JPWO2016143593A1 - Valve timing control device for internal combustion engine and method for manufacturing the valve timing control device - Google Patents

Abstract

An electric motor for rotating the camshaft relative to the timing sprocket, an eccentric shaft portion provided on the motor output shaft of the electric motor, the outer peripheral surface being eccentric with respect to the rotation center, and the sprocket body are integrally coupled, An inner tooth constituent portion having a plurality of inner teeth formed on the inner periphery, a plurality of rollers 48 disposed between the outer peripheral surface of the eccentric shaft portion and each of the inner teeth, and a fixed end portion 9a of the driven member 9 And a retainer 41 having a roller retaining hole 41c that retains each of the rollers. The retainer includes an outer peripheral surface and an inner periphery of a region including a hole edge of each roller retaining hole. Annular concave relief grooves 42a and 42b, in which the grinding tool is in a non-contact state, were cut out on the surface. Accordingly, it is possible to suppress a decrease in durability and a decrease in grinding efficiency of the grinding tool for grinding the cage.

Description

  The present invention relates to a valve timing control device for an internal combustion engine that controls the opening and closing timing of, for example, an intake valve and an exhaust valve, and a method for manufacturing the valve timing control device.

  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.

  In this valve timing control device, the rotational force of a DC electric motor is transmitted to a driven member via a speed reduction mechanism, so that the camshaft is rotated relative to the timing sprocket.

  The speed reduction mechanism is a roller type, and when the eccentric shaft portion rotates eccentrically with the rotation of the motor output shaft of the electric motor, the outer peripheral surface of the ball bearing on the outer peripheral side of the eccentric shaft portion and a plurality of internal tooth components A plurality of rollers arranged between the inner teeth of the inner teeth are guided in the radial direction within the roller holding holes of the cage every rotation of the motor output shaft, and the other teeth that pass over the crests of the inner teeth are adjacent to each other. It moves while rolling to the inner teeth and rolls in the circumferential direction while repeating this in sequence. Thereby, the rotation of the motor output shaft is transmitted to the driven member while being decelerated.

JP 2012-197755 A

  By the way, the retainer retains each roller in a freely rolling manner inside each roller retaining hole. However, when forming the retainer including the roller retaining hole, that is, each roller retaining hole is opened. After the opening process, the outer peripheral surface of the retainer is finished with a grinding tool in order to ensure a minute clearance accuracy with the tip of the internal tooth.

  However, when finishing the outer peripheral surface, since the entire outer peripheral surface including the roller holding holes is processed by the grinding tool, the grinding tool passes through the roller holding holes. At this time, the leading edge of the roller holding hole is easily damaged. As a result, the grinding tool must be replaced in a short time, resulting in a decrease in the durability of the grinding tool.

  The present invention has been devised in view of the above-described conventional technical problems, and an object of the present invention is to provide a valve timing control device for an internal combustion engine that can suppress a decrease in durability of a grinding tool for grinding a cage. It is said.

According to the first aspect of the present invention, there is provided a driving rotator to which a rotational force is transmitted from a crankshaft, a driven rotator to which a rotational force of the drive rotator is transmitted and provided integrally with a camshaft, An electric motor for rotating the driven rotator relative to the drive rotator, an eccentric shaft portion provided on a motor output shaft of the electric motor and having an outer peripheral surface eccentric with respect to the rotation center, and the drive rotation An internal tooth component having a plurality of internal teeth that are provided on the body and disposed opposite to the outer peripheral surface of the eccentric shaft portion in the radial direction; and the outer peripheral surface of the eccentric shaft portion and the internal teeth of the internal tooth component portion A plurality of rollers disposed between, and a cylindrical retainer provided in the driven rotating body, wherein a plurality of through portions that hold the plurality of rollers are formed in a predetermined region in the axial direction,
The retainer is characterized in that an annular recess is formed on at least one of an outer peripheral surface and an inner peripheral surface of a region including the entire hole edge of each through portion.

  According to this invention, the fall of the durability of the grinding tool which grinds a holder | retainer can be suppressed.

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 components 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 a rear view of the electric power feeding plate provided to this embodiment. It is a longitudinal cross-sectional view of the follower member and holder | retainer which are provided to this embodiment. It is the C section enlarged view of FIG. It is a principal part expanded sectional view which shows 2nd Embodiment of this invention.

  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, but can also be applied to the exhaust valve side.

  As shown in FIGS. 1 and 2, the valve timing control device is rotatably supported on a timing sprocket 1 that is a first member that is rotationally driven by a crankshaft of an internal combustion engine, and a cylinder head 01 via a bearing 02. And a camshaft 2 which is provided relative to the timing sprocket 1 and is rotated by a driven member 9 which is a second member to be described later by a rotational force transmitted from the timing sprocket 1, and the timing A phase change mechanism 3 disposed between the sprocket 1 and the camshaft 2 to change the relative rotational phases of the two and 1 according to the engine operating state, and a cover member disposed on the front end side of the phase change mechanism 3 4 is 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. A gear portion 1b that receives the rotational force from the crankshaft via the timing chain, an internal gear component portion 19 that is integrally provided on the front end side of the sprocket body 1a and that constitutes a part of the speed reduction mechanism 12 described later, It is composed of

  The timing sprocket 1 has a single large-diameter ball bearing 43 interposed between the sprocket body 1a and the driven member 9 provided at the front end of the camshaft 2. The timing sprocket 1 and the camshaft 2 are supported by a bearing 43 so as to be relatively rotatable.

  The large-diameter ball bearing 43 is composed of an outer ring 43a and an inner ring 43b, and a ball 43c interposed between the two rings, and the outer ring 43a is fixed to the inner peripheral side of the sprocket body 1a. On the other hand, the inner ring 43 b is press-fitted and fixed to the outer peripheral side of the driven member 9.

  The sprocket body 1a is formed with an annular groove-shaped outer ring fixing portion 1b opened on the camshaft 2 side on the inner peripheral side. The outer ring fixing portion 1b is formed in a stepped diameter shape, and the outer ring 43a of the large-diameter ball bearing 43 is press-fitted in the axial direction, and the outer ring 43a is positioned on one side in the axial direction. .

  The internal tooth component 19 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 of the phase change mechanism 3, and has a plurality of wave shapes on the inner periphery. The inner teeth 19a are formed.

  Further, an annular holding plate 20 is arranged at the rear end portion of the sprocket body 1a opposite to the internal tooth constituent portion 19. The holding plate 20 is integrally formed of a metal plate material. As shown in FIGS. 1 and 4, the outer diameter is set to be substantially the same as the outer diameter of the sprocket body 1a, and the inner diameter is the large-diameter ball. The diameter is set smaller than the inner diameter of the outer ring of the bearing 43.

  The inner peripheral portion 20a of the holding plate 20 is disposed in contact with the outer end surface of the outer ring 43a in the axial direction, and protrudes radially inward, that is, toward the central axis direction at a predetermined position of the inner peripheral edge. The stopper convex part 20b is provided integrally.

  The stopper projection 20b is formed in a substantially fan shape, and the tip edge 20c is formed in an arc shape along an arcuate inner peripheral surface of a stopper groove 2b described later. Further, six bolt insertion holes 20d through which the respective bolts 7 are inserted are formed through the outer peripheral portion of the holding plate 20 at equal intervals in the circumferential direction.

  Six bolt insertion holes 1c and 20d are formed in the outer peripheral portions of the sprocket main body 1a (internal tooth constituting portion 19) and the holding plate 20 at substantially equal intervals in the circumferential direction. The sprocket body 1a and the internal gear component 19 are configured as a casing of the speed reduction mechanism 12 described later.

  As shown in FIG. 1, the motor housing 5 includes the housing body 5 a formed by pressing a ferrous metal material into a bottomed cylindrical shape, and a power feeding plate 11 that seals the front end opening of the housing body 5 a. It is equipped with.

  The housing body 5a has a disk-shaped partition wall 5b on the rear end side, and a large-diameter shaft insertion hole 5c through which an eccentric shaft portion 39 to be described later is inserted is formed in the approximate center of the partition wall 5b. In addition, a cylindrical extending portion 5d protruding in the axial direction of the camshaft 2 is integrally provided at the hole edge of the shaft insertion hole 5c. A female screw hole 6 is formed along the axial direction inside the outer peripheral portion of the partition wall 5b. In addition, the said internal-tooth structure part 19 is contact | abutted from the axial direction at the rear-end surface of the partition 5b of the housing main body 5a.

  The female screw hole 6 is formed at a position corresponding to each of the bolt insertion holes 1c and 20d, and the timing sprocket 1 (internal gear component 19) and the holding plate 20 are formed by six bolts 7 inserted through these holes. And the housing main body 5a is fastened together from the axial direction.

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

  As shown in FIGS. 1 and 4, the flange portion 2 a is joined from the axial direction by the cam bolt 10 with the front end surface being in contact with the driven member 9 from the axial direction, A stopper recess 2b into which the stopper protrusion 20b of the plate 20 is engaged is formed 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 20b rotated within this length range are in contact with the opposing edges 2c and 2d in the circumferential direction, 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.

  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 the 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 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. A cylindrical portion 9b that protrudes in the axial direction from the inner peripheral front end surface, and a cylindrical retainer 41 that is formed integrally with the outer peripheral portion of the fixed end portion 9a and holds a plurality of rollers 48. Yes.

  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 pressed and fixed to the flange portion 2 a from the axial direction by the axial force of the cam bolt 10.

  As shown in FIG. 1, the cylindrical portion 9b has an insertion hole 9c through which the shaft portion 10b of the cam bolt 10 is inserted, and a needle bearing 38 on the outer peripheral side.

  The phase change mechanism 3 includes the electric motor 8 disposed on the front end side of the cylindrical portion 9b of the driven member 9, a speed reduction mechanism 12 that reduces the rotational speed of the electric motor 8 and transmits the speed to the camshaft 2. Is mainly composed of

  As shown in FIGS. 1 and 2, the electric motor 8 is a brushed DC motor, a motor housing 5 that is a yoke that rotates integrally with the timing sprocket 1, and rotates inside the motor housing 5. The motor output shaft 13 provided freely, four arc-shaped permanent magnets 14 each being a stator fixed to the inner peripheral surface of the motor housing 5 by an adhesive, and the above-mentioned fixed to the front end of the motor housing 5 And a power supply plate 11.

  The motor output shaft 13 is formed in a stepped cylindrical shape and functions as an armature, and has a large diameter portion 13a on the camshaft 2 side and a cover member 4 side through a stepped portion 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 fixed to the outer periphery, and an eccentric shaft portion 39 constituting a part of the speed reduction mechanism 12 is integrally formed on the rear end side.

  On the other hand, the commutator 21 is press-fitted and fixed to the outer periphery of the small-diameter portion 13b. The commutator 21 is fixed to the annular member 21a fixed to the outer periphery of the small-diameter portion 13b and the outer peripheral surface of the annular member 21a. And an annular conductive portion 21b. The annular member 21a has an outer diameter set to be substantially the same as the outer diameter of the large diameter portion 13a, and is disposed at a substantially central position in the axial direction of the small diameter portion 13b.

  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, and the inner peripheral portion of the iron core rotor 17 is the motor output. The shaft 13 is fixed to the outer periphery of the stepped portion while being positioned in the axial direction.

  On the other hand, in the commutator 21, a terminal of the coil wire from which the coil 18 is drawn is electrically connected to each segment in which the conductive portion 21 b is divided into the same number as the number of poles of the iron core rotor 17.

  Each of the permanent magnets 14 is disposed with a predetermined gap in the circumferential direction and is formed in a cylindrical shape as a whole, and has a plurality of magnetic poles in the circumferential direction, and its axial position is the iron core rotor 17. The power supply plate 11 is offset from the axial center.

  As shown in FIGS. 1 and 5, the power supply plate 11 includes a disk-shaped metal plate portion 16 made of an iron-based metal material, and a disc integrally provided on both front and rear side surfaces of the metal plate portion 16. And a resin portion 22 having a shape. The power feeding plate 11 is configured as a part of a power feeding mechanism for the electric motor 8.

  The metal plate 16 is positioned and fixed by caulking an annular stepped groove formed on the inner periphery of the front end portion of the motor housing 5 with an outer peripheral portion 16a not covered with the resin portion 22 being centered. A shaft insertion hole 16b through which the small diameter portion 13b of the motor output shaft 13 and the like are inserted is formed through the portion. Further, the metal plate 16 is formed by punching two rectangular holding holes 16c, 16d at predetermined positions continuous to the inner peripheral edge of the shaft insertion hole 16b, and each holding hole 16c, 16d includes: Brush holders 23a and 23b described later are fitted and held.

  As shown in FIGS. 1 and 5, the power supply plate 11 is disposed inside the holding holes 16 c and 16 d of the metal plate 16, and has a plurality of rivets 40 on the front end portion 22 a of the resin portion 22. And a pair of copper cylindrical brush holders 23a, 23b fixed inside and slidably accommodated in the radial direction inside the brush holders 23a, 23b, with the spring force of the coil springs 24a, 24b. A pair of switching brushes 25a and 25b, which are commutators in which each arcuate tip surface is elastically contacted with the outer peripheral surface of the conductive portion 21b of the commutator 21 from the radial direction, and the front end portion 22a side of the resin portion 22, respectively. The inner and outer double power supply slip rings 26a and 26b fixed with the mold with the outer surface exposed, the switching brushes 25a and 25b and the slip rings 26a, Harness 27a 6b which is a conductor for electrically connecting, and 27b, are provided.

  The small slip ring 26a on the inner peripheral side and the large diameter slip ring 26b on the outer peripheral side 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 disc shape, and is disposed on the front end side of the power supply plate 11 so as to face the front end portion of the housing body 5 a so as to cover the front end portion. And is composed of a disc plate-like cover main body 28 and a synthetic resin cover 29 that covers the front end of the cover main body 28.

  The cover body 28 includes an outer layer portion 28a formed with a predetermined thickness from a synthetic resin material, and a reinforcing portion 28b as a core material fixed to the inside of the outer layer portion 28a.

  The outer layer portion 28a is formed in a substantially disc shape, and has an outer diameter larger than the outer diameter of the housing body 5a, and an arc-shaped boss portion 28c projecting at four locations on the outer peripheral portion. Bolt insertion holes 28d through which bolts 61 fixed to the chain case 60, which is a conductive member, are inserted are respectively formed in four metal sleeves 28e molded with a resin material.

  In addition, in FIG. 6 of the outer layer portion 28a, two lower left and right boss portions 28c, 28c are formed with circular opening windows that face pin insertion holes 28j formed in the reinforcing portion 28b described later. Yes.

  The reinforcing portion 28b is integrally formed of an aluminum alloy material, and is formed in a substantially disk-like flat plate shape smaller than the outer diameter of the outer layer portion 28a. Two extending portions having a letter shape project from the radial direction. In each of the extending portions, the pin insertion holes 28j and 28j for positioning are formed to penetrate at positions corresponding to the respective opening windows of the outer layer portion 28a.

  When the cover member 4 is attached to the chain case 60 with the bolts 61, the pin insertion holes 28j allow the two positioning pins 62 and 62, which are positioning convex portions, to be inserted to position the cover body 28 with respect to the chain case 60. It is to be offered to.

  The chain case 60 is integrally formed of an aluminum alloy material, and is disposed so as to cover the entire outer periphery such as the phase changing mechanism 3 such as the timing sprocket 1 and the electric motor 8 and the tip of the crankshaft protruding from the cylinder block. ing. Further, as shown in FIG. 1, the chain case 60 is formed with four female screw holes 60b into which the front ends of the bolts 61 are screwed at predetermined positions on the front end surface 60c of the annular front end 60a. In addition, two pin press-fitting holes (not shown) are formed at the lower position of the front end face 60c. On the other hand, the rear end portion is fixed to a cylinder head (not shown) made of an aluminum alloy material for an internal combustion engine by bolts.

  As shown in FIG. 8, a seal groove 28k is formed on one end surface of the outer peripheral portion 28a, and the space between the front end surface 60c of the front end portion 60a of the chain case 60 is sealed in the seal groove 28k. A synthetic rubber seal member 55 is fitted and fixed.

  The cover portion 29 has an outer peripheral shape that is substantially U-shaped along the inner peripheral shape of the receiving groove 49, and an annular locking convex portion 29 a that is integrally formed on the outer peripheral edge. It is fitted and fixed by press-fitting from the axial direction into a locking groove formed at the peripheral edge of the housing groove.

  As shown in FIG. 2, the cover main body 28 has a pair of copper-made brush holders 30a, 30b made of copper and fixed in the axial direction at positions facing the slip rings 26a, 26b in the axial direction. ing. In each brush holder 30a, 30b, a pair of power supply brushes 31a, 31b whose tip surfaces are in sliding contact with the slip rings 26a, 26b are slidably held in the axial direction.

  The brush holders 30 a and 30 b and the power supply brushes 31 a and 31 b are arranged side by side on the inner side and the outer side of the cover main body 28, and their rear end portions face the outer side surface of the cover main body 28.

  Further, as shown in FIG. 1, a circular concave groove 36a is formed at a substantially central position of the inner end surface of the cover main body 28 on the electric motor 8 side. The groove 36a is formed to be recessed outward in the axial direction of the cover main body 28, and has an inner diameter larger than an outer diameter of a distal end portion 50b of the detected portion 50, which will be described later, and its depth is the cover main body. It is formed to be slightly smaller than the axial length of 28 and has a thin bottom wall.

  Each of the power supply brushes 31 a and 31 b is urged in the direction of each slip ring by a torsion coil spring (not shown) provided on the front end surface of the cover member 4.

The torsion coil springs are arranged in parallel and linearly with respect to the respective power supply brushes 31a and 31b. Each of the brush holders 30a and 30b is formed with an opening at the front and rear ends, and from the opening on the front end side. The front end portions of the power supply brushes 31a and 31b are movable forward and backward, and the rear end side portions of the power supply brushes 31a and 31a through slit holes (not shown) formed in the longitudinal direction of the respective side walls. One end of the pigtail harness is connected to the stub.

  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.

  A power supply connector 33 for supplying current from a battery to the power supply brushes 31a and 31b via a control unit (not shown) is integrally provided at the lower end of the cover body 28. A signal connector 34 for outputting the rotation angle signal detected by the section 51 to the control unit is provided in parallel with the power supply connector 33 and along the radial direction.

  The power feeding connector 33 has an opening projecting from the lower end on the outer peripheral side of the cover main body 28 along the radial direction, and a pair of elongated terminal pieces made of a conductive material embedded in the cover main body 28. Each of the one end portions exposed to the outside is connected to the pigtail harness. Further, the other end portion disposed inside the opening and exposed to the outside is connected to the female connector terminal on the control unit side.

  On the other hand, as shown in FIG. 1, the signal connector 34 has an opening formed substantially along the radial direction at the lower end on the outer peripheral side of the cover member 4, and is formed in parallel with the opening of the power supply connector 33. In addition, the overall width is substantially the same as the width of the cover member 4. The signal connector 34 has a plurality of terminal pieces 34 a made of a conductive material partially embedded in the cover body 28, and three connection end portions 34 b exposed to the outside are integrated on the printed circuit board 53. In addition to being connected to the circuit 54, the other end 34c is connected to a female connector terminal (not shown) on the control unit side.

  Between the small diameter portion 13b of the motor output shaft 13 and the central portion sandwiching the bottom wall of the concave groove 36a of the cover main body 28 is an angle detection mechanism that detects the rotational angle position of the motor output shaft 13. An angle sensor 35 is provided.

  This angle sensor 35 is an electromagnetic induction type, and as shown in FIG. 1, is fixed to the detected portion 50 fixed in the small diameter portion 13 b of the motor output shaft 13 and the substantially central position of the cover main body 28. And a detection unit 51 that receives a detection signal from the detected unit 50.

  The detected portion 50 is formed in a substantially bottomed cylindrical shape made of a synthetic resin material, and a three-leaf thin rotor to be detected 52 is fixed to the outer surface of the bottom wall of the axial front end portion. An annular protrusion 50a that is press-fitted into the small diameter portion 13b of the motor output shaft 13 is integrally provided on the outer periphery.

  The detected portion 50 has an outer diameter smaller than the inner diameter of the concave groove 36 a, and a tip portion protruding from the tip of the small diameter portion 13 b of the motor output shaft 13 is the concave groove of the cover body 28. The rotor 52 to be detected is disposed so as to be opposed to the bottom surface of the thin bottom wall of the concave groove 36a with a minute gap C interposed therebetween.

  The detection unit 51 includes a substantially rectangular printed board 53 extending in a radial direction from a substantially central position of the cover main body 28, and an integrated circuit (ASIC) provided on the outer surface of one end of the printed board 53 in the longitudinal direction. ) 54 and a receiving circuit and an oscillating circuit (not shown) provided on the other end side of the same outer surface as the integrated circuit 54.

  The printed circuit board 53 has a positioning small hole formed in the center of the reception and oscillation circuit (not shown). The positioning small hole is press-fitted into the positioning projection 28n so that the detected rotor 52 The center and the center of the receiving and oscillating circuit are positioned.

  The printed circuit board 53 is fixed to the front end surface of the cover main body 28 by a predetermined fixing means such as a screw. The receiving and oscillating circuit has a small gap C between the bottom wall of the concave groove 36a. Via the axial direction of the rotor 52 to be detected.

  Therefore, when the detected rotor 52 rotates with the rotation of the motor output shaft 13, an induced current flows between the receiving / transmitting circuit (not shown) and the detected rotor 52. By the action, the integrated circuit 54 detects the rotation angle of the motor output shaft 13 and outputs this detection signal to the control unit.

  The motor output shaft 13 and the eccentric shaft portion 39 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. And the needle bearing 38 arranged on the side in the axial direction.

  The needle bearing 38 includes a cylindrical bearing retainer 38a press-fitted into the inner peripheral surface of the eccentric shaft portion 39, and a needle roller 38b that is a plurality of rolling elements rotatably held inside the bearing retainer 38a. It 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 motor output shaft 13 (eccentric shaft portion 39) and the inner peripheral surface of the extending portion 5d of the motor housing 5, lubricating oil from the inside of the speed reduction mechanism 12 to the electric motor 8 is provided. A small-diameter oil seal 46 is provided to prevent this leakage.

  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, an accelerator opening sensor, etc., not shown, and based on this detection information In addition to performing engine control, the coil 18 is energized through the power supply brushes 31a and 31b, the slip rings 26a and 26b, the switching brushes 25a and 25b, the commutator 21, and the like to perform rotation control of the motor output shaft 13. The speed reduction mechanism 12 controls the relative rotation phase of the camshaft 2 with respect to the timing sprocket 1.

  As shown in FIGS. 1 to 3, the speed reduction mechanism 12 is provided on the outer periphery of the eccentric shaft portion 39 and the eccentric shaft portion 39 that is integrally coupled to the motor output shaft 13 and performs an eccentric rotational motion. Medium diameter ball bearing 47, the roller 48 provided on the outer periphery of the medium diameter ball bearing 47, the retainer 41 that allows the movement in the radial direction while holding the roller 48 in the rolling direction, and the holding It is mainly comprised from the said driven member 9 integral with the vessel 41.

  As shown in FIG. 1, the eccentric shaft portion 39 is slightly eccentric in the radial direction from the axis of the motor output shaft 13 with respect to the axis of the cam surface 39 a formed on the outer peripheral surface.

  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 39, whereas the outer ring 47b is in a free state without being fixed in the axial direction. In other words, the outer ring 47b has an axial end of the electric motor 8 that does not come into contact with any part, and the axial end of the outer ring 47b faces the inner side of the base 41a of the retainer 41 facing the outer ring 47b. A minute first gap C1 is formed and is in a free state.

  Further, the outer peripheral surface of each roller 48 is in contact with the outer peripheral surface of the outer ring 47b so as to be able to roll, and between the outer peripheral surface of the outer ring 47b and the cylindrical portion 41b of the retainer 41. An annular second gap C2 is formed, and the second intermediate gap C2 allows the entire medium-diameter ball bearing 47 to move in the radial direction along with the eccentric rotation of the eccentric shaft portion 39, that is, eccentrically movable. Yes.

  Each of the rollers 48 is formed of an iron-based metal, and is fitted in the internal teeth 19a of the internal tooth component 19 while moving in the radial direction along with the eccentric movement of the medium-diameter ball bearing 47, and the retainer 41 The roller holding hole 41c is oscillated in the radial direction while being guided in the circumferential direction by both side edges.

  As shown in FIGS. 1, 6, and 7, 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 9 a, and extends in the same direction as the cylindrical portion 9 b. It is formed in a protruding cylindrical shape.

  The retainer 41 includes a cylindrical base portion 41a integrally coupled to the fixed end portion 9a of the driven member 9, a cylindrical portion 41b extending in the axial direction from the base portion 41a, and a shaft of the cylindrical portion 41b. The roller holding hole 41c, which is a through portion that is formed so as to penetrate substantially in the center in the direction and that holds the plurality of rollers 48 in a rollable manner, is provided.

  The base portion 41a extends in the radial direction from the outer peripheral edge of the front end of the fixed end portion 9a, and is further bent into an L shape in the axial direction. The outer cylindrical portion 41d, which is an annular portion extending in the axial direction, has the cylindrical shape. It is continuously and integrally coupled to the portion 41b.

  The cylindrical portion 41b extends in the direction of the partition wall 5b of the motor housing 5 through an annular concave housing space in which a tip end portion 41e is separated by the internal tooth constituent portion 19 and the partition wall 5b.

  The roller holding portion 41c is formed in a rectangular shape elongated in the front-rear direction with the tip end side closed, and a plurality of the roller holding portions 41c are formed at equal intervals in the circumferential direction. This is less than the total number of teeth of the internal teeth 19a of the internal tooth component 19, and thereby a reduction ratio is obtained.

  Further, recess grooves 42a and 42b, which are recesses, are formed in the outer peripheral surface and the inner peripheral surface of the cylindrical portion 41b, that is, the inner peripheral surface and the outer peripheral surface of the cylindrical portion 41b including the forming portion of the roller holding hole 41c. Has been.

  As shown in FIGS. 6 and 7, both the escape grooves 42 a and 42 b are formed in an annular concave shape, and a cylindrical shape including a roller holding hole 41 c from the leading edge of the outer cylindrical portion 41 d of the base portion 41 a. It extends to the tip 41e of the portion 41b. Further, the depth dimensions of the escape grooves 42a and 42b, that is, the depth dimensions D and D from the inner peripheral surface and the outer peripheral surface of the outer cylinder portion 41d are set to a depth of about 0.1 to 0.2 mm, respectively. Has been.

Further, the surface roughness of the inner peripheral surface and the outer peripheral surface of the outer cylindrical portion 41d is formed higher than the surface roughness of the inner peripheral surface and the outer peripheral surface of the escape grooves 42a, 42b (cylindrical portion 41b). Yes.
[Cage processing method]
That is, in order to mold the retainer 41, first, the rough material of the driven member 9 is bent into a L-shaped cross section as described above by a press molding machine, and then the base 41a and the cylindrical portion are formed. The entire outer surface of 41b is cut to adjust the shape.

  Next, both the escape grooves 42a and 42b having a depth of about 0.1 to 0.2 mm are formed on the inner and outer peripheral surfaces of the cylindrical portion 41b, that is, the inner and outer peripheral surfaces including the positions where the roller holding holes 41c are formed. Each is roughed by cutting.

  Subsequently, the plurality of roller holding holes 41c are perforated by, for example, an end mill or press molding at a substantially central position in the axial direction of the cylindrical portion 41b.

  Thereafter, the entire inner peripheral surface 41f and outer peripheral surface 41g of the outer cylinder portion 41d of the base portion 41a are finished by grinding. Thus, the surface roughness of the inner and outer peripheral surfaces 41f and 41g of the outer cylinder portion 41d is made sufficiently higher than that of the escape grooves 42a and 42b.

  In this manner, the inner peripheral surface of the outer cylinder portion 41d is finished to increase the surface roughness between the outer peripheral surface of each roller 48 and each inner tooth 19a and an outer ring 47b of a ball bearing 47 described later. In order to obtain a very small clearance, a gap between the inner peripheral surface of the outer cylindrical portion 41b and the outer peripheral surface of the outer ring 47b of the ball bearing 47, and the outer peripheral surface of the outer cylindrical portion 41b and the inner teeth 19a This is to increase the accuracy of the gap between the tooth tips.

  Moreover, by doing in this way, thickness can be ensured in the radial direction of the outer cylinder part 41d, and the fall of intensity | strength can be suppressed.

The speed reduction mechanism 12 is lubricated by lubricating oil supply / discharge means, which is formed inside the bearing 02 of the cylinder head 01 and is supplied with lubricating oil from a main oil gallery (not shown). And an oil supply hole 58 formed in the direction of the internal axis of the camshaft 2 and communicating with the oil supply path via a groove groove 58a, and penetratingly formed in the direction of the internal axis of the driven member 9. The small diameter oil hole 59 having one end opened to the oil supply hole 58 through the annular groove 58b and the other end opened in the vicinity of the needle bearing 38 and the medium diameter ball bearing 47, and the large diameter ball bearing. And an oil discharge hole 62 for discharging the lubricating oil to the outside through the inside of 43.
[Operation of valve timing control device]
Hereinafter, the operation of the valve timing control device in the present embodiment will be described. First, the timing sprocket 1 is rotated through the timing chain in accordance with the rotational drive of the crankshaft of the engine, and the rotational force is The motor housing 5 is transmitted to the motor housing 5 through the female screw forming portion 6 and rotates synchronously. On the other hand, the rotational force of the internal tooth component 19 is transmitted from each roller 48 to the camshaft 2 via the cage 41 and the driven member 9. As a result, the plurality of drive cams provided on the camshaft 2 opens and closes the intake valves of the respective cylinders.

  When a predetermined engine is operated after the engine is started, the coil of the electric motor 8 is supplied from the control unit via each terminal piece of the power feeding connector, each pigtail harness, the power feeding brushes 31a and 31b, and each slip ring 26a and 26b. 18 is energized. As a result, the motor output shaft 13 is rotationally driven, and forward / reverse rotational force is transmitted to the camshaft 2 via the speed reduction mechanism 12.

  That is, when the eccentric shaft portion 39 rotates eccentrically with the rotation of the motor output shaft 13, the rollers 48 are guided in the radial direction by the roller holding holes 41c of the cage 41 for each rotation of the motor output shaft 13. It moves over the one internal tooth 19a of the internal tooth component 19 while rolling to another adjacent internal tooth 19a, and repeatedly contacts this in the circumferential direction. 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 difference between the number of the inner teeth 19a 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.

  And in this embodiment, since the annular escape grooves 42a and 42b were formed in the inner and outer peripheral surfaces of the cylindrical portion 41b of the cage 41, the inner and outer peripheral surfaces 41f and 41g of the outer cylindrical portion 41d of the base portion 41a were formed. When finishing with a grinding tool, the cutting edge of the grinding tool can avoid the roller holding holes 41c, that is, can perform grinding without contact with each opening edge of the roller holding holes 41c. .

  For this reason, since it is possible to sufficiently suppress the occurrence of scratches on the cutting edge of the grinding tool (the tip of the grinding stone), the life of the grinding tool can be extended, durability can be improved, and the replacement time of the grinding tool can be extended. Therefore, it is possible to suppress a decrease in grinding efficiency.

  Further, when grinding the inner and outer peripheral surfaces 41f and 41g of the outer cylinder part 41d, it can protrude from the opening edge of each roller holding hole 41c and simultaneously remove burrs, and around the roller holding holes 41c when drilling It is also possible to release the residual stress generated in. By releasing this residual stress, the opening accuracy of each roller holding hole 41c is also improved.

  Moreover, in this embodiment, since the rigidity of the cover member 4 improves by the said reinforcement part 28b of an aluminum alloy material, the whole deformation | transformation by a heat | fever etc. is suppressed. For this reason, since excessive stress does not act on the outer layer portion 28a, the occurrence of cracks and breakage can be sufficiently suppressed.

  As a result, the sealing performance of the cover member 4 is maintained, so that intrusion of water, dust and the like into the electric motor 8 can be suppressed, and a decrease in durability is suppressed.

  Further, as described above, since the deformation of the entire cover member 4 can be sufficiently suppressed by the reinforcing portion 28b, the central portion of the cover member 4 due to repeated expansion and contraction due to heat protrudes inward or outward. It is also possible to suppress deformation into a shape.

  As a result, uneven deformation around the detection portion 51 of the angle detection sensor 35 is suppressed, and a change in the distance of the minute gap C between the tip portion 51a of the detected portion 51 can be suppressed. As a result, good detection accuracy of the angle detection sensor 35 is always obtained.

Furthermore, since the reinforcing portion 28b is formed of an aluminum alloy material, the overall weight of the cover member 4 can be reduced as compared with the case where the reinforcing portion 28b is formed of an iron-based metal. As a result, it is possible to contribute to weight reduction of the vehicle with the weight reduction of the valve timing control device.
[Second Embodiment]
FIG. 8 shows a second embodiment. The axial lengths of the relief grooves 42a and 42b formed on the inner and outer peripheral surfaces of the cylindrical portion 41b of the retainer 41 are the lengths of the roller holding holes 41c in the axial direction. Is set so as not to extend to the tip 41e (annular portion) of the cylindrical portion 41b.

  As a result, the finishing grinding is applied to the inner and outer peripheral surfaces 41f and 41g of the outer cylinder portion 41d which is an annular portion and the inner and outer peripheral surfaces 41h and 41i of the tip portion 41e which is also an annular portion. It has become.

  Therefore, according to this embodiment, the cutting edge of the grinding tool can be ground in a non-contact state with the opening edge of the roller holding hole 1c, so that the same effect as that of the first embodiment can be obtained.

  In addition, since the inner and outer peripheral surfaces 41h and 41i of the tip portion 41e are not cut, the thickness is ensured and the decrease in rigidity of the cage 41 can be suppressed.

  If the cutting edge of the grinding tool has a width from the outer cylinder part 41d to the tip part 41e of the cylindrical part 41b, both inner peripheral surfaces 41f and 41h and both outer peripheral faces are used. Since 41g and 41i can be ground simultaneously, the grinding efficiency is improved.

  The present invention is not limited to the configuration of each of the embodiments described above, and as the through portion, in addition to the roller holding hole 41c, the tip portion 41e of the cylindrical portion 41b may be cut out to form a long groove. Is possible. Further, the opening area of the roller holding hole 41c, the axial length of the cylindrical portion 41b, and the like can be arbitrarily changed according to the specifications and size of the apparatus.

  The escape grooves 42a and 42b can be formed on at least one of the inner and outer peripheral surfaces of the cylindrical portion 41b.

  In addition to the timing sprocket, the drive rotator may be a timing pulley or the like.

  Further, in each of the above embodiments, the electric motor 8 is provided integrally with the timing sprocket 1, but it is also possible to provide the electric motor 8 separately and to be fixed to the chain case, for example.

Claims (13)

A driving rotating body to which rotational force is transmitted from the crankshaft;
A rotational force of the drive rotator is transmitted, and a driven rotator integrally provided on the camshaft;
An electric motor for rotating the driven rotator relative to the drive rotator by rotating;
An eccentric shaft portion provided on the motor output shaft of the electric motor, the outer peripheral surface being eccentric with respect to the rotation center;
An internal tooth component having a plurality of internal teeth provided in the drive rotor and opposed to the outer peripheral surface of the eccentric shaft portion from the radial direction;
A plurality of rollers disposed between an outer peripheral surface of the eccentric shaft portion and each internal tooth of the internal tooth constituent portion;
A cylindrical retainer provided in the driven rotating body and having a plurality of penetrating portions that hold the plurality of rollers formed in a predetermined region in the axial direction;
With
A valve timing control for an internal combustion engine, wherein the retainer has an annular recess formed in at least one of an outer peripheral surface and an inner peripheral surface of a region including the entire hole edge of each through portion. apparatus. The valve timing control apparatus for an internal combustion engine according to claim 1,
A valve timing control device for an internal combustion engine, wherein a surface roughness of an annular portion other than the concave portion of the cage is made higher than that of the concave portion. The valve timing control device for an internal combustion engine according to claim 2,
A valve timing control device for an internal combustion engine, wherein the concave portion is formed on both an outer peripheral surface and an inner peripheral surface of a cage. 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 concave portion is formed up to an axial tip end side other than a base portion on the driven rotor side of the cage. 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 concave portion is formed in a region between a base portion on the driven rotor side of the cage and a tip portion in an axial direction. 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 penetrating portion is formed by a hole penetrating the retainer in a radial direction. 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 penetrating portion is formed by a long groove opened in the axial direction from the tip end side of the cage. 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 electric motor is configured such that a motor housing rotates integrally with the drive rotating body. The valve timing control device for an internal combustion engine according to claim 8,
The valve timing control device for an internal combustion engine, wherein the electric motor rotates a motor output shaft in both forward and reverse directions with respect to the driven rotor. 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 electric motor is formed separately from the drive rotating body and is fixed to a cylinder head or a chain case of the engine. A driving rotating body to which rotational force is transmitted from the crankshaft;
A rotational force of the drive rotator is transmitted, and a driven rotator integrally provided on the camshaft;
An electric motor for rotating the driven rotator relative to the drive rotator by rotating;
An eccentric shaft portion provided on the motor output shaft of the electric motor, the outer peripheral surface being eccentric with respect to the rotation center;
An internal tooth component having a plurality of internal teeth provided in the drive rotor and opposed to the outer peripheral surface of the eccentric shaft portion from the radial direction;
A plurality of rollers disposed between an outer peripheral surface of the eccentric shaft portion and each internal tooth of the internal tooth constituent portion;
A cylindrical retainer provided in the driven rotating body and having a plurality of penetrating portions that hold the plurality of rollers formed in a predetermined region in the axial direction;
A method for manufacturing a valve timing control device for an internal combustion engine comprising:
A step of notching an annular recess in at least one of the outer peripheral surface or inner peripheral surface of the cage;
Forming each of the through portions at a position where the concave portion of the cage is formed;
A step of performing grinding for finishing on at least one of the outer peripheral surface and the inner peripheral surface other than the recess formed in the cage; and
A method for manufacturing a valve timing control device for an internal combustion engine, comprising: In the manufacturing method of the valve timing control device of the internal-combustion engine according to claim 11,
A method for manufacturing a valve timing control device for an internal combustion engine, characterized in that a surface roughness of an outer peripheral surface or an inner peripheral surface other than the concave portion is higher than that of an outer peripheral surface or an inner peripheral surface of the concave portion. In the manufacturing method of the valve timing control device of the internal-combustion engine according to claim 12,
A method for manufacturing a valve timing control device for an internal combustion engine, comprising the step of performing the grinding on both an outer peripheral surface and an inner peripheral surface other than the recess formed in the cage.

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