter shaft insertion hole 13b through which the shaft 14 and the like are inserted is formed. In addition, a cylindrical extending portion 13c protruding in the axial direction of the camshaft 2 is integrally provided at the hole edge of the shaft insertion hole 13b. Further, a female screw hole 13d is formed along the axial direction inside the outer peripheral side of the partition wall 13a.

  The female screw hole 13d is formed at a position corresponding to each of the bolt insertion holes 1c and 7d, and the timing sprocket 1, the stopper plate 7 and the motor housing 13 are shared in the axial direction by six bolts 19 inserted through these holes. Tightened and fixed. In addition, the said internal-tooth structure part 5 is contact | abutted from the axial direction at the outer peripheral part rear end surface of the partition 13a of the motor housing 13. FIG.

  As shown in FIG. 1, the motor output shaft 14 has a peripheral wall formed in a stepped diameter shape and is formed at the rear end of the camshaft 2 via a stepped wall 14c formed at a substantially central position in the axial direction. A large-diameter portion 14a and a small-diameter portion 14b formed at the front end portion on the opposite side in the axial direction, and an insertion hole 14d through which the cam bolt 10 can be inserted is formed in the inner axial direction. Yes.

  The large-diameter portion 14a has an iron core rotor 17 fixed to the outer periphery, and an eccentric shaft portion 36, which will be described later, is integrally provided along the axial direction on the rear end side.

  On the other hand, as shown in FIGS. 1, 6, and 7, the small-diameter portion 14 b has a commutator 20 press-fitted and fixed in the vicinity of the stepped wall 14 c on the outer periphery, and a detected member of an angle sensor 35 to be described later. 50 is inserted and fixed.

  Further, as shown in FIG. 9, the small-diameter portion 14b is formed with a first guide surface 14f whose diameter gradually increases from the tip edge on the outer peripheral surface of the tip portion 14e on the cover member 4 side, and the tip portion 14e. A second guide surface 14g having a gradually reduced taper shape is formed on the inner peripheral surface from the front edge toward the inner side. In addition, an annular fitting groove 40 is formed at the end portion of the first guide surface 14f of the tip portion 14e. The fitting groove 40 is formed to have a substantially rectangular cross section, and the depth of the fitting groove 40 is the inner side of a fitting portion 66 formed on the rear end side of a cylindrical portion 62 (fitting fixing portion) of a fixing member 60 described later. The depth is set so that it can be elastically deformed and fully fitted.

  As shown in FIGS. 1 and 6, the iron core rotor 17 is formed of a magnetic material having a plurality of magnetic poles, and the outer peripheral side is configured as a bobbin having a slot around which the coil wire of the coil 18 is wound. The motor output shaft 14 is fixed while being positioned in the axial direction on the outer periphery of the large diameter portion 14a on the step wall 14c side.

  On the other hand, the commutator 20 includes an annular member 20a on the inner circumferential side and an annular electrode portion 20b provided on the outer circumference of the annular member 20a. The electrode portion 20b is formed in an annular shape with a conductive material, and the ends of the coil wires led out of the coil 18 are electrically connected to the segments divided into the same number as the number of poles of the iron core rotor 17. Yes.

  Each of the permanent magnets 15 is formed in a cylindrical shape and has a plurality of magnetic poles in the circumferential direction, and its axial position is the axial direction of the iron core rotor 17 as shown in FIG. The power supply plate 16 is offset from the center of the power supply plate 16.

  As shown in FIGS. 1, 2 and 5, the power supply plate 16 is a disk-shaped metal plate 16 a made of an iron-based metal material, and a disk-shaped plate in which both front and rear side surfaces of the metal plate portion 16 a are molded. And a resin portion 16b.

  The metal plate 16a is positioned and fixed by caulking in an annular stepped concave groove formed on the inner periphery of the front end portion of the motor housing 13 at the exposed outer peripheral portion, and at the center portion of the motor output shaft 14 A shaft insertion hole 16c through which the small diameter portion 14b is inserted is formed through.

  Further, as shown in FIG. 5, the power supply plate 16 is disposed inside a plurality of holding holes formed in the metal plate 16a and fixed to the front end portion of the resin portion 16b by a plurality of rivets 32. A pair of brush holders 23a, 23b made of copper, and accommodated in the brush holders 23a, 23b so as to be slidable along the radial direction, and each arcuate tip by the spring force of the coil springs 24a, 24b. A state in which the outer surfaces of the pair of switching brushes 25a and 25b, which are commutators elastically contacting the outer peripheral surface of the electrode portion 24b of the commutator 20 from the radial direction, are exposed on the front end side of the resin portion 16b. The inner and outer double power supply slip rings 26a and 26b, which are fixed by molding, are electrically connected to the switching brushes 25a and 25b and the slip rings 26a and 26b. Harness 27a for connecting, and 27b, are provided. The slip rings 26a and 26b are formed by punching a thin plate made of a copper material into an annular shape by pressing.

  As shown in FIGS. 1 and 2, the cover member 4 is formed in a substantially disk shape and is disposed so as to cover the front end side of the power feeding plate 16, and is a disk plate shape mainly made of a synthetic resin material. The cover main body 28 and a synthetic resin cap 29 that covers the front end of the cover main body 28.

  The cover body 28 is formed to have a predetermined thickness and has an outer diameter larger than the outer diameter of the motor housing 13, and a reinforcing plate 28a, which is a metal core, is fixed inside the mold. Has been.

  Further, the cover main body 28 has a bolt insertion hole 28c into which a bolt fixed to the chain case 22 is inserted into an arc-shaped boss portion 28b projecting from four locations on the outer peripheral portion. Each is formed by a metal sleeve. The reinforcing plate 28a is formed in a substantially disk shape, and a circular through hole 28d is formed at the center position.

  An oil seal 39 that restricts the inflow of oil toward the electric motor 11 is interposed between the inner peripheral surface of the insertion hole 22a formed in the chain case 22 and the outer peripheral surface of the motor housing 13. ing.

  The cover main body 28 has a pair of square cylindrical brush holders 30a and 30b fixed to positions facing the slip rings 26a and 26b in the axial direction. Inside the brush holders 30a and 30b, power supply brushes 31a and 31b whose tip surfaces are in sliding contact with the slip rings 26a and 26b are slidably held in the axial direction.

  A circular concave groove 28e is formed at a substantially central position of the inner surface of the cover main body 28 on the electric motor 11 side. The concave groove 28e is formed to be recessed outward in the axial direction of the cover body 28, and has an inner diameter larger than that of the distal end portion 50a of the detected member 50, and its depth is the axial direction of the cover body 28. Is formed to be slightly smaller than the width and the thickness of the bottom wall.

  The cap 29 is formed in a rectangular shape, and an annular engaging portion 29 a formed integrally with the outer peripheral edge is engaged and fixed in an engaging groove formed in the outer peripheral portion of the cover main body 28.

  On the outer surface of the cover body 28 on the cap 29 side, a pair of torsion coil springs (not shown) for urging the power feeding brushes 31a and 31b in the direction of the slip rings 26a and 26b are provided.

  Each of the brush holders 30a and 30b has front end portions of the power supply brushes 31a and 31b that are movable forward and backward from the opening on the front end side, and a pigtail harness (not shown) through the opening on the rear end side. Are connected to the rear ends of the power supply brushes 31a and 31b by integral molding.

  Each of the power supply brushes 31a and 31b is formed in a prismatic shape and set to a predetermined axial length, and each flat tip surface is in contact with each of the slip rings 26a and 26b from the axial direction. It has become.

  Further, at the lower end of the cover main body 28, the power supply connector 33 for supplying current from the control unit (not shown) to the power supply brushes 31a and 31b and the detection unit 51 of the angle sensor 35 are detected. A signal connector 34 for outputting a rotation angle signal to the control unit is provided in parallel and in the radial direction.

  The power supply connector 33 has one end of a terminal piece partially embedded in the cover body 28 connected to the pigtail harness, and the other end exposed to the outside is a female on the control unit side. Connected to the terminal.

  On the other hand, in the signal connector 34, as shown in FIG. 1, one end 34a of a terminal piece partially embedded in the cover body 28 is connected to the integrated circuit of the detection unit 51 of the angle sensor 35. At the same time, the other end 34b exposed to the outside is connected to the female terminal on the control unit side.

  As shown in FIGS. 1, 2, and 4, the speed reduction mechanism 12 includes the eccentric shaft portion 36 that performs an eccentric rotational motion, a medium-diameter ball bearing 47 that is provided on the outer periphery of the eccentric shaft portion 36, The roller 48 provided on the outer periphery of the medium-diameter ball bearing 47 and the retainer 49 that allows the roller 48 to move in the radial direction while holding the roller 48 in the rolling direction.

  In the eccentric shaft portion 36, the axis Y of the cam surface 36 a formed on the outer peripheral surface is slightly eccentric in the radial direction from the axis X of the motor output shaft 14.

  The eccentric shaft portion 36 and the motor output shaft 14 are provided on the outer peripheral surface of the cylindrical portion 9b of the driven member 9 and the small-diameter ball bearing 37 provided on the outer peripheral surface of the shaft portion 10b of the cam bolt 10. The ball bearing 37 is rotatably supported by a needle bearing 38 disposed on the side in the axial direction.

  In the small-diameter ball bearing 37, the inner ring is fixed in a clamped state between the front end edge of the cylindrical portion 9 b of the driven member 9 and the head 10 a of the cam bolt 10, while the outer ring has a stepped diameter increasing shape of the eccentric shaft portion 36. The inner peripheral surface is press-fitted and fixed, and is positioned in the axial direction by abutting against a step edge formed on the inner peripheral surface.

  The needle bearing 38 is a general one and has a plurality of needle rollers rotatably held inside a cylindrical retainer press-fitted into the inner peripheral surface of the eccentric shaft portion 36. The outer peripheral surface of the cylindrical portion 9b of the driven member 9 is rolling.

  Further, between the outer peripheral surface of the large-diameter portion 14 a of the motor output shaft 14 and the inner peripheral surface of the extending portion 13 c of the motor housing 13, lubricating oil from the inside of the speed reduction mechanism 12 to the electric motor 11 is supplied. A small-diameter oil seal 46 is provided to prevent leakage.

  The medium-diameter ball bearing 47 is disposed so as to be substantially overlapped at the radial position of the needle bearing 38, and includes an inner ring 47a, an outer ring 47b, and a ball 47c interposed between the wheels 47a and 47b. It is composed of The inner ring 47a is press-fitted and fixed to the outer peripheral surface of the eccentric shaft portion 36, whereas 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 electric motor 11 side in the axial direction is not in contact with any part, and the other end surface in the axial direction is between the inner side surface of the retainer 49 facing the minute end. One gap is formed and is in a free state. Further, the outer peripheral surface of the outer ring 47b is in contact with the outer peripheral surface of each roller 48 so as to be able to roll, and an annular second gap is formed on the outer peripheral side of the outer ring 47b. Due to the second gap, the entire medium-diameter ball bearing 47 can move in the radial direction along with the eccentric rotation of the eccentric shaft portion 36, that is, can move eccentrically.

  As shown in FIGS. 1, 2 and 4, the retainer 49 is bent in a substantially L-shaped cross section from the front end of the outer peripheral portion of the fixed end portion 9a to the same direction as the cylindrical portion 9b. It is formed in a protruding bottomed cylindrical shape.

  The cylindrical tip 49a of the retainer 49 extends in the direction of the partition wall 13a of the motor housing 13 through an annular concave storage space defined by the internal tooth component 5 and the partition wall 13a. In addition, a plurality of substantially rectangular roller holding holes 49b that hold the plurality of rollers 48 in a freely rollable manner are provided at substantially equal intervals in the circumferential direction of the cylindrical tip 49a. Is formed. The roller holding hole 49b is formed in a rectangular shape elongated in the front-rear direction with the tip end side closed, and the total number (the number of rotors 48) is the total number of teeth of the internal teeth 5a of the internal tooth component 5. Thus, the reduction ratio is obtained.

  Each of the rollers 48 is formed of an iron-based metal, and is fitted in the inner teeth 5a of the inner tooth constituent portion 5 while moving in the radial direction along with the eccentric movement of the medium-diameter ball bearing 47, and in the roller holding holes 49b. While being guided in the circumferential direction by both side edges, it is configured to swing in the radial direction.

  A rotation detection mechanism that detects the rotational angle position of the motor output shaft 14 is provided between the small-diameter portion 14b of the motor output shaft 14 and the central portion sandwiching the bottom wall of the concave groove 28e of the cover body 28. An angle sensor 35 is provided.

  The angle sensor 35 is of an electromagnetic induction type, and the detected member 50 fixed in the small-diameter portion 14b of the motor output shaft 14 is opposed to the detected member 50 at a substantially central position of the cover body 28. A detection unit 51 that is fixed and receives a detection signal from the detection target member 50.

  As shown in FIGS. 1, 7, and 8, the member 50 to be detected is formed on a front end surface of a substantially covered cylindrical support portion 52 and a small-diameter protruding portion 52 b in the axial direction described later of the support portion 52. There are three detected rotors 53a to 53c which are fixed detection portions, and a flange portion 54 which is a restriction portion provided integrally on the outer peripheral surface of the support portion 52 on the protruding portion 52b side. .

  The support portion 52 is integrally formed of a hard synthetic resin material that is an insulating material, and has a cylindrical base portion 52a that is an insertion portion that is inserted into the insertion hole 14d, and an axial protrusion from the distal end side of the cylindrical base portion 52a. And a small-diameter protruding portion 52b.

  The cylindrical base 52a is formed with an annular seal holding groove 52c for holding a seal ring 55, which is an elastic seal member, on the outer peripheral surface at a substantially central position in the axial direction. Further, the cylindrical base portion 52a has a tapered guide surface 52d on the outer peripheral edge on the rear end side on the camshaft 2 side with respect to the seal holding groove 52c for ensuring a good insertion property into the insertion hole 14d. Is formed.

  As shown in FIG. 8, the protruding portion 52b has an annular engaging groove 56 as an engaging portion formed on the base front end surface side of the flange portion 54, and the detected rotors 53a to 53c. Inclined protrusions 57 that are formed in a gradually increasing diameter shape (upwardly inclined shape) along the direction of the engagement groove 56 from the end edge side of the groove are integrally formed.

  Each of the detected rotors 53a to 53c is formed of an excitation conductor, and three ohmic magnetic materials are arranged at 120 ° in the circumferential direction on the front end surface of the protruding portion 51b, and the overall outer diameter is The protrusion 51b is formed substantially the same as the outer diameter, and is fixed to the mold while being exposed from the front end surface of the protrusion 51b.

  The flange portion 54 is integrally formed with the support portion 52 by a synthetic resin material of an insulating material, and has an outer diameter larger than an outer diameter of the small diameter portion 14b of the motor output shaft 14, and a cylindrical base portion 52a is formed. When inserted into the insertion hole 14d at the maximum, the inner side surface 54a abuts against the tip edge 14h of the small diameter portion 14b from the axial direction to restrict further insertion.

  The protruding portion 52b protrudes from the tip of the small-diameter portion 14b via the flange portion 54 in a state where the cylindrical base portion 52a is inserted and fixed in the insertion hole 14d to the maximum, and the detected rotors 53a to 53c It is exposed to the front.

  As shown in FIGS. 1 and 2, the detection unit 51 includes a substantially rectangular printed board 58 extending in a radial direction from a substantially central position of the cover body 28, and one end in the longitudinal direction of the printed board 58. An unillustrated integrated circuit (ASIC) provided on the outer surface of the part and an unillustrated receiving coil and exciting coil provided on the other end of the same outer surface as the integrated circuit are provided.

  In the printed circuit board 58, the center of the detected rotor 53 and the center of the receiving and exciting coil are positioned and fixed, and the receiving and exciting coil is detected through the bottom wall of the concave groove 28e and the minute clearance. It faces the rotors 53a to 53c from the axial direction.

  The integrated circuit detects the rotation angle of the motor output shaft 14 by detecting a change in inductance between the receiving coil and the exciting coil, and the detected rotors 53a to 53c and the receiving coil. It is like that. That is, an induction current flows between the excitation coil and the detected rotors 53a to 53c, and the integrated circuit detects the rotational angle position of the motor output shaft 14 by this electromagnetic induction action, and controls this information signal. Output to the unit.

  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 based on this information signal. In addition, rotation control of the electric motor 11 is performed by an information signal from the angle sensor 35 or the like. That is, the rotation of the motor output shaft 14 is controlled by energizing the coil 18 through the power supply brushes 31a and 31b, the slip rings 26a and 26b, the switching brushes 25a and 25b, the commutator 20, and the like. The relative rotation phase of the camshaft 2 with respect to the timing sprocket 1 is controlled.

  Note that in the inside of the speed reduction mechanism 12, there is an oil passage hole formed in the bearing 02 of the cylinder head 01 and the inner shaft direction of the camshaft 2, and oil formed so as to penetrate in the inner shaft direction of the driven member 9. Lubricating oil is supplied through the holes.

  As shown in FIGS. 1 and 6 to 8, the detected member 50 is fixed by a fixing member 60 to the distal end portion of the small diameter portion 14 b of the motor output shaft 14. .

  The fixing member 60 is formed by integrally forming a thin metal plate into a cup shape by press molding, and a disc portion whose movement is restricted by contacting the outer surface 54b of the flange portion 54 on the cover member 4 side. 61 and a cylindrical portion 62 that is bent substantially at right angles from the outer peripheral edge of the disc portion 61 and extends along the direction of the motor output shaft 14. Note that the disc portion 61 does not necessarily have a disc shape as long as the disc portion 61 can come into surface contact with the outer side surface 54b. For example, the disc portion 61 may have a polygonal shape. Moreover, the cylindrical part 62 should just extend along the motor output shaft 14 direction from the outer periphery of the disc part 61, and the part of the circumferential direction may be notched by the notch part 65a.

  The disc portion 61 has a through hole 63 through which the projecting portion 52b of the support portion 52 is inserted at a central position, and is bent at a substantially right angle from a hole edge of the through hole 63 so as to form the cylinder. An annular extending portion 64 which is a locking portion extending in the direction opposite to the portion 61 is provided.

  The extending portion 64 is engaged with the engaging groove 56 formed in the protruding portion 52 b of the cylindrical base portion 52 from the radial direction, and an inner diameter of the inner peripheral surface thereof is outside the annular bottom surface of the engaging groove 56. A small annular first gap C1 is formed between the inner peripheral surface and the annular bottom surface. Therefore, the detected member 50 and the fixing member 60 are slightly movable in the radial direction, that is, in the direction perpendicular to the detected member 50 axis via the first gap C1.

  Further, in a state where the extending portion 64 is engaged with the engaging groove 56, the distal end edge of the extending portion 64 abuts on one side surface of the engaging groove 56 facing this or is disposed with a gap.

  As shown in FIGS. 7 to 9, the cylindrical portion 62 has a length in the axial direction from the outer surface 54 b of the flange portion 54 after assembly of the detected member 50 to the motor output shaft 14. In addition to being formed up to the length of the groove 40, four notches 65a to 65d are formed at approximately 90 ° in the circumferential direction. Among the four cutout portions 65a to 65d, two 65a and 65b formed at opposite positions of 180 ° are formed in a rectangular shape reaching the disc portion 61 along the axial direction. The other two 65c and 65d facing each other at 180 ° are formed in an arc shape that does not reach the disc portion 61. These notches 65a to 65d allow the distal end 62a side of the cylindrical portion 62 to be elastically deformed in the radial direction.

  The cylindrical portion 62 has an inner diameter larger than the outer diameter of the flange portion 54, and a relatively large annular second gap C <b> 2 is formed between the inner peripheral surface and the outer peripheral surface of the flange portion 54. Has been.

  The first gap C <b> 1 and the second gap C <b> 2 constitute an adjustment mechanism for automatic alignment of the detected member 50 with respect to the motor output shaft 14.

  Further, a fitting portion 66 that is elastically locked to the fitting groove 40 is integrally provided at the rear end portion 62 a of the cylindrical portion 62. The fitting portion 66 is formed in an annular shape and is bent in a substantially circular arc shape with a concave inward, and is engaged with the fitting groove 40 from the radial direction so that the base portion 66a is fitted. The movement in the axial direction is restricted by elastic contact with the outer peripheral edge of the groove 40.

The axial movement of the detected member 50 is restricted by the locking of the base portion 66a of the cylindrical portion 62 with the fitting groove 40 and the contact of the disc portion 61 with the outer surface 54b of the flange portion 54. It is configured as a regulation mechanism.
[Operation of this embodiment]
Hereinafter, the operation of the present embodiment will be described. First, the timing sprocket 1 is rotated through the timing chain as the crankshaft of the engine is driven to rotate, and the rotational force is generated by the internal gear component 5 and the internal thread forming portion 6. The motor housing 13 is synchronously rotated. 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.

  When a predetermined engine is operated after the engine is started, the electric motor 11 is supplied from the control unit through the terminal pieces of the power supply connector 33, the pigtail harnesses, the power supply brushes 31a and 31b, the slip rings 26a and 26b, and the like. The coil 18 is energized. As a result, the motor output shaft 14 is rotationally driven, and forward and reverse rotational forces are transmitted to the camshaft 2 via the speed reduction mechanism 12.

  That is, when the eccentric shaft portion 36 rotates eccentrically with the rotation of the motor output shaft 14, each roller 48 is guided in the radial direction by each roller holding hole 49 b of the retainer 49 for each rotation of the motor output shaft 14. It moves while rolling over one internal tooth 5a of the internal tooth constituent part 5 and moving to another adjacent internal tooth 5a, and rolling in the circumferential direction while repeating this in sequence. The rotational force of the motor output shaft 14 is transmitted to the driven member 9 while the rotation of the motor output shaft 14 is decelerated by the rolling contact of the rollers 48. The reduction ratio at this time can be arbitrarily set according to the difference between the number of the inner teeth 5a and the number of rollers 48.

  As a result, the camshaft 2 rotates relative to the timing sprocket 1 in the forward and reverse directions and the relative rotational phase is converted, so that the opening / closing timing of the intake valve is controlled to be advanced or retarded. Therefore, the opening / closing timing of the intake valve is converted to the maximum on the advance side or the retard side, and the fuel efficiency and output of the engine can be improved.

In addition, even if the motor output shaft 14 does not rotate, an induced current flows between the detected member 50 and the detection unit 51 of the angle sensor 35, and the integrated circuit causes the motor output shaft 14 to be The rotation angle is detected, and the current rotation angle position of the motor output shaft 14 is detected by the control unit based on this detection signal. The control unit outputs a rotational drive signal to the electric motor 11 according to the rotational angle position and the rotational position of the crankshaft, and the aforementioned relative rotational phase of the camshaft 2 with respect to the crankshaft is set according to the current engine operating state. It is designed to control with high accuracy.
[Assembly of detected member to motor output shaft]
In order to assemble the detected member 50 into the small diameter portion 14b of the motor output shaft 14, first, the detected member 50 is placed on the base with the protruding portion 52b facing upward, as shown in FIG. Thereafter, the fixing member 60 is fitted from above the detected member 50 with the cylindrical portion 62 facing downward.

  That is, when the fitting portion 66 of the cylindrical portion 62 of the fixing member 60 is applied to the outer peripheral edge of the flange portion 54 and pushed in the arrow direction as it is, the cylindrical portion 62 moves downward while being guided by the outer peripheral edge of the flange portion 54. .

  Subsequently, since the hole edge of the through-hole 63 abuts on the outer peripheral edge of the upper end of the protruding portion 52b of the detected member 50, it is pushed downward as it is, but the extension portion 64 is not easily expanded and deformed. Push the upper surface of the disc part 61 downward with several fingers. Thereby, the inner peripheral edge of the through hole 63, that is, the inner peripheral surface of the extending portion 64 moves while riding on the outer peripheral surface of the inclined protrusion 57 of the protruding portion 52b. At this time, the extending portion 64 is slightly expanded in diameter, but when reaching the engaging groove 56, the extending portion 64 is reduced in diameter to the original shape and engaged in the engaging groove 56. Thereby, the fixing member 60 is securely attached to the detected member 50.

  Thereafter, with the fixing member 60 attached to the detected member 50, the detected member 50 is attached to the inside of the small diameter portion 14b of the motor output shaft 14. That is, when the detected member 50 is held and the rear end side of the support portion 52 is inserted and pushed into the inside from the front end opening of the small diameter portion 14b, the rear end portion of the support portion 52 is brought into contact with the second guide surface 14g. It moves in the axial direction while being guided. Then, in the fixing member 60, the fitting portion 66 is slidably guided along the tapered first guide surface 14f of the small diameter portion 14, and at the same time, the cylindrical portion 62 is elastic through the notches 65a to 65d. Smoothly moves in the axial direction. When the fitting portion 66 reaches the fitting groove 40, the fitting portion 66 is fitted into the fitting groove 40 along with the diameter reduction of the cylindrical portion 62. This completes the assembly work of the detected member 50 to the small diameter portion 14b of the motor output shaft 14 (see FIGS. 6, 7, and 9).

  Thus, in this embodiment, the fixing member 60 is securely attached to the detected member 50 in advance, and the detected member 50 is assembled to the motor output shaft 14 by the fixing member 60. Although a two-step assembly process is required, each mounting operation does not require a large pressure input and can be performed with one touch using the operator's fingers.

  Therefore, since it is not necessary to use a conventional press-fitting jig, the mounting operation is facilitated and the work efficiency can be improved.

  Since the annular extending portion 64 of the fixing member 60 is engaged with the entire annular engaging groove 56 of the detection member 50, the engaging force is increased. The detection member 50 can be firmly assembled. Therefore, the fixing member 60 can be prevented from inadvertently dropping from the detected member 50 during the assembly to the motor output shaft 14.

  Further, since the extending portion 64 extends along the axial direction, the inclination of the fixing member 60 with respect to the detected member 50 can be suppressed, and the fixing member 60 is not prepared from the detected member 50. Can also be prevented from falling off.

  Further, the axial direction of the detected member 50 in the state of being attached to the small diameter portion 14b by the engaging action of the extending portion 64 with respect to the engaging groove 56 and the fitting action of the fitting portion 66 with respect to the fitting groove 40. The movement can be sufficiently restricted.

  On the other hand, as described above, in a state where the attachment work of the detected member 50 to the motor output shaft 14 is completed, the first gap C1 is provided between the extending portion 64 and the engaging groove 56 as shown in FIG. Since the second gap C2 is also formed between the outer peripheral surface of the flange portion 54 and the inner peripheral surface of the cylindrical portion 62, the detected member 50 is interposed via the fixing member 60. Can be slightly moved in the radial direction with respect to the motor output shaft 14. As a result, the axis of the detected member 50 can be automatically aligned with respect to the axis of the motor output shaft 14, so that the rotation detection accuracy of the motor output shaft 14 by the detection unit 51 can be improved. .

  That is, the cylindrical base portion 52a of the detected member 50 is inserted into the motor output shaft 14 so that the shaft center with respect to the motor output shaft 14 is matched, and the fixing member 60 is automatically aligned. Thus, the influence on the alignment of the detected member 50 and the motor output shaft 14 can be suppressed.

  Moreover, since it can align automatically, the perimeter of the fitting part 66 can contact | abut to the fitting groove 40 uniformly, Therefore The one-sided contact with respect to the fitting groove 40 of the fitting part 66 can be suppressed. Therefore, uneven wear between the fitting portion 66 and the fitting groove 40 due to the vibration of the internal combustion engine, the alternating torque of the camshaft 2 or the like can be suppressed. In addition, the structure is not simply self-aligning, but the annular extending portion 64 of the fixing member 60 is engaged with the annular engaging groove 56 of the detected member 50, so that the first Even if the gap C <b> 1 and the second gap C <b> 2 are provided, the fixing member 60 does not easily fall off the detected member 50.

Further, since the first guide surface 14f and the second guide surface 14g provide a smooth guide action in the axial direction of the detected member 50 and the fixing member 60 with respect to the motor output shaft 14, the mounting operation is further improved. It becomes easy.
[Second Embodiment]
FIG. 10 shows the second embodiment, and the basic structure of each component is the same as that of the first embodiment, except that the extending portion 64 of the fixing member 60 is intermittently formed in the circumferential direction. did.

  That is, four notches 67a to 67d are formed at approximately 90 ° in the circumferential direction of the extending portion 64, and therefore the extending portion 64 is also divided into four. Since the circumferential length of each of the notches 67a to 67d is formed at an angular length of about 60 °, each extending portion 64 is also formed at an angular length of about 60 °.

  Accordingly, each of the extending portions 64 can be elastically deformed in the diameter increasing direction. Therefore, when the fixing member 60 is attached to the member to be detected 50 as shown in FIG. When each extending portion 64 is pushed into the outer peripheral surface of the inclined protrusion 57 of the protruding portion 52 b, each extending portion 64 is elastically deformed in the diameter increasing direction following the tapered surface of the inclined protrusion 57. For this reason, it becomes easier to engage each extending part 64 with the engaging groove 56 by a small pushing force, and this engaging action becomes easy.

Since other configurations are the same as those in the first embodiment, the operational effects are also the same.
[Third Embodiment]
11 and 12 show the third embodiment, the basic structure is the same as that of the first embodiment, and the difference is that the through-hole 63 and the extension part 64 are formed in a four-leaf ring. .

  That is, the inner diameters of the hole edge of the through hole 63 and the inner peripheral surface of the extending portion 64 are formed slightly larger than the outer diameter of the inclined protrusion 57 of the protruding portion 52b, and the hole of the through hole 63 is formed. Four protrusions 64a to 64d that are deformed inwardly into a circular arc concave shape are formed at 90 ° positions in the circumferential direction of the edge and the extending portion 64. Each of the protrusions 64 a to 64 d is formed so that the inner diameter of a circular locus connecting the inner end edges thereof is slightly smaller than the outer diameter of the inclined protrusion 57.

Therefore, when the fixing member 60 is attached to the detected member 50, as shown in FIG. 12, when the extending portion 64 is pushed into the outer peripheral surface of the inclined protrusion 57 of the protruding portion 52b through the through hole 63, the Each protrusion 64a-64d is slidably contacted along the taper surface of the inclination protrusion 57, and slightly elastically deforms in the diameter increasing direction. Thus, since the sliding frictional resistance of only the protrusions 64a to 64d is obtained, it becomes easier to engage each extending portion 64 with the engaging groove 56 by a small pushing force, and this engaging action is facilitated. Other than that, the same operational effects as those of the first embodiment can be obtained.
[Fourth Embodiment]
FIG. 13 shows the fourth embodiment, and the fixing member 60 has the same structure as that of the first embodiment, but a part of the inclined protrusion 57 of the protruding portion 52b of the detection member 50 is cut off and intermittent in the circumferential direction. Is formed.

  That is, four notch grooves 68 are formed at a position of about 90 ° in the circumferential direction of the inclined protrusion 57, and therefore the inclined protrusion 57 is also divided into four. Since the circumferential length of each notch groove 68 is formed at an angular length of about 60 °, each inclined protrusion 57 is also formed at an angular length of about 60 °.

  Therefore, when the fixing member 60 is attached to the detected member 50, as shown in FIG. 12, when the extending portion 64 is pushed into the outer peripheral surface of each inclined protrusion 57 of the protruding portion 52b through the through hole 63, The sliding frictional resistance at each inclined protrusion 57 becomes smaller than that in the first embodiment. For this reason, it becomes easier to engage each extending part 64 with the engaging groove 56 by a small pushing force, and this engaging action becomes easy. Other than that, the same operational effects as those of the first embodiment can be obtained.

In addition, since the overall structure is simplified, the manufacturing work efficiency can be improved.
[Fifth Embodiment]
FIGS. 14-16 shows 5th Embodiment, and while the protrusion part 52b of the to-be-detected member 50 is cut off the inclination protrusion 57 currently formed in the outer peripheral surface, it is formed in flat cylinder shape, and a protrusion part An annular groove 69 as an engaging portion is formed at a position on the flange portion 54 side of 52b. On the other hand, an annular protrusion 70 as an engaging portion is integrally formed on the inner peripheral edge of the through hole 63 of the fixing member 60.

  The annular groove 69 is formed in a slit shape, and the depth thereof is deeper than the engagement groove 56 of the first embodiment or the like, and the groove width W thereof is a disk of the fixing member 60. It is formed slightly larger than the thickness width of the portion 61.

  On the other hand, the annular protrusion 70 is formed in an annular shape extending radially inward from the inner peripheral edge of the through hole 63 of the disk portion 61. When the fixing member 60 is attached to the detection member 50, the annular protrusion 70 is formed. The fixing member 60 as a whole is attached by being locked in the annular groove 69 from the radial direction.

  In addition, as shown in FIG. 16, the annular protrusion 70 is formed so that its inner diameter is sufficiently smaller than the depth of the annular groove 69, that is, the outer diameter of the bottom surface. An annular first gap C <b> 1 is formed between the peripheral surface and the bottom surface of the annular groove 69.

  Therefore, when the fixing member 60 is attached to the detected member 50, as shown in FIG. 14, the annular protrusion 70 of the disk portion 61 of the fixing member 60 is positioned on the outer peripheral edge of the protruding portion 52b. The disc 61 is pushed down with a relatively strong force by the operator's finger. Then, the annular protrusion 70 is slightly bent outward in the axial direction opposite to the pushing direction, while the inner peripheral edge is in sliding contact with the outer peripheral surface of the protruding portion 52b and the inner surface of the disc portion 61 is in contact with the flange portion 54. At the same time as the above movement is restricted, as shown in FIGS. 15 and 16, the annular protrusion 70 is locked in the annular groove 69 by its own elastic force. Thereby, the fixing member 60 is securely attached to the detected member 50.

  At this time, since the first gap C1 is formed between the inner peripheral edge of the annular protrusion 70 and the bottom surface of the annular groove 69, the motor output shaft cooperates with the second gap C2. It is possible to automatically align the member 50 to be detected with respect to the 14 axial centers.

  As described above, in the present embodiment, since the annular annular protrusion 70 is inserted into the slit-like annular groove 69 from the radial direction and engaged, the engagement force is increased, and the member 50 to be detected is engaged. On the other hand, the fixing member 60 can be firmly attached. As a result, the maintenance management becomes easy, and the fixing member 60 is inadvertently removed from the detected member 50 when the detected member 50 is attached to the motor output shaft 14 from the axial direction via the fixing member 60. It will not drop out.

The annular protrusion 70 may be formed so that a slit along the radial direction is formed at a predetermined position in the circumferential direction and can be elastically deformed by the slit.

[Sixth Embodiment]
FIGS. 17 and 18 show a sixth embodiment. An annular elastic member 71 as an engaging portion is elastically fixed to the detected member 50 on the flat outer peripheral surface of the protruding portion 52b without the inclined projection. Yes. On the other hand, the fixing member 60 has substantially the same structure as that of the first embodiment, but the inner diameter of the through hole 63 of the disc portion 61 and the extending portion 64 that is a locking portion is formed large, and the inner diameter is It is formed slightly smaller than the outer diameter of the elastic member 71.

  Further, the elastic member 71 is formed in an annular shape with a predetermined thickness, for example, by a synthetic rubber material, the width length is formed shorter than the axial length of the protruding portion 52b, and the inner diameter is the protruding portion 52b. It is formed slightly smaller than the outer diameter. Accordingly, the elastic member 71 is fixed by being tightened in a band shape by its own elastic force with respect to the outer peripheral surface of the protruding portion 52b. The elastic member 71 is formed in an arc shape so that the axial end portion 71a of the inner peripheral surface comes into contact with the arc base portion of the flange portion 54.

  Therefore, in order to attach the fixing member 60 to the detected member 50, as shown in FIG. 19, the elastic member 71 is pressed against the flange portion 54 side in advance on the outer peripheral surface of the protruding portion 52b. Keep it.

  In this state, the fixing member 60 is press-fitted into the outer peripheral surface of the elastic member 71 through the through-hole 63 and the extending portion 64 with the operator's finger, and the disc portion 61 reaches the outer side surface 54 b of the flange portion 54. If pushed in, the attachment work to the detected member 50 is completed. Thereafter, the detected member 50 is attached to the motor output shaft 14 via the fixing member 60 in the same procedure as in the first embodiment.

  As described above, since the fixing member 60 is attached to the detected member 50 only by the elastic member 71, the attaching operation is simple and the work efficiency can be improved.

In the present embodiment, the first gap does not exist, but the second gap C2 exists, and the extending portion 64 is elastically press-fitted into the elastic member 71, so that the radial movement is possible. Can perform self-alignment.
[Seventh Embodiment]
19 and 20 show a seventh embodiment, and the fixing member 60 is merely provided with only the through-hole 63 without providing the extending portion 64 at the hole edge of the through-hole 63 of the disc portion 61. On the other hand, an annular elastic member 72 that is an engaging portion is fixed to the outer peripheral surface of the flange portion 54 of the member 50 to be detected.

  The elastic member 72 is formed integrally with, for example, a synthetic rubber material, has an inner diameter that is slightly smaller than the outer diameter of the flange portion 54, and a width that is substantially the same as the width of the flange portion 54. Has been.

  Therefore, in order to attach the fixing member 60 to the member 50 to be detected, as shown in FIG. 21, the elastic member 72 is elastically fixed to the outer peripheral surface of the flange portion 54 by its own elastic force in the diameter reducing direction. deep. In this state, the fixing member 69 is fitted with the inner peripheral surface of the cylindrical portion 62 positioned on the outer peripheral surface of the elastic member 72 while being pushed by the operator. If the inner peripheral surface of the elastic member 72 moves while sliding on the outer peripheral surface of the elastic member 72 and is pushed in until the disc portion 61 abuts against the outer surface 54b of the flange portion 54, the mounting operation is completed (see FIG. 22).

  As described above, in the present embodiment, as in the sixth embodiment, the fixing member 60 is simply pushed in the axial direction with one touch, and the attachment to the detected member 50 is completed. Since it can be attached to the small-diameter portion 14b with a single touch, this attachment operation becomes extremely easy, and the cylindrical portion 62 is supported by the elastic force of the elastic member 72, so that it can be reliably attached.

  A first gap C1 is formed between the hole edge of the through-hole 63 of the disc portion 61 and the outer peripheral surface of the protruding portion 52b, and the cylindrical portion 62 is slightly moved in the radial direction by the elastic member 72. Since it is movable, self-alignment is also possible. In addition, the entire structure is simplified and the manufacturing operation is facilitated.

The present invention is not limited to the configuration of each of the above-described embodiments. For example, the drive rotator may be a pulley in addition to a sprocket.
[Second Embodiment]
21 and 22 show an embodiment of the second invention, in which a fixing member 60 is attached to a detected member 50 by a screw mechanism, and the detected member 50 has a male threaded portion 73 on the outer periphery of a protruding portion 52b. And an annular groove 74 is formed on the outer peripheral portion of the outer surface of the flange portion 54 on the cover member 5 side.

  The annular groove 74 is formed in a thin annular shape, and the outer peripheral portion in the radial direction is opened, while the inner peripheral wall surface 74a is formed in the inner peripheral portion in the radial direction.

  The fixing member 60 is formed such that the inner diameter of the through hole 63 of the disc portion 61 is larger than the outer diameter of the inner peripheral wall 74a in the radial direction of the annular groove 74, and the inner surface of the disc portion 61 is The bottom surface of the annular groove 74 can be fitted from the axial direction. Further, the thickness of the disc member 61 is formed smaller than the depth of the annular groove 74.

  An annular ring nut 75, which is a nut portion, is screwed onto the male screw portion 73 of the detected member 50. The ring nut 75 has an internal thread portion 75 a that is screwed into the external thread portion 73 on the inner peripheral surface, and an outer diameter that is substantially the same as the outer diameter of the flange portion 54. Other configurations are the same as those of the first embodiment.

  Therefore, in order to attach the fixing member 60 to the detected member 50, first, as shown in FIG. 21, the fixing member 60 is held and positioned from the upper position of the detected member 50 with the protrusion 52b as the center. The disc portion 61 is placed on the outer surface of the annular groove 74 from the axial direction.

  Thereafter, the ring nut 75 is held, and the male screw portion 73a of the projecting portion 52b is screwed from above through the female screw portion 75a, and is rotated and tightened as it is. Then, as shown in FIG. 22, the disc portion 61 is held in a sandwiched state between the ring nut 75 and the outer surface of the annular groove 74 while being fitted in the annular groove 74. . Thereby, the attachment of the fixing member 60 to the detected member 50 is completed.

  Thereafter, the detected member 50 is attached to the motor output shaft 14 via the fixing member 60 by the same operation as in the above embodiments.

  Thus, in this embodiment, since the fixing member 60 is attached to the detected member 50 by the ring nut 75, the attaching operation is facilitated and can be reliably attached.

  Further, since the first gap C1 is formed between the hole edge of the through hole 63 of the disc part 61 and the inner peripheral surface 74a of the annular groove 74, the cylindrical part 62 and the flange part second gap are formed. The self-alignment of the fixing member 60 in cooperation with C2 is the same as in the above embodiments.

As another preferred aspect of the present invention, a drive rotator to which a rotational force is transmitted from a crankshaft, a driven rotator that is provided so as to be relatively rotatable with the drive rotator, and is fixed to the camshaft, An electric motor for rotating the driven rotor relative to the drive rotor by a motor output shaft;
A cover member disposed opposite to the front end side of the electric motor from the axial direction, an insertion portion inserted and held in the distal end portion of the motor output shaft, and an outer periphery of the distal end portion of the insertion portion on the cover member side A flange portion that restricts further insertion of the insertion portion in a state of being in axial contact with the tip surface of the motor output shaft, and a protrusion portion that protrudes forward from the flange portion of the insertion portion. A detected member having a detected rotor, a disc portion having a through hole through which the protruding portion is inserted at the center, and abutting against an outer surface of the flange portion on the cover member side, and the disc A cylindrical member that protrudes in the direction of the motor output shaft at the outer peripheral edge of the portion and is fitted and fixed to the outer periphery of the tip of the motor output shaft by an elastic force via the outer peripheral surface of the flange portion And provided on the cover member, A rotation detection mechanism for detecting a rotation angle of the motor output shaft via a member, an engagement portion formed on an outer peripheral surface of the protrusion, and a hole edge of a through hole of the disc portion; A locking portion for restricting the axial movement of the detected member in cooperation with the fitting and fixing of the cylindrical portion to the outer periphery of the tip end portion of the motor output shaft in a state of being engaged with the engaging portion; And a regulating mechanism.

  As yet another preferred aspect, the engaging portion of the restricting mechanism is formed by an engaging groove.

  As still another preferred aspect, the locking portion of the restriction mechanism is extended outward from the hole edge of the through hole along the axial direction, and is extended by the extending portion that engages the engagement groove from the radial direction. Is formed.

  As another preferred embodiment, the engaging groove is formed in an annular shape over the entire outer peripheral surface of the protruding portion, while the extending portion is formed over the entire circumference of the hole edge of the through hole of the fixing member. Has been.

  As another preferred embodiment, the extension portion is formed by a plurality of arc pieces via notches formed at substantially equal intervals in the circumferential direction of the hole edge of the through hole.

  As another preferable aspect, the protruding portion is integrally formed with an inclined protrusion having a diameter-expanding taper on the outer peripheral surface from the outer peripheral edge of the tip toward the groove portion.

  As another preferred aspect, the inclined protrusion is formed in an annular shape on the entire outer peripheral surface of the protruding portion, or is formed intermittently in the circumferential direction of the outer peripheral surface of the protruding portion.

  As another preferred embodiment, the cylindrical portion of the fixing member has at least one cutout portion formed along the axial direction at a predetermined position in the circumferential direction.

  As another preferred embodiment, the engaging portion of the protruding portion is formed by a slit-like annular groove formed by cutting along the outer surface of the base portion of the flange portion, while the locking portion of the disc portion is The circular plate portion is formed by an annular protrusion that extends radially inward from the edge of the through hole of the disk portion and engages in the annular groove from the radial direction.

  As another preferred mode, a guide surface is formed on the inner peripheral surface of the front end portion of the motor output shaft so as to be gradually enlarged in diameter from the front end surface side to the inner direction.

  As still another preferred aspect, the fixing member is integrally formed by press molding.

  As another preferred aspect, the engaging portion of the restriction mechanism is formed by an elastic member that elastically contacts the locking portion from the outside in the radial direction.

  As another preferred embodiment, the elastic member is formed in an annular shape that is fixed to the outer peripheral surface of the protruding portion by its own elastic force, while the locking portion is axially outward from the hole edge of the through hole. And is formed by a cylindrical extending portion that is in pressure contact with the outer surface of the elastic member from the outside in the radial direction.

  As another preferred embodiment, an adjustment mechanism that allows the detected member to move in the radial direction is formed between the engaged engaging portion and the engaging portion.

  Furthermore, as another preferred embodiment, a driving rotating body to which a rotational force is transmitted from the crankshaft, a driven rotating body that is provided so as to be relatively rotatable with the driving rotating body and is fixed to the camshaft, and a cylindrical motor output An electric motor for rotating the driven rotating body relative to the driving rotating body by a shaft; a cover member disposed opposite to the front end side of the electric motor from the axial direction; and an interior of the front end side of the motor output shaft An insertion portion that is inserted and held in the insertion portion, and an outer periphery of a tip portion of the insertion portion on the cover member side, and further insertion of the insertion portion in a state where the insertion portion is in contact with the front end surface of the motor output shaft from the axial direction. There is a detected member having a flange portion to be controlled and a detected rotor provided in a protruding portion protruding forward from the flange portion of the insertion portion, and a through hole through which the protruding portion is inserted is provided in the center. And before A disc portion that abuts on the outer surface of the flange portion on the cover member side, and protrudes in the direction of the motor output shaft at the outer peripheral edge of the disc portion, and the tip of the motor output shaft passes through the outer peripheral surface of the flange portion A fixing member having a cylindrical part fitted and fixed to the outer periphery of the part by an elastic force, and a rotation detection mechanism that is provided on the cover member and detects a rotation angle of the motor output shaft via the detected member. An annular groove formed on the outer peripheral portion of the outer surface of the flange portion on the cover member side, and the inner peripheral portion of the through hole side of the disc portion is fitted from the axial direction, and the outer peripheral surface of the protruding portion And an annular nut portion that holds the inner peripheral portion of the disc portion in the bottom surface of the annular groove in a state of being fastened to the male screw portion, and the motor output In cooperation with the fixing of the cylindrical portion to the outer periphery of the tip of the shaft, A restriction mechanism for restricting the movement direction, with a.

  As another preferable aspect, the inner peripheral edge of the through hole of the disk part is formed in a state where the inner peripheral part of the disk part is fitted into the annular groove from the axial direction and the nut part is fastened to the female screw part. And a gap between the inner circumferential edge and the inner circumferential surface on the radial side of the annular groove facing from the radial direction.

1. Timing sprocket (drive rotor)
DESCRIPTION OF SYMBOLS 1a ... Sprocket body 2 ... Camshaft 3 ... Phase change mechanism 4 ... Cover member 5 ... Motor housing 8 ... Electric motor 9 ... Follower member (follower rotating body)
DESCRIPTION OF SYMBOLS 11 ... Electric motor 12 ... Deceleration mechanism 14 ... Motor output shaft 14a ... Large diameter part 14b ... Small diameter part 14d ... Insertion hole 16 ... Feed plate 21 ... Ring groove 21a ... Step surface (step part)
28 ... Cover body 35 ... Angle sensor (rotation angle detection mechanism)
40 ... Fitting groove 50 ... Detected member 51 ... Detecting body 52 ... Supporting portion (insertion portion)
52a ... cylindrical base 52b ... tip 52b ... projections 53a to 53c ... detected rotor (detected part)
54 ... Flange 54a ... Inner side 54b ... Outer side 56 ... Engagement groove (engagement part)
60 ... fixing member 61 ... disc part 62 ... cylindrical part (fitting and fixing part)
63 ... through hole 64 ... extension part (locking part)
64a to 64d ... projecting parts 65a to 65d ... notch part 66 ... fitting part 67a to 67d ... notch part 68 ... notch groove 69 ... annular groove 71 ... elastic member 72 ... elastic member 73 ... male screw part 74 ... annular groove 75 ... Ring nut (nut part)
75a ... Female thread

Claims (16)

A driving rotating body to which rotational force is transmitted from the crankshaft;
A driven rotator which is provided so as to be rotatable relative to the drive rotator and is fixed to the camshaft;
An electric motor for rotating the driven rotor relative to the drive rotor by a cylindrical motor output shaft;
A cover member disposed opposite to the front end side of the electric motor from the axial direction;
An insertion portion that is inserted and held in the distal end portion of the motor output shaft, and an outer periphery of the distal end portion of the insertion portion on the cover member side, and is inserted in a state in which the insertion portion is in contact with the distal end surface of the motor output shaft from the axial direction. A detected member having a flange part that restricts further insertion of the part, and a detected rotor provided in a protruding part protruding forward from the flange part of the insertion part,
A disk portion that has a through-hole through which the protruding portion is inserted, abuts against the outer surface of the flange portion on the cover member side, and protrudes in the motor output shaft direction on the outer peripheral edge of the disk portion; A fixing member having a fitting fixing portion fitted and fixed to the outer periphery of the tip end portion of the motor output shaft via the outer peripheral surface of the flange portion;
A rotation detection mechanism provided on the cover member and detecting a rotation angle of the motor output shaft via the detected member;
An engaging portion formed on the outer peripheral surface of the protruding portion and a shaft of the fixing member with respect to the detected member provided at the hole edge of the through hole of the disc portion and engaging with the engaging portion A restricting mechanism that restricts movement in the direction, and
A gap formed between the engaging portion and the locking portion in an engaged state, and allowing a radial movement of the detected member;
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 valve timing control device for an internal combustion engine, wherein the engagement portion of the restriction mechanism is formed by an engagement groove. The valve timing control device for an internal combustion engine according to claim 2,
The locking portion of the restriction mechanism is formed by an extending portion that extends along the axial direction from a hole edge of the through hole and engages with the engaging groove from the radial direction. A valve timing control device for an internal combustion engine. The valve timing control apparatus for an internal combustion engine according to claim 3,
The engaging groove is formed in an annular shape on the entire outer peripheral surface of the protruding portion, while the extending portion is formed over the entire circumference of the hole edge of the through hole of the fixing member. A valve timing control device for an internal combustion engine. 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 extension portion is formed by a plurality of arc pieces through notches formed at substantially equal intervals in the circumferential direction of the hole edge of the through hole. . The valve timing control device for an internal combustion engine according to claim 2,
The valve timing control device for an internal combustion engine, wherein the projecting portion is integrally formed with an inclined projection having a diameter-expanding taper from the outer peripheral edge toward the groove portion on the outer peripheral surface. The valve timing control apparatus for an internal combustion engine according to claim 6,
The valve timing control device for an internal combustion engine, wherein the inclined protrusion is formed in an annular shape on the entire outer peripheral surface of the protruding portion, or is formed intermittently in the circumferential direction of the outer peripheral surface of the protruding portion. . 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 cylindrical portion of the fixing member has at least one notch portion formed in a predetermined position in the circumferential direction along the axial direction. The valve timing control apparatus for an internal combustion engine according to claim 1,
While the engaging portion of the protruding portion is formed by a slit-shaped annular groove formed by cutting along the outer surface of the base portion of the flange portion,
The locking portion of the disc portion is formed by an annular protrusion that extends radially inward from a hole edge of the through hole of the disc portion and engages in the annular groove from the radial direction. A valve timing control device for an internal combustion engine. 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 guide surface is formed on the inner peripheral surface of the front end portion of the motor output shaft so as to increase in diameter from the front end surface side of the front end portion toward the inside. 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 fixing member is integrally formed by press molding. 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 engaging portion of the restriction mechanism is formed by an elastic member that elastically contacts the locking portion from the outside in the radial direction. The valve timing control device for an internal combustion engine according to claim 12,
While the elastic member is formed in an annular shape that is fixed to the outer peripheral surface of the protrusion by its own elastic force,
The locking portion is formed by a cylindrical extending portion that extends axially outward from the hole edge of the through hole and presses against the outer surface of the elastic member from the radial outer side. A valve timing control device for an internal combustion engine. 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 an adjustment mechanism that allows movement of the detected member in the radial direction is formed between the engaged engaging portion and the engaging portion. A driving rotating body to which rotational force is transmitted from the crankshaft;
A driven rotator which is provided so as to be rotatable relative to the drive rotator and is fixed to the camshaft;
An electric motor for rotating the driven rotor relative to the drive rotor by a cylindrical motor output shaft;
A cover member disposed opposite to the front end side of the electric motor from the axial direction;
An insertion portion that is inserted and held inside the tip end side of the motor output shaft, and is provided on the outer periphery of the tip end portion of the insertion portion on the cover member side, in a state of being in contact with the front end surface of the motor output shaft from the axial direction A detected member having a flange portion that restricts further insertion of the insertion portion, and a detected rotor provided in a protruding portion protruding forward from the flange portion of the insertion portion;
There is a through-hole through which the projecting portion is inserted, and a disc portion that abuts on the outer surface of the flange portion on the cover member side, and the outer peripheral edge of the disc portion projects in the motor output shaft direction. A fixing member having a cylindrical portion fitted and fixed to the outer periphery of the tip end portion of the motor output shaft by an elastic force via the outer peripheral surface of the flange portion;
A rotation detection mechanism provided on the cover member and detecting a rotation angle of the motor output shaft via the detected member;
An annular groove formed on the outer peripheral portion of the outer surface of the flange portion on the cover member side, the inner peripheral portion on the through hole side of the disc portion is fitted from the axial direction, and the outer peripheral surface of the protruding portion The motor output shaft having a formed male screw portion and an annular nut portion that holds the inner peripheral portion of the disc portion in the bottom surface of the annular groove in a state of being fastened to the male screw portion. A regulation mechanism that regulates the axial movement of the detected member in cooperation with the fixing of the cylindrical portion with respect to the outer periphery of the tip portion of
A valve timing control apparatus for an internal combustion engine, comprising: The valve timing control device for an internal combustion engine according to claim 15,
The inner peripheral part of the disk part is fitted in the annular groove from the axial direction, and the nut part is fastened to the female thread part, and the inner peripheral edge of the through hole of the disk part and the inner peripheral edge have a diameter. A valve timing control device for an internal combustion engine, characterized in that a gap is formed between the inner circumferential surface on the radial direction side of the annular groove facing from the direction.

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