EP2573336A1 - Phase variable device for engine - Google Patents
Phase variable device for engine Download PDFInfo
- 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
Links
- 230000007246 mechanism Effects 0.000 claims abstract description 64
- RDYMFSUJUZBWLH-UHFFFAOYSA-N endosulfan Chemical compound C12COS(=O)OCC2C2(Cl)C(Cl)=C(Cl)C1(Cl)C2(Cl)Cl RDYMFSUJUZBWLH-UHFFFAOYSA-N 0.000 claims abstract description 31
- 230000008878 coupling Effects 0.000 claims abstract description 25
- 238000010168 coupling process Methods 0.000 claims abstract description 25
- 238000005859 coupling reaction Methods 0.000 claims abstract description 25
- 230000008859 change Effects 0.000 claims abstract description 10
- 239000011435 rock Substances 0.000 claims description 6
- 238000004519 manufacturing process Methods 0.000 abstract description 12
- 239000000470 constituent Substances 0.000 description 25
- 230000000979 retarding effect Effects 0.000 description 6
- 230000033001 locomotion Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000009877 rendering Methods 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- 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.
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Abstract
Description
- 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
- 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 ThisPatent 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. By putting 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.
- On the other hand, when the camshaft is subjected to an external disturbing torque arising from a reaction of a valve spring and transmitted to the drive rotor 101, the first link 111 is pressed against a guide groove 113 of the first link formed in the drive cylinder 115 of the drive rotor 101, so that the circular eccentric members 110-112 are unrotatably fixed, thereby preventing the camshaft from changing its phase angle relative to the drive rotor 101. The variable cam phaser disclosed in
Patent Document 1 has a self-locking mechanism for preventing any phase angle change caused by such external disturbing torque as discussed above. -
-
PATENT DOCUMENT 1PCT/JP2009/61327 - Since the self-locking mechanism disclosed in
Patent Document 1 has a f'our-link mechanism 108, the self'-locking mechanism must achieve self-locking function with a required accuracy of the four-link mechanism 108. As a consequence, the self-locking mechanism turns out to be very complex and costly. Thus, a need exists to provide a simple self-locking mechanism. - It is, therefore, 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: - a drive rotor driven by the crankshaft of the engine;
- a control rotor;
- a camshaft coaxial with the drive rotor and adapted to rotatably support the drive rotor;
- a torque means for providing the control rotor with a torque for rotating the control rotor relative to the drive rotor;
- a phase angle varying mechanism for varying the relative phase angle between the drive rotor and the control rotor in accord with the relative rotation of the control rotor relative to the drive rotor; and a self-locking mechanism mounted in the phase varying mechanism for preventing a phase change from occurring between the drive rotor and the camshaft caused by an unexpected cam torque appearing on the camshaft, the variable cam phaser characterized in that the self-locking mechanism comprises:
- an eccentric circular cam integral with the camshaft; and
- a lock plate having
- a support groove for supporting, at positions further offset from the camshaft axis in the direction (referred to as eccentric direction) from the camshaft axis towards the cam center of the eccentric circular cam, the periphery of the eccentric circular cam from both sides thereof,
- a coupling mechanism for transmitting the relative rotational torque from the control rotor to the eccentric circular cam, and
- a cylindrical body formed integral with the drive rotor and circumscribing the periphery of the lock plate.
- (Function) Upon receipt of an external disturbing torque from a valve, the lock plate in rotation together with the camshaft is subjected to a substantially radial force via the support groove that is adapted to immovably holding the eccentric circular cam integral with the camshaft, and hence the lock plate is pressed against the cylinder of' the drive rotor As a consequence, the drive rotor and the camshaft both driven by the crankshaft are interlocked and prohibited from undergoing a relative rotation by the external disturbing torque, thereby keeping the phase angle between them unchanged.
- As recited in
claim 2, the phase angle varying apparatus ofclaim 1 may be configured such that: - the support groove extends in a radial direction of the lock plate;
- the eccentric circular cam is provided on the outer periphery thereof with a lock plate bush; and
- the lock plate bush has on the opposite sides of the outer periphery thereof a pair of flat faces spaced apart across the line of eccentric direction and supported by the support groove
- (Function) With the eccentric circular cam held in the support groove and with the lock plate bush kept in surface contact with the support groove via the paired flat faces, the contact stress generated on the wall of the support groove is reduced as compared with the stress that would be otherwise generated if the eccentric circular cam were in direct contact with the support groove As a result, substantially no uneven friction wear will take place in contacting surfaces, which allows the lock plate and eccentric circular cam to be kept in good condition without suffering a backlash or play, which in turn facilitates prompt generation and transmission of' a pressure between the lock plate and the cylinder of the drive rotor under an external disturbing torque.
- As recited in
claim 3, the variable cam phaser ofclaim 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 - (Function) When the eccentric circular cam is held in surface contact with the support groove of the lock plate via the lock plate bush, it may happen that the torque that causes the lock plate to rotate relative to the cylinder under an external disturbing torque becomes dominant over the radial force that forces the lock plate against the cylinder of the drive rotor, thereby rendering the self lock mechanism inoperable However, when the lock plate is divided into two part by the slits extending from the support groove to the periphery of the lock plate, the relative torque generated on one of the divided lock plate constituent members is not well transmitted to the other member. As a consequence, under an external disturbing torque, the torque generated on the entire lock plate is reduced. Accordingly, the pressure exerted to the drive rotor cylinder of the lock plate is enhanced.
- As recited in
claim 4, the variable cam phaser ofclaim 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). - (Function) By providing one of' the slits with such force to widen one of the slits, the gaps that are formed during manufacture between th e lock plate and drive rotor cylinder and between the lock plate bush an d the support groove are reduced, thereby reducing the plays of members of the self-locking mechanism during self-locking operation That is, a pressure needed to force the lock plate against the drive rotor cylinder can be instantaneously generated under an external disturbing torque.
- As recited in
claim 5, the variable cam phaser ofclaim 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. - (Function) 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. As a consequence, 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 - As recited in
claim 6, the variable cam phaser defined inclaim - (Function) In this configuration, as defined in
claim 6, since a force is exerted on each of the divided members of' the lock plate bush by the urging means via the lock plate, gaps that are formed between the divided lock plate bushes and the eccentric circular cam can be reduced in size than the gaps formed with undivided lock plate bushes, so that the plays of self-locking constituent members are still reduced. That is, a pressure created by an external disturbing torque is instantly transmitted to the drive rotor cylinder This implies that precision requirement for the eccentric circular cam and rock plate bush can be relaxed and hence the production costs of the self-locking mechanism can be reduced - Further, as recited in
claim 7, the variable cam phaser defined in any one ofclaims 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 - (Function) Strictly speaking, a gap due to manufacturing error is formed between the support groove and the respective lock plate bushes. However, when the flat faces are stepped and abutted against the rock plate at positions offset from the cam center of the eccentric circular cam, the arcuate moving distance traveled by the flat faces before they come into contact with the support groove under an external disturbing torque is reduced as compared with the case where the planes are not stepped In other words, plays of the rock plate bushes are still minimized then, so that a still instantaneous pressure is generated and transmitted to the drive rotor cylinder of the lock plates under an external disturbing torque
- Still further, as recited in claim 8, the 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. - (Function) If the positional relationship between the control rotor and the lock plate is set too strict, a manufacturing error may make it difficult to press the lock plate against the drive rotor cylinder under an external disturbing torque By providing a minute clearance between each of the coupling members and the associated hole, the lock plate is less restricted to move in the radial direction, which makes it easy for the lock plate to be pressed against the drive rotor cylinder under an external disturbing torque.
- The 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. - The variable cam phaser in accordance with
claim 2 is equipped with a self-locking mechanism having an improved self-locking function and durability - The variable cam phaser in accordance with any one of
claims 3 through 8 has a still improved self-locking function -
-
Fig. 1 is an exploded perspective figure of' a variable cam phaser for an automobile engine in accordance with a first embodiment of the invention, as viewed from the front end thereof -
Fig 2 is an exploded perspective figure of the apparatus ofFig. 1 , as viewed from the rear end thereof -
Fig. 3 is a front view of' the apparatus of the first embodiment (excluding cover 70). -
Fig. 4 is a cross section taken along line A-A ofFig 3 . -
Fig. 5 is a cross section taken along line E-E ofFig. 4 -
Fig 6 shows cross sections of' the apparatus taken along line B-B ofFig 4 (Fig. 6(a) ) and along line C-C ofFig. 4 (Fig. 6(b) ) -
Fig. 7 illustrates a self-locking mechanism of the first embodiment. -
Fig. 8 is a cross section of a self-loci mechanism in accordance with a second embodiment of the invention, taken long a line that corresponds to line E-E ofFig. 4 . -
Fig 9 illustrates a variation of a spring member used in the second embodiment. -
Fig. 10 illustrates a variation of the lock plates -
Fig 11 is a cross section of a self-locking mechanism in accordance with a third embodiment of the invention, taken along a line that corresponds to line E-E ofFig 4 - The invention will now be described in detail by way of example with reference to the accompanying drawings 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.
- Referring to
Figs 1 through 6 , there is shown a structure of' a first embodiment of the invention. Avariable cam phaser 1 comprises adrive 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 phaseangle varying mechanism 10, and a self-lookingmechanism 11. The end of the apparatus having a second electromagnetic clutch shown inFig. 1 will be hereinafter referred to as the front end, while the end having thedrive rotor 2 will be referred to as the rear end. The rotational direction (clockwise direction) of thedrive 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 asprocket 4 and adrive cylinder 5 having acylinder 20, integrated together with a multiplicity ofbolts 2a. Thecamshaft 6 shown inFig 4 is immovably and coaxially integrated with the rear end of acenter shaft 7 by means of abolt 37 screwed into a threadedfemale hole 6a formed in the front end of the camshaft and the centralcircular hole 7e of thecenter shaft 7. - The
first control rotor 3 is a generally bottomed cylinder having aflange portion 3a at the front edge thereof, acylindrical portion 3b extending rearward, and a bottom 3c The bottom 3c has a centralcircular throughhole 3d, a pair of pin holes 28, anarcuate 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 aguide 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 firstcylindrical portion 7a,flange portion 7b, secondcylindrical portion 7c, eccentriccircular cam 12 having a cam center L1 eccentrically offset from the camshaft axis L0, and a thirdcylindrical portion 7d, arranged along the axis L0 in the order mentioned from the rear end towards the front end Thedrive rotor 2 comprises asprocket 4 and adrive cylinder 5 which are integrated together by means ofbolts 2a Provided between thesprocket 4 and thedrive cylinder 5 is acenter shaft 7, which has aflange portion 7b. Thecenter shaft 7 also has first and secondcylindrical portions circular hole 4a of thesprocket 4 and in thecircular hole 5a of thedrive cylinder 5a, respectively, so that thedrive rotor 2 is rotatably mounted on thecamshaft 6 via thecenter shaft 7. The thirdcylindrical portion 7d is fitted in the centralcircular hole 3d of thefirst control rotor 3 It is noted that thedrive rotor 2,first control rotor 3,camshaft 6, andcenter shaft 7 are coaxial with the axis L0. - The torque means 9 consists of a first
electromagnetic clutch 21 for providing thefirst control rotor 3 with a first torque (braking torque to retard thecontrol rotor 3 relative to the drive rotor 2), and areverse rotation mechanism 22 for providing thefirst 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 acoupling mechanism 16, and is adapted to couple thefirst control rotor 3 unrotatably with thecamshaft 6. - The self-locking
mechanism 11 is arranged between thedrive rotor 2 andcenter shaft 7 so as to prevent a phase angle disturbance from occurring between thedrive rotor 2 andcamshaft 6 under an external disturbing torque applied to thecamshaft 6 by a valve spring (not shown). The self-lockingmechanism 11 consists of the eccentriccircular cam 12 of thecenter shaft 7,lock plate bush 13 andlock plate 14, and thecylinder 20 of thedrive rotor 2. - The
lock plate bush 13 has acircular hole 13a for receiving therein the eccentriccircular cam 12 of thecenter shaft 7, and is provided on the opposite sides thereof with a pair offlat faces Figs. 1 and5 . Thelock plate bush 13 is rotatably mounted on the periphery of the eccentriccircular cam 12 such that the twoflat faces Fig. 5 - The
lock plate 14 is generally disk shaped and has a substantiallyrectangular support groove 15 extending along a diameter. Thelock plate 14 consists of a pair of twoconstituent members slits narrow sides support groove 15 and extending to the circumference of thelock plate 14. The flat faces 23 and 24 of thelock plate bush 13 are held in contact with thelong sides support groove 15 - The periphery of the
lock plate 14 is inscribed in thecylindrical portion 20 of thedrive cylinder 5. The flat faces 23 and 24 of thelock plate bush 13 are sandwiched between the long sides (15c and 15d) of thesupport groove 15 Under this condition, the portion of the periphery of the eccentriccircular 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 thesupport groove 15 via thelock 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 thefirst control rotor 3, and a pair of second pin holes 29 each formed in the respectiveconstituent members lock plate 14. Each of the coupling pins 27 is fixedly fitted at one end thereof in either thefirst pin hole 28 orsecond 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 Thelock plate 14 is pressed against the innercircumferential surface 20a of thecylinder 20 of thedrive 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 orsecond pin hole lock plate 14 against the innercircumferential surface 20a if thelock plate 14 is fixed to thefirst control rotor 3. - The
lock plate 14, inscribed in thecylinder 20 of thedrive cylinder 5 and holding thelock plate bush 13 therein, is unrotatably integrated with thefirst control rotor 3 by means of the coupling pins 27 inserted the first andsecond pin first control rotor 3 via the eccentriccircular cam 12,lock plate bush 13 andlock plate 14 - The
camshaft 6 becomes integral with thefirst control rotor 3 under an external disturbing torque exerted by the torque means 9, and undergoes a relative rotation relative to thedrive rotor 2 in either the phase-advancing direction D1 or phase retarding direction D2. As a result, the phase angle between thecamshaft 6 and drive rotor 2 (or a crankshaft, not shown) is changed, thereby changing the valve timing. - It is noted here in connection with the torque means 9 that the first
electromagnetic clutch 21 is firmly secured inside the engine (not shown) ahead of thefirst control rotor 3 When thefront end 3e of theflange portion 3a is attracted by the first electromagnetic clutch 21 onto thefriction member 21a of the firstelectromagnetic clutch 21, thefirst control rotor 3 is retarded in rotation relative to thedrive rotor 2 rotating in D1 direction. - The
reverse rotation mechanism 22 consists of thearcuate groove 30 and theoblique guide groove 31 of thefirst control rotor 3, asecond control rotor 32, a disk shapedpin guide plate 33, a secondelectromagnetic clutch 38 for putting a brake on thesecond control rotor 32, first and second link pins 34 and 35, and aring member 36. - The
second control rotor 32 is arranged inside thecylindrical portion 3b of thefirst control rotor 3 and rotatably mounted on the coaxial thirdcylindrical portion 7d of thecenter shaft 7 that passes through the centralcircular throughhole 32a of thesecond control rotor 32. Thesecond control rotor 32 is provided in a rear section thereof' with a stepped eccentriccircular hole 32b, whose center ol is offset from the camshaft axis L0. Thering member 36 is slidably inscribed in the stepped eccentriccircular hole 32b - The disc shaped
pin guide plate 33 is arranged inside thecylindrical portion 3b of thefirst control rotor 3 and between the bottom 3c andsecond control rotor 32 such that thepin guide plate 33 is rotatably supported by the third cylindrical portion passing through the centralcircular throughhole 33a of thepin guide plate 33 Thepin guide plate 33 has agroove 33b and aguide groove 33c that extends independently of thecircular throughhole 33a in substantially opposite radial directions (the guide grooves hereinafter referred to as radial guide grooves). Theradial groove 33b is formed in correspondence with thearcuate groove 30 and extends from a position near the centralcircular throughhole 33a to the periphery of the pin guide plate. Theradial guide groove 33c is formed in correspondence with theoblique guide groove 31 and extends to a point near the periphery. - A
thin round shaft 34a and a thickhollow shaft 34b integrated with the thinround shaft 34a at the front end of' the thinround shaft 34a constitutes afirst link pin 34. The thickhollow shaft 34b is supported on both sides thereof by theradial groove 33b. The rear end of the thinround shaft 34a passes through thearcuate groove 30 andsupport groove 15, and is securely fixed to a mountinghole 5b of thedrive cylinder 5. On the other hand, the thinround shaft 34a can move in thearcuate groove 30 between the opposite ends of thearcuate groove 30. - A
second link pin 35 consists of' afirst member 35c which is made up of athin shaft 35a integrally connected to the rear end of' athick round shaft 35b, a firsthollow shaft 35d, a secondhollow shaft 35e, and a thirdhollow shaft 35f The first through thirdhollow shafts 35d-35f are mounted in sequence on the thinround shaft 35a and retained together at their rear ends. Thethick round shaft 35b is inserted in thesupport groove 15. The firsthollow shaft 35d has an arcuate periphery that can fit theoblique guide groove 31, and is movable along theoblique guide groove 31 with its upper and lower sides supported by theoblique guide groove 31. The secondhollow shaft 35e has a cylindrical shape and is movable along theradial guide groove 33c with its opposite sides held by theradial guide groove 33c The thirdhollow shaft 35f has a cylindrical shape and is rotatably fitted in thecircular hole 36a formed in thering member 36. - It is noted that a
holder 39 and awasher 40 each having a centralcircular hole 39a and 40a, respectively, are placed on the the leading end of the thirdcylindrical portion 7d of' thecenter shaft 7 Theholder 39,washer 40, andcenter shaft 7 are securely fixed to thecamshaft 6 with thebolt 37 screwed into a threadedbore 6a through thecircular holes drive rotor 2 and thesecond control rotor 2 inclusive, arranged round the periphery of thecenter shaft 7, are securely fixed together between theflange portion 6b of thecamshaft 6 and theholder 39. The axial clearance of these elements can be optimized by adjusting the thickness of thewasher 40 Arranged in front of the bolt and the first and secondelectromagnetic clutches cover 70. - The operation of 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. Normally, thefirst control rotor 3 is in rotation in D1 direction (Fig. 6 ) together with thedrive rotor 2 When thefirst control rotor 3 is attracted by, and abutted against, the firstelectromagnetic clutch 21 for braking, the center shaft 7 (camshaft 6) is retarded in D2 direction together with the integratedfirst control rotor 3, relative to thedrive rotor 2 which is rotating in D1 direction As a consequence, the phase angle of thecamshaft 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. - Under this condition, the first
hollow shaft 35d of thesecond link pin 35 moves in theoblique guide groove 31 in substantially the clockwise direction D3 (Fig 6(c) ), and the secondhollow shaft 35e moves in theradial guide groove 33c in D4 direction towards the axis L0 (Fig. 6(b) ). Thus, the thirdhollow shaft 35f shown inFig. 6(a) provides thering member 36 with a torque that causes thering member 36 to slide within thecircular hole 32b. The thinround shaft 34a moves in thearcuate groove 30 in the clockwise direction D1 The opposite ends 30a and 30b of thearcuate groove 30 serve as stoppers for stopping the thinhollow shaft 34a that comes into abutment with the ends - On the other hand, the
second control rotor 32 is normally in rotation in D1 direction together with the drive rotor 2 (Fig. 6(a) ) As the secondelectromagnetic clutch 38 is activated, thefront end 32c of thesecond control rotor 32 is attracted onto the friction member 38a, resulting in a rotational delay of thesecond control rotor 32 in D2 direction relative to thefirst control rotor 3. In response to the eccentric rotation of the stepped eccentriccircular hole 32b in D2 direction within thering member 36 shown inFig 6(a) , thering member 36 slidably rotates in the stepped eccentriccircular hole 32b. In response to the movement of thering member 36, the secondhollow shaft 35e shown inFig 6(b) moves in the radial direction D5 within theradial guide groove 33c together with the thirdhollow shaft 35f and firsthollow shaft 35d. In this case, thefirst control rotor 3 shown inFig. 6(c) is acted upon by a torque in the direction opposite to the torque generated by the firstelectromagnetic clutch 21. This torque is exerted, via the wall of theoblique groove 31, by the firsthollow shaft 35d moving in theoblique groove 31 in the substantially counterclockwise direction D6, causing thefirst control rotor 3 to be rotated in the phase advancing direction D1 still more relative to thedrive rotor 2 rotating in D1 direction. Accordingly, the phase angle of' thecamshaft 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 - Next, operation of the self-locking
mechanism 11 will now be described in detail The 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 thefirst control rotor 3 in the phase advancing direction D1 or retarding direction D2 relative to thedrive rotor 2, as described above. However, if an external disturbing torque is transmitted from a valve spring (not shown) to thecamshaft 6, the relative phase angle between the camshaft and driverotor 2 is changed, which will result in an unexpected deviation in open/close timing of the valve The self-lockingmechanism 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 thelock plate 14 and thecylinder 20 of thedrive 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. - When the
camshaft 6 and thecenter shaft 7 are subjected to an external disturbing torque in the phase retarding direction D2 or phase advancing direction D1, the eccentriccircular 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 Assume now that: 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; and line L3 passing through the cam center L1 is perpendicular to line L2; and line L3 intersects the eccentriccircular cam 12 at point P1 Under this condition, when the eccentriccircular cam 12 is subjected to a torque in the in D2 direction, theguide plate bush 13 is acted upon by a force F1 exerted by the eccentriccircular cam 12 at the intersection point P1 in the direction of line L3. When the eccentriccircular cam 12 is acted upon by an external disturbing torque in D1 direction, thelock plate bush 13 is acted upon by a force F2 exerted by the eccentriccircular cam 12 at intersection point P2 along line L3 (directed from cam center L1 to intersection point P2). - It is noted that the forces F1 and F2 are transmitted along line L3 from the
lock plate bush 13 to thelock plate 14 via the flat faces 23 and 24 in surface contact with the respectivelong sides support groove 15. These forces F1 and F2 are further transmitted from peripheries of theconstituent members lock plate 14 to the innercircumferential surface 20a of thedrive cylinder 5 at points P3 and P4 where line L3 meets the peripheries of theconstituent members - Local frictional forces arise at points P3 and P4 from the forces F1 and F2 between the inner
circumferential surface 20a of'drive cylinder 5 and theperipheries drive cylinder 5 relative to thelock plate 14. These local frictional forces can be determined as follows. Denoting by L4 the tangential lines of the respective peripheries of the constituent members (14c and 14d) at the intersection points P3 and P4; by L5 a line perpendicular to line L3; by L6 a line perpendicular to line L4; by θ1 and θ2 the angles (hereinafter referred to as friction angles) of lines L5 and L6 at the intersection points P3 and P4, respectively, with respect to the tangential line L4; and by µ the friction coefficient of the frictional surface, the forces acting on thedrive rotor 2 at the intersection points P3 and P4, respectively, that may cause a phase angle deviation between thedrive rotor 2 andcamshaft 6 are given by F1*sinθ1 and F2*sinθ2, respectively The local frictional forces preventing slides that may occur between the innercircumferential surface 20a and theperipheries - When the frictional forces exceed the forces that can incur a phase angle chance, the
drive cylinder 5 and thelock plate 14 are firmly secured to each other. Then, thelock plate bush 13 and the eccentric circular cam 12 (center shaft 7) are also immovably secured to each other. As a consequence, thecontrol rotor 2 andcamshaft 6 are immovably locked to each other under the external disturbing torque, thereby resulting in no relative phase change between them - In the case when the following conditions
lock plate 14 with respect to thedrive cylinder 5 exceeds the force that can cause an angular phase change, so that a self-locking function is established between them Thus, by setting the friction angles θ1 and θ2 such thatcamshaft 6 under an external disturbing torque, thereby preventing a change in phase-angle - It is noted that if' the
lock plate bush 13 having flat faces 23 and 24 is inserted between the eccentriccircular cam 12 andsupport groove 15, the contact stresses that appear on thesupport groove 15 in surface contact with thelong sides circular cam 12 is held in thesupport groove 15 with the line L2 passing through the axis L0 and L1 aligned with thelong sides lock plate bush 13 may be omitted. - Next, referring to
Fig 8 , there is shown a self-lockingmechanism 41 in accordance with a second embodiment of the invention. The self-lockingmechanism 41 has substantially the same elements as the first self-lockingmechanism 11 except thatlock plate bush 42 andlock plate 43 have different shapes from the corresponding lock plate bush and lock plate of the first embodimentA spring member 44 corresponds to the urging means ofclaim 4. - Specifically, the
lock plate bush 42 is similar in shape to thelock plate bush 13 of the first embodiment, except that thelock plate bush 42 has no flat faces like 23 or 24 In the second embodiment, thelock plate 43 is provided with aslit 46 and aslit 47 for mounting aspring member 44. Thus, theslit 47 is larger than theslit 46. Other features of thelock plate 43 are the same as those of thelock plate 14. - The
lock plate bush 42 is mounted on the eccentriccircular cam 12 that passes through thecircular hole 42a of thelock plate 42. Thelock plate bush 42 has a substantially elongaterectangular support groove 45 extending in a substantially diametrical direction Thelock plate bush 42 is divided into twoconstituent members short sides support groove 45 to the periphery of thelock plate 43 Theslit 46 has the same shape as theslit 25 of thelock plate 14 of the first embodiment, but theslit 47 differs from theslit 26 of the first embodiment in that theslit 47 has a larger width thanslit 46. - Mounted in the
slit 47 is aspring member 44, which has an arcuateconvex portion 44a andcurved portions convex portion 44a, where the width of the arcuateconvex portion 44a is larger than the that of theslit 47. Aspring member 44 provides theconstituent members slit 47 when its arcuateconvex portion 44a is fitted in theslit 47 and thecurved portions constituent members mechanism 41, any gaps introduced during manufacture between theperipheries constituent members circumferential surface 20a of thedrive cylinder 5, and between thelock plate bush 42 andsupport groove 45 are reduced, thereby reducing plays of these members, and hence improving the pressure transmission to the innercircumferential surface 20a of thelock plate 43 in self-locking action. Thus, a positive self-locking function is established. - An external disturbing torque is transmitted from the cam center L1 of the eccentric
circular cam 12 to the innercircumferential surface 20a ofdrive cylinder 5 along line L3, and generates forces F1 and F2 at the intersection points P7 and P8, which forces are transmitted from thelock plate bush 42 to the respectiveconstituent members lock plate bush 42 and the lock plateconstituent members lock plate bush 42. Further, these forces acts on the innercircumferential surface 20a of thedrive cylinder 5 at the intersection points P7 and P8 of line L3 with the peripheral surface (43c and 43d). In this case, as in the first embodiment, by setting the friction angles between the tangential lines passing through the intersection point P7 and P8 and the line perpendicular to line L3 (the friction angles corresponding to the friction angles θ1 and θ2 defined in the first embodiment) in the range a self-locking function is established between thelock plate 43 and thecylinder 20 of thedrive cylinder 5 under an external disturbing torque - It is noted that the urging means for widening the width of the
slit 47 is not limited to the 44 as shown inFig. 8 : it may alternatively be atrapezoidal member 48a and aspring member 48b as shown inFig 9(a) and (b) . As shown inFig 9(a) , thelock plate 43 has cut-awayportions slit 47. Atrapezoidal member 48a is arranged between the cut-awayportions trapezoidal member 48a is provided in the periphery thereof with arecess 48c for receiving aspring member 48b corresponding to thespring member 44. Thetrapezoidal member 48a is acted upon by a spring force exerted by thespring member 48b in the direction D7 towards the axis L0. This force will act on the faces of the cut-awayportions slit 47. - As shown in
Fig. 9(b) , a C-shapedleaf spring 49 for compressing the lock plateconstituent members slit 47 and narrow the width of theslit 46. The C-shapedleaf spring 49 is arranged such that its opening is aligned with theslit 46 between the lock plateconstituent members leaf spring 49 shown inFig. 9(b) may be fixed to the constituent member the 43b with the right half of the C-shapedleaf spring 49 while the right half portion mounted on theconstituent member 43b so that theconstituent member 43b is urged to rotate in the D2 direction relative to theconstituent member 43a. Thus, the peripheries of the lock plateconstituent members circumferential surface 20a of thedrive cylinder 5 by the C-shapedleaf spring 49. As a consequence, gaps formed between the innercircumferential surface 20a of thedrive cylinder 5 and theperipheries lock plate 43, and between alock plate bush 50 and thesupport groove 45 as well due to manufacturing errors, are reduced by the urging force of the C-shapedleaf spring 49, and so are the plays of the associated elements. - As shown in
Fig. 9(b) , thelock plate bush 50 may be split into two lock plate bushconstituent members slits lock plate bush 50 is divided, the gaps formed between theinner periphery 50e of thelock plate bush 50 and the outer periphery of the eccentriccircular 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 inFigs. 8 and9 , precision requirements for the eccentriccircular cam 12,lock plate bush 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 asupport groove 52 to theouter periphery 51a of the C-shapedobject 51 as shown inFig 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 theinner periphery 20a of thecylinder 20 so that theinner periphery 20a are constantly pushed radially outward (in the direction of d2 and d3 inFig. 10 ). In this configuration, the same self-locking function as described above in connection withFigs. 8 and9 can be obtained without the spring member - Next, referring to
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-lockingmechanism 61 has essentially the same structure as the second self-lockingmechanism 41 except that thespring member 44 is removed from thewasher 40 and that thelock plate bush 42 is replaced by alock 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 aflat face 62a/62b and steppedportion 62c/62d projecting therefrom to the right/left - The
lock plate bush 62 is mounted on the eccentriccircular cam 12 coaxially with the eccentriccircular cam 12 that passes through thecircular hole 62e of thelock plate bush 62 such that the stepped faces 63 and 64 are parallel to line L2 extending from the axis L0 toward the L1. On the other hand, the stepped faces 63 and 64 are mounted on the eccentriccircular cam 12 in a symmetric fashion with respect to line L2 and offset from the cam center L1. In other words, provided in a region of thelock plate 62 further offset from the intersection points C1 and C2 where line L3 intersects theflat faces flat faces long sides support groove 45 - As the eccentric
circular cam 12 is acted upon by a force in D2 direction or D1 direction due to an external disturbing torque, thelong sides 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 withlong sides support groove 45 at positions further offset than the cam center L1 of theeccentric camshaft 12. Furthermore, the forces F3 and F4 are transmitted from thelock plate 43 to the innercircumferential surface 20a of thedrive cylinder 5 at the intersection points P9 and P10 where line L7 intersects theouter peripheries constituent members cylinder 20 of thedrive cylinder 5 to thelock plate 43 In this case, by setting the friction angles θ1 and θ2 between the tangential lines at intersection points P9 and P10 and the line perpendicular to line L7 to satisfylock plate 43 and thecylinder 20 of thedrive cylinder 5 by an external disturbing torque - It is noted that minute gaps exist between the stepped faces 63 and 64 and the
support face 45 due to manufacturing errors. In the third embodiment, however, the stepped faces 63 and 64 are in contact with thesupport face 45 at further offset positions than the cam axis L1 of the eccentriccircular cam 12 that they exhibit less plays in the self-locking mechanism as compared with the first embodiment in which the eccentriccircular cam 12 only has non-stepped flat faces 23 and 24. This is due to the fact that, if such minute gaps exist, an external disturbing toque facilitates the flat faces to move round the axis L0 until the flat faces come into contact with thesupport groove 45, whereby the stepped faces 63 and 64 (offset from the cam center L1) are in contact with thesupport groove 15 at positions further offset from the cam center L1 than the non-stepped faces 23 and 24 of the eccentriccircular cam 12 of the first embodiment, so that the distance from the point of surface contact to the rotational axis is longer in the third embodiment than in the first embodiment As a consequence, fluctuations in phase angle caused by the gaps are more reduced in the third embodiment for a given gap than in the first embodiment. As a result, by reducing the plays involved in the self-locking mechanism, the pressure that acts on thecylinder 20 of thelock plate 43 under an external disturbing torque is enhanced, thereby securing the function of the self-locking mechanism This is true if thespring member 44 is removed from theslit 47. -
- 1
- variable cam phaser for automobile engine
- 2
- drive rotor
- 3
- first control rotor (control rotor of claim 1)
- 6
- camshaft
- 9
- torque means
- 10
- phase angle varying mechanism
- 11
- self-locking mechanism
- 12
- eccentric circular cam
- 13
- lock plate bush
- 14
- lock plate
- 14a and 14b
- lock plate constituent members
- 15
- support groove
- 16
- coupling mechanism
- 20
- cylindrical portion
- 23 & 24
- a pair of flat faces
- 25 & 26
- a pair of slits
- 27
- coupling members
- 28
- coupling holes of control rotor
- 29
- coupling holes of lock plate
- 44
- means (spring member)
- 50
- lock plate bush
- 51
- C-shape lock plate
- 53
- slit
- 63 & 64
- stepped face
- L0
- camshaft axis
- L1
- cam center of eccentric circular cam
Claims (8)
- A variable cam phaser for an automobile engine including:a drive rotor driven by the crankshaft of the engine;a control rotor;a camshaft coaxial with the drive rotor and adapted to rotatably support the drive rotor;a torque means for providing the control rotor with a torque for rotating the control rotor relative to the drive rotor;a phase angle varying mechanism for varying the relative phase angle between the drive rotor and the control rotor in accord with the relative rotation of the control rotor relative to the drive rotor; and a self-locking mechanism mounted in the phase varying mechanism for preventing a phase change from occurring between the drive rotor and the camshaft caused by an unexpected cam torque appearing on the camshaft, the variable cam phaser characterized in that the self-locking mechanism comprises:an eccentric circular cam integral with the camshaft; anda lock plate having
a support groove for supporting, at positions further offset from the camshaft axis in the direction (referred to as eccentric direction) from the camshaft axis towards the cam center of the eccentric circular cam, the periphery of the eccentric circular cam from both sides thereof,
a coupling mechanism for transmitting the relative rotational torque from the control rotor to the eccentric circular cam, anda cylindrical body formed integral with the drive rotor and circumscribing the periphery of the lock plate - The variable cam phaser according to claim 1, wherein
the support groove extends in a radial direction of the lock plate;
the eccentric circular cam is provided on the outer periphery thereof with a lock plate bush; and
the lock plate bush has on the opposite sides of the outer periphery thereof a pair of flat faces spaced apart across the line of eccentric direction and supported by the support groove - The variable cam phaser according to claim 2, wherein 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
- The variable cam phaser according to claim 3, wherein one of the two slits may be provided with urging means for providing a force to widen that slit.
- The variable cam phaser according to claim 2, wherein
the lock plate is provided with two slits extending from the support groove to the periphery of the lock plate; and
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 variable cam phaser according to claim 4 or 5, wherein the lock plate bush is divided into two parts by a pair of' slits
- The variable cam phaser according to any one claims 3 through 6, wherein
the flat faces of the lock plate bush are a pair of stepped faces projecting to the right and left to the line of eccentric direction; and
the stepped faces are offset in the eccentric direction away from the cam center towards the eccentric axis of the cam center. - The variable cam phaser according to any one of' claims 3 through 7, wherein
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
a minute clearance is provided between each coupling member and an associated coupling hole of either the control rotor or the lock plate.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2010/058370 WO2011145175A1 (en) | 2010-05-18 | 2010-05-18 | Phase variable device for engine |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2573336A1 true EP2573336A1 (en) | 2013-03-27 |
EP2573336A4 EP2573336A4 (en) | 2013-12-18 |
EP2573336B1 EP2573336B1 (en) | 2015-03-04 |
Family
ID=44991299
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10851739.2A Not-in-force EP2573336B1 (en) | 2010-05-18 | 2010-05-18 | Phase variable device for engine |
Country Status (6)
Country | Link |
---|---|
US (1) | US20130125846A1 (en) |
EP (1) | EP2573336B1 (en) |
JP (1) | JP5616440B2 (en) |
KR (1) | KR20130072190A (en) |
CN (1) | CN102859126A (en) |
WO (1) | WO2011145175A1 (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100256451A1 (en) | 2007-08-27 | 2010-10-07 | Aircraft Medical Limited | Laryngoscope insertion section |
US8726867B2 (en) | 2010-10-12 | 2014-05-20 | Nittan Valve Co., Ltd. | Phase varying apparatus for automobile engine technical |
WO2013157110A1 (en) * | 2012-04-19 | 2013-10-24 | 日鍛バルブ株式会社 | Engine variable phase device |
WO2013157131A1 (en) * | 2012-04-20 | 2013-10-24 | 日鍛バルブ株式会社 | Engine variable phase device |
EP2910744A1 (en) | 2012-10-09 | 2015-08-26 | Nittan Valve Co., Ltd. | Automotive engine phase-adjusting device |
JP6029691B2 (en) * | 2013-01-11 | 2016-11-24 | 日鍛バルブ株式会社 | Phase change device for automotive engine |
DE112016005069T5 (en) * | 2015-12-02 | 2018-07-12 | Borgwarner Inc. | DIVIDED EXHAUST GAS TURBOCHARGER |
Citations (3)
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WO2009098752A1 (en) * | 2008-02-04 | 2009-08-13 | Nittan, Valve, Co., Ltd. | Phase variable device in car engine |
WO2010026645A1 (en) * | 2008-09-05 | 2010-03-11 | 日鍛バルブ株式会社 | Cam shaft phase variable device in engine for automobile |
WO2010046974A1 (en) * | 2008-10-22 | 2010-04-29 | 日鍛バルブ株式会社 | Cam shaft phase variable device in engine for automobile |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2003129805A (en) * | 2001-10-22 | 2003-05-08 | Hitachi Unisia Automotive Ltd | Valve timing control device for internal combustion engine |
JP3937164B2 (en) * | 2002-04-19 | 2007-06-27 | 株式会社デンソー | Valve timing adjustment device |
JP5102071B2 (en) * | 2008-03-03 | 2012-12-19 | 日鍛バルブ株式会社 | Phase variable device for automobile engine |
KR20140073595A (en) * | 2009-06-05 | 2014-06-17 | 니탄 밸브 가부시키가이샤 | Phase changing device for engine |
US8726867B2 (en) * | 2010-10-12 | 2014-05-20 | Nittan Valve Co., Ltd. | Phase varying apparatus for automobile engine technical |
-
2010
- 2010-05-18 US US13/697,908 patent/US20130125846A1/en not_active Abandoned
- 2010-05-18 KR KR1020127024883A patent/KR20130072190A/en not_active Application Discontinuation
- 2010-05-18 JP JP2012515663A patent/JP5616440B2/en not_active Expired - Fee Related
- 2010-05-18 WO PCT/JP2010/058370 patent/WO2011145175A1/en active Application Filing
- 2010-05-18 CN CN2010800664074A patent/CN102859126A/en active Pending
- 2010-05-18 EP EP10851739.2A patent/EP2573336B1/en not_active Not-in-force
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2009098752A1 (en) * | 2008-02-04 | 2009-08-13 | Nittan, Valve, Co., Ltd. | Phase variable device in car engine |
EP2249000A1 (en) * | 2008-02-04 | 2010-11-10 | Nittan Valve Co., Ltd. | Phase variable device in car engine |
WO2010026645A1 (en) * | 2008-09-05 | 2010-03-11 | 日鍛バルブ株式会社 | Cam shaft phase variable device in engine for automobile |
EP2320036A1 (en) * | 2008-09-05 | 2011-05-11 | Nittan Valve Co., Ltd. | Cam shaft phase variable device in engine for automobile |
WO2010046974A1 (en) * | 2008-10-22 | 2010-04-29 | 日鍛バルブ株式会社 | Cam shaft phase variable device in engine for automobile |
EP2341222A1 (en) * | 2008-10-22 | 2011-07-06 | Nittan Valve Co., Ltd. | Cam shaft phase variable device in engine for automobile |
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Title |
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Also Published As
Publication number | Publication date |
---|---|
US20130125846A1 (en) | 2013-05-23 |
JPWO2011145175A1 (en) | 2013-07-22 |
KR20130072190A (en) | 2013-07-01 |
EP2573336A4 (en) | 2013-12-18 |
CN102859126A (en) | 2013-01-02 |
EP2573336B1 (en) | 2015-03-04 |
WO2011145175A1 (en) | 2011-11-24 |
JP5616440B2 (en) | 2014-10-29 |
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