WO2018034198A1 - Dispositif de commande de synchronisation de soupape de moteur à combustion interne, procédé permettant la fabrication dudit dispositif de commande de synchronisation de soupape et élément de support de brosse - Google Patents

Dispositif de commande de synchronisation de soupape de moteur à combustion interne, procédé permettant la fabrication dudit dispositif de commande de synchronisation de soupape et élément de support de brosse Download PDF

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Publication number
WO2018034198A1
WO2018034198A1 PCT/JP2017/028670 JP2017028670W WO2018034198A1 WO 2018034198 A1 WO2018034198 A1 WO 2018034198A1 JP 2017028670 W JP2017028670 W JP 2017028670W WO 2018034198 A1 WO2018034198 A1 WO 2018034198A1
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WO
WIPO (PCT)
Prior art keywords
control device
timing control
valve timing
combustion engine
internal combustion
Prior art date
Application number
PCT/JP2017/028670
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English (en)
Japanese (ja)
Inventor
根本　博之
小久保　直樹
進太郎 高田
Original Assignee
日立オートモティブシステムズ株式会社
ユニオンマシナリ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by 日立オートモティブシステムズ株式会社, ユニオンマシナリ株式会社 filed Critical 日立オートモティブシステムズ株式会社
Priority to JP2018534362A priority Critical patent/JP6720319B2/ja
Publication of WO2018034198A1 publication Critical patent/WO2018034198A1/fr

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

Definitions

  • the present invention relates to a valve timing control device for an internal combustion engine, a method for manufacturing the valve timing control device, and a brush holding member.
  • a valve timing control device for controlling the opening / closing timing is provided.
  • a valve timing control device described in the following Patent Document 1 uses a pair of power supply brushes provided on a cover member that covers a front end portion of an electric motor, by supplying current supplied from a battery power source via a pigtail harness.
  • the electric motor is fed to change the relative rotational phase of the camshaft with respect to the crankshaft.
  • the power feeding brush is slidably held inside a rectangular tube-like brush holder embedded in a synthetic resin holding member attached to a cover member, and is axially attached to each slip ring by a spring force of a spring. It comes to contact from.
  • the brush holder has a coupling force with the holding member due to vibration transmitted from the power supply brush or the like, or sliding frictional resistance of the power supply brush. There is a risk of lowering with time. As a result, there is a possibility that the brush holder may rattle within the holding member or may fall off the holding member in some cases.
  • the present invention has been devised in view of the above-mentioned conventional technical problems, and it is possible to increase the coupling force of the brush holder to the holding member and to suppress the occurrence of rattling and dropping of the brush holder. It is an object of the present invention to provide a control device and a method for manufacturing the valve timing control device.
  • the brush holder is formed with a concave portion and a convex portion on one end edge and the other end facing each other in the circumferential direction in a state of being bent into a cylindrical shape,
  • the opposing convex portions are fitted into the concave portions in an intersecting manner, and the respective convex portions protrude outward, and are embedded and fixed to the holding member of the synthetic resin material.
  • 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 longitudinal cross-sectional view of the holding member provided for this embodiment. It is a front view of the holding member. It is a rear view of the state which removed the cap from the holding member.
  • the brush holder used for this embodiment is shown, A is a perspective view, B is a right view, C is a rear view, D is a top view.
  • A is a top view which shows the state which cut and raised the holder base material from the metal plate material
  • B is a top view which shows the state which shape
  • C Is a plan view showing a state in which long holes and convex portions are formed in the holder base material
  • D is a plan view showing a state in which the holder base material is bent inward via a bending groove
  • E is a holder base material from a metal plate. It is a top view which shows the state which cut off the material.
  • FIG. 10D is a sectional view taken along line DD of FIG. 10C. It is a side view which shows the state which bent the holder base material shown to FIG. 10D.
  • valve timing control device for an internal combustion engine and a method for manufacturing the valve timing control device according to the present invention will be described with reference to the drawings.
  • the valve timing control device includes a timing sprocket 1 that is a driving rotating body that is rotationally driven by a crankshaft of an internal combustion engine via a timing chain, and a bearing on a cylinder head 01.
  • a camshaft 2 rotatably supported by a bracket 02 and rotated by a rotational force transmitted from the timing sprocket 1; and a cover member 3 fixed to a chain cover 6 disposed at a front position of the timing sprocket 1.
  • the phase change mechanism 4 is provided between the timing sprocket 1 and the camshaft 2 and changes the relative rotational phase of both 1 and 2 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.
  • a gear portion 1b that receives the rotational force from the crankshaft via the timing chain, an internal gear component 5 that is integrally provided on the front end side of the sprocket body 1a and that constitutes a part of the speed reduction mechanism 13 described later, It is composed of
  • the timing sprocket 1 has a single large-diameter ball bearing 43 interposed between the sprocket body 1a and a driven member 9 (described later) provided at the front end of the camshaft 2.
  • the timing sprocket 1 is supported on the camshaft 2 by a large-diameter 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 wheels 43a and 43b.
  • the outer ring 43a is fixed to the inner peripheral side of the sprocket body 1a, whereas the inner ring 43b is fixed to the outer peripheral side of the driven member 9.
  • the internal tooth component 5 is integrally provided on the outer peripheral side of the front end portion of the sprocket body 1a, is formed in a cylindrical shape extending forward of the phase change mechanism 4, and has a plurality of wave-shaped inner portions on the inner periphery. Teeth 5a are formed.
  • annular holding plate 8 is disposed at the rear end portion of the sprocket body 1a opposite to the internal tooth constituting portion 5.
  • the holding plate 8 is integrally formed of a metal plate material, and as shown in FIG. 1, the outer diameter is set to be substantially the same as the outer diameter of the sprocket body 1a.
  • the holding plate 8 has an inner diameter that is smaller than the inner diameter of the outer ring 43 a of the large-diameter ball bearing 43.
  • a stopper convex portion 8b 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 8a of the holding plate 8.
  • the stopper convex portion 8b is formed in a substantially fan shape, and the tip edge 8c is formed in an arc shape along an arcuate inner peripheral surface of a stopper groove 2b described later.
  • a rear end portion of a motor housing 14 to be described later is disposed opposite to the front end side of the internal tooth constituent portion 5.
  • the partition wall 14b at the rear end of the motor housing 14 six female screw holes 14d are formed at positions corresponding to the bolt insertion holes 1c and 8d. Accordingly, the timing sprocket 1, the holding plate 8 and the motor motor housing 14 are fastened together in the axial direction by the six bolts 7 inserted and screwed into the holes 1c, 8d and 14d.
  • sprocket body 1a and the internal gear component 5 are configured as a casing of a speed reduction mechanism 13 described later.
  • the chain cover 6 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. The placement is fixed.
  • the chain cover 6 has female screw holes 6c formed in bosses 6b formed at four locations in the circumferential direction of the annular wall 6a that constitutes an opening formed at a position corresponding to the phase changing mechanism 4. Has been.
  • the camshaft 2 has two drive cams per cylinder for opening an intake valve (not shown) on the outer periphery, and is integrally provided with a flange portion 2a at the front end.
  • a driven member 9 is coupled from the axial direction by a cam bolt 10 through a flange portion 2a.
  • the outer peripheral portion of the front end surface of the flange portion 2 a is disposed in contact with the outer end surface in the axial direction of the inner ring 43 b of the large-diameter ball bearing 43.
  • a stopper concave groove 2 b into which the stopper convex portion 8 b of the holding plate 8 is engaged is 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 8b rotated in this length range abut against the circumferential opposite edges 2c and 2d, respectively.
  • the cam bolt 10 has an end surface of the head 10a that supports the inner ring of the small-diameter ball bearing 37 from the axial direction, and an outer periphery of the shaft portion 10b from the end of the camshaft 2 to the inner axial direction.
  • a male screw 10c is formed to be screwed onto the formed female screw.
  • the driven member 9 is integrally formed of an 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 And a cylindrical portion 9b protruding in the axial direction from the inner peripheral front end face.
  • the rear end surface of the fixed end portion 9 a is disposed in contact with the front end surface of the flange portion 2 a of the camshaft 2, and is fixed in pressure contact with the flange portion 2 a by the axial force of the cam bolt 10 from the axial direction.
  • the cylindrical portion 9b has a through hole 9d through which the shaft portion 10b of the cam bolt 10 is inserted, and a needle bearing 38, which is a bearing member, is provided on the outer peripheral side. Yes.
  • the phase changing mechanism 4 is mainly composed of an electric motor 12 disposed on the front end side of the cylindrical portion 9b of the driven member 9, and a speed reducing mechanism 13 that reduces the rotational speed of the electric motor 12 and transmits it to the camshaft 2. Has been.
  • the electric motor 12 is a brushed DC motor, a motor housing 14 that is a yoke that rotates integrally with the timing sprocket 1, and a motor housing 14 that is rotatable inside the motor housing 14.
  • a motor output shaft 15 provided, four arc-shaped permanent magnets 16 which are stators fixed to the inner peripheral surface of the motor housing 14, and a power feeding plate 17 provided at the front end of the motor housing 14. ing.
  • the motor housing 14 has a cylindrical housing body 14a formed by pressing a ferrous metal material into a bottomed cylindrical shape.
  • the housing main body 14a has a partition wall 14b which is a disk-like bottom wall on the rear end side, and a large-diameter shaft insertion hole 14c through which an eccentric shaft portion 39 which will be described later is inserted is formed substantially at the center of the partition wall 14b.
  • a cylindrical extending portion that protrudes in the axial direction of the camshaft 2 is integrally provided at the hole edge of the shaft portion insertion hole 14c.
  • a female screw hole 14d is formed on the outer peripheral side of the front end face of the partition wall 14b.
  • the motor output shaft 15 is formed in a stepped cylindrical shape and functions as an armature, and a large diameter portion 15a on the camshaft 2 side via a stepped portion 15c formed at a substantially central position in the axial direction, and a brush holding member to be described later And a small-diameter portion 15b on the holding member 28 side.
  • the large-diameter portion 15a has an iron core rotor 18 fixed to the outer periphery, and an eccentric shaft portion 39 constituting a part of the speed reduction mechanism 13 is integrally formed on the rear end side.
  • the small-diameter portion 15b has an annular member 20 made of a nonmagnetic material press-fitted and fixed to the outer periphery, and a commutator 21 is press-fitted and fixed to the outer peripheral surface of the annular member 20 from the axial direction. Axial positioning is performed.
  • a plug body 42 that is supplied into the motor output shaft 15 and the eccentric shaft portion 39 and lubricates the bearings 37 and 38 to suppress leakage to the outside is press-fitted and fixed. Has been.
  • the iron core rotor 18 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 18a is wound.
  • the commutator 21 is formed in an annular shape by a conductive material, and the terminal of the coil wire from which the coil 18a is drawn is electrically connected to each segment divided into the same number as the number of poles of the iron core rotor 18.
  • Each permanent magnet 16 is formed in a cylindrical shape as a whole and has a plurality of magnetic poles in the circumferential direction, and its axial position is offset from the fixed position of the iron core rotor 18.
  • the power feeding plate 17 has a shaft insertion hole 17 a through which one end portion of the motor output shaft 15 is inserted at a central position, and is a disc integrally provided on the inner peripheral side.
  • the non-magnetic material resin portion 22 and a disk-shaped cored bar 17b embedded in the resin portion 22 are configured.
  • the power feeding plate 17 is accommodated in a pair of resin holders 23a and 23b provided in the resin portion 22 and slidably disposed along the radial direction inside the resin holders 23a and 23b. 24b, the front end surfaces of the pair of first brushes 25a and 25b, which are switching brushes (commutators) whose respective end surfaces elastically contact the outer peripheral surface of the commutator 21 from the radial direction, and the resin holders 23a and 23b.
  • the inner and outer double annular power supply slip rings 26a and 26b, which are embedded and fixed with the outer end surfaces exposed, and the first brushes 25a and 25b are electrically connected to the slip rings 26a and 26b. 27a, 27b.
  • the feeding plate 17 is positioned and fixed by caulking the outer peripheral portion of the cored bar 17 b exposed from the outer periphery of the resin portion 22 to the concave step portion formed on the inner periphery of the front end portion of the motor housing 14.
  • 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 14.
  • the cover member 3 includes a bulging cover main body 3a and an annular mounting flange 3b integrally formed on the outer peripheral edge on the opening side of the cover main body 3a.
  • the cylindrical wall 3c formed on the outer peripheral side of the cover body 3a has a holding hole 3d formed therein, and a part of the holding member 28 is fitted and held on the inner peripheral surface of the holding hole 3d.
  • a large-diameter oil seal 50 is interposed between the inner peripheral surface of the cover main body 3a on the mounting flange 3b side and the outer peripheral surface of the motor housing 14.
  • a holding member 28 integrally formed of a synthetic resin material is attached to the cover body 3a.
  • the holding member 28 is formed in a substantially L shape in a side view, and has a cylindrical brush holding portion 28a inserted into the holding hole 3d, and the brush holding portion 28a.
  • a connector portion 28b having a substantially rectangular cross section integrally formed at the upper end portion, a bracket portion 28c integrally protruding from one side surface of the brush holding portion 28a and bolted to the cover body 3a, and a large portion inside. It is mainly composed of a pair of power supply terminal pieces 31 and 31 embedded therein.
  • the brush holding portion 28a extends in a substantially horizontal direction (axial direction), and has a pair of bottomed cylindrical shapes formed in parallel with the internal vertical position (inner and outer peripheral sides with respect to the axis of the motor housing 14).
  • a pair of brush holders 29 and 29 are embedded and fixed in the fixing holes 28h and 28h, respectively.
  • each of the brush holders 29 and 29 is formed into a rectangular cross section by bending a conductive metal plate material into a rectangular tube shape by press molding. Specifically, the first side wall portion 29a, the second side wall portion 29b bent in a direction perpendicular to the one circumferential edge of the first side wall portion 29a, and the one circumferential edge of the second side wall portion 29b And a fourth side wall portion 29d bent in a right angle direction from one circumferential edge of the third side wall portion 29c.
  • the other end edge (terminal) in the circumferential direction of the first side wall portion 29a and the one end edge (terminal) in the circumferential direction of the fourth side wall portion 29d facing the other end edge in a crossing manner from a right angle direction from the circumferential direction. are provided with a plurality of concave and convex portions 29e, 29f, 29g, and 29h.
  • first concave portions 29e are cut out on both side portions and the central portion in the width direction, and two first convex portions are formed on both sides of the central concave portion 29e.
  • 29f is provided integrally.
  • one end edge of the fourth side wall portion 29d is integrally provided with three second convex portions 29g that are fitted into the first concave portions 29e of the first side wall portion 29a so as to intersect each other at both sides and the central portion in the width direction.
  • two second concave portions 29h into which the first convex portions 29f of the first side wall portion 29a are fitted in an intersecting manner are formed between the second convex portions 29g.
  • the first recesses 29e are formed to have the same width and the width is larger than the widths of the first protrusions 29f.
  • the width of the second convex portion 29g is slightly smaller than the width of the first concave portion 29e so that the second convex portion 29g can be fitted with almost no gap.
  • the second recesses 29h are formed to have the same width and the width of each of the second protrusions 29g, and the first protrusions 29f are fitted with almost no gap. It has become so.
  • each first convex portion 29f is formed so that its protruding length is slightly larger than the wall thickness of the brush holder 29 (fourth side wall portion 29d). In the state of being fitted to 29h, the tip portion slightly protrudes from the second recess 29f to the outside.
  • each second convex portion 29g is formed so that its protruding length is larger than the thickness width of the brush holder 29 (first side wall portion 29a) and is fitted in each first concave portion 29e.
  • the tip portion protrudes relatively large from the first recess 29e to the outside.
  • the two first convex portions 29f of the first side wall portion 29a and the three second convex portions 29g of the fourth side wall portion 29d extend from the respective edges along the plane to the respective side wall portions 29a and 29d.
  • the first and second recesses 29e and 29h are engaged with each other at an angle of approximately 90 ° in an intersecting manner.
  • the first convex portion 29f protrudes outward from the one end edge of the fourth side wall portion 29d at an angle of about 90 °
  • the second convex portion 29g is the same from the other end edge of the first side wall portion 29a. It protrudes outward at an angle of about 90 °.
  • each of the second convex portions 29g holds down the outer surfaces of the two second convex portions 29g positioned on the outer side, as shown in FIG. 9C.
  • the second protrusions 29g are held in a sandwiched state, they are crushed by a press from each outer surface side of the second protrusions 29g.
  • both sides of each first convex portion 29f fitted in the second concave portion 29h are press-contacted (contacted) while being plastically deformed inward as shown by a one-dot chain line, and between the two 29f and 29g
  • the bond strength is increased.
  • the width on the distal end W1 side of the second convex portion 29g is slightly larger than the width W on the base side.
  • the second side wall portion 29b and the fourth side wall portion 29d opposite to the second side wall portion 29b are respectively provided with bulged portions 29i bulging in a substantially arc shape that slidably support the outer periphery of coil springs 32a and 32b described later. Is formed.
  • each brush holder 29, 29, a pair of power supply brushes 30a, 30b whose tip surfaces abut on the power supply slip rings 26a, 26b from the axial direction are slidably held in the axial direction.
  • Each of the power supply brushes 30a and 30b is formed in a rectangular tube shape and set to a predetermined axial length, and constitutes a part of the power supply mechanism together with the power supply slip rings 26a and 26b.
  • Through holes 28g and 28g through which pigtail harnesses 33 and 33 to be described later are inserted are formed through the bottom wall 28f located on the bottom side of the pair of fixing holes 28h and 28h, respectively.
  • a space S where each of the through holes 28g and 28g faces is formed outside the bottom wall 28f.
  • the space S is formed in a circular shape, and the depth of the space S is when the power supply brushes 30 a and 30 b are moved backward in the brush holders 29 and 29. Is set to a size that is absorbed by bending deformation. Further, the space S is liquid-tightly closed by a circular cap 36 whose one end opening in the axial direction is formed of the same synthetic resin material as the holding member 28.
  • a partition wall 35 that separates the space S into two spaces S1 and S2 corresponding to the fixing holes 28h and 28h is formed on the side of the space S of the bottom wall 28f. Is provided.
  • the partition wall 35 is formed in a substantially crank shape by a synthetic resin material that is an insulating material, and is formed together with the holding member 28 when forming the space S on the outer surface side of the bottom wall 28f.
  • the character-shaped space portions S1 and S2 are partitioned.
  • the two spaces S1 and S2 are formed in a shape in which L-shapes are combined with each other via a partition wall 35.
  • the pair of power supply terminal pieces 31 are formed in a parallel and crank shape along the vertical direction, and the terminals 31a, 31a on one side (lower end side) are arranged in an exposed state on the outer surface of the bottom wall 28f.
  • the terminals 31b and 31b on the other side (upper end side) project from the female fitting groove 28d of the connector portion 28b.
  • the other terminals 31b and 31b are connected to a control unit (not shown) via a female terminal (not shown) and a harness.
  • Each terminal 31a, 31a on one side is formed in an approximately L shape along the shape of each space portion S1, S2, and is arranged in contact with the upper surface of the bottom wall 28f.
  • Each terminal 31a, 31a has a pair of pigtail harnesses 33, 33, which will be described later, inserted into each one end located at a position corresponding to each of the through holes 28g, 28g, and two insertion holes 31c bent in contact with each other. , 31c are formed through.
  • columnar protrusions 40a and 40b are provided upright at two corners of the bottom wall 28f that are bent into the L-shape of the partition wall 35, respectively.
  • each of the power supply brushes 30a and 30b is formed in a substantially rectangular shape, and the rear end face and the hole edges of the fixing holes 28h and 28h, that is, the bottom wall 28f.
  • the pair of second coil springs 32a and 32b elastically mounted between the inner surfaces is biased toward the slip rings 26a and 26b, respectively.
  • each of the pigtail harnesses 33, 33 has a length when the feeding brushes 30a, 30b are advanced to the maximum by the spring force of the coil springs 32a, 32b, as shown in FIG. It is set to a length that regulates the maximum sliding position so that it does not fall off from 29b.
  • each of the pigtail harnesses 33 and 33 has one end portions 33a and 33a fixed to the rear end portions of the power feeding brushes 30a and 30b by soldering.
  • the other end portions 33b and 33b are fixed to the other end portions of the one side terminals 31a and 31a by soldering via the outer surfaces of the projecting portions 40a and 40b, and the two are electrically connected.
  • the other side terminals 31b and 31b facing the fitting groove 28d into which the male terminal (not shown) is inserted at the upper end portion are electrically connected to the control unit (not shown) via the male terminal. .
  • the bracket portion 28c formed in a substantially triangular shape is screwed into a pair of female screw holes (not shown) formed in the cover body 3a in a bolt insertion hole 28e formed through the center.
  • the holding member 28 is fixed to the cover main body 3a.
  • the motor output shaft 15 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 on the head 10a side of the cam bolt 10.
  • the ball bearing 37 is rotatably supported by a needle bearing 38 disposed on the side in the axial direction.
  • the lubricating oil leaks from the inside of the speed reduction mechanism 13 into the electric motor 12.
  • a small-diameter oil seal 46 is provided.
  • the control unit detects the current engine operating state based on information signals from various sensors such as crank angle sensor, air flow meter, water temperature sensor, accelerator opening sensor, etc. 18a is energized to control the rotation of the motor output shaft 15, and the relative rotation phase of the camshaft 2 with respect to the timing sprocket 1 is controlled via the speed reduction mechanism 13.
  • the speed reduction mechanism 13 includes an 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 bearing 47.
  • a cylindrical roller 41 provided integrally with the outer peripheral portion of the fixed end portion 9a, and a cylindrical retainer 41 that allows a plurality of rollers 48 to move in the rolling direction while allowing the rollers 48 to move in the radial direction.
  • the driven member 9 integrated with the cage 41 is mainly constituted.
  • the axis Y of the cam surface 39a formed on the outer peripheral surface is slightly eccentric from the axis X of the motor output shaft 15 in the radial direction.
  • the retainer 41 is formed in a cylindrical shape that is bent in 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. .
  • the retainer 41 has a cylindrical tip portion 41a extending in the direction of the partition wall 14b of the motor housing 14 via an annular concave accommodation space 44 formed between the female screw hole 14d and the extending portion 5d.
  • a plurality of substantially rectangular roller holding holes 41b that respectively hold a plurality of rollers 48 so as to roll freely are provided at substantially equal intervals in the circumferential direction of the cylindrical tip portion 41a. Are formed at equally spaced positions in the circumferential direction.
  • the total number of the roller holding holes 41 b (rollers 48) is one less than the total number of teeth of the internal teeth 5 a of the internal tooth component 5.
  • the medium-diameter ball bearing 47 is arranged 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. ing.
  • 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 C1 is formed and is in a free state.
  • each roller 48 is in contact with the outer peripheral surface of the outer ring 47b so as to be freely rotatable, and an annular second gap C2 is formed on the outer peripheral side of the outer ring 47b. Due to the second gap C2, 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 roller 48 is made of an iron-based metal, and is fitted into the inner teeth 5a of the inner tooth component 5 while moving in the radial direction along with the eccentric movement of the medium-diameter ball bearing 47. While being guided in the circumferential direction by both side edges of 41b, it is configured to swing in the radial direction.
  • Lubricating oil is supplied into the speed reduction mechanism 13 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), as shown in FIG.
  • An oil supply hole 51 that is formed in the axial direction and communicates with the oil supply passage through the groove groove, and 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
  • the small-diameter oil hole 52 opened in the vicinity of the needle bearing 38 and the medium-diameter ball bearing 47, and an oil discharge hole (not shown) formed through the driven member 9 in the same manner.
  • a holder base material is formed by punching a rectangular slit hole 62 around an elongated strip-shaped conductive metal plate 60 with one end 61a in the longitudinal direction coupled to the metal plate 60. 61 is formed (first step).
  • three folding grooves 61 b are formed by performing coining along the width direction at three positions at equal intervals in the longitudinal direction at a position on the inner surface side of the holder base material 61.
  • Form (second step) At this time, the two bulging portions 29i are press-molded at the portions to be the second side wall portion 29b and the fourth side wall portion 29d.
  • two long holes 61 c having a predetermined length are punched in parallel along the longitudinal direction of the holder base material 61 on the one end 61 a side of the holder base material 61.
  • Each of the long holes 61 c is formed at a position where the span between them is about 2/5 of the width of the holder base material 61.
  • two convex portions 61e corresponding to the two long holes 61c are stamped and formed in parallel on the other end portion 61d side (third step).
  • chamfered circular arc surfaces 61f are respectively formed on both side edges on the inner surface side where the respective bending grooves 61b of the holder base material 61 are formed.
  • the holder base material 61 is bent inward through the respective bending grooves 61b to be formed into a rectangular tube shape, and each of the two convex portions 61e has two lengths. It engages with the hole 61c.
  • the holder base material 61 is cut out along the width direction from the substantially central position in the longitudinal direction of the long hole 61c (fourth step). At this time, three second convex portions 29g appear between both the long holes 61c and on both sides, and two second concave portions 29h appear.
  • each second convex portion 29g is crushed from the upper surface with a predetermined torque to be plastically deformed (fifth step).
  • each second convex portion 29g is brought closer to each first convex portion 29f, and the respective base portions are brought into close contact with each other. Therefore, the width W of each base part of the first convex part 29f and the second convex part 29g is smaller than the width W1 of each tip part. For this reason, the 2nd convex part 29g and the 1st convex part 29f are couple
  • the bonding strength may be increased by press-fitting the first convex portion 29f into the second concave portion 29h.
  • the first convex portion 29f is inserted.
  • the pressure is made by plastic deformation, there is less variation in manufacturing errors, and the manufacturing accuracy of the brush holder 29 particularly on the inner peripheral side can be increased. Further, the first convex portion 29f is difficult to come off from the second concave portion 29h.
  • the holding member 28 is embedded and fixed inside by molding each brush holder 29 together with a resin material at the time of synthetic resin injection molding (sixth step).
  • the holder base material 61 is bent from each of the bending grooves 61b, so that the first side wall portion 29a to the fourth side wall portion 29d are formed, and further, the two elongated holes 61c are cut to form grooves.
  • the part which became is formed as two 2nd recessed parts 29h of the 4th side wall part 29d, and the remainder part by cutting
  • disconnection is formed as the 3rd 2nd convex parts 29g of the 4th side wall part 29d.
  • the two convex portions 61e are formed as two first convex portions 29f of the first side wall portion 29a, and the groove between the convex portions 61e and the grooves on both sides are formed as three first concave portions 29e. Yes.
  • the brush holder 29 can be continuously formed by combining stamping and bending (bending) processing by press molding, so that the forming operation is facilitated and mass production is facilitated. Since this is possible, the cost can be reduced.
  • the coil 18a of the electric motor 12 is supplied from the control unit via the terminal pieces 31, the pigtail harnesses 33 and 33, 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 15 is rotationally driven, and the rotational force that is reduced in speed is transmitted to the camshaft 2 via the speed reduction mechanism 13.
  • each roller 48 is guided in the radial direction by each roller holding hole 41 b of the retainer 41 for each rotation of the motor output shaft 15. It moves over one internal tooth 5a of the component 5 while rolling to another adjacent internal tooth 5a. Each roller 48 rolls in the circumferential direction while repeating this sequentially.
  • the rotational force is transmitted to the driven member 9 while the rotation of the motor output shaft 15 is decelerated by the rolling contact of the rollers 48.
  • the reduction ratio at this time can be arbitrarily set according to the number of rollers 48 and 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.
  • each brush holder 29 when the holding member 28 is resin-molded, each brush holder 29 is embedded and fixed together in the brush holding portion 28a of the holding member 28. At this time, each brush holder 29 has 2 The coupling strength with respect to the brush holding portion 28a is sufficiently increased by the two first convex portions 29f and the three second convex portions 29g. For this reason, after the holding member 28 is finally assembled to the cover member 3, even if there is vibration transmitted from the power supply brushes 30a, 30b or the sliding friction resistance of the power supply brushes 30a, 30b, etc. There is no risk of rattling in the portion 28a or dropping off from the brush holding portion 28a. Therefore, the occurrence of a failure of the valve timing control device can be suppressed.
  • the chamfered circular arc surface 61f is formed on the inner peripheral edge of the front end portion and the rear end portion of the brush holder 29, guides when the power supply brushes 30a and 30b are inserted into the brush holder 29 are provided. Because of this function, the insertability is improved. Further, when the power supply brushes 30a and 30b slide in the brush holder 29, the arcuate surface 61f eliminates the catch and smooth slidability is obtained. Therefore, since wear of power supply brushes 30a and 30b can be suppressed, adhesion of wear powder to oil seal 50 of the valve timing control device can be suppressed.
  • each brush holder 29 can be formed in a different polygon or cylinder instead of a rectangular cylinder. Even in this case, it is possible to secure sufficient coupling strength with the brush holding portion 28a by providing the convex portions 29f and 29g.
  • the tip portion may be provided with a triangle shape or a round shape larger than the base portion. It is.
  • the size and shape of the space portion S and the space portions S1 and S2 can be arbitrarily changed by changing the brush holding portion 28a and the partition wall 35.
  • the present invention is not limited to the power supply brush for supplying power to the slip ring, and can be applied to any brush holder embedded in a synthetic resin holding member.

Landscapes

  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Manufacture Of Motors, Generators (AREA)
  • Motor Or Generator Current Collectors (AREA)

Abstract

L'invention concerne un support de brosse (29) formé plié en une forme de tube quadrangulaire et comprenant une première section de paroi latérale (29a), une deuxième section de paroi latérale (29b), une troisième section de paroi latérale (29c) et une quatrième section de paroi latérale (29d). Deux premières sections en saillie (29f) et de premières sections évidées (29e) sont formées sur l'autre extrémité de la première section de paroi latérale et sur une extrémité de la quatrième section de paroi latérale faisant face à de secondes sections évidées (29h), qui viennent en prise avec les premières sections en saillie de façon croisée, et de secondes sections en saillie (29g), qui viennent en prise avec les premières sections évidées de façon croisée, sont formées. Les premières et secondes sections en saillie, dans un état en saillie, sont incorporées et fixées à une section de support de brosse en résine synthétique (28a). La force reliant le support de brosse à l'élément de support est ainsi augmentée, ce qui supprime le cliquetis ou la chute du support de brosse.
PCT/JP2017/028670 2016-08-15 2017-08-08 Dispositif de commande de synchronisation de soupape de moteur à combustion interne, procédé permettant la fabrication dudit dispositif de commande de synchronisation de soupape et élément de support de brosse WO2018034198A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2018534362A JP6720319B2 (ja) 2016-08-15 2017-08-08 内燃機関のバルブタイミング制御装置と該バルブタイミング制御装置の製造方法及びブラシ保持部材

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-159057 2016-08-15
JP2016159057 2016-08-15

Publications (1)

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WO2018034198A1 true WO2018034198A1 (fr) 2018-02-22

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PCT/JP2017/028670 WO2018034198A1 (fr) 2016-08-15 2017-08-08 Dispositif de commande de synchronisation de soupape de moteur à combustion interne, procédé permettant la fabrication dudit dispositif de commande de synchronisation de soupape et élément de support de brosse

Country Status (2)

Country Link
JP (1) JP6720319B2 (fr)
WO (1) WO2018034198A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08317606A (ja) * 1995-05-12 1996-11-29 Kokusan Denki Co Ltd 回転電機のブラシ保持装置
JP2010142003A (ja) * 2008-12-10 2010-06-24 Sanyo Electric Co Ltd 整流子電動機
WO2016125545A1 (fr) * 2015-02-06 2016-08-11 日立オートモティブシステムズ株式会社 Dispositif de commande de synchronisation de soupape pour moteur à combustion interne

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08317606A (ja) * 1995-05-12 1996-11-29 Kokusan Denki Co Ltd 回転電機のブラシ保持装置
JP2010142003A (ja) * 2008-12-10 2010-06-24 Sanyo Electric Co Ltd 整流子電動機
WO2016125545A1 (fr) * 2015-02-06 2016-08-11 日立オートモティブシステムズ株式会社 Dispositif de commande de synchronisation de soupape pour moteur à combustion interne

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JPWO2018034198A1 (ja) 2019-06-13
JP6720319B2 (ja) 2020-07-08

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