WO2015087648A1 - 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
- WO2015087648A1 WO2015087648A1 PCT/JP2014/079799 JP2014079799W WO2015087648A1 WO 2015087648 A1 WO2015087648 A1 WO 2015087648A1 JP 2014079799 W JP2014079799 W JP 2014079799W WO 2015087648 A1 WO2015087648 A1 WO 2015087648A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve timing
- combustion engine
- internal combustion
- timing control
- control device
- Prior art date
Links
Images
Classifications
-
- 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
-
- 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
-
- 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
- H02K13/10—Arrangements of brushes or commutators specially adapted for improving commutation
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K5/00—Casings; Enclosures; Supports
- H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/006—Structural association of a motor or generator with the drive train of a motor vehicle
-
- 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
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.
- a valve timing control device for controlling the opening / closing timing is provided.
- valve timing control device changes the valve timing to the electric motor by using a power supply brush and a slip ring as a current supplied from a battery power source via a pigtail harness.
- the power consumption is reduced as much as possible by supplying power only at times.
- valve timing control device described in the publication, a coil spring is arranged in series with the power supply brush on the rear end side of the power supply brush in order to elastically contact the power supply brush with the slip ring from the axial direction.
- the camshaft axial length of the holding body for holding the power supply brush and the coil spring that is, the length in the width direction is inevitably increased, and the overall size of the valve timing control device in the axial direction is inevitably increased. ing.
- the accommodation space in the engine room of the internal combustion engine in which the valve timing control device is mounted may be limited.
- An object of the present invention is to provide a valve timing control device for an internal combustion engine that can reduce the overall length of the device by shortening the axial length of the brush holding portion of the holding body.
- a driving rotating body to which a rotational force is transmitted from a crankshaft
- a driven rotating body fixed to a camshaft to which the rotating force is transmitted from the driving rotating body
- the motor housing the motor housing
- An electric motor provided to rotate together with the drive rotator or the driven rotator and to rotate the drive rotator and the driven rotator relative to each other by being supplied with an electric current; and provided outside the electric motor, the electric motor
- a power supply brush that supplies power to the motor, and a slip ring that is provided on the other side of the rotating member and the fixed member and is in sliding contact with the power supply brush,
- a torsion coil spring for urging the power supply brush in the slip ring direction is arranged in parallel with the power supply brush on a side portion of the power supply brush.
- the axial length of the entire valve timing control device can be shortened as much as possible, so that the device can be miniaturized.
- 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. 2 is a cross-sectional view taken along the line CC of FIG. It is a cross-sectional view of the holding body provided for the second embodiment.
- FIG. 1 It is a perspective view which shows the state which the other end part of the torsion coil spring contact
- FIG. 1 It is sectional drawing of the main structural members provided to this embodiment, Comprising: A shows the state before attaching a holding body to a cover member, and B has shown the state after attaching. It is a cross-sectional view of the holding body provided for the third embodiment. It is sectional drawing of the main structural members provided to this embodiment, Comprising: A shows the state before attaching a holding body to a cover member, and B has shown the state after attaching.
- valve timing control device for an internal combustion engine according to the present invention will be described with reference to the drawings.
- the present invention 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 arcuate 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 extends in the vertical direction so as to cover the cylinder head 01 as the engine body and the chain outside the figure wound around the timing sprocket 1 on the front end side of the cylinder block outside the figure. 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 integrally formed on the outer peripheral edge on the opening side of the cover 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 cylindrical housing body 5a formed by pressing a ferrous metal material into a bottomed cylinder, and a synthetic resin that seals the front end opening of the housing body 5a. And a sealing plate 11 made of a nonmagnetic material.
- the housing main body 5a has a disk-shaped partition wall 5b on the rear end side, and a large-diameter shaft insertion hole 5c through which an eccentric shaft portion 39, which will be described later, is inserted is formed substantially at 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 shaft insertion 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 2 b into which the stopper convex portions 61 b of the holding plate 61 are engaged are formed on the outer periphery of the flange portion 2 a 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 36 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 36a of the retainer 36 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 FIGS. 1 and 2, a plurality of substantially rectangular roller holders for holding the plurality of rollers 48 so as to roll freely are provided at substantially equal intervals in the circumferential direction of the cylindrical tip portion 36a. Holes 36b are formed at equally spaced positions in the circumferential direction. The total number of the roller holding holes 36 b (rollers 48) is smaller than the total number of teeth of the internal teeth 19 a of the internal tooth component 19.
- 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 provided rotatably, a pair of semicircular arc permanent magnets 14 and 15 which are stators fixed to the inner peripheral surface of the motor housing 5, and a stator fixed to the sealing plate 11. 16.
- 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 wire of the coil 18 is wound.
- the commutator 21 is formed in an annular shape by a conductive material, and the end of the coil wire from which the coil 18 is drawn is electrically connected to each segment divided into the same number as the number of poles of the iron core rotor 17. ing.
- the permanent magnets 14, 15 are formed in a cylindrical shape as a whole and have a plurality of magnetic poles in the circumferential direction, and their axial positions are fixed to the axial center of the iron core rotor 17. It is offset on the child 16 side. Accordingly, the front end portions of the permanent magnets 14 and 15 are arranged so as to overlap with the switching brushes 25a and 25b described later of the commutator 21 and the stator 16 in the radial direction.
- the stator 16 includes a disk-shaped resin plate 22 integrally provided on the inner peripheral side of the sealing plate 11 and a pair of resin plates 22 provided on the inner side of the resin plate 22.
- Resin holders 23a and 23b and the resin holders 23a and 23b are slidably accommodated in the radial direction, and the distal end surfaces thereof are outer peripheral surfaces of the commutator 21 by the spring force of the coil springs 24a and 24b.
- a pair of switching brushes 25a and 25b which are switching brushes (commutators) that elastically contact with each other from the radial direction, and two inner and outer parts that are embedded and fixed to the front end surfaces of the resin holders 23a and 23b with their outer end surfaces exposed.
- the sealing plate 11 is positioned and fixed by caulking to a concave step portion formed on the inner periphery of the front end portion of the motor housing 5, and a shaft through which one end portion of the motor output shaft 13 is inserted at the center position.
- the insertion hole 11a is formed through.
- a holding body 28 integrally molded with a synthetic resin material is fixed to the cover body 3a.
- the holding body 28 is formed in a substantially L shape in 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.
- 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 guide portions 29a and 29b are press-fitted and fixed in a pair of prismatic fixing holes 28g and 28g, respectively.
- the brushes for power feeding 30a and 30b are guided inside the brush guide portions 29a and 29b so as to be slidable in the axial direction.
- a partition wall 35 for partitioning the fixing holes 28g, 28g is integrally provided in the brush holding portion 28a.
- Each of the brush guide portions 29a and 29b has openings at the front and rear ends, and the front end portions of the power supply brushes 30a and 30b are held from the front end openings so as to be movable forward and backward.
- One end portions 33a and 33a of pigtail harnesses 33 and 33, which will be described later, are connected to the rear ends of the power supply brushes 30a and 30b by soldering.
- the brush guide portions 29a and 29b are formed with engaging grooves 40 and 40 extending in the axial direction from the hole edge of the rear end opening.
- Each of the engaging grooves 40, 40 is formed in an elongated slit shape, and is formed up to approximately half the length in the axial direction of each brush guide portion 29a, 29b.
- Each of the power supply brushes 30a and 30b is formed in a prismatic shape and set to a predetermined axial length, and each of the front end surfaces 30c and 30d is respectively connected to the power supply slip rings 26a and 26b from the axial direction. It comes to contact.
- each side portion of each fixing hole 28g, 28g of the brush holding portion 28 that is, each side portion in the horizontal direction shown in FIG.
- torsion coil springs 42 and 42 are accommodated in the spring accommodating chambers 41 and 41, respectively.
- the spring accommodating chambers 41 and 41 are disposed adjacent to the side walls where the engaging grooves 40 and 40 of the brush guide portions 29a and 29b are formed. Are formed in a substantially rectangular shape in plan view, and are arranged in parallel to each of the fixing holes 28g, 28g in a form continuous from the lateral direction.
- the torsion coil springs 42 and 42 are supported inside the spring accommodating chambers 41 and 41 by support shafts 45 and 45 inserted through a central portion 42a wound in a coil shape. Are inserted into the central portion 42a of each torsion coil spring 42 in advance, and both end portions in the axial direction are formed in U-shaped grooves 41a, 41b formed between the opposing inner surfaces of the spring accommodating chamber 41, the grooves 41a, Each torsion coil spring 42 is accommodated and held while being positioned in each spring accommodating chamber 41 by press-fitting to the maximum lowered position of the bottom of 41b.
- each torsion coil spring 42 has a linear end portion 42b that is elastically supported by the upper surface of the bottom wall 28f of the brush holding portion 28a from the upper end opening portion of the spring accommodating chamber 41, while each other is a linear end portion.
- End portions 42c are engaged with the respective engaging grooves 40 and elastically contact the rear end surfaces of the power supply brushes 30a and 30b, and the power supply brushes 30a and 30b are attached in the direction of the slip rings 26a and 26b. It has come to force.
- Each of the other end portions 42c is bent in a substantially L shape at the front end side, and the center of the rear end surface in the axial direction of each of the power supply brushes 30a and 30b is in a line contact state on the front end side of the L shape. It comes to be elastic.
- each torsion coil spring 42 is such that the linear portion of the other end 42 c is the bottom edge of the engaging groove 40 in a free state before the holding body 28 is attached to the cover member 3. 40a, and is separated from each of the power supply brushes 30a, 30b with a small gap. Therefore, each of the power supply brushes 30a and 30b is supported by the pigtail harness 33 without receiving a spring force, so that the power supply brushes 30a and 30b are prevented from falling off from the brush guide portions 29a and 29b.
- the holding body 28 is attached to the cover member 3, and the front end surfaces 30c, 30d of the power supply brushes 30a, 30b abut against the corresponding slip rings 26a, 26b to provide brush guidance.
- the spring force gradually increases while the other end portions 42c elastically contact the rear end surfaces, and the power supply brushes 30a and 30b. Is urged toward the slip rings 26a, 26b.
- 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 end portions 33b and 33b of the pair of pigtail harnesses 33 and 33 are connected by soldering.
- the lengths of the pigtail harnesses 33 and 33 are the power supply brushes 30a and 30b, the other end portions 42c and 42c of the torsion coil springs 42 and 42 are the bottoms of the engagement grooves 40, respectively.
- the length is set so as not to drop off from the brush guide portions 29a and 29b in a state where the spring force does not act upon contact with the edge 40a (FIG. 4A).
- an annular seal member 34 is fitted and held in an annular fitting groove formed on the base side outer periphery of the brush holding portion 28a, and the brush holding portion 28a is used for the holding.
- the seal member 34 is in elastic contact with the tip surface of the cylindrical wall 3b to seal the inside of the brush holding portion 28a.
- 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 pair of boss portions 28 c are formed in a substantially triangular shape, and an annular metal washer 53 is coupled in an embedded state at a substantially center, and is formed in the center of the metal washer 53.
- the holding body 28 is attached to the cover body 3a by a mounting bolt (not shown) inserted through the bolt insertion hole 53a.
- 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 to control the rotation of the motor output shaft 13, and the relative rotation phase of the camshaft 2 with respect to the timing sprocket 1 is controlled via the speed reduction mechanism 8.
- 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 36 that allows the roller 48 to move in the radial direction while retaining the roller 48 in the rolling direction; and the follower member 9 that is integral with the retainer 36; 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 two wheels 47a and 47b. It is configured.
- 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 36 facing it.
- 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 inner teeth 19a of the inner tooth component 19 while moving in the radial direction along with the eccentric movement of the medium-diameter ball bearing 47.
- the roller holding hole 36b 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 an oil supply passage through which lubricating oil is supplied from a main oil gallery (not shown), and as shown in FIG. And an oil supply hole 51 communicating with the oil supply passage through a groove groove, and penetrating in the direction of the internal axis of the driven member 9, and one end opened to the oil supply hole 51.
- the other end of the small-diameter oil hole 52 opened in the vicinity of the needle bearing 38 and the medium-diameter ball bearing 47, and the three large-diameter oil discharge holes that are formed in the driven member 9 and that are not illustrated. , Is composed of.
- 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 rotates through the timing chain 42 in accordance with the rotational drive of the crankshaft of the engine, and the rotational force is generated by the internal gear component 19 and the female screw forming portion.
- the motor housing 5 rotates synchronously via 6.
- the rotational force of the internal tooth component 19 is transmitted from each roller 48 to the camshaft 2 via the cage 36 and the driven member 9.
- the cam of the camshaft 2 opens and closes the intake valve.
- the electric motor 12 When a predetermined engine is operated after the engine is started, the electric motor 12 is supplied from the control unit via the terminal pieces 31 and 31, the pigtail harnesses 33 and 33, the power supply brushes 30a and 30b, the slip rings 26a and 26b, and the like.
- the coil 18 is energized.
- 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 36b of the retainer 36 every 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 number of rollers 48 or the like.
- 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 torsion coil springs 42 and 42 that urge the power supply brushes 30a and 30b toward the slip rings 26a and 26b are not in series with the power supply brushes 30a and 30b. Since they are provided in parallel via the spring accommodating chambers 41, 41, it is possible to shorten the axial length (length in the width direction) of the brush holding portion 28a as much as possible.
- the coil springs 42 and 42 are provided so as to overlap the power supply brushes 30 aluminum and 30 b in the axial direction.
- the axial length of the entire valve timing control device can be shortened, and the size can be reduced.
- the accommodation space in the engine room of the internal combustion engine equipped with the valve timing control device can be reduced.
- the torsion coil springs 42 and 42 are housed inside the spring housing chambers 41 and 41 via the support shafts 45, so that the torsion coil springs 42 and 42 are not substantially projected from the bottom surface 28f of the brush holding portion 28a. Therefore, the length in the width direction can be shortened as much as possible.
- [Second Embodiment] 8 to 10 show the second embodiment, and the basic configuration is the same as that of the first embodiment, except that the positions of the engagement grooves 40 and the other end portions 42c of the torsion coil springs 42 are different. The shape has been changed.
- each other end portion 40c of each torsion coil spring 40 has a tip portion bent in an L-shape further bent into a convex curve shape, and the tip side of this convex curve portion 42d is each power supply brush. It is in contact with one end face of 30a, 30b.
- the torsion coil springs 42 are provided in parallel with the power supply brushes 30a and 30b. Since the tip end side of the other end portion 40c of the torsion coil spring 40 is a convex curved portion 42d, it comes into contact with each end face of each of the power supply brushes 30a and 30b in a state closer to point contact than point contact or line contact. Therefore, the contact surface pressure is increased and the elastic contact can be achieved more stably and reliably.
- FIG. 11 and 12 show a third embodiment, in which each pigtail harness is abolished and each torsion coil spring 42, 42 is formed of a conductive material, and each one end 42b of each torsion coil spring 42, 42 is shown. , 42b are brought into contact with the one side terminals 31a, 31a of the terminal pieces 31, 31, and capacitors 55, 55 are connected between the one side terminals 31a, 31a and the metal washers 53, 53. Is.
- the spring accommodating chambers 41 and 41 are formed in a substantially L shape in plan view, and the lower spring accommodating chamber 41 is the upper spring accommodating chamber 41. In contrast, it is arranged and formed at a symmetrical position on a diagonal line.
- the terminal pieces 31 and 31 are arranged in a state where the one side terminals 31a and 31a are bent into L-shapes and separated into two forks, and the metal washers 53 and 53 of the boss portions 28c and 28c are arranged. It comes to approach.
- Each of the torsion coil springs 42 is formed of, for example, alloy steel containing copper as a conductive material, each central portion 42a is accommodated and held in each spring accommodating chamber 41 via a support shaft 45, and each end portion 42b is Each of the one side terminals 31a and 31a is in elastic contact with the upper surface, and each of the other end portions 42c is in elastic contact with one end surface of each of the power supply brushes 30a and 30b.
- the torsion coil spring 42 functions as a so-called inductor.
- Each of the capacitors 55, 55 has one lead wire 55a, 55a connected to the upper surface of the one side terminal 31a, 31a by soldering or the like, and the other lead wire 55b, 55b is an outer periphery of the metal washer 53, 53. It is also connected to the surface by soldering.
- the metal washers 53 and 53 are formed of a conductive material, and one end surface thereof is electrically connected to the cover member 3 and used as a ground.
- the brush guide portions 29a and 29b are formed with stopper portions 29c and 29c whose lower end portions are bent inwardly.
- each of the power supply brushes 30a and 30b has a tip having a small diameter, and the stepped portions 30e and 30e are locked to the stopper members 29c and 29c so that the maximum advancing movement is restricted. It has become so. This is to prevent the power supply brushes 30a and 30b from falling off in the free state before the assembly shown in FIG. 12A with the abolition of the pigtail harness.
- each of the power supply brushes 30a and 30b is interposed via each torsion coil spring 42. Therefore, the electromagnetic noise generated when the electric motor 12 is driven can be effectively reduced.
- Electromagnetic noise due to separation between the power supply brushes 30a and 30b and the slip rings 26a and 26b is generated by vibration.
- each capacitor 55 is provided in the middle of the electric path to reduce electromagnetic noise.
- electromagnetic noise is considered to be generated particularly at the two locations, the power supply brushes 30a and 30b.
- the capacitors 55 are provided on the control unit side (not shown). In other words, even if the capacitor 55 or the inductor is installed at a position away from the electromagnetic noise generation source, noise will be radiated in the middle of the electrical path. It was.
- the electromagnetic noise flows from the power supply brushes 30a and 30b to the one-side terminals 31a and 31a via the torsion coil springs 42 and 42 as inductors, and from there through the capacitors 55 and 55 to the respective metals. It flows to the cover member 3 through washers 53, 53, and further flows to the ground side of the internal combustion engine. Thereby, the electromagnetic noise can be effectively reduced.
- each torsion coil spring 42 is used as an inductor, the number of parts can be reduced and the cost can be reduced.
- the present invention is not limited to the configuration of each of the above embodiments.
- the urging member that urges each of the power supply brushes 30a and 30b may be provided in parallel with each of the power supply brushes.
- a plate spring or the like can be used in addition to the torsion coil spring 42.
- each support shaft 45 from a conductive material and configure each support shaft 45 as an inductor.
Abstract
Description
前記給電用ブラシの側部に、該給電用ブラシを前記スリップリング方向へ付勢する捩りコイルばねを、前記給電用ブラシと並列に配置したことを特徴としている。
〔第2実施形態〕
図8~図10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、異なるところは各係入溝40の形成位置と、各捩りコイルばね42の他端部42cの形状を変更したものである。
〔第3実施形態〕
図11及び図12は第3実施形態を示し、前記各ピグテールハーネスを廃止して、各捩りコイルばね42、42を導電材によって形成すると共に、該各捩りコイルばね42、42の各一端部42b、42bを前記各端子片31,31の一方側端子31a、31aに当接させ、さらに、前記各一方側端子31a、31aと前記金属ワッシャ53、53との間にコンデンサ55、55を接続したものである。
Claims (17)
- 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、
前記モータハウジングが駆動回転体または従動回転体と共に回転するように設けられ、電流が供給されることによって前記駆動回転体と従動回転体を相対回転させる電動モータと、
該電動モータの外側に設けられて、該電動モータに給電する給電用ブラシと、
前記回転部材と固定部材の他方側に設けられて、前記給電用ブラシが摺接するスリップリングと、を備え、
前記給電用ブラシの側部に、該給電用ブラシを前記スリップリング方向へ付勢する捩りコイルばねを、前記給電用ブラシと並列に配置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、
前記捩りコイルばねは、導電性材料によって形成されていると共に、直線状に延びた端部が前記給電用ブラシの軸方向一端面に常時に弾接して該給電用ブラシに給電し、
前記捩りコイルばねにコンデンサが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、
前記捩りコイルばねは、前記直線状端部の先端側が湾曲状に折曲形成されていると共に、該先端側の凸状湾曲部が前記給電用ブラシの前記一端面に点接触で弾接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。 - 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、
前記給電用ブラシは、保持体に設けられたブラシ保持部のブラシ案内部内に前記スリップリング方向へ移動可能に保持されていると共に、前記ブラシ案内部の一端縁に、前記捩りコイルばねの直線状端部が軸方向から係入する係入溝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、
前記係入溝は、前記保持部の軸方向に沿ってスリット状に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、
前記給電用ブラシと保持部は、断面ほぼ四角形状に形成され、前記保持体の対向する両側壁に前記係入溝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、
前記給電用ブラシと保持部は、断面ほぼ長方形状に形成され、前記保持部の各長辺部の対向する両側壁に前記係入溝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、
前記給電用ブラシを前記スリップリングに弾接させる前の自由状態では、前記捩りコイルばねの直線状端部が前記係入溝の底縁に係止されて、それ以上前記給電用ブラシを付勢しないように形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、
前記捩りコイルばねは、コルソン合金とベリリウム銅のいずれかの導電性合金材を含んで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、
前記給電用ブラシは、正極側と負極側の2つを有し、前記捩りコイルばねは、前記ばね収容室を介して前記給電用ブラシに対して平行にまたは対角線上の対称位置に配設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、
前記電動モータは、前記モータハウジングの内周にステータとしての永久磁石が設けられ、前記駆動回転体と共に回転するように設けられており、前記電動モータのロータが前記永久磁石に対して回転する回転力を、減速機構を介して前記従動回転体に伝達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11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、
前記電動モータは、前記ロータにコイルが巻回されたDCモータ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12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、
前記保持体は、内燃機関のシリンダヘッドに固定されたカバー部材に取り付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13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、
前記カバー部材は、アルミニウム合金材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14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、
前記保持体と該保持体に一体に設けられたコネクタ部を、合成樹脂材によって形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。 - 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、
前記モータハウジングが駆動回転体または従動回転体と共に回転するように設けられ、電流が供給されることによって前記駆動回転体と従動回転体を相対回転させる電動モータと、
該電動モータの外側に設けられて、該電動モータに給電する給電用ブラシと、
前記回転部材と固定部材の他方側に設けられて、前記給電用ブラシが摺接するスリップリングと、を備え、
前記給電用ブラシと、該給電用ブラシを前記スリップリング方向へ付勢する捩りコイルばねを、軸方向に少なくとも一部が重なるように配置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16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、
前記捩りコイルばねは、導電性材料によって形成されていると共に、直線状に延びた端部が前記給電用ブラシの軸方向一端面に常時に弾接して該給電用ブラシに給電し、
前記捩りコイルばねにコンデンサが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。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US15/039,905 US20170002701A1 (en) | 2013-12-11 | 2014-11-11 | Valve timing control device for internal combustion engine |
JP2015552368A JP6174160B2 (ja) | 2013-12-11 | 2014-11-11 | 内燃機関のバルブタイミング制御装置 |
CN201480066838.9A CN105814289B (zh) | 2013-12-11 | 2014-11-11 | 内燃机的气门正时控制装置 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013255529 | 2013-12-11 | ||
JP2013-255529 | 2013-12-11 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2015087648A1 true WO2015087648A1 (ja) | 2015-06-18 |
Family
ID=53370963
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2014/079799 WO2015087648A1 (ja) | 2013-12-11 | 2014-11-11 | 内燃機関のバルブタイミング制御装置 |
Country Status (4)
Country | Link |
---|---|
US (1) | US20170002701A1 (ja) |
JP (1) | JP6174160B2 (ja) |
CN (1) | CN105814289B (ja) |
WO (1) | WO2015087648A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2016158158A1 (ja) * | 2015-03-30 | 2016-10-06 | 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 |
WO2017026240A1 (ja) * | 2015-08-10 | 2017-02-16 | 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 |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105099601B (zh) * | 2014-04-25 | 2020-10-27 | 北京三星通信技术研究有限公司 | 一种灵活fdd系统中上行传输的方法和设备 |
WO2016021227A1 (en) * | 2014-08-06 | 2016-02-11 | Nec Corporation | Method and system for device-to-device communication |
US10965182B2 (en) * | 2018-03-01 | 2021-03-30 | Schaeffler Technologies AG & Co. KG | Hybrid module including axial retention housing for bearing |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0660275U (ja) * | 1993-01-14 | 1994-08-19 | ジェコー株式会社 | モータにおけるブラシ保持構造 |
JP2008005689A (ja) * | 2006-05-24 | 2008-01-10 | Denso Corp | 燃料ポンプ |
JP2008263775A (ja) * | 2008-05-19 | 2008-10-30 | Aisin Seiki Co Ltd | 直流ブラシモータ |
JP2009124797A (ja) * | 2007-11-12 | 2009-06-04 | Igarashi Denki Seisakusho:Kk | 電動モータ |
JP2009225625A (ja) * | 2008-03-18 | 2009-10-01 | Hitachi Ltd | ブラシ付き電動モータ |
JP2012132367A (ja) * | 2010-12-22 | 2012-07-12 | Hitachi Automotive Systems Ltd | 内燃機関のバルブタイミング制御装置 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4389588A (en) * | 1982-03-24 | 1983-06-21 | Alexander Rankin | Current carrying constant force brush holder assembly |
JPH05248214A (ja) * | 1992-03-06 | 1993-09-24 | Isuzu Ceramics Kenkyusho:Kk | エンジンのバルブ駆動装置 |
JP4250823B2 (ja) * | 1999-09-16 | 2009-04-08 | アイシン精機株式会社 | 直流ブラシモータ |
JP4348941B2 (ja) * | 2002-11-26 | 2009-10-21 | 日産自動車株式会社 | 車輪用回転電機の取付構造 |
JP4935187B2 (ja) * | 2006-05-24 | 2012-05-23 | 株式会社デンソー | 電動モータおよび燃料ポンプ |
JP5538053B2 (ja) * | 2010-04-28 | 2014-07-02 | 日立オートモティブシステムズ株式会社 | 内燃機関の可変動弁装置 |
JP5654950B2 (ja) * | 2011-06-07 | 2015-01-14 | 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 |
-
2014
- 2014-11-11 JP JP2015552368A patent/JP6174160B2/ja active Active
- 2014-11-11 WO PCT/JP2014/079799 patent/WO2015087648A1/ja active Application Filing
- 2014-11-11 CN CN201480066838.9A patent/CN105814289B/zh not_active Expired - Fee Related
- 2014-11-11 US US15/039,905 patent/US20170002701A1/en not_active Abandoned
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0660275U (ja) * | 1993-01-14 | 1994-08-19 | ジェコー株式会社 | モータにおけるブラシ保持構造 |
JP2008005689A (ja) * | 2006-05-24 | 2008-01-10 | Denso Corp | 燃料ポンプ |
JP2009124797A (ja) * | 2007-11-12 | 2009-06-04 | Igarashi Denki Seisakusho:Kk | 電動モータ |
JP2009225625A (ja) * | 2008-03-18 | 2009-10-01 | Hitachi Ltd | ブラシ付き電動モータ |
JP2008263775A (ja) * | 2008-05-19 | 2008-10-30 | Aisin Seiki Co Ltd | 直流ブラシモータ |
JP2012132367A (ja) * | 2010-12-22 | 2012-07-12 | Hitachi Automotive Systems Ltd | 内燃機関のバルブタイミング制御装置 |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2016158158A1 (ja) * | 2015-03-30 | 2016-10-06 | 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 |
JPWO2016158158A1 (ja) * | 2015-03-30 | 2017-12-21 | 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 |
WO2017026240A1 (ja) * | 2015-08-10 | 2017-02-16 | 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 |
JPWO2017026240A1 (ja) * | 2015-08-10 | 2018-07-05 | 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 |
Also Published As
Publication number | Publication date |
---|---|
US20170002701A1 (en) | 2017-01-05 |
CN105814289B (zh) | 2019-05-10 |
JP6174160B2 (ja) | 2017-08-02 |
JPWO2015087648A1 (ja) | 2017-03-16 |
CN105814289A (zh) | 2016-07-27 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5976505B2 (ja) | 内燃機関のバルブタイミング制御装置 | |
JP6295181B2 (ja) | 内燃機関のバルブタイミング制御装置 | |
JP2013167181A (ja) | 内燃機関のバルブタイミング制御装置 | |
JP6174160B2 (ja) | 内燃機関のバルブタイミング制御装置 | |
JP6042233B2 (ja) | 内燃機関のバルブタイミング制御システム | |
KR101624776B1 (ko) | 내연 기관의 밸브 타이밍 제어 장치 및 마개체의 제거 방법 | |
JP5978111B2 (ja) | 内燃機関のバルブタイミング制御装置 | |
JP6001506B2 (ja) | 内燃機関の可変動弁装置 | |
JP6096611B2 (ja) | 内燃機関のバルブタイミング制御装置及び該バルブタイミング制御装置に用いられる給電機構 | |
JP2016048053A (ja) | 内燃機関のバルブタイミング制御装置及びバルブタイミング制御システム | |
JP6030781B2 (ja) | 内燃機関のバルブタイミング制御装置 | |
JP6266810B2 (ja) | 内燃機関のバルブタイミング制御装置 | |
JP6381455B2 (ja) | 内燃機関のバルブタイミング制御装置 | |
JP5718764B2 (ja) | 内燃機関のバルブタイミング制御装置 | |
KR101646314B1 (ko) | 내연 기관의 밸브 타이밍 제어 장치 및 이 밸브 타이밍 제어 장치에 이용되는 커버 부재 | |
JP5993352B2 (ja) | 内燃機関の可変動弁装置及びローラ減速機構 | |
JP6274900B2 (ja) | 内燃機関のバルブタイミング制御装置 | |
WO2016125545A1 (ja) | 内燃機関のバルブタイミング制御装置 | |
WO2016009790A1 (ja) | 内燃機関の可変動弁装置 | |
JP6381785B2 (ja) | 内燃機関のバルブタイミング制御装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 14869784 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2015552368 Country of ref document: JP Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 15039905 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 14869784 Country of ref document: EP Kind code of ref document: A1 |