EP2573336A1 - Dispositif à variation de phase pour moteur - Google Patents

Dispositif à variation de phase pour moteur Download PDF

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Publication number
EP2573336A1
EP2573336A1 EP10851739A EP10851739A EP2573336A1 EP 2573336 A1 EP2573336 A1 EP 2573336A1 EP 10851739 A EP10851739 A EP 10851739A EP 10851739 A EP10851739 A EP 10851739A EP 2573336 A1 EP2573336 A1 EP 2573336A1
Authority
EP
European Patent Office
Prior art keywords
lock plate
camshaft
rotor
cam
eccentric
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP10851739A
Other languages
German (de)
English (en)
Other versions
EP2573336B1 (fr
EP2573336A4 (fr
Inventor
Michihiro Kameda
Masayasu Nagado
Masaaki Niiro
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nittan Corp
Original Assignee
Nittan Valve Co Ltd
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.)
Filing date
Publication date
Application filed by Nittan Valve Co Ltd filed Critical Nittan Valve Co Ltd
Publication of EP2573336A1 publication Critical patent/EP2573336A1/fr
Publication of EP2573336A4 publication Critical patent/EP2573336A4/fr
Application granted granted Critical
Publication of EP2573336B1 publication Critical patent/EP2573336B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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
    • F01L1/34409—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 by torque-responsive means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • 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

  • This invention relates to a variable cam phaser for an automobile engine for varying the relative phase angle between the crankshaft of the engine and the camshaft of the apparatus to change open/close timing of valves of the engine, the apparatus equipped with a self-locking mechanism for preventing an unexpected change in the phase angle caused by an external disturbing torque transmitted from the valve
  • Patent Document 1 Such variable cam phaser as stated above equipped with a self-locking mechanism for preventing such unexpected change in phase angle is disclosed in Patent Document 1 listed below
  • This Patent Document 1 teaches a multiplicity of eccentric circular members (eccentric circular cam 110, first link 111, second link 112) each member having an eccentric center and arranged at a prescribed axial position of the camshaft such that the four centers of the eccentric members function as a whole as a four-link mechanism 108.
  • a brake on the four-link mechanism 108 with a first or second electromagnetic clutch 105 or 106, respectively, via a first or second control rotor 102 or 103, respectively, the phase angle of the drive rotor 101, operable connected to the camshaft and crankshaft, can be changed relative to the camshaft
  • This four-link mechanism 108 can vary the relative phase angle between the camshaft and crankshaft (drive rotor 101) in the phase advancing or retarding direction through rotations of the eccentric circular cam 110 integral with the camshaft, first link 111 rotatably supported by the eccentric circular cam 110, and second link 112 rotatably supported by the first link 111 about their pivots in association with a braked movement of either the first or second control rotor 102 or 103, respectively.
  • an object of the present invention to provide a structurally simpler and more cost effective variable cam phaser for aut omobile engine having a self-locking mechanism.
  • An inventive variable cam phaser for an automobile engine as recited in claim 1 includes:
  • phase angle varying apparatus of claim 1 may be configured such that:
  • variable cam phaser of claim 2 may be further configured such that the lock plate is divided into two parts by a pair of slits each extending from the support groove to the periphery of the lock plate
  • variable cam phaser of claim 3 may be configured such that one of the two slits may be provided with means for providing a force to widen that slit (said means hereinafter referred to as urging means).
  • variable cam phaser of claim 2 may be configured such that the lock plate is provided with two slits extending from the support groove to the periphery of the lock plate and that the radius of curvatures of the lock plate on the opposite sides thereof across the line of eccentric direction are slightly larger than the inner radius of the cylinder circumscribing the lock-plate.
  • the lock plate inscribed in the cylinder has a slightly larger radius of curvature than the inner radius of the cylinder, and is acted upon by a radially inward forces exerted by the cylinder.
  • the gaps between the lock plates and the drive rotor cylinder and between the lock plate bush and the support groove, formed by manufacturing errors for example are still reduced. That is, in this configuration, as in the configuration defined in claim 4, clearances (plays) of members of self-locking mechanism are reduced during a self-locking operation under an external disturbing torque, and thud a required pressure to the drive rotor cylinder of the lock plate is instantly generated
  • variable cam phaser defined in claim 4 or 5 may be further configured such that the lock plate bush is divided into two parts by a pair of slits
  • variable cam phaser defined in any one of claims 2 through 6 may be configured such that the flat faces of the lock plate bushes are a pair of stepped faces projecting to the right and left with respect to the line of eccentric direction, and that the stepped faces are offset in the eccentric direction away from the cam center towards the eccentric axis of the cam center
  • variable cam phaser defined in any one of claims 1 through 7 may be configured such that the coupling mechanism consists of coupling members each engaging with one of paired coupling holes formed in the control rotor and with one of paired coupling holes formed in the rock plate; and that a minute clearance is provided between each coupling member and an associated coupling hole of either the control rotor or the lock plate.
  • variable cam phaser for automobile engine defined in claim 1 has a self-locking mechanism which is simpler in structure and cost effective than conventional one in that the mechanism consists of such members as a drive rotor cylinder, disc shaped lock plate, and support groove.
  • variable cam phaser in accordance with claim 2 is equipped with a self-locking mechanism having an improved self-locking function and durability
  • variable cam phaser in accordance with any one of claims 3 through 8 has a still improved self-locking function
  • variable cam phaser shown in the respective embodiments are installed in an automobile engine, adapted to transmit the rotation of the crankshaft of the engine to the camshaft of the apparatus to open/close air suction/exhaustion valves of the engine in synchronism with the crankshaft so that the valve timing of the air suction/exhaustion valves is changed in accord with such parameters of the operating conditions of the engine as an engine load and rpm.
  • a variable cam phaser 1 comprises a drive rotor 2 driven by the crankshaft, a first control rotor 3 (referred to as control rotor in claim 1), a camshaft 6 ( Fig. 4 ), torque means 9, a phase angle varying mechanism 10, and a self-looking mechanism 11.
  • the end of the apparatus having a second electromagnetic clutch shown in Fig. 1 will be hereinafter referred to as the front end, while the end having the drive rotor 2 will be referred to as the rear end.
  • phase advancing direction D1 The rotational direction (clockwise direction) of the drive rotor 2 about the axis L0 of the camshaft as viewed from the front end will be referred to as phase advancing direction D1, and the opposite rotational direction (counterclockwise direction) will be referred to as phase retarding direction D2.
  • the drive rotor 2 consists of a sprocket 4 and a drive cylinder 5 having a cylinder 20, integrated together with a multiplicity of bolts 2a.
  • the camshaft 6 shown in Fig 4 is immovably and coaxially integrated with the rear end of a center shaft 7 by means of a bolt 37 screwed into a threaded female hole 6a formed in the front end of the camshaft and the central circular hole 7e of the center shaft 7.
  • the first control rotor 3 is a generally bottomed cylinder having a flange portion 3a at the front edge thereof, a cylindrical portion 3b extending rearward, and a bottom 3c
  • the bottom 3c has a central circular throughhole 3d, a pair of pin holes 28, an arcuate groove 30 extending along a circle of a given radius about the central axis L0 (the groove hereinafter referred to as arcuate groove 30), and a guide groove 31 whose radius decreases in the phase advancing direction D1 about the central axis L0 (the groove hereinafter referred to as oblique guide groove 31).
  • the center shaft 7 is a contiguous body comprising a first cylindrical portion 7a, flange portion 7b, second cylindrical portion 7c, eccentric circular cam 12 having a cam center L1 eccentrically offset from the camshaft axis L0, and a third cylindrical portion 7d, arranged along the axis L0 in the order mentioned from the rear end towards the front end
  • the drive rotor 2 comprises a sprocket 4 and a drive cylinder 5 which are integrated together by means of bolts 2a Provided between the sprocket 4 and the drive cylinder 5 is a center shaft 7, which has a flange portion 7b.
  • the center shaft 7 also has first and second cylindrical portions 7a and 7c, respectively, which are fitted in the circular hole 4a of the sprocket 4 and in the circular hole 5a of the drive cylinder 5a, respectively, so that the drive rotor 2 is rotatably mounted on the camshaft 6 via the center shaft 7.
  • the third cylindrical portion 7d is fitted in the central circular hole 3d of the first control rotor 3 It is noted that the drive rotor 2, first control rotor 3, camshaft 6, and center shaft 7 are coaxial with the axis L0.
  • the torque means 9 consists of a first electromagnetic clutch 21 for providing the first control rotor 3 with a first torque (braking torque to retard the control rotor 3 relative to the drive rotor 2), and a reverse rotation mechanism 22 for providing the first control rotor 3 with a second torque which is opposite in direction with respect to the first torque
  • the phase angle varying mechanism 10 includes the center shaft 7 (rotatably supporting the drive rotor 2), self-locking 11, and a coupling mechanism 16, and is adapted to couple the first control rotor 3 unrotatably with the camshaft 6.
  • the self-locking mechanism 11 is arranged between the drive rotor 2 and center shaft 7 so as to prevent a phase angle disturbance from occurring between the drive rotor 2 and camshaft 6 under an external disturbing torque applied to the camshaft 6 by a valve spring (not shown).
  • the self-locking mechanism 11 consists of the eccentric circular cam 12 of the center shaft 7, lock plate bush 13 and lock plate 14, and the cylinder 20 of the drive rotor 2.
  • the lock plate bush 13 has a circular hole 13a for receiving therein the eccentric circular cam 12 of the center shaft 7, and is provided on the opposite sides thereof with a pair of flat faces 23 and 24, as shown in Figs. 1 and 5 .
  • the lock plate bush 13 is rotatably mounted on the periphery of the eccentric circular cam 12 such that the two flat faces 23 and 24 are maintained substantially parallel with respect to a line L2 connecting the camshaft axis L0 and the cam center L1 as shown in Fig. 5
  • the lock plate 14 is generally disk shaped and has a substantially rectangular support groove 15 extending along a diameter.
  • the lock plate 14 consists of a pair of two constituent members 14a and 14b divided by a pair of slits 25 and 26 formed at the opposite narrow sides 15a and 15b of the support groove 15 and extending to the circumference of the lock plate 14.
  • the flat faces 23 and 24 of the lock plate bush 13 are held in contact with the long sides 15c and 15d of the support groove 15
  • the periphery of the lock plate 14 is inscribed in the cylindrical portion 20 of the drive cylinder 5.
  • the flat faces 23 and 24 of the lock plate bush 13 are sandwiched between the long sides (15c and 15d) of the support groove 15 Under this condition, the portion of the periphery of the eccentric circular cam 12 eccentrically offset (from the cam center L1) beyond a line L3 that passes through the cam center L1 perpendicularly to the line L2 is supported by the support groove 15 via the lock plate bush 13.
  • the coupling mechanism 16 consists of' a pair of coupling pins 27, a pair of first pin holes 28 formed in the bottom 3b of the first control rotor 3, and a pair of second pin holes 29 each formed in the respective constituent members 14a and 14b of the lock plate 14.
  • Each of the coupling pins 27 is fixedly fitted at one end thereof in either the first pin hole 28 or second pin hole 29, but at the other end loosely fitted in the other first pin hole or second pin hole with a minute gap between pin and the hole
  • the lock plate 14 is pressed against the inner circumferential surface 20a of the cylinder 20 of the drive cylinder 5 and unrotatably held therein when an external disturbing torque is transmitted thereto, as described in detail later
  • the minute gap provided in either the first or second pin hole 28 or 29 is to circumvent a difficulty of pressing the lock plate 14 against the inner circumferential surface 20a if the lock plate 14 is fixed to the first control rotor 3.
  • the center shaft 7 (camshaft 6) is unrotatably integrated with the first control rotor 3 via the eccentric circular cam 12, lock plate bush 13 and lock plate 14
  • the camshaft 6 becomes integral with the first control rotor 3 under an external disturbing torque exerted by the torque means 9, and undergoes a relative rotation relative to the drive rotor 2 in either the phase-advancing direction D1 or phase retarding direction D2.
  • the phase angle between the camshaft 6 and drive rotor 2 is changed, thereby changing the valve timing.
  • the first electromagnetic clutch 21 is firmly secured inside the engine (not shown) ahead of the first control rotor 3
  • the first electromagnetic clutch 21 is retarded in rotation relative to the drive rotor 2 rotating in D1 direction.
  • the reverse rotation mechanism 22 consists of the arcuate groove 30 and the oblique guide groove 31 of the first control rotor 3, a second control rotor 32, a disk shaped pin guide plate 33, a second electromagnetic clutch 38 for putting a brake on the second control rotor 32, first and second link pins 34 and 35, and a ring member 36.
  • the second control rotor 32 is arranged inside the cylindrical portion 3b of the first control rotor 3 and rotatably mounted on the coaxial third cylindrical portion 7d of the center shaft 7 that passes through the central circular throughhole 32a of the second control rotor 32.
  • the second control rotor 32 is provided in a rear section thereof' with a stepped eccentric circular hole 32b, whose center ol is offset from the camshaft axis L0.
  • the ring member 36 is slidably inscribed in the stepped eccentric circular hole 32b
  • the disc shaped pin guide plate 33 is arranged inside the cylindrical portion 3b of the first control rotor 3 and between the bottom 3c and second control rotor 32 such that the pin guide plate 33 is rotatably supported by the third cylindrical portion passing through the central circular throughhole 33a of the pin guide plate 33
  • the pin guide plate 33 has a groove 33b and a guide groove 33c that extends independently of the circular throughhole 33a in substantially opposite radial directions (the guide grooves hereinafter referred to as radial guide grooves).
  • the radial groove 33b is formed in correspondence with the arcuate groove 30 and extends from a position near the central circular throughhole 33a to the periphery of the pin guide plate.
  • the radial guide groove 33c is formed in correspondence with the oblique guide groove 31 and extends to a point near the periphery.
  • a thin round shaft 34a and a thick hollow shaft 34b integrated with the thin round shaft 34a at the front end of' the thin round shaft 34a constitutes a first link pin 34.
  • the thick hollow shaft 34b is supported on both sides thereof by the radial groove 33b.
  • the rear end of the thin round shaft 34a passes through the arcuate groove 30 and support groove 15, and is securely fixed to a mounting hole 5b of the drive cylinder 5.
  • the thin round shaft 34a can move in the arcuate groove 30 between the opposite ends of the arcuate groove 30.
  • a second link pin 35 consists of' a first member 35c which is made up of a thin shaft 35a integrally connected to the rear end of' a thick round shaft 35b, a first hollow shaft 35d, a second hollow shaft 35e, and a third hollow shaft 35f
  • the first through third hollow shafts 35d-35f are mounted in sequence on the thin round shaft 35a and retained together at their rear ends.
  • the thick round shaft 35b is inserted in the support groove 15.
  • the first hollow shaft 35d has an arcuate periphery that can fit the oblique guide groove 31, and is movable along the oblique guide groove 31 with its upper and lower sides supported by the oblique guide groove 31.
  • the second hollow shaft 35e has a cylindrical shape and is movable along the radial guide groove 33c with its opposite sides held by the radial guide groove 33c
  • the third hollow shaft 35f has a cylindrical shape and is rotatably fitted in the circular hole 36a formed in the ring member 36.
  • a holder 39 and a washer 40 each having a central circular hole 39a and 40a, respectively, are placed on the the leading end of the third cylindrical portion 7d of' the center shaft 7
  • the holder 39, washer 40, and center shaft 7 are securely fixed to the camshaft 6 with the bolt 37 screwed into a threaded bore 6a through the circular holes 39a, 40a, and 7e.
  • all the elements between the drive rotor 2 and the second control rotor 2 inclusive, arranged round the periphery of the center shaft 7, are securely fixed together between the flange portion 6b of the camshaft 6 and the holder 39.
  • the axial clearance of these elements can be optimized by adjusting the thickness of the washer 40 Arranged in front of the bolt and the first and second electromagnetic clutches 21 and 38, respectively, is a cover 70.
  • the torque means 9 for changing the phase angle between the camshaft 6 and drive rotor 2 (and the crankshaft not shown) will now be described.
  • the first control rotor 3 is in rotation in D1 direction ( Fig. 6 ) together with the drive rotor 2
  • the center shaft 7 (camshaft 6) is retarded in D2 direction together with the integrated first control rotor 3, relative to the drive rotor 2 which is rotating in D1 direction
  • the phase angle of the camshaft 6 relative to the drive rotor 2 (and of the crankshaft not shown) is varied in the phase retarding direction D2, thereby changing the open/close timing of the valve.
  • the first hollow shaft 35d of the second link pin 35 moves in the oblique guide groove 31 in substantially the clockwise direction D3 ( Fig 6(c) ), and the second hollow shaft 35e moves in the radial guide groove 33c in D4 direction towards the axis L0 ( Fig. 6(b) ).
  • the third hollow shaft 35f shown in Fig. 6(a) provides the ring member 36 with a torque that causes the ring member 36 to slide within the circular hole 32b.
  • the thin round shaft 34a moves in the arcuate groove 30 in the clockwise direction D1
  • the opposite ends 30a and 30b of the arcuate groove 30 serve as stoppers for stopping the thin hollow shaft 34a that comes into abutment with the ends
  • the second control rotor 32 is normally in rotation in D1 direction together with the drive rotor 2 ( Fig. 6(a) )
  • the front end 32c of the second control rotor 32 is attracted onto the friction member 38a, resulting in a rotational delay of the second control rotor 32 in D2 direction relative to the first control rotor 3.
  • the ring member 36 slidably rotates in the stepped eccentric circular hole 32b.
  • the second hollow shaft 35e shown in Fig 6(b) moves in the radial direction D5 within the radial guide groove 33c together with the third hollow shaft 35f and first hollow shaft 35d.
  • the first control rotor 3 shown in Fig. 6(c) is acted upon by a torque in the direction opposite to the torque generated by the first electromagnetic clutch 21.
  • This torque is exerted, via the wall of the oblique groove 31, by the first hollow shaft 35d moving in the oblique groove 31 in the substantially counterclockwise direction D6, causing the first control rotor 3 to be rotated in the phase advancing direction D1 still more relative to the drive rotor 2 rotating in D1 direction.
  • the phase angle of' the camshaft 6 relative to the drive rotor 2 (and crankshaft not shown) is advanced in D1 direction back to the original phase angle, thereby restoring the open/close timing of the valve
  • phase angle of the center shaft 7 (and of' the camshaft 6) relative to the drive rotor 2 (and of the crankshaft not shown) is determined by a rotation of the first control rotor 3 in the phase advancing direction D1 or retarding direction D2 relative to the drive rotor 2, as described above.
  • an external disturbing torque is transmitted from a valve spring (not shown) to the camshaft 6, the relative phase angle between the camshaft and drive rotor 2 is changed, which will result in an unexpected deviation in open/close timing of the valve
  • the self-locking mechanism 11 of' this embodiment takes advantage of such external disturbing torque to prevent such phase angle deviation
  • Fig. 7 illustrates how a self-lock function takes place between the periphery (14c and 14d) of the lock plate 14 and the cylinder 20 of the drive cylinder 5 when an external disturbing torque is transmitted to rotate the camshaft 6 (center shaft 7) in clockwise direction D1 or counterclockwise direction D2.
  • the eccentric circular cam 12 is acted upon by a torque that causes the cam center L1 to be eccentrically rotated about the camshaft axis L0 in either D2 direction or D1 direction
  • the cam axis L1 is eccentrically offset from the camshaft axis L0 by a distance s
  • line L2 passes through the axis L0 and cam center L1
  • line L3 passing through the cam center L1 is perpendicular to line L2
  • line L3 intersects the eccentric circular cam 12 at point P1
  • the guide plate bush 13 is acted upon by a force F1 exerted by the eccentric circular cam 12 at the intersection point P1 in the direction of line L3.
  • the lock plate bush 13 having flat faces 23 and 24 is inserted between the eccentric circular cam 12 and support groove 15, the contact stresses that appear on the support groove 15 in surface contact with the long sides 15c and 15d will be reduced.
  • the self-locking function can be established even if the eccentric circular cam 12 is held in the support groove 15 with the line L2 passing through the axis L0 and L1 aligned with the long sides 15c and 15d substantially in parallel thereto
  • the lock plate bush 13 may be omitted.
  • a self-locking mechanism 41 in accordance with a second embodiment of the invention.
  • the self-locking mechanism 41 has substantially the same elements as the first self-locking mechanism 11 except that lock plate bush 42 and lock plate 43 have different shapes from the corresponding lock plate bush and lock plate of the first embodiment
  • a spring member 44 corresponds to the urging means of claim 4.
  • the lock plate bush 42 is similar in shape to the lock plate bush 13 of the first embodiment, except that the lock plate bush 42 has no flat faces like 23 or 24
  • the lock plate 43 is provided with a slit 46 and a slit 47 for mounting a spring member 44.
  • the slit 47 is larger than the slit 46.
  • Other features of the lock plate 43 are the same as those of the lock plate 14.
  • the lock plate bush 42 is mounted on the eccentric circular cam 12 that passes through the circular hole 42a of the lock plate 42.
  • the lock plate bush 42 has a substantially elongate rectangular support groove 45 extending in a substantially diametrical direction
  • the lock plate bush 42 is divided into two constituent members 43a and 43b by a pair of linear slits that extend radially outwardly from the short sides 45a and 45b of the support groove 45 to the periphery of the lock plate 43
  • the slit 46 has the same shape as the slit 25 of the lock plate 14 of the first embodiment, but the slit 47 differs from the slit 26 of the first embodiment in that the slit 47 has a larger width than slit 46.
  • a spring member 44 which has an arcuate convex portion 44a and curved portions 44b and 44c at the opposite ends of the arcuate convex portion 44a, where the width of the arcuate convex portion 44a is larger than the that of the slit 47.
  • a spring member 44 provides the constituent members 43a and 43b with a force for widening the width of the slit 47 when its arcuate convex portion 44a is fitted in the slit 47 and the curved portions 44b and 44c are supported by the constituent members 43a and 43b.
  • An external disturbing torque is transmitted from the cam center L1 of the eccentric circular cam 12 to the inner circumferential surface 20a of drive cylinder 5 along line L3, and generates forces F1 and F2 at the intersection points P7 and P8, which forces are transmitted from the lock plate bush 42 to the respective constituent members 43a and 43b through line contact between the lock plate bush 42 and the lock plate constituent members 43a and 43b at the intersection point P5 and P6 of the tangential line L3 with the periphery of the lock plate bush 42. Further, these forces acts on the inner circumferential surface 20a of the drive cylinder 5 at the intersection points P7 and P8 of line L3 with the peripheral surface (43c and 43d).
  • the urging means for widening the width of the slit 47 is not limited to the 44 as shown in Fig. 8 : it may alternatively be a trapezoidal member 48a and a spring member 48b as shown in Fig 9(a) and (b) .
  • the lock plate 43 has cut-away portions 47a and 47b that narrows in diameter along the camshaft axis L0 and towards the periphery of the slit 47.
  • a trapezoidal member 48a is arranged between the cut-away portions 47a and 47b
  • the trapezoidal member 48a is provided in the periphery thereof with a recess 48c for receiving a spring member 48b corresponding to the spring member 44.
  • the trapezoidal member 48a is acted upon by a spring force exerted by the spring member 48b in the direction D7 towards the axis L0. This force will act on the faces of the cut-away portions 47a and 47b at right angle thereto, thereby widening the slit 47.
  • a C-shaped leaf spring 49 for compressing the lock plate constituent members 43a and 43b is arranged round the peripheries of the lock plate constituent members so as to widen the width of the slit 47 and narrow the width of the slit 46.
  • the C-shaped leaf spring 49 is arranged such that its opening is aligned with the slit 46 between the lock plate constituent members 43a and 43b.
  • the left half portion of the C-shaped leaf spring 49 shown in Fig. 9(b) may be fixed to the constituent member the 43b with the right half of the C-shaped leaf spring 49 while the right half portion mounted on the constituent member 43b so that the constituent member 43b is urged to rotate in the D2 direction relative to the constituent member 43a.
  • the lock plate bush 50 may be split into two lock plate bush constituent members 50a and 50b separated by slits 50c and 50d formed along line L2.
  • the lock plate bush 50 is divided, the gaps formed between the inner periphery 50e of the lock plate bush 50 and the outer periphery of the eccentric circular cam 12 due to manufacturing errors are still reduced, thereby further reducing plays of the constituent members and providing still effective self-locking function. Since plays of the locking members due to manufacturing errors can be reduced with the urging means as shown in Figs. 8 and 9 , precision requirements for the eccentric circular cam 12, lock plate bush 42 and 50, and for rock plate 43 can be relaxed to lower the production cost.
  • This lock plate may be made in the form of a C-shaped object 51 having an opening or slit 53 that extends from a support groove 52 to the outer periphery 51a of the C-shaped object 51 as shown in Fig 10 , wherein the outer diameter of the C-shaped object 51 (as measured along line L3) can be made slightly larger than the inner diameter of the inner periphery 20a of the cylinder 20 so that the inner periphery 20a are constantly pushed radially outward (in the direction of d2 and d3 in Fig. 10 ).
  • the same self-locking function as described above in connection with Figs. 8 and 9 can be obtained without the spring member
  • FIG 11 there is shown another self-locking mechanism for use with an automobile variable cam phaser in accordance with a third embodiment of the invention
  • the self-locking mechanism 61 has essentially the same structure as the second self-locking mechanism 41 except that the spring member 44 is removed from the washer 40 and that the lock plate bush 42 is replaced by a lock plate bush 62 having a different configuration.
  • the lock plate bush 62 has a pair of right and left stepped faces 63 and 64, respectively, each having a flat face 62a/62b and stepped portion 62c/62d projecting therefrom to the right/left
  • the lock plate bush 62 is mounted on the eccentric circular cam 12 coaxially with the eccentric circular cam 12 that passes through the circular hole 62e of the lock plate bush 62 such that the stepped faces 63 and 64 are parallel to line L2 extending from the axis L0 toward the L1.
  • the stepped faces 63 and 64 are mounted on the eccentric circular cam 12 in a symmetric fashion with respect to line L2 and offset from the cam center L1.
  • the stepped faces 63 and 64 projecting to the right and left of the flat faces 62a and 62b.
  • Line L7 connecting the centers of the flat faces 63 and 64 is substantially parallel to line L3, and intersects line L2 at a right angle at point C3 which is eccentrically further offset from the camshaft axis L0 than the cam center L1.
  • the stepped faces 63 and 64 are held in position by the long sides 45a and 45b of the support groove 45
  • the long sides 45a and 45b of the support groove 45 are respectively subjected to outward forces oriented to the left and right direction, respectively, along line L7, across the stepped faces 63 and 64 which are in surface contact with long sides 45a and 45b of the support groove 45 at positions further offset than the cam center L1 of the eccentric camshaft 12.
  • the forces F3 and F4 are transmitted from the lock plate 43 to the inner circumferential surface 20a of the drive cylinder 5 at the intersection points P9 and P10 where line L7 intersects the outer peripheries 43c and 43d of the lock plate constituent members 43a and 43b, respectively.
  • the stepped faces 63 and 64 are in contact with the support face 45 at further offset positions than the cam axis L1 of the eccentric circular cam 12 that they exhibit less plays in the self-locking mechanism as compared with the first embodiment in which the eccentric circular cam 12 only has non-stepped flat faces 23 and 24.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP10851739.2A 2010-05-18 2010-05-18 Dispositif à variation de phase pour moteur Not-in-force EP2573336B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2010/058370 WO2011145175A1 (fr) 2010-05-18 2010-05-18 Dispositif à variation de phase pour moteur

Publications (3)

Publication Number Publication Date
EP2573336A1 true EP2573336A1 (fr) 2013-03-27
EP2573336A4 EP2573336A4 (fr) 2013-12-18
EP2573336B1 EP2573336B1 (fr) 2015-03-04

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Application Number Title Priority Date Filing Date
EP10851739.2A Not-in-force EP2573336B1 (fr) 2010-05-18 2010-05-18 Dispositif à variation de phase pour moteur

Country Status (6)

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US (1) US20130125846A1 (fr)
EP (1) EP2573336B1 (fr)
JP (1) JP5616440B2 (fr)
KR (1) KR20130072190A (fr)
CN (1) CN102859126A (fr)
WO (1) WO2011145175A1 (fr)

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Publication number Priority date Publication date Assignee Title
GB2452400B (en) 2007-08-28 2010-12-29 Aircraft Medical Ltd Laryngoscope insertion section
CN103140653A (zh) 2010-10-12 2013-06-05 日锻汽门株式会社 发动机的相位可变装置
JP5840768B2 (ja) * 2012-04-19 2016-01-06 日鍛バルブ株式会社 エンジンの位相可変装置
JP5840769B2 (ja) * 2012-04-20 2016-01-06 日鍛バルブ株式会社 エンジンの位相可変装置
KR20150063378A (ko) * 2012-10-09 2015-06-09 니탄 밸브 가부시키가이샤 자동차용 엔진의 위상 가변 장치
WO2014109050A1 (fr) * 2013-01-11 2014-07-17 日鍛バルブ株式会社 Dispositif à phase variable pour moteur d'automobile
DE112016005069T5 (de) * 2015-12-02 2018-07-12 Borgwarner Inc. Geteilter abgasverstärkungs-turbolader

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WO2010026645A1 (fr) * 2008-09-05 2010-03-11 日鍛バルブ株式会社 Dispositif de variation de phase d'arbre à cames dans un moteur pour automobile
WO2010046974A1 (fr) * 2008-10-22 2010-04-29 日鍛バルブ株式会社 Dispositif de phase variable d’arbre à cames dans un moteur pour automobile

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JP3937164B2 (ja) * 2002-04-19 2007-06-27 株式会社デンソー バルブタイミング調整装置
JP5102071B2 (ja) * 2008-03-03 2012-12-19 日鍛バルブ株式会社 自動車用エンジンにおける位相可変装置
US8505508B2 (en) * 2009-06-05 2013-08-13 Nittan Valve Co., Ltd. Phase varying device for engine
CN103140653A (zh) * 2010-10-12 2013-06-05 日锻汽门株式会社 发动机的相位可变装置

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WO2009098752A1 (fr) * 2008-02-04 2009-08-13 Nittan, Valve, Co., Ltd. Dispositif de variation de phase dans un moteur d'automobile
EP2249000A1 (fr) * 2008-02-04 2010-11-10 Nittan Valve Co., Ltd. Dispositif de variation de phase dans un moteur d'automobile
WO2010026645A1 (fr) * 2008-09-05 2010-03-11 日鍛バルブ株式会社 Dispositif de variation de phase d'arbre à cames dans un moteur pour automobile
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Also Published As

Publication number Publication date
JPWO2011145175A1 (ja) 2013-07-22
EP2573336B1 (fr) 2015-03-04
KR20130072190A (ko) 2013-07-01
US20130125846A1 (en) 2013-05-23
EP2573336A4 (fr) 2013-12-18
JP5616440B2 (ja) 2014-10-29
CN102859126A (zh) 2013-01-02
WO2011145175A1 (fr) 2011-11-24

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