WO2020039743A1 - Dispositif de commande de réglage de distribution pour moteur à combustion interne - Google Patents

Dispositif de commande de réglage de distribution pour moteur à combustion interne Download PDF

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Publication number
WO2020039743A1
WO2020039743A1 PCT/JP2019/025724 JP2019025724W WO2020039743A1 WO 2020039743 A1 WO2020039743 A1 WO 2020039743A1 JP 2019025724 W JP2019025724 W JP 2019025724W WO 2020039743 A1 WO2020039743 A1 WO 2020039743A1
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WO
WIPO (PCT)
Prior art keywords
peripheral surface
combustion engine
valve timing
control device
timing control
Prior art date
Application number
PCT/JP2019/025724
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English (en)
Japanese (ja)
Inventor
亮 田所
Original Assignee
日立オートモティブシステムズ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by 日立オートモティブシステムズ株式会社 filed Critical 日立オートモティブシステムズ株式会社
Priority to JP2020538209A priority Critical patent/JPWO2020039743A1/ja
Publication of WO2020039743A1 publication Critical patent/WO2020039743A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/356—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear making the angular relationship oscillate, e.g. non-homokinetic drive

Definitions

  • the present invention relates to a valve timing control device for an internal combustion engine.
  • Patent Document 1 As an electric valve timing control device for an internal combustion engine, there is one described in Patent Document 1 filed by the present applicant earlier.
  • the valve timing control device includes a sprocket having a gear portion around which a chain is wound, a driven member provided at one end of a camshaft in a rotation axis direction, and a camshaft that reduces a rotation speed of an electric motor to reduce the rotation speed of the electric motor. And a speed reduction mechanism for transmitting to the shaft.
  • the deceleration mechanism includes an eccentric shaft portion to which a rotational force is transmitted from a motor output shaft of the electric motor, a plurality of corrugated inner teeth integrally provided on the inner peripheral surface of the sprocket on the electric motor side, and A plurality of rollers provided between the internal teeth and the outer ring of the medium-diameter ball bearing, and a retainer that allows radial movement of the entire roller while partitioning the rollers in the plurality of retaining holes.
  • a large-diameter ball bearing as a bearing is press-fitted between the inner peripheral surface of the sprocket and the outer peripheral surface of the driven member from an axially outer side opposite to the electric motor.
  • the front end side of the sprocket of each internal tooth is inclined radially inward, and a part of the roller is locally pressed inward between each internal tooth of the internal tooth forming part and the outer ring of the medium diameter ball bearing. Therefore, there is a possibility that friction between a part of the roller and the bottom surface of the internal teeth and between the roller and the medium-diameter ball bearing may increase.
  • the present invention has been devised in view of the above-mentioned conventional technical problems, and has as its object to provide a valve timing control device for an internal combustion engine that can reduce friction and noise during driving.
  • the invention according to claim 1 of the present application is, in particular, a plurality of internal teeth provided at a position on an inner peripheral surface of a driving rotating body, which is radially opposed to an outer peripheral surface of an eccentric shaft portion, An intermediate member disposed between the internal teeth of the eccentric shaft portion and an outer peripheral surface of the eccentric shaft portion for reducing the rotation of the eccentric shaft portion and transmitting the rotation to the driven rotary body in cooperation with the plurality of internal teeth; and Of the inner peripheral surface of the rotator, a bearing press-fitted between the inner peripheral surface and the outer peripheral surface of the driven rotator having the plurality of internal teeth and a position offset on the opposite side in the rotation axis direction,
  • the drive rotating body is characterized in that the plurality of internal teeth are formed in a tapered shape having a diameter that increases radially outward from the rotation axis.
  • FIG. 2 is an exploded perspective view showing main components in the embodiment. It is a front view of the sprocket provided for this embodiment.
  • FIG. 4 is an enlarged view of a portion A in FIG. 3.
  • FIG. 4 is a sectional view taken along line BB of FIG. 3.
  • FIG. 6 is an enlarged view of a portion C in FIG. 5.
  • FIG. 2 is a sectional view taken along line DD of FIG. 1.
  • FIG. 2 is an enlarged view of a main part of the embodiment shown in FIG. 1. It is a principal part enlarged view of a prior art.
  • the present invention is applied to, for example, an in-line four-cylinder internal combustion engine having two intake valves in one cylinder.
  • FIG. 1 is a longitudinal sectional view showing one embodiment of a valve timing control device according to the present invention
  • FIG. 2 is an exploded perspective view showing main components in the present embodiment.
  • this valve timing control device rotates a timing sprocket 1 (hereinafter, referred to as a sprocket 1) as a driving rotating body on a cylinder head 01 via a bearing bracket 02.
  • a camshaft 2 which is freely supported and rotates by the rotational force transmitted from the sprocket 1, is disposed between the sprocket 1 and the camshaft 2, and changes the relative rotational phase between the two, depending on the engine operating state.
  • a phase changing mechanism 3 3
  • FIG. 3 is a front view of the sprocket used in the present embodiment
  • FIG. 4 is an enlarged view of a portion A in FIG. 3
  • FIG. 5 is a sectional view taken along line BB of FIG. 3
  • FIG. 6 is an enlarged view of a portion C in FIG. is there.
  • the sprocket 1 is rotationally driven by a crankshaft of an internal combustion engine via a timing chain. As shown in FIGS. 1 to 6, the sprocket 1 is integrally provided on the outer periphery of the sprocket main body 1a, and is wound around the sprocket main body 1a, which is entirely formed of a ferrous metal in a cylindrical shape. And a gear portion 1b that receives rotational force from a crankshaft via a timing chain (not shown).
  • the sprocket main body 1a has an inner peripheral surface 1c formed to have a stepped diameter, and a rear end 1d axially outside the inner peripheral surface 1c (on the camshaft 2 side) is formed in a flat annular shape.
  • a plurality of corrugated internal teeth 5 are formed at the front end on the inner side in the axial direction of the inner peripheral surface 1c. As shown in FIGS. 3 to 6, each of the internal teeth 5 has a tooth bottom surface 5a and a tooth tip 5b rising from the tooth bottom surface 5a.
  • the internal teeth 5 are formed at substantially the same positions as the gear portion 1b in the rotation axis direction, that is, at positions overlapping the gear portion 1b in the radial direction.
  • the rear end portion 1d is arranged at a position offset from the gear portion 1b toward the camshaft 2 in the rotation axis direction, and is formed at a position that does not overlap the gear portion 1b in the radial direction.
  • the inner peripheral surface 1 c has a rear end 1 d having an inner diameter set to be substantially uniform, while a front end, that is, a tooth bottom 5 a of the internal teeth 5 is formed.
  • the tooth tip 5b is inclined in a tapered shape from the rear end side to the front end side (tooth trace). That is, the entire internal teeth 5 at the front end of the inner peripheral surface 1c are formed to be inclined in a tapered (flapper) shape with a diameter increasing toward the front from the rear end 1d.
  • the inclination S is set to an angle of about 5 ⁇ m to 10 ⁇ m with respect to the rotation axis X of the sprocket 1. In this embodiment, for example, the angle is set to about 7 ⁇ m.
  • One large-diameter ball bearing 6 is interposed between the sprocket main body 1a and a driven member 9 described below provided at the front end of the camshaft 2.
  • the large-diameter ball bearing 6 has an inner race 6a, an outer race 6b, and a plurality of balls 6c held between the inner race 6a and the outer race 6b via a cage 6d.
  • the inner race 6a is press-fitted into the outer peripheral surface 9g of the driven member 9 described later, while the outer race 6b is press-fitted into the axially outer rear end 1d of the inner peripheral surface 1c of the sprocket body 1a. .
  • the large-diameter ball bearing 6 supports the sprocket 1 so as to be rotatable relative to the driven member 9.
  • annular holding plate 8 is arranged on the rear end surface of the sprocket body 1a on the camshaft 2 side, as shown in FIGS.
  • the holding plate 8 is integrally formed of a metal plate material, and has an insertion hole 8a through which the camshaft 2 is inserted at a central position.
  • a stopper projection 8b protruding radially inward, that is, toward the center axis direction, is integrally provided.
  • the stopper projection 8b is formed in a substantially fan-like shape, and has a distal end formed in an arc shape along an arc-shaped inner peripheral surface of a stopper groove 2e described later.
  • a plurality of (eight in the present embodiment) bolt insertion holes 1e and 8c are formed through the outer peripheral portions of the sprocket body 1a and the holding plate 8 at substantially equal circumferential positions.
  • a rear end portion of a motor housing 14, which will be described later, is arranged on the front end side of the sprocket main body 1a so as to face the rotation axis direction.
  • a plurality of (eight in the present embodiment) female screw holes 14d are formed in the peripheral wall at the rear end of the motor housing 14 at positions corresponding to the bolt insertion holes 1e and 8c. Then, the sprocket 1, the holding plate 8 and the motor housing 14 are fixedly fastened together by eight bolts 7 which are inserted and screwed into the holes 1e, 8c and 14d from the axial direction of the rotating shaft of the motor housing 14. .
  • the sprocket main body 1a is configured as a casing of the speed reduction mechanism 12 described later.
  • the camshaft 2 has two drive cams per cylinder for opening an intake valve (not shown) on the outer periphery. As shown in FIG. 1, the camshaft 2 has a flange 2b integrally provided at one end 2a in the rotation axis direction, and a female screw hole 2c extending from the one end 2a along the internal rotation axis direction. Are formed.
  • a driven member 9 is connected to the driven member 9 via a flange portion 2 b by a cam bolt 10 from the rotation axis direction.
  • An annular protrusion 2d is provided integrally with the edge of the female screw hole 2c of the flange 2b.
  • the flange portion 2 b is arranged such that the outer peripheral portion of the front end surface is in contact with the axially outer end surface of the inner ring 6 a of the large-diameter ball bearing 6.
  • a stopper concave groove 2e into which the stopper convex portion 8b of the holding plate 8 enters is formed along the circumferential direction.
  • the stopper groove 2e is formed in an arc shape having a predetermined length in the circumferential direction.
  • the both ends of the stopper projection 8b rotate in the length range of the stopper groove 2e and come into contact with the opposite edges in the circumferential direction.
  • the cam bolt 10 has a head portion 10a and a shaft portion 10b integrally provided at the center of one end surface of the head portion 10a.
  • the outer periphery of one end of the head 10a supports an inner ring of a small-diameter ball bearing 35 described later in the axial direction.
  • the shaft portion 10b has a male screw 10c that is screwed into the female screw hole 2c of the camshaft 2 on the outer periphery of the tip portion.
  • the driven member 9 is integrally formed of a metal material, for example, an iron-based metal, and as shown in FIGS. 1 and 2, a disk-shaped fixed end 9a formed on the rear end side (camshaft 2 side). And a cylindrical portion 9b protruding from the inner peripheral front end surface of the fixed end portion 9a in the axial direction of the rotation shaft of the driven member 9.
  • the fixed end 9a is formed at the center thereof with an insertion hole 9c communicating with the inside of the cylindrical portion 9b and through which the shaft 10b of the cam bolt 10 is inserted.
  • An annular fitting groove 9d into which the annular protrusion 2d of the camshaft 2 is fitted is formed at the rear end side edge of the insertion hole 9c.
  • the protrusion 2d is fitted in the fitting groove 9d from the axial direction, whereby the driven member 9 is positioned in the radial direction with respect to the camshaft 2.
  • the inner end 6a of the large-diameter ball bearing 6 is press-fitted and fixed to the fixed end portion 9a from the axially outer side of the camshaft 2, as described above, on the flat annular outer peripheral surface 9g.
  • the fixed end portion 9a is disposed in contact with the front end surface of the flange portion 2b of the camshaft 2, and is fixed to the flange portion 2b by an axial force by the axial force of the cam bolt 10.
  • the cylindrical portion 9b has an insertion hole 9e continuously formed therein, and a needle bearing 36 described later is provided on the outer peripheral side. Further, a small-diameter cylindrical portion 9f for holding a small-diameter ball bearing 35 described later is integrally provided on the outer periphery of the distal end portion of the cylindrical portion 9b.
  • the phase changing mechanism 3 includes an electric motor 11 disposed on the front end side of the cylindrical portion 9 b of the driven member 9, a reduction mechanism 12 for reducing the rotation speed of the electric motor 11 and transmitting the rotation speed to the camshaft 2, And a cover member 13 fixed to the chain case 40 and arranged at the front end of the main body.
  • the electric motor 11 is a brushed DC motor, a motor housing 14 that rotates integrally with the sprocket 1, and a motor rotatably provided inside the motor housing 14.
  • the motor includes an output shaft 15, four arc-shaped permanent magnets 16 fixed to the inner peripheral surface of the motor housing 14, and a power supply plate 17 provided at a front end of the motor housing 14.
  • the motor housing 14 functions as a yoke formed by pressing a metal material such as an iron-based metal material into a bottomed cylindrical shape by press molding, and a disk-shaped partition wall 14a is provided on the rear end side of the sprocket 1 side. I have.
  • the partition wall 14a is provided integrally with a cylindrical extension portion 14b at a substantially central position through which an eccentric shaft portion 34 described later can be inserted inside.
  • the motor output shaft 15 is formed in a stepped cylindrical shape and functions as an armature, and has a large diameter portion 15a on the camshaft 2 side and a small diameter portion on the cover member 13 side via a stepped portion formed at a substantially central position in the axial direction. 15b.
  • the large-diameter portion 15a has an iron core rotor 18 fixed to the outer periphery thereof, and an eccentric shaft portion 34 that constitutes a part of the speed reduction mechanism 12 is integrally provided at a rear end portion of the camshaft 2 side.
  • An oil seal 19 that seals between the electric motor 11 and the speed reduction mechanism 12 is provided between the outer peripheral surface of the large diameter portion 15a and the inner peripheral surface of the extension 14b of the motor housing 14.
  • a non-magnetic annular member 20 is press-fitted and fixed to the outer periphery of the small diameter portion 15b.
  • a commutator 21 is press-fitted and fixed to the outer peripheral surface of the annular member 20 in the axial direction.
  • a bottomed cylindrical plug member 22 for sealing the outside and the inside of the motor output shaft 15 is press-fitted and fixed inside the distal end side of the small diameter portion 15b.
  • the plug member 22 is formed of synthetic rubber having a core metal embedded therein, and is pressed into the inner peripheral surface of the small-diameter portion 15b from the front end in the axial direction. Further, the maximum press-in movement position of the plug member 22 is regulated by a C-ring 22a fitted and fixed to the inner peripheral surface of the small diameter portion 15b.
  • the iron core rotor 18 is formed of a magnetic material having a plurality of magnetic poles, and has an outer peripheral side configured as a bobbin having a slot for winding the coil wire of the coil 18a.
  • the commutator 21 is formed in an annular shape by a conductive material, and the terminal of the coil wire from which the coil 18a is drawn out is electrically connected to each segment divided into the same number as the number of poles of the iron core rotor 18.
  • Each permanent magnet 16 is formed in a cylindrical shape as a whole, has a plurality of magnetic poles in the circumferential direction, and the position of the motor housing 14 in the rotation axis direction is offset and arranged ahead of the fixed position of the iron core rotor 18. .
  • the motor output shaft 15 and the eccentric shaft portion 34 are provided on the outer peripheral surface of the shaft portion 10b on the head 10a side of the cam bolt 10 and the small-diameter ball bearing 35 provided on the outer peripheral surface of the cylindrical portion 9b of the driven member 9.
  • the ball bearing 35 is rotatably supported by a needle bearing 36 disposed on an axial side portion of the ball bearing 35.
  • the power supply plate 17 is entirely formed in a disk shape, and a shaft insertion hole 17a through which one end of the motor output shaft 15 is inserted is formed at the center position.
  • the power supply plate 17 has a disk-shaped resin portion made of a non-magnetic material, and a disk-shaped metal core 17b with most of the resin portion embedded inside the resin portion.
  • the power supply plate 17 slides along a plurality of (four in the present embodiment) holders 23a, 23b, 24a, 24b provided in the resin portion along the inside of each of the holders 23a to 24b.
  • Two switching brushes (not shown) are commutators that are freely accommodated and arranged, and each end face resiliently contacts the outer peripheral surface of the commutator 21 by the spring force of the coil spring from the radial direction.
  • the power supply plate 17 is positioned and fixed by caulking the outer peripheral portion of the core bar 17b exposed from the outer periphery of the resin portion to a concave step formed on the inner periphery of the front end of the motor housing 14.
  • the chain case 40 is disposed and fixed vertically along the cylinder head of the internal combustion engine and the front end side of the cylinder block so as to cover a chain (not shown) wound around the sprocket 1.
  • a flange portion 40a is integrally provided on an outer peripheral edge of a front end portion.
  • the cover member 13 is integrally formed of a synthetic resin in a deep dish shape and is arranged so as to cover the front end of the motor housing 14.
  • the cover member 13 has a cover main body 13a which is a substantially flat bottom wall, and a cylindrical peripheral wall 13b extending from the outer periphery of the cover main body 13a toward the sprocket 1.
  • a cylindrical portion 13c having a working hole 13d therein is provided integrally at a substantially central position of the cover body 13a.
  • a holding hole 13e for inserting and holding the brush holding member 26 is formed in the outer peripheral portion of the cover body 13a so as to penetrate along the peripheral wall 13b.
  • the peripheral wall 13b is integrally provided with a mounting flange 13f on the outer periphery, and is integrally provided with a plurality (three in the present embodiment) of boss portions 13g at predetermined angular positions in the circumferential direction of the mounting flange 13f. .
  • Each boss 13g is formed with a bolt hole through which a bolt for coupling with the chain case 40 is inserted.
  • An oil seal 27 is fitted and fixed in a seal groove formed on the front end surface of the mounting flange 13f. The oil seal 27 seals between the mounting flange 13f and the flange 40a of the chain case 40.
  • a second oil seal 28 for sealing the inside of the electric motor 11 is provided between the inner peripheral surface of the peripheral wall 13b and the outer peripheral surface of the motor housing 14.
  • the brush holding member 26 is mainly formed of a synthetic resin material, is inserted into the holding hole 13e of the cover main body 13a, and is connected to the cover main body 13a by a bolt (not shown). It has a substantially cylindrical brush holding portion 26a and a female connector portion 26b provided at the upper end of the brush holding portion 26a in the drawing.
  • the brush holding portion 26a is provided therein with a pair of prismatic conductive power supply brushes 29a and 29b that are in contact with the power supply slip rings 25a and 25b, respectively, from the axial direction.
  • the two power supply brushes 29a and 29b are slidably held in rectangular tubular brush holders 30a and 30b molded and fixed in the brush holding portion 26a.
  • each of the power supply brushes 29a and 29b is urged toward the slip rings 25a and 25b by the spring force of coil springs 31a and 31b provided on the rear end side.
  • each of the power supply brushes 29a and 29b has a distal end projecting from each of the brush holders 30a and 30b elastically abutting against the exposed flat upper surface of each of the slip rings 25a and 25b.
  • the female connector portion 26b has a pair of terminal pieces, and one end of each terminal piece is electrically connected to each of the power supply brushes 29a and 29b via the pigtail harnesses 32a and 32b. The other end of each terminal piece of the connector 26b is electrically connected to a control unit (not shown) by a male connector (not shown).
  • 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) to control the engine. Further, the control unit controls the rotation of the motor output shaft 15 by energizing the coil 18a, and controls the relative rotation phase of the camshaft 2 with respect to the sprocket 1 via the speed reduction mechanism 12.
  • FIG. 7 is a sectional view taken along line DD of FIG.
  • the reduction mechanism 12 includes an eccentric shaft portion 34 that performs eccentric rotation, a medium-diameter ball bearing 37 provided on the outer periphery of the eccentric shaft portion 34, and a medium-diameter ball bearing.
  • a roller 38 provided on the outer circumference of the fixed end 9a and a cylindrical retainer 39 integrally provided on the outer circumference of the fixed end portion 9a to allow a plurality of rollers 38 to move in the rolling direction while holding the rollers 38 in the rolling direction.
  • the driven member 9 integrated with the retainer 39.
  • the roller 38 and the retainer 39 constitute an intermediate member.
  • the axis Y of the cam surface 34a formed on the outer peripheral surface is slightly eccentric in the radial direction from the axis X of the motor output shaft 15.
  • the medium-diameter ball bearing 37 is arranged so as to substantially entirely overlap with the needle bearing 36 via the eccentric shaft 34 at the radial position.
  • the medium-diameter ball bearing 37 is composed of a ball 37c that is rotatably disposed between the inner ring 37a, the outer ring 37b, and both wheels 37a, 37b via a cage 37d.
  • the inner ring 37a is press-fitted and fixed to the outer peripheral surface of the eccentric shaft portion 34, whereas the outer ring 37b is free without being fixed in the axial direction.
  • the outer ring 37b has a small first end face in the rotation axis direction that does not contact any part, and a small first face between the other end face in the axial direction and the inner surface of the base 39a of the holder 39 opposed thereto.
  • a gap is formed and it is in a free state.
  • the outer peripheral surface of each roller 38 is in rolling contact with the outer peripheral surface of the outer ring 37b.
  • An annular second gap is formed on the outer peripheral side of the outer ring 37b. The second gap allows the entire medium-diameter ball bearing 37 to move in the radial direction with the eccentric rotation of the eccentric shaft portion 34, that is, to be eccentric.
  • Each roller 38 is formed of, for example, an iron-based metal, and has an outer peripheral side meshed with and held by the internal teeth 5 of the sprocket body 1a while moving in the radial direction with the eccentric movement of the medium-diameter ball bearing 37. Further, each roller 38 has a smaller total number of internal teeth 5 than the total number of internal teeth 5.
  • each roller 38 swings radially while being guided in the circumferential direction by holding pieces provided on both sides of a later-described roller holding hole 39c of the holder 39.
  • the retainer 39 is bent forward into a substantially L-shaped cross section from the front end of the outer peripheral portion of the fixed end portion 9a, and is integrally connected to the fixed end portion 9a. And a cylindrical portion 39b that is integrally formed on the outer periphery of the cylindrical portion 9b and protrudes in the same direction as the cylindrical portion 9b.
  • the cylindrical portion 39b extends in the direction of the partition wall 14a of the motor housing 14 via an annular concave receiving space formed between the female screw hole 14d and the extending portion.
  • the cylindrical portion 39b has a plurality of (for example, 50 in this embodiment) roller holding holes 39c each of which is rotatably holding the plurality of rollers 38, and is formed at equal intervals in the circumferential direction. I have.
  • Each of the roller holding holes 39c is formed in a long and narrow rectangular shape along the rotation axis direction of the cylindrical portion 39b at a certain interval in the circumferential direction of the cylindrical portion 39b via each holding piece. That is, the roller holding hole 39c is formed by punching the cylindrical portion 39b in a rectangular shape from the outer peripheral surface of the cylindrical portion 39b in the direction of the rotation axis by a punch of a press molding machine. Thus, the roller holding holes 39c are arranged at equal intervals in the circumferential direction of the cylindrical portion 39b with the respective holding pieces.
  • the rotational force is transmitted to the eccentric shaft portion 34 of the speed reduction mechanism 12, and the entire medium-diameter ball bearing 37 eccentrically moves, and the position where each roller 38 in each roller holding hole 39 c meshes with the internal tooth 5 moves in the circumferential direction. By doing so, the rotation speed is reduced.
  • Lubricating oil is supplied to the inside of the speed reduction mechanism 12 by lubricating oil supply means.
  • the lubricating oil supply means is formed in the direction of the internal rotation axis of the camshaft 2 and penetrates the oil supply passage through which lubricating oil is supplied from a main oil gallery (not shown) and the width direction of the fixed end portion 9a. And an oil supply hole communicating with the oil supply passage.
  • the oil supply hole has a downstream open end opened near the needle bearing 36 and the medium-diameter ball bearing 37 so as to supply lubricating oil to the inside of the speed reduction mechanism 12.
  • the sprocket 1 rotates with the rotation drive of the crankshaft of the engine, and the rotation force of the sprocket 1 rotates synchronously with the motor housing 14, that is, the electric motor 11 via the internal teeth 5.
  • the rotational force of the internal teeth 5 is transmitted from each roller 38 to the camshaft 2 via the retainer 39 and the driven member 9. Thereby, the cam of the camshaft 2 opens and closes the intake valve.
  • control unit supplies electricity to the coil 18a of the electric motor 11 via the power supply brushes 29a and 29b and the slip rings 25a and 25b.
  • the motor output shaft 15 is driven to rotate, and the reduced torque is transmitted to the camshaft 2 via the reduction mechanism 12.
  • each roller 38 is guided one by one in the roller holding hole 39 c of the holder 39 in the radial direction for each rotation of the motor output shaft 15. It moves while rolling over the internal teeth 5 to another adjacent internal tooth 5.
  • Each roller 38 rolls in the circumferential direction while sequentially repeating this.
  • the rotation of the motor output shaft 15 is transmitted to the driven member 9 while the rotation of the motor output shaft 15 is reduced by the rolling contact of the rollers 38.
  • the reduction ratio at this time can be arbitrarily set depending on the number of rollers 38 and the like.
  • the camshaft 2 rotates forward and reverse relative to the sprocket 1 to change the relative rotation phase, and controls the opening / closing timing of the intake valve to be advanced or retarded.
  • the inner ring 6a and the outer ring 6b of the large-diameter ball bearing 6 are connected to the outer peripheral surface 9g of the fixed end 9a of the driven member 9 and the inner peripheral surface 1c of the sprocket body 1a.
  • the camshaft 2 is press-fitted into the rear end 1d from the outside in the rotation axis direction. Then, the rear end portion 1d side of the inner peripheral surface 1c is pushed radially outward by the press-fitting load, so that the tooth bottom surface 5a side of the internal teeth 5 is deformed in the diameter reducing direction by this reaction force.
  • the front end 5 d of the bottom surface 5 a of the internal teeth 5 partially hits the outer surface of the axial front end 38 a of the roller 38.
  • the friction between each of the internal teeth 5 and each of the rollers 38 increases, and the vibration noise may increase.
  • the roller 38 may also come into contact with the outer peripheral surface of the outer ring 37b of the medium-diameter ball bearing 37.
  • the tooth bottom surface 5a of the internal teeth 5 and the outer surface of the roller 38 are partially formed.
  • the friction may increase due to the contact (one contact), and the vibration noise may increase.
  • the tooth bottom 5a and the tooth tip 5b of the internal teeth 5, which are a part of the internal peripheral surface 1a of the sprocket main body 1a, are tapered in advance toward the electric motor 11 in a tapered shape. It is formed in.
  • the inner tooth 5 side of the inner peripheral surface 1c is reduced in diameter by the press-fitting load, so that the tooth bottom 5a and the tooth tip 5b of the inner tooth 5 are moved with respect to the outer surface of the roller 38 as shown in FIG. They are almost parallel in the direction of the rotation axis. That is, the width of the clearance C in the axial direction becomes substantially uniform between the inner surface of the internal teeth 5 and the outer surface of the roller 38 without one-side contact. For this reason, the friction between each of the internal teeth 5 and each of the rollers 38 is sufficiently reduced, and the generation of vibration noise is suppressed.
  • the inner teeth 5 side of the inner peripheral surface 1c is formed in advance in a tapered shape with a large diameter, there is no need to perform machining after press-fitting the large-diameter ball bearing 6, so that the work can be simplified.
  • the large-diameter ball bearing 6 can be firmly fixed by press-fitting between the rear end 1d of the inner peripheral surface 1c and the outer peripheral surface 9g of the fixed end 9a, but the inner peripheral surface 1c expands in accordance with the press-fit.
  • the diameter taper angle can be adjusted between about 5 ⁇ m to 10 ⁇ m.
  • an annular protrusion is provided on the outer peripheral edge of the rear end portion of the motor housing 14 on the sprocket 1 side, and at the time of assembly, the protrusion is attached to the outer peripheral surface of the front end portion of the sprocket main body 1a from the axial direction. It is also possible to adopt a configuration in which press-fitting is performed. In this case, if the protrusion is pressed into the outer peripheral surface of the front end portion of the sprocket body 1a, the press-fit load may cause the inner teeth 5 side of the sprocket body 1a to be deformed radially inward, that is, deformed in the radially reduced direction.
  • the inner teeth 5 side of the inner peripheral surface 1c of the sprocket main body 1a is formed in advance into a tapered shape with a large diameter, as in the present embodiment, the inner surface of the inner teeth 5 and the outer surface of the roller 38 can be adjusted. In the axial direction can be made substantially uniform in width. Therefore, the friction between each of the internal teeth 5 and each of the rollers 38 can be sufficiently reduced, and the generation of vibration noise can be suppressed.
  • valve timing control device for an internal combustion engine based on the above-described embodiment, for example, the following embodiments can be considered.
  • a driving rotating body to which a rotational force from a crankshaft is transmitted, a driven rotating body fixed to a camshaft and rotating integrally with the camshaft, and an electric motor for rotating a motor output shaft.
  • An eccentric shaft portion provided on the motor output shaft and eccentric with respect to the rotation axis of the motor output shaft; and an inner peripheral surface of the drive rotating body, which has a diameter relative to an outer peripheral surface of the eccentric shaft portion.
  • a plurality of internal teeth provided at positions facing each other from the direction, and are disposed between the plurality of internal teeth and the outer peripheral surface of the eccentric shaft portion, and the eccentric shaft portion of the eccentric shaft portion cooperates with the plurality of internal teeth.
  • An intermediate member that reduces the rotation and transmits the rotation to the driven rotor, and an inner peripheral surface of the inner peripheral surface of the driving rotor that is offset from the plurality of internal teeth and the opposite side in the rotation axis direction.
  • the plurality of internal teeth are formed in a tapered shape that expands in diameter from the rotation axis toward the outside in the radial direction.
  • the inner peripheral surface on which the internal teeth of the driving rotary body are formed expands in the axial direction opposite to the bearing when the bearing is removed from between the driving rotary body and the driven rotary body.
  • the inner peripheral surface into which the bearing is press-fitted is formed parallel to the rotation axis of the driven rotor while being formed in a diameter taper shape.
  • each internal tooth side of the drive rotating body is formed in an enlarged shape before the bearing is press-fitted, the diameter of the inner peripheral surface of the bearing side generated when the bearing is press-fitted is increased.
  • the inner peripheral surface on the side of each internal tooth becomes substantially parallel to the rotation axis of the driven rotating body.
  • the inner peripheral surface (bottom surface) on each internal tooth side of the driving rotating body does not tilt inward in the radial direction, so that generation of an uneven load on the roller, which is one of the intermediate members, can be suppressed. As a result, it is possible to sufficiently suppress the increase in friction and the generation of sound vibration.
  • the bearing is constituted by a ball bearing, and an inner ring of the ball bearing is press-fitted and fixed to an outer peripheral surface of the driven rotating body.
  • the diameter-increased inclination of the inner peripheral surface of each of the internal teeth is provided on both the tooth tip and the tooth bottom of each of the internal teeth.
  • the drive rotating body has a gear portion on the outer periphery of which a rotational force from the crankshaft is transmitted via a chain,
  • the gear portion is provided at a position overlapping with each of the internal teeth in a radial direction from a rotation axis of the driving rotator.
  • the inclination angle of the inner peripheral surface of each of the internal teeth is set to an angle of about 5 ⁇ m to 10 ⁇ m with respect to the rotation axis of the driving rotating body.
  • the intermediate member is provided on a plurality of rollers disposed between an inner surface of each of the internal teeth and an outer peripheral surface of the eccentric shaft portion, and the plurality of rollers are provided on the driven rotating body. And a cage that restricts circumferential movement while allowing radial movement with respect to the eccentric shaft.
  • a driving rotator having a gear portion around which a chain is wound and a rotational force from a crankshaft is transmitted, a driven rotator fixed to a camshaft and rotating integrally with the camshaft,
  • An electric motor for rotating a motor output shaft an eccentric shaft portion provided on the motor output shaft and eccentric with respect to a rotation axis of the motor output shaft, and an inner peripheral surface of the drive rotating body,
  • a plurality of internal teeth provided at a position facing the outer peripheral surface of the eccentric shaft portion from the radial direction, disposed between an inner peripheral portion of each of the internal teeth and an outer peripheral surface of the eccentric shaft portion,
  • An intermediate member that cooperates with an internal tooth to reduce the rotation of the eccentric shaft portion and transmits the rotation to the driven rotary body, and a rotation axial direction outer side from an inner peripheral surface of the drive rotary body where the internal teeth are formed.
  • the gear portion is provided closer to each of the internal teeth than the bearing in the rotation axis direction of the drive rotor, and each of the internal teeth has an inner diameter from the bearing side in the rotation axis direction of the drive rotor. It is inclined so as to gradually increase in the opposite direction.
  • the inclination of the inner diameter of each of the internal teeth is provided at both the tooth tip and the tooth bottom of the internal tooth along the tooth trace direction of the internal tooth.
  • the inclination of the inner diameter of each of the internal teeth is inclined so as to open axially outward from the inner edge of the inner peripheral surface with respect to the inner peripheral surface of the drive rotating body where the bearing is inserted. I have.
  • the gear portion is provided at a position overlapping with each of the internal teeth in a radial direction from a rotation axis of the drive rotating body.
  • the inclination angle of the inner diameter of each of the internal teeth is set to an angle of about 5 ⁇ m to 10 ⁇ m with respect to the rotation axis of the driving rotator.
  • the intermediate member is provided on a plurality of rollers disposed between an inner surface of each of the internal teeth and an outer peripheral surface of the eccentric shaft portion, and the plurality of rollers are provided on the driven rotating body. And a cage that restricts circumferential movement while allowing radial movement with respect to the eccentric shaft.
  • SYMBOLS 1 Timing sprocket (drive rotary body), 1a ... Sprocket main body, 1c ... Inner peripheral surface, 1d ... Rear end part, 2 ... Camshaft, 3 ... Phase change mechanism, 5 ... Internal teeth, 5a ... Teeth bottom, 5b ... Tooth tip, 6 ... large diameter ball bearing, 6a ... inner ring, 6b ... outer ring, 6c ... ball, 9 ... driven member (driven rotating body), 9a ... fixed end part, 9b ... cylindrical part, 9g ... outer peripheral surface, 11 ...
  • Electric motor 12: reduction mechanism
  • 13 cover member
  • 14 motor housing
  • 15 motor output shaft
  • 34 eccentric shaft
  • 37a inner ring
  • 37b outer ring
  • 38 roller (middle) Member
  • 39a base
  • 39b cylindrical portion
  • 39c roller holding hole
  • C axial clearance.

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

Abstract

La présente invention concerne un dispositif de commande de réglage de distribution comprenant : une pluralité de dents internes (5) disposées à des emplacements situés dans la surface circonférentielle interne (1c) d'un corps de pignon (1a) et faisant face radialement à la surface circonférentielle externe d'un arbre excentrique (34) ; des galets (38) et des supports (39) qui sont disposés entre la surface circonférentielle externe de l'arbre excentrique et les dents internes respectives et qui ralentissent la rotation de l'arbre excentrique en coopération avec les dents internes de façon à transmettre la rotation à un élément entraîné ; et un roulement à billes de grand diamètre (6) qui est ajusté par pression, depuis l'extérieur dans la direction axiale, entre la surface circonférentielle externe (9g) d'une extrémité fixe (9a) et une extrémité arrière (1d) située axialement à l'opposé des dents internes dans la surface circonférentielle interne, dans la surface circonférentielle interne (1c), l'extrémité arrière (1d) étant formée en parallèle avec l'axe de rotation de l'élément entraîné (9), tandis que la surface circonférentielle interne sur le côté des dents internes est effilée de telle sorte que son diamètre devient plus grand radialement vers l'extérieur depuis l'extrémité arrière vers l'extrémité avant. Par conséquent, le frottement et la vibration sonore peuvent être réduits pendant la conduite.
PCT/JP2019/025724 2018-08-22 2019-06-27 Dispositif de commande de réglage de distribution pour moteur à combustion interne WO2020039743A1 (fr)

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JP2018-155103 2018-08-22
JP2018155103 2018-08-22

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008095552A (ja) * 2006-10-06 2008-04-24 Denso Corp バルブタイミング調整装置
JP2013167181A (ja) * 2012-02-15 2013-08-29 Hitachi Automotive Systems Ltd 内燃機関のバルブタイミング制御装置
JP2015102065A (ja) * 2013-11-27 2015-06-04 アイシン精機株式会社 弁開閉時期制御装置
JP2016217281A (ja) * 2015-05-22 2016-12-22 日立オートモティブシステムズ株式会社 内燃機関のバルブタイミング制御装置及びこの装置の組立方法

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008095552A (ja) * 2006-10-06 2008-04-24 Denso Corp バルブタイミング調整装置
JP2013167181A (ja) * 2012-02-15 2013-08-29 Hitachi Automotive Systems Ltd 内燃機関のバルブタイミング制御装置
JP2015102065A (ja) * 2013-11-27 2015-06-04 アイシン精機株式会社 弁開閉時期制御装置
JP2016217281A (ja) * 2015-05-22 2016-12-22 日立オートモティブシステムズ株式会社 内燃機関のバルブタイミング制御装置及びこの装置の組立方法

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