WO2015118915A1 - 内燃機関のバルブタイミング制御装置 - Google Patents
内燃機関のバルブタイミング制御装置 Download PDFInfo
- Publication number
- WO2015118915A1 WO2015118915A1 PCT/JP2015/050744 JP2015050744W WO2015118915A1 WO 2015118915 A1 WO2015118915 A1 WO 2015118915A1 JP 2015050744 W JP2015050744 W JP 2015050744W WO 2015118915 A1 WO2015118915 A1 WO 2015118915A1
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- WO
- WIPO (PCT)
- Prior art keywords
- timing control
- combustion engine
- internal combustion
- valve timing
- control device
- Prior art date
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Classifications
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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
-
- 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
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K13/00—Structural associations of current collectors with motors or generators, e.g. brush mounting plates or connections to windings; Disposition of current collectors in motors or generators; Arrangements for improving commutation
- H02K13/003—Structural associations of slip-rings
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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
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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
- F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
-
- 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
- F01L2001/3522—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 with electromagnetic brake
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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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L2013/10—Auxiliary actuators for variable valve timing
- F01L2013/103—Electric motors
-
- 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
- F01L2250/00—Camshaft drives characterised by their transmission means
- F01L2250/02—Camshaft drives characterised by their transmission means the camshaft being driven by chains
-
- 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
- F01L2301/00—Using particular materials
-
- 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
- F01L2820/00—Details on specific features characterising valve gear arrangements
- F01L2820/03—Auxiliary actuators
- F01L2820/032—Electric motors
Definitions
- the present invention relates to a valve timing control device for an internal combustion engine that controls opening and closing timings of intake valves and exhaust valves.
- This valve timing control device is a power feeding plate (power feeding mechanism) that feeds a coil of an electric motor to a front end portion of a cylindrical motor housing fixed to one axial end portion of a timing sprocket to which rotational force is transmitted from a crankshaft. Is provided.
- This power supply plate includes a metal plate portion formed in an annular shape and resin portions molded on both front and rear sides of the metal plate portion.
- the metal plate portion is caulked and fixed to the front end portion of the motor housing, and two switching brushes that are in sliding contact with the commutator are held on the inner side surface via the resin portion.
- two slip rings with which the power supply brush slides in the axial direction are fixed on the outer surface side of the resin portion.
- the current supplied from the battery power supply is supplied to the power supply brush, the slip ring, and the switching power supply.
- the metal plate portion is formed in an annular shape having a narrow radial width, a sufficient strength cannot be obtained as a whole, and the outer peripheral portion is disposed on the motor.
- the load stress slightly causes bending and deformation.
- the present invention has been devised in view of the above-described conventional technical problems, and provides a valve timing control device for an internal combustion engine that can secure the strength of a rigid plate portion and suppress a decrease in flatness of a slip ring.
- the purpose is to do.
- the power feeding plate is formed in a disc shape, and the outer peripheral portion is caulking fixed or press-fitted to the drive rotating body, and the rigid plate portion is molded.
- the rigid plate portion is formed with a holding hole for holding the power supply brush inside through the resin portion, and radially inward in a portion avoiding the holding hole. While the extended reinforcing portion is integrally provided, the resin portion is molded on both side surfaces of the rigid plate portion including the holding hole, and the slip ring is held on the outer surface side. It is said.
- the strength of the rigid plate portion can be sufficiently ensured by the reinforcing portion, and as a result, the decrease in slip ring flatness can be suppressed.
- FIG. 2 is a sectional view taken along line AA in FIG. 1.
- FIG. 2 is a sectional view taken along line BB in FIG.
- FIG. 6 is a cross-sectional view taken along the line CC of FIG.
- It is a front view of the rigid plate part provided for this embodiment.
- It is a front view of the electric power feeding plate with which 2nd Embodiment is provided. It is a rear view of the same electric power feeding plate.
- valve timing control device for an internal combustion engine according to the present invention will be described with reference to the drawings.
- the valve timing control device is applied to the intake valve side.
- the valve timing control device is rotatably supported on a timing sprocket 1 that is a driving rotating body that is rotationally driven by a crankshaft of an internal combustion engine, and a cylinder head 01 via a bearing 02.
- the camshaft 2 rotated by the rotational force transmitted from the timing sprocket 1, the cover member 3 fixed to the chain cover 49 disposed at the front position of the timing sprocket 1, the timing sprocket 1 and the camshaft 2
- a phase changing mechanism 4 which is disposed between the two and changes the relative rotational phase of the two and two in accordance with the engine operating state.
- the timing sprocket 1 is formed integrally with an iron-based metal in an annular shape, and the inner peripheral surface is integrally provided on the outer periphery of the sprocket body 1a with a stepped diameter, and is wound outside the drawing.
- the gear part 1b which receives the rotational force from a crankshaft via this timing chain, and the internal-tooth structure part 19 integrally provided in the front-end side of the said sprocket main body 1a are comprised.
- the timing sprocket 1 has a single large-diameter ball bearing 43 interposed between a sprocket body 1a and a driven member 9 (described later) provided at the front end of the camshaft 2.
- the timing sprocket 1 and the camshaft 2 are supported by a ball bearing 43 so as to be relatively rotatable.
- the large-diameter ball bearing 43 includes an outer ring 43a, an inner ring 43b, and a ball 43c interposed between the two wheels 43a and 43b.
- the outer ring 43a is fixed to the inner peripheral side of the sprocket body 1a.
- the inner ring 43 b is 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 60 opened on the camshaft 2 side on the inner peripheral side.
- the outer ring fixing portion 60 is formed in a stepped diameter shape so that 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 axial side. .
- 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 changing mechanism 4, and has a plurality of wave shapes on the inner periphery.
- the inner teeth 19a are formed.
- annular female thread forming portion 6 integral with a motor housing 5 to be described later is disposed opposite to the front end side of the internal tooth constituting portion 19.
- annular holding plate 61 is disposed at the rear end of the sprocket body 1a opposite to the internal tooth component 19.
- the holding plate 61 is integrally formed of a metal plate material.
- the outer diameter is set to be substantially the same as the outer diameter of the sprocket body 1 a and the inner diameter is the same as that of the large-diameter ball bearing 43.
- the diameter is set smaller than the inner diameter of the outer ring 43a.
- the inner peripheral portion 61a of the holding plate 61 is disposed in contact with the outer end surface in the axial direction of the outer ring 43a. Further, a stopper convex portion 61b protruding inward in the radial direction, that is, in the central axis direction is integrally provided at a predetermined position on the inner peripheral edge of the inner peripheral portion 61a.
- the stopper convex portion 61b is formed in a substantially fan shape, and the tip edge 61c is formed in an arc shape along an arc-shaped inner peripheral surface of a stopper groove 2b described later. Further, six bolt insertion holes 61d through which the respective bolts 7 are inserted are formed in the outer peripheral portion of the holding plate 61 at equal intervals in the circumferential direction.
- bolt insertion holes 1c and 61d are formed in the outer peripheral portions of the sprocket main body 1a (internal tooth constituting portion 19) and the holding plate 61, respectively, at substantially equal intervals in the circumferential direction.
- the female screw forming portion 6 is formed with six female screw holes 6a at positions corresponding to the bolt insertion holes 1c and 61d, and the timing sprocket 1 and the holding plate are formed by six bolts 7 inserted through these female screw holes 6a.
- 61 and the motor motor housing 5 are fastened and fixed together in the axial direction.
- the sprocket body 1a and the internal gear component 19 are configured as a casing for a speed reduction mechanism 8 to be described later.
- the outer diameters of the sprocket body 1a, the inner tooth component 19, the holding plate 61, and the female screw forming portion 6 are set to be substantially the same.
- the chain cover 49 is vertically arranged so as to cover a cylinder head 01 as an engine body and a chain (not shown) wound around the timing sprocket 1 on the front end side of a cylinder block (not shown). Along the arrangement is fixed. Further, boss portions 49b are integrally formed at four locations in the circumferential direction of the annular wall 49a constituting the opening formed at a position corresponding to the phase changing mechanism 4, and each boss is formed from the annular wall 49a. A female screw hole 49c is formed over the inside of the portion 49b.
- the cover member 3 is integrally formed in a cup shape with an aluminum alloy material, and is disposed so as to cover the front end portion of the motor housing 5. And an annular mounting flange 3b formed integrally with the outer peripheral edge on the opening side of the cover main body 3a.
- a cylindrical wall 3c is integrally formed along the axial direction on the outer peripheral side of the cover body 3a. The cylindrical wall 3c is formed short in the axial direction and has a holding hole 3d formed therein. .
- the mounting flange 3b is provided with four bosses 3e at approximately equal intervals in the circumferential direction (approximately 90 ° positions) at approximately equal intervals in the circumferential direction. As shown in FIG. 1, each boss portion 3e is formed with a bolt insertion hole 3g through which a bolt 54 screwed into each female screw hole 49d formed in the chain cover 49 is inserted. The cover member 3 is fixed to the chain cover 49 by 54.
- a large-diameter oil seal 50 is interposed between the inner peripheral surface of the stepped portion on the outer peripheral side of the cover body 3a and the outer peripheral surface of the motor housing 5.
- the large-diameter oil seal 50 is formed in a substantially U-shaped cross section, a core metal is embedded in the synthetic rubber base material, and an annular base on the outer peripheral side is the inner periphery of the cover member 3. It is fitted and fixed to a step ring portion 3h provided on the surface.
- the motor housing 5 includes a housing body 5a formed of a ferrous metal material in a bottomed cylindrical shape by press molding, a power feeding plate 11 that seals a front end opening of the housing body 5a, It has.
- the housing main body 5a has a disk-shaped partition wall 5b on the rear end side, and a large-diameter large-diameter hole 5c through which an eccentric shaft portion 39, which will be described later, is inserted is formed at substantially the center of the partition wall 5b.
- a cylindrical extending portion 5d protruding in the axial direction of the camshaft 2 is integrally provided at the hole edge of the large diameter hole 5c.
- the female thread forming portion 6 is integrally provided on the outer peripheral side of the front end surface of the partition wall 5b.
- 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.
- the flange portion 2a has an outer diameter set to be slightly larger than an outer diameter of a fixed end portion 9a of a driven member 9 to be described later, and after assembling each component, the outer peripheral portion of the front end surface Is arranged in contact with the axially outer end surface of the inner ring 43b of the large-diameter ball bearing 43. Further, the front end face of the flange portion 2a is coupled from the axial direction by the cam bolt 10 in a state of being in contact with the driven member 9 from the axial direction.
- stopper concave grooves 2b into which the stopper convex portions 61b of the holding plate 61 are engaged are formed on the outer periphery of the flange portion 2a along the circumferential direction.
- the stopper concave groove 2b is formed in a circular arc shape having a predetermined length in the circumferential direction, and both end edges of the stopper convex portion 61b rotated within this length range abut against the circumferential opposite edges 2c and 2d, respectively.
- the relative rotational position of the camshaft 2 on the maximum advance angle side or the maximum retard angle side with respect to the timing sprocket 1 is regulated.
- the stopper convex portion 61b is disposed at a position closer to the camshaft 2 than a portion of the holding plate 61 fixed to the outer ring 43a of the large-diameter ball bearing 43 facing the outer side in the axial direction. 9 is not in contact with the fixed end 9a in the axial direction. Therefore, interference between the stopper convex portion 61b and the fixed end portion 9a can be sufficiently suppressed.
- the cam bolt 10 has an end surface of the head portion 10a that supports the inner ring of the small-diameter ball bearing 37 from the axial direction, and an inner shaft extending from the end portion of the camshaft 2 to the outer periphery of the shaft portion 10b.
- a male screw 10c is formed to be screwed onto the female screw formed in the direction.
- the driven member 9 is integrally formed of iron-based metal, and as shown in FIG. 1, a disk-shaped fixed end portion 9a formed on the rear end side (camshaft 2 side), and the fixed end portion 9a.
- the rear end surface of the fixed end portion 9a is in contact with the front end surface of the flange portion 2a of the camshaft 2, and is fixed to the flange portion 2a by pressure contact with the axial force of the cam bolt 10 from the axial direction.
- the cylindrical portion 9b has an insertion hole 9d through which the shaft portion 10b of the cam bolt 10 is inserted, and a needle bearing 38 as a bearing member provided on the outer peripheral side. It has been.
- the retainer 41 is bent into a substantially L-shaped cross section forward from the front end of the outer peripheral portion of the fixed end portion 9a, and protrudes in the same direction as the cylindrical portion 9b. Is formed.
- the cylindrical tip portion 41a of the retainer 41 extends in the direction of the partition wall 5b of the motor housing 5 through an annular concave storage space 44 formed between the female screw forming portion 6 and the extending portion 5d. ing. Further, as shown in FIG. 1 and FIG. 2, a plurality of substantially rectangular roller holders that hold the plurality of rollers 48 in a freely rolling manner at substantially equal intervals in the circumferential direction of the cylindrical tip portion 41 a. Holes 41b are formed at equally spaced positions in the circumferential direction. The total number of the roller holding holes 41 b (rollers 48) is smaller than the total number of teeth of the internal teeth 19 a of the internal tooth component 19. As a result, the reduction ratio is obtained.
- the phase changing mechanism 4 includes the electric motor 12 disposed on the front end side of the cylindrical portion 9b of the driven member 9, a speed reducing mechanism 8 that reduces the rotational speed of the electric motor 12 and transmits the speed to the camshaft 2. Is mainly composed of
- the electric motor 12 is a brushed DC motor, the motor housing 5 being a yoke that rotates integrally with the timing sprocket 1, and the motor housing 5.
- a motor output shaft 13 that is rotatably provided, a pair of semicircular arc permanent magnets 14 and 15 that are stators fixed to the inner peripheral surface of the motor housing 5, and the power supply plate 11 are provided.
- 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 through a stepped portion 13c formed at a substantially central position in the axial direction, and the opposite side. And a 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 8 is integrally formed on the rear end side.
- the annular member 20 is press-fitted and fixed to the outer periphery of the small-diameter portion 13b, and the commutator 21 is press-fitted and fixed to the outer peripheral surface of the annular member 20 from the axial direction. Is positioned.
- the outer diameter of the annular member 20 is set to be substantially the same as the outer diameter of the large-diameter portion 13a, and the axial length is set slightly shorter than the small-diameter portion 13b.
- a plug body 55 that is supplied into the motor output shaft 13 and the eccentric shaft portion 39 and suppresses leakage of the lubricating oil for lubricating the bearings 37 and 38 to the outside. It is press-fitted and fixed.
- 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 18 is wound.
- the commutator 21 is formed in an annular shape with a conductive material, and the ends of the wires drawn out of the coil 18 are electrically connected to each segment divided into the same number as the number of poles of the iron core rotor 17. Yes.
- the permanent magnets 14, 15 are formed in a cylindrical shape as a whole and have a plurality of magnetic poles in the circumferential direction, and the position in the axial direction is the power supply with respect to the axial center of the iron core rotor 17. It is offset on the plate 11 side. Accordingly, the front end portions of the permanent magnets 14 and 15 are arranged so as to overlap with switching brushes 25a and 25b described later provided on the commutator 21 and the power feeding plate 11 in the radial direction.
- the power supply plate 11 includes a disk-shaped rigid plate portion 16 (fixed plate portion) made of an iron-based metal material, and circular molds molded on both front and rear sides of the rigid plate portion 16. And a plate-like resin portion 22.
- the power feeding plate 11 is configured as a part of a power feeding mechanism for the electric motor 12.
- the rigid plate 16 has an annular stepped groove 5 e in which an outer peripheral portion 16 a not covered with the resin portion 22 is formed on the inner periphery of the front end portion of the motor housing 5. It is positioned and fixed by caulking, and a shaft insertion hole 16b through which one end of the motor output shaft 13 and the like are inserted is formed through the center.
- the rigid plate 16 is formed by punching two holding holes 16c and 16d having different shapes at predetermined positions continuous to the inner peripheral edge of the shaft insertion hole 16b. Brush holders 23a and 23b described later are fitted and held. Furthermore, a substantially triangular first reinforcing portion 34 is integrally provided at the remaining portion of the holding holes 16c and 16d after being punched, and the shaft insertion hole 16b is opposite to the first reinforcing portion 34. The arc-shaped second reinforcing portion 35 is integrally provided at the position.
- the first reinforcing portion 34 has a top portion 34a facing the shaft insertion hole 16b and a small-diameter hole 34b formed through the center.
- the second reinforcing portion 35 extends in an arc shape along the inner peripheral surface of the shaft insertion hole 16b, has an area larger than that of the first reinforcing portion 34, and is equally spaced in the circumferential direction.
- Three weight balancer holes 35a, 35b, and 35c are formed through.
- three U-shaped grooves 16e are formed at predetermined positions in the circumferential direction of the outer peripheral portion 16a so as to perform positioning in the circumferential direction with respect to the housing body 5a through a jig (not shown).
- the power supply plate 11 is disposed inside the holding holes 16 c and 16 d of the rigid plate 16, and a plurality of rivets 40 are provided on the front end portion 22 a of the resin portion 22.
- Each of the front end surfaces is a pair of switching brushes 25a and 25b which are commutators elastically contacting the outer peripheral surface of the commutator 21 from the radial direction, and the entire outer surface is exposed on the front end portion 22a side of the resin portion 22.
- harness 27a, and 27b, is provided.
- These and the power feeding plate 11 constitute a power feeding mechanism.
- Each slip ring 26a, 26b has a part on the back side exposed from the resin portion 22, and one end portion of each pigtail harness 27a, 27b is connected to the exposed portion by soldering.
- a holding body 28 integrally molded with a synthetic resin material is fixed to the cover body 3a of the cover member 3.
- the holding body 28 is formed in a substantially L shape in a side view, and has a substantially bottomed cylindrical brush holding portion 28 a inserted into the holding hole 3 d of the cover member 3.
- a connector portion 28b on the opposite side of the brush holding portion 28a, a boss portion 28 integrally projecting on one side surface of the brush holding portion 28a and bolted to the cover body 3a, and a part thereof inside Is mainly composed of a pair of power supply terminal pieces 31, 31 embedded therein.
- the brush holding portion 28 a extends substantially in the horizontal direction (axial direction) and is parallel to the internal vertical position (inner and outer peripheral sides with respect to the axis of the motor housing 5).
- a pair of rectangular tube-shaped brush holders 29a and 29b are press-fitted and fixed in a pair of prismatic fixing holes formed in FIG.
- the power supply brushes 30a and 30b are held in the brush holders 29a and 29b so as to be slidable in the axial direction.
- Each of the brush holders 29a and 29b has an opening at the front and rear ends thereof, and the front ends of the power supply brushes 30a and 30b can be moved forward and backward from the opening on the front end side.
- One end of the pigtail harness (not shown) is connected to the rear end of each of the power supply brushes 30a and 30b via the opening by soldering.
- Each of the power supply brushes 30a and 30b is formed in a prismatic shape and is set to a predetermined axial length, and each flat front end surface is in contact with each of the power supply slip rings 26a and 26b from the axial direction. It comes to touch.
- a pair of coil springs 42a and 42b for urging the power supply brushes 30a and 30b in the direction of the slip rings 26a and 26b are provided on the inner rear end sides of the brush holders 29a and 29b of the brush holding portion 28. Is provided.
- the pair of power feeding terminal pieces 31 and 31 are formed in a parallel and substantially crank shape along the vertical direction, and the terminals 31a and 31a on one side (lower end side) are exposed.
- the other side (upper end side) terminals 31b and 31b are projected from the female fitting groove 28d of the connector portion 28b.
- the terminals 31a and 31a on the one side are arranged in contact with the upper surface of the bottom wall 28f, and the other ends of a pair of pigtail harnesses (not shown) are connected by soldering.
- each pigtail harness has a length that prevents the power supply brushes 30a and 30b from falling off the brush holders 29a and 29b even when the power supply brushes 30a and 30b are pushed out by the spring force of the coil springs 42a and 42b. Is set.
- annular sealing member 33 is fitted and held as shown in FIG.
- the connector portion 28b is electrically connected to the control unit (not shown) via the male terminal by the other side terminals 31b and 31b facing the fitting groove 28d in which a male terminal (not shown) is inserted into the upper end portion. It is connected.
- 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 retainer 38a press-fitted into the inner peripheral surface of the eccentric shaft portion 39, and a needle roller 38b, which is a plurality of rolling elements rotatably held inside the retainer 38a. Has been.
- the needle roller 38 b rolls on the outer peripheral surface of the cylindrical portion 9 b of the driven member 9.
- the small-diameter ball bearing 37 has an inner ring fixed between the front end edge of the cylindrical portion 9 b of the driven member 9 and the head 10 a of the cam bolt 10, while an outer ring has a step difference of the eccentric shaft portion 39. While being press-fitted and fixed to the inner peripheral surface of the diameter, the axial positioning is performed by contacting a step edge formed on the inner peripheral surface.
- lubricating oil from the inside of the speed reduction mechanism 8 into the electric motor 12 is provided 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 8 into the electric motor 12 is provided.
- a small-diameter oil seal 46 is provided to prevent this leakage. The oil seal 46 separates the electric motor 12 and the speed reduction mechanism 8 with a sealing function.
- the control unit detects the current engine operating state based on information signals from various sensors such as a crank angle sensor, an air flow meter, a water temperature sensor, and an accelerator opening sensor (not shown), and performs engine control based on this information signal.
- the coil 18 is energized through the power supply brushes 30a, 30b, the slip rings 26a, 26b, the switching brushes 25a, 25b, the commutator 21, and the like to control the rotation of the motor output shaft 13, thereby reducing the speed reduction mechanism 8.
- the relative rotation phase of the camshaft 2 with respect to the timing sprocket 1 is controlled.
- the speed reduction mechanism 8 includes the eccentric shaft portion 39 that performs an eccentric rotational motion, a medium-diameter ball bearing 47 provided on the outer periphery of the eccentric shaft portion 39, and the medium-diameter ball.
- the roller 48 provided on the outer periphery of the bearing 47; the retainer 41 that allows the roller 48 to move in the radial direction while retaining the roller 48 in the rolling direction; and the driven member 9 that is integral with the retainer 41; Is mainly composed of
- the axial center Y of the cam surface 39a formed on the outer peripheral surface is slightly eccentric in the radial direction from the axial center X of the motor output shaft 13.
- 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. That is, in the outer ring 47b, one end surface on the electric motor 12 side in the axial direction does not come into contact with any part, and the other end surface in the axial direction is between the inner side surface of the retainer 41 facing the minute end. One gap C is formed and is in a free state.
- the outer peripheral surface of the outer ring 47b is in contact with the outer peripheral surface of each roller 48 so as to be freely rotatable, and an annular second gap C1 is formed on the outer peripheral side of the outer ring 47b. Due to the second gap C1, the entire medium-diameter ball bearing 47 can move in the radial direction along with the eccentric rotation of the eccentric shaft portion 39, that is, can move eccentrically.
- Each of the rollers 48 is formed of an iron-based metal, and is fitted into the internal teeth 19a of the internal gear component 19 while moving in the radial direction along with the eccentric movement of the medium-diameter ball bearing 47.
- the roller holding hole 41b is caused to swing in the radial direction while being guided in the circumferential direction by both side edges.
- the inside of the speed reduction mechanism 8 is supplied with lubricating oil by lubricating oil supply means.
- This lubricating oil supply means is formed inside the bearing 02 of the cylinder head 01, and is formed in the oil supply passage through which the lubricating oil is supplied from a main oil gallery (not shown) and in the direction of the internal axis of the camshaft 2.
- An oil supply hole 51 communicating with the oil supply passage through a groove groove is formed so as to penetrate in the inner axial direction of the driven member 9. One end opens into the oil supply hole 51 and the other end is the needle.
- the small-diameter oil hole 52 opened in the vicinity of the bearing 38 and the medium-diameter ball bearing 47, and an oil discharge hole (not shown) formed through the driven member 9 are also formed.
- this lubricating oil supply means lubricating oil is supplied and stays in the accommodation space 44, from which the medium-diameter ball bearing 47 and each roller 48 are lubricated, and further, the eccentric shaft portion 39 and the motor output shaft 13 It flows into the interior and is used to lubricate movable parts such as the needle bearing 38 and the small-diameter ball bearing 37.
- the lubricating oil staying in the housing space 44 is prevented from leaking into the motor housing 5 by the small diameter oil seal 46.
- 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 generated by the internal tooth component 19 and the female screw forming portion 6. Is transmitted to the motor housing 5 through the motor housing 5, and the motor housing 5 rotates synchronously.
- 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 cam of the camshaft 2 opens and closes the intake valve.
- the coil 18 of the electric motor 12 is supplied from the control unit through the terminal pieces 31 and 31, the pigtail harness, the power supply brushes 30a and 30b, the slip rings 26a and 26b, and the like. Is energized. As a result, the motor output shaft 13 is rotationally driven, and the rotational force of this rotational force is transmitted to the camshaft 2 via the speed reduction mechanism 8.
- the rollers 48 are guided in the radial direction by the roller holding holes 41b of the retainer 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.
- the camshaft 2 rotates relative to the timing sprocket 1 in the forward and reverse directions and the relative rotational phase is converted, and the opening / closing timing of the intake valve is controlled to be advanced or retarded.
- the maximum position restriction (angular position restriction) of forward and reverse relative rotation of the camshaft 2 with respect to the timing sprocket 1 is such that each side surface of the stopper convex portion 61b is set to one of the opposing surfaces 2c and 2d of the stopper concave groove 2b. This is done by abutting.
- 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.
- the outer peripheral portion 16a of the rigid plate portion 16a is press-fitted from the axial direction into the stepped concave groove 5e. After that, the outer peripheral portion of the stepped concave groove 5e is caulked and fixed to the inside.
- the rigid plate portion 16 is not a simple annular shape, and the first reinforcing portion 34 and the second reinforcing portion 34 are not provided on the inner peripheral portion. Since the reinforcing portion 35 is provided, the overall rigidity is increased. Accordingly, the rigid plate portion 16 is not deformed due to the load stress during caulking, and the entire power supply plate 11 including the resin portion 22 is maintained flat. As a result, a decrease in flatness of the slip rings 26a and 26b integrally fixed to the resin portion 22 is suppressed, and a smooth sliding property with the power supply brushes 30a and 30b can be obtained at all times. .
- the reinforcing portions 34 and 35 are provided and these are disposed opposite to each other in the radial direction, the reinforcing effect of the rigid plate portion 16 is increased.
- first reinforcing portion 34 and the second reinforcing portion 35 are disposed so as to partially overlap the slip rings 26a and 26b in the axial direction, the resin of the slip rings 26a and 26b is used.
- the support rigidity by the part 22 becomes high. Also by this, the flatness of each slip ring 26a, 26b can be made high.
- the brush holders 23a and 23b of the switching brushes 25a and 25b are fixed to the resin portion 22 in a state where the brush holders 23a and 23b are disposed in the thinned holding holes 16c and 16d of the rigid plate portion 16, respectively. That is, since the rigid plate portion 16 is disposed and fixed at substantially the center in the axial direction, the length in the axial direction of the power feeding mechanism can be made as short as possible. As a result, the entire apparatus can be reduced in the axial direction.
- the power feeding plate 11 is fixed by using, for example, a slip ring or the like. In comparison, the number of parts can be reduced and assembly work can be facilitated.
- the power feeding plate 11 exposes a part of the back side of each slip ring 26a, 26b from the resin part 22, and one end of each pigtail harness 27a, 27b is connected to the exposed part by soldering. Therefore, the connection structure is simplified and the connection work is facilitated.
- the holding holes 16c, 16d are used to fix the brush holders 23a, 23b, the switching brushes 25a, 25b and the like to the one side in the radial direction of the rigid plate portion 16 by the resin portion 22.
- the overall weight balance may be deteriorated.
- the three weight balance holes 35a to 35c are formed in the second reinforcing portion 35 at positions facing the brush holders 23a and 23b and the switching brushes 25a and 25b in the radial direction, the entire weight balance is formed. Can be achieved.
- the rigid plate portion 16 is integrally molded with the resin portion 22 on the front and rear surface sides excluding the outer peripheral portion 16a, and the slip rings 26a and 26b and the brush holders 23a and 23b are integrally formed on the resin portion 22. Since it is fixed to the mold, each fixing work becomes easy.
- each of the holding holes 16c and 16d and the weight balance holes 35a to 35c is filled with the resin of the resin portion 22, the circumferential positioning when the rigid plate portion 16 is fixed to the housing body 5a is performed.
- the caulking force can be secured by exposing the outer peripheral portion 16a of the rigid plate portion 16, and the heat generated when the power supply brushes 30a, 30b and the slip rings 26a, 26b slide are also generated. It is possible to dissipate heat from the outer peripheral portion 16a.
- the U-shaped groove 16e provided in the outer peripheral portion 16a of the rigid plate portion 16 can be used as a mark for positioning in the circumferential direction with respect to the housing body 5a when fixed by caulking. Can be used for the confirmation test of the slip torque of the power feeding plate 11 with respect to the housing body 5a.
- FIG. 9 shows the second embodiment, and the basic configuration is the same as that of the first embodiment, except that four switching brushes are provided on the power supply plate 11.
- the rigid plate portion 16 of the power supply plate 11 has four holding holes 16f to 16i having different shapes at radial positions around the shaft insertion hole 16b. Further, a substantially rectangular first reinforcing portion 34 projecting inward is provided between two holding holes 16f and 16i adjacent in the circumferential direction, and the first reinforcing portion 34 is opposed to the first reinforcing portion 34 in the radial direction.
- the second reinforcing portion 35 having an arc shape is provided on the top. Furthermore, between the circumferential direction of the said 1st reinforcement part 34 and the 2nd reinforcement part 35, the substantially trapezoidal 3rd, 4th reinforcement parts 64 and 65 are protrudingly provided inward.
- the reinforcing portions 34, 35, 64, 65 are respectively provided with weight balance holes 34b, 34c, 35a to 35c, 64a, 65a.
- the resin portion 22 is molded on both side surfaces of the rigid plate portion 16, that is, on both side surfaces including the holding holes 16f to 16i and the reinforcing portions 34, 35, 64, 65.
- Four brush holders 23a to 23d are integrally provided by rivets 40 on both sides at positions corresponding to the holding holes 16f to 16i of the resin portion 22, and the brush holders 23a to 23d are provided inside the brush holders 23a to 23d.
- the switching brushes 25a to 25d, each tip of which abuts on the outer peripheral surface of the commutator 21, are urged in the advancing direction by the coil springs 24a to 24d.
- each slip ring 26a, 26b is embedded and fixed in the front end portion of the resin portion 22, and one end portion of each pigtail harness 27a to 27d is soldered to a part of the back surface exposed from the resin portion 22.
- Each configuration such as being connected by is the same as that of the first embodiment.
- the rigidity of the rigid plate portion 16 is ensured by the reinforcing portions 34, 35, 64, and 65, bending deformation at the time of caulking and fixing is suppressed, and the flatness of the slip rings 26a and 26b is reduced.
- the effects such as being able to be suppressed are the same as in the first embodiment.
- the present invention is not limited to the configuration of each of the embodiments described above, and an effect can be obtained if the configuration is such that a load is applied to the outer peripheral portion 16a of the rigid plate portion 16.
- a load is applied to the outer peripheral portion 16a of the rigid plate portion 16.
- press fitting or bolt fixing may be used in addition to caulking. Even in the case of this press-fitting or bolt fixing, the load applied to the rigid plate portion 16 at the time of the press-fitting or bolt fixing is so large that the above-mentioned technical problems may be caused.
- the rigidity can be ensured by the action of the above-described embodiments, the bending deformation can be suppressed.
- the rigid plate portion 16 is not limited to the iron-based metal, and may be a plate formed of a resin material having higher rigidity than the resin portion 22, for example.
- the number of the power supply brushes may be three or five other than two and four, and in these cases, the weight balance is arbitrarily formed to adjust the weight balance.
- the rigidity around the switching brushes is improved by the reinforcing portion, and the heat generated by each switching brush can be effectively radiated from the reinforcing portion.
- the valve timing control apparatus for an internal combustion engine according to claim 7 A valve timing control device for an internal combustion engine, wherein a resin portion is not provided on an outer peripheral portion to which the rigid plate portion is caulked and fixed.
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Abstract
Description
そして、バッテリー電源から供給された電流を、前記給電用ブラシとスリップリング及び切換用ブラシとコミュテータを利用して前記電動モータにバルブタイミングを変更するときに給電して、該電動モータの回転力を、減速機構を介してカムシャフトに伝達することにより、前記タイミングスプロケットに対するカムシャフトの相対回転位相を変換して吸気弁や排気弁の開閉タイミングを制御するようになっている。
〔本実施形態の作動〕
以下、本実施形態の作動について説明すると、まず、機関のクランクシャフトの回転駆動に伴ってタイミングチェーンを介してタイミングスプロケット1が回転して、その回転力が内歯構成部19と雌ねじ形成部6を介してモータハウジング5に伝達されて、該モータハウジング5が同期回転する。一方、前記内歯構成部19の回転力が、各ローラ48から保持器41及び従動部材9を経由してカムシャフト2に伝達される。これによって、カムシャフト2のカムが吸気弁を開閉作動させる。
〔第2実施形態〕
図9は第2実施形態を示し、基本構成は第1実施形態と同じであるが、異なるところは、給電プレート11に切換用ブラシを4つ設けたものである。
〔請求項a〕
請求項5に記載の内燃機関のバルブタイミング制御装置において、
前記切換用ブラシは、給電プレートの周方向に少なくとも2つ設けられ、該両切換用ブラシの間に前記剛性プレート部の前記補強部が配置されていることを特徴とする内燃機関のバルブタイミング制御装置。
〔請求項b〕
請求項7に記載の内燃機関のバルブタイミング制御装置において、
前記剛性プレート部のかしめ固定される外周部には、樹脂部を設けないことを特徴とする内燃機関のバルブタイミング制御装置。
Claims (19)
- クランクシャフトから回転力が伝達される駆動回転体と、
該駆動回転体から回転力が伝達されるカムシャフトに固定された従動回転体と、
前記駆動回転体に設けられた電動モータと、
該電動モータのモータ出力軸の回転を減速して前記従動回転体に伝達する減速機構と、
給電回路から供給された電流を前記電動モータに給電する給電用ブラシと、
前記駆動回転体に設けられ、前記給電ブラシが接触するスリップリングを有する給電プレートと、
を備え、
前記給電プレートは、円盤状に形成され、外周部が前記駆動回転体に固定された剛性プレート部と、該剛性プレート部の外面をモールドした樹脂部と、を有し
前記剛性プレート部は、前記樹脂部より剛性が高く形成され、前記樹脂部を介して前記給電ブラシを内部に保持する保持孔が貫通形成されていると共に、該保持孔を避けた部位に径方向内側に延出した補強部が一体に設けられていることを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項1に記載の内燃機関のバルブタイミング制御装置において、
前記樹脂部は、剛性プレート部の両側面をモールドしていると共に、外側面側に前記スリップリングを保持したことを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項2に記載の内燃機関のバルブタイミング制御装置において、
前記剛性プレート部の補強部の一部が、前記スリップリングと軸方向で重なり合うように配置されていることを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項3に記載の内燃機関のバルブタイミング制御装置において、
前記スリップリングは、前記樹脂部の外側面側に位置して前記給電ブラシが接触する表面が露出していると共に、前記樹脂部には前記スリップリングの裏面の一部が露出した露出部が設けられ、該露出部に前記電動モータのコイルに接続されるハーネスの一端部が接続されていることを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項4に記載の内燃機関のバルブタイミング制御装置において、
前記電動モータのモータ出力軸の外周にコミュテータが設けられていると共に、前記剛性プレート部の保持孔内に、前記スリップリングの裏面と電気的に接続された切換用ブラシが配置され、
該切換用ブラシの先端部が前記コミュテータの外周面に摺接して電動モータのコイルに通電するように構成したことを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項4に記載の内燃機関のバルブタイミング制御装置において、
前記スリップリングは、径方向に内外二重に2つ配置され、
前記補強部は、前記2つのスリップリングに対して前記出力軸の軸方向で重なるように配置されていることを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項1に記載の内燃機関のバルブタイミング制御装置において、
前記剛性プレートの固定は、前記駆動回転体にかしめ固定または圧入固定またはボルト固定であることを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項1に記載の内燃機関のバルブタイミング制御装置において、
前記剛性プレート部は、前記補強部に径方向で対向した位置に内方へ延出した第2補強部を有することを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項8に記載の内燃機関のバルブタイミング制御装置において、
前記第2補強部は、前記第1補強部よりも周方向の幅が大きく形成されていると共に、前記第1補強部と径方向から対向した位置にバランス孔が形成されていることを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項8に記載の内燃機関のバルブタイミング制御装置において、
前記第2補強部は、前記第1補強部よりも周方向の幅が大きく形成されていると共に、径方向の幅が短く形成されていることを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項9に記載の内燃機関のバルブタイミング制御装置において、
前記バランス孔は、前記剛性プレート部の両側面に形成された樹脂部に覆われていることを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項1に記載の内燃機関のバルブタイミング制御装置において、
前記剛性プレート部は、鉄系金属によって形成されていることを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項1に記載の内燃機関のバルブタイミング制御装置において、
前記駆動回転体の軸方向の一端部に、横断面ほぼL字形状の環状凹溝が形成されていると共に、該環状凹溝の底面に前記剛性プレート部の外周部を軸方向から当接させると共に、前記一端部の円環溝を構成する部位をかしめて剛性プレート部を固定したことを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項1に記載の内燃機関のバルブタイミング制御装置において、
前記給電プレートの樹脂部は、前記駆動回転体の内周面から離間して設けられていることを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項1に記載の内燃機関のバルブタイミング制御装置において、
前記剛性プレート部は、外周部に少なくとも一つの切欠部を有することを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項15に記載の内燃機関のバルブタイミング制御装置において、
前記切欠部は、剛性プレート部を前記駆動回転体の一端部にかしめ固定した状態でも外部に露出していることを特徴とする内燃機関のバルブタイミング制御装置。 - クランクシャフトから回転力が伝達される駆動回転体と、
カムシャフトに固定された従動回転体と、
前記駆動回転体と一体に設けられた電動モータと、
該電動モータのモータ出力軸の回転を減速して前記従動回転体に伝達する減速機構と、
給電回路から供給された電流を前記電動モータに給電する給電用ブラシと、
前記駆動回転体に設けられ、前記給電ブラシが接触するスリップリングを有する給電プレートと、
を備え、
前記給電プレートは、外周部が前記駆動回転体にかしめ固定または圧入固定された円盤状の固定プレート部と、該固定プレート部の両側面にモールドされた樹脂部と、を備え、
前記固定プレート部に、前記モータ出力軸の一端部が挿通する軸挿通孔が形成され、前記樹脂部を介して前記給電ブラシを保持する少なくとも2つの貫通部がそれぞれ前記軸挿通孔と連結して形成されていると共に、前記固定プレートの周方向の前記2つの貫通部の間に径方向内側に延出した補強部が一体に設けられている一方、
前記樹脂部は、前記貫通部を含む固定プレート部の両側面にモールドされ、外側面に前記スリップリングが保持されていることを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項17に記載の内燃機関のバルブタイミング制御装置において、
前記給電プレートは、前記スリップリングの裏面側の一部が前記他方側の部位に形成された開口部を介して露出するように形成されていると共に、該露出部と前記切換用ブラシはピグテールハーネスによって電気的に接続されていることを特徴とする内燃機関のバルブタイミング制御装置。 - 請求項18に記載の内燃機関のバルブタイミング制御装置において、
前記露出部は、前記固定プレート部の貫通部と前記樹脂部の開口部を介して外部に露出していることを特徴とする内燃機関のバルブタイミング制御装置。
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CN201580007570.6A CN105980672B (zh) | 2014-02-06 | 2015-01-14 | 内燃机的气门正时控制装置 |
DE112015000706.7T DE112015000706T5 (de) | 2014-02-06 | 2015-01-14 | Ventilsteuerungseinrichtung für Motor mit innerer Verbrennung |
JP2015560908A JP6030781B2 (ja) | 2014-02-06 | 2015-01-14 | 内燃機関のバルブタイミング制御装置 |
US15/109,924 US9932865B2 (en) | 2014-02-06 | 2015-01-14 | Valve timing control device for internal combustion engine |
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US6302073B1 (en) * | 1999-03-23 | 2001-10-16 | Tcg Unitech Aktiengesellschaft | Device for adjusting the phase angle of a camshaft of an internal combustion engine |
JP4358180B2 (ja) * | 2005-11-04 | 2009-11-04 | 株式会社日立製作所 | 内燃機関のバルブタイミング制御装置 |
JP2008002324A (ja) * | 2006-06-21 | 2008-01-10 | Hitachi Ltd | 位相角検出装置及び該位相角検出装置を用いた内燃機関のバルブタイミング制御装置 |
JP2011064105A (ja) * | 2009-09-16 | 2011-03-31 | Hitachi Automotive Systems Ltd | 内燃機関のバルブタイミング制御装置 |
JP5718764B2 (ja) | 2011-08-09 | 2015-05-13 | 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 |
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2015
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- 2015-01-14 DE DE112015000706.7T patent/DE112015000706T5/de not_active Withdrawn
- 2015-01-14 CN CN201580007570.6A patent/CN105980672B/zh not_active Expired - Fee Related
- 2015-01-14 JP JP2015560908A patent/JP6030781B2/ja active Active
- 2015-01-14 WO PCT/JP2015/050744 patent/WO2015118915A1/ja active Application Filing
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JP2012251537A (ja) * | 2011-06-07 | 2012-12-20 | Hitachi Automotive Systems Ltd | 内燃機関のバルブタイミング制御装置 |
Cited By (2)
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JP2019190384A (ja) * | 2018-04-26 | 2019-10-31 | 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 |
JP7038000B2 (ja) | 2018-04-26 | 2022-03-17 | 日立Astemo株式会社 | 内燃機関のバルブタイミング制御装置 |
Also Published As
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CN105980672A (zh) | 2016-09-28 |
US20160326917A1 (en) | 2016-11-10 |
JPWO2015118915A1 (ja) | 2017-03-23 |
DE112015000706T5 (de) | 2016-11-10 |
JP6030781B2 (ja) | 2016-11-24 |
CN105980672B (zh) | 2018-10-09 |
US9932865B2 (en) | 2018-04-03 |
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