WO2011145175A1 - エンジンの位相可変装置 - Google Patents

エンジンの位相可変装置 Download PDF

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Publication number
WO2011145175A1
WO2011145175A1 PCT/JP2010/058370 JP2010058370W WO2011145175A1 WO 2011145175 A1 WO2011145175 A1 WO 2011145175A1 JP 2010058370 W JP2010058370 W JP 2010058370W WO 2011145175 A1 WO2011145175 A1 WO 2011145175A1
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WO
WIPO (PCT)
Prior art keywords
lock plate
camshaft
eccentric
engine
rotator
Prior art date
Application number
PCT/JP2010/058370
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
美千広 亀田
真康 永洞
正昭 新納
Original Assignee
日鍛バルブ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日鍛バルブ株式会社 filed Critical 日鍛バルブ株式会社
Priority to CN2010800664074A priority Critical patent/CN102859126A/zh
Priority to PCT/JP2010/058370 priority patent/WO2011145175A1/ja
Priority to US13/697,908 priority patent/US20130125846A1/en
Priority to JP2012515663A priority patent/JP5616440B2/ja
Priority to KR1020127024883A priority patent/KR20130072190A/ko
Priority to EP10851739.2A priority patent/EP2573336B1/en
Publication of WO2011145175A1 publication Critical patent/WO2011145175A1/ja

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

  • the present invention provides a self-locking mechanism that prevents the assembly angle from being displaced due to disturbance torque from the valve side in a phase variable mechanism that changes the opening / closing timing of the valve by changing the assembly angle (relative phase angle) of the crankshaft and camshaft.
  • the present invention relates to a phase varying device for an automobile engine provided with a mechanism.
  • variable phase mechanism that changes the valve opening and closing timing by changing the assembly angle (relative phase angle) of the crankshaft and camshaft
  • a self-locking mechanism is provided to prevent the assembly angle from being displaced due to disturbance torque from the valve side.
  • Japanese Patent Application Laid-Open Publication No. 2004-228688 discloses an engine phase varying device.
  • the device disclosed in Patent Document 1 below includes a plurality of eccentric circular members (eccentric circular cam 110, first link 111, second link 112) provided continuously at predetermined positions around the camshaft central axis. Constitutes a four-joint link mechanism 108 that operates like a four-joint link, and this four-joint link mechanism 108 is braked by the first or second electromagnetic clutch (105, 106). 102, 103), the assembly angle of the drive rotating body 101 operated by the camshaft and the crankshaft is changed.
  • the four-joint link mechanism 108 is supported by an eccentric circular cam 110 integrated with the camshaft, a first link 111 supported by the eccentric circular cam 110 so as to be eccentrically rotatable, and supported by the first link 111 so as to be eccentrically rotatable.
  • the second link 112 rotates eccentrically around each support shaft in conjunction with the braking of either the first or second control rotor (102, 103), and the camshaft and crankshaft (drive rotation)
  • the relative phase angle of the body 101) is changed to either the advance side or the retard side.
  • the engine phase varying device disclosed in Patent Document 1 includes a self-locking mechanism that prevents the camshaft and crankshaft from being misaligned due to disturbance torque.
  • the self-locking mechanism provided in the engine phase varying device of Patent Document 1 is configured through the four-bar linkage mechanism 108, and the self-locking structure must be realized while maintaining the operation accuracy of the four-bar linkage mechanism 108. Therefore, from the viewpoint of realizing the self-locking mechanism, it can be said that the structure is complicated and the manufacturing cost is high, so it is desirable to realize a simpler self-locking mechanism.
  • the engine phase varying device of the present application provides an engine phase varying device having a simpler configuration and having a self-locking mechanism that is easily and inexpensively realized.
  • an engine phase varying device comprising: a drive rotator driven by a crankshaft; a control rotator; a camshaft supporting the drive rotator coaxially and relatively rotatably; and a relative to the drive rotator.
  • a rotation operation force applying means for applying a rotation torque to the control rotator, and an assembly for changing an assembly angle of the camshaft and the drive rotator according to a relative rotation of the control rotator with respect to the drive rotator.
  • An engine phase variable device comprising: an angle changing mechanism; and a self-locking mechanism that is provided in the assembly angle changing mechanism and prevents a drive rotating body and a cam shaft from being misaligned due to cam torque.
  • the locking mechanism includes an eccentric circular cam integrated with the camshaft and the camshaft in an eccentric direction from the center of the camshaft toward the camcenter of the eccentric circular cam.
  • a lock plate having a holding groove that holds the outer periphery of the eccentric circular cam from both sides on the eccentric side from the center, and a coupling mechanism that transmits the relative rotational torque from the control rotating body to the eccentric circular cam;
  • a cylindrical portion that is integrally formed with the drive rotator and that inscribes the outer periphery of the lock plate.
  • the engine phase varying device according to the first aspect, wherein the holding groove is formed by extending in the radial direction of the lock plate, and the lock plate bush attached to the outer periphery of the eccentric circular cam is provided.
  • the lock plate bush has a pair of flat surfaces provided on the left and right sides of the eccentric direction and sandwiched between the holding grooves on the outer periphery.
  • the eccentric circular cam is directly in line contact with the holding groove by holding the eccentric circular cam in the holding groove through the lock plate bush and bringing the lock plate bush into surface contact with the holding groove through a pair of flat surfaces. Since the contact stress generated in the holding groove is reduced as compared with the case where the contact is made, uneven wear does not occur at the contact portion, and the lock plate and the eccentric circular cam are held without rattling. As a result of preventing the rattling, the pressing force of the lock plate to the drive rotating body cylindrical portion at the time of occurrence of the disturbance is instantly and reliably generated.
  • claim 3 is the engine phase varying device according to claim 2, wherein the lock plate is divided into two by a pair of slits formed from the holding groove toward the outer peripheral surface of the lock plate.
  • a biasing force in a direction of expanding the width of the slit is applied to one of the slits to the lock plate divided into two.
  • a biasing means was provided.
  • the lock plate is provided with a slit that opens from the holding groove toward the outer peripheral surface of the lock plate, and the eccentric direction is changed.
  • the lock plate is formed slightly larger in length than the inner diameter of the cylindrical portion that inscribes the outer diameter of the lock plate on both the left and right sides.
  • the lock plate has an outer diameter slightly larger than the inner diameter of the cylindrical portion, and is inscribed in a state where it receives an inward biasing force from the cylindrical portion.
  • the gap between the lock plate and the cylindrical portion of the drive rotator, and the gap between the lock plate bush and the holding groove, which are generated due to manufacturing errors or the like, become smaller. That is, according to this configuration, the backlash of each member at the time of occurrence of self-locking is reduced as in the fourth aspect, and the pressing force to the drive rotating body cylindrical portion of the lock plate at the time of occurrence of disturbance is instantaneously generated. I can do it.
  • claim 6 is the engine phase varying device according to claim 4 or 5, wherein the lock plate bush is divided into two by a pair of slits.
  • a seventh aspect of the present invention is the engine phase varying device according to any one of the second to sixth aspects, wherein the pair of flat surfaces of the lock plate bush protrudes left and right across the eccentric direction. Stepped surfaces were provided, and the pair of stepped surfaces were provided more eccentrically than the cam center of the eccentric circular cam in the eccentric direction.
  • An eighth aspect of the present invention is the engine phase varying device according to any one of the first to seventh aspects, wherein the coupling mechanism includes a pair of coupling holes respectively provided in the control rotating body and a lock plate, It is formed by a connecting member that engages with both of the connecting holes, and a slight clearance is formed between the connecting member on either the control rotating body side or the lock plate side and the connecting member.
  • the coupling mechanism includes a pair of coupling holes respectively provided in the control rotating body and a lock plate, It is formed by a connecting member that engages with both of the connecting holes, and a slight clearance is formed between the connecting member on either the control rotating body side or the lock plate side and the connecting member.
  • a self-locking mechanism can be provided easily and inexpensively by realizing a simpler structure than the conventional one, that is, the cylindrical portion of the drive rotating body, the disk-shaped lock plate, and the holding groove. I can do it.
  • the durability of the self-locking mechanism is improved and the self-locking function is more reliably exhibited.
  • the self-locking function is more reliably exhibited.
  • FIG. 4 is a cross-sectional view taken along line AA in FIG. 3.
  • FIG. 5 is a cross-sectional view taken along line EE in FIG. 4.
  • A) It is BB sectional drawing of FIG.
  • B) It is CC sectional drawing of FIG.
  • C) It is DD sectional drawing of FIG. It is explanatory drawing of the self-locking mechanism of 1st Example.
  • FIG. 9 is a cross-sectional view of a portion corresponding to EE in FIG.
  • FIG. 10 is a cross-sectional view of a portion corresponding to EE in FIG. 4 showing a third embodiment of the self-locking mechanism.
  • the engine phase varying device shown in each embodiment is assembled to the engine, transmits the rotation of the crankshaft to the camshaft so that the intake and exhaust valves open and close in synchronization with the rotation of the crankshaft,
  • This is a device for changing the opening / closing timing of the intake / exhaust valve of the engine according to the operating state such as the rotational speed.
  • the engine phase varying device 1 includes a drive rotator 2 driven and rotated by a crankshaft, a first control rotator 3 (a control rotator according to claim 1), a camshaft 6 (FIG. 4), and a rotation.
  • the operation force applying means 9, the assembly angle changing mechanism 10, and the self-locking mechanism 11 are configured.
  • the second electromagnetic clutch side in FIG. the rotation direction of the drive rotating body 2 around the camshaft central axis L0 viewed from the front of the apparatus will be described as the advance side D1 direction (clockwise), and the direction opposite to D1 as the retard side D2 direction (counterclockwise). .
  • the drive rotator 2 is formed by integrating a sprocket 4 receiving a driving force from a crankshaft and a drive cylinder 5 having a cylindrical portion 20 by a plurality of bolts 2a.
  • the camshaft 6 shown in FIG. 4 is integrated with the rear end side of the center shaft 7 coaxially and relatively unrotatably by inserting a bolt 37 into the central circular hole 7e of the center shaft 7 and the female screw hole 6a in front of the camshaft. It has become.
  • the first control rotator 3 has a bottomed cylindrical shape in which a flange portion 3a at the front edge, a cylindrical portion 3b continuous to the rear, and a bottom portion 3c are continuous.
  • the bottom 3c has a central through-hole 3d, a pair of pin holes 28, a circumferential groove 30 provided on a circumference having a predetermined radius from the central axis L0, and a distance from the central axis L0 to the groove. It has a curvilinear diameter-reduced guide groove 31 that decreases in the direction of the side D1.
  • the center shaft 7 includes a first cylindrical portion 7a, a flange portion 7b, a second cylindrical portion 7c, an eccentric circular cam 12 having a cam center L1 eccentric from the cam shaft central axis L0, and a third cylindrical portion 7d from the rear side to the front side. It is formed continuously in the axial direction toward the second control rotator in FIG. 1 (the same applies hereinafter).
  • the drive rotator 2 is configured such that the sprocket 4 integrated with the bolt 2a and the drive cylinder 5 sandwich the flange portion 7b, and the first and second cylinder portions (7a) via the circular holes (4a, 5a).
  • the drive rotator 2, the first control rotator 3, the camshaft 6, and the center shaft 7 are coaxially disposed on the center axis L0.
  • the rotation operation force applying means 9 brakes the first control rotator 3 and applies a relative rotation torque to the drive rotator 2.
  • the first electromagnetic clutch 21 is applied to the first control rotator 3.
  • a reverse rotation mechanism 22 that applies a relative rotation torque in the opposite direction.
  • the assembly angle changing mechanism 10 is a mechanism that unifies the camshaft 6 and the control rotator 3 so that they cannot be rotated relative to each other, and a center shaft 7 that supports the drive rotator 2 so as to be relatively rotatable, and a self-locking mechanism. 11 and the coupling mechanism 16.
  • the self-locking mechanism 11 is interposed between the drive rotator 2 and the center shaft 7, and the drive rotator 2 and the camshaft 6 are assembled due to disturbance torque received by a camshaft 6 from a valve spring (not shown).
  • This mechanism prevents the occurrence of angular misalignment, and is constituted by the eccentric circular cam 12 of the center shaft 7, the lock plate bush 13, the lock plate 14, and the cylindrical portion 20 of the drive rotating body 2.
  • the lock plate bush 13 has a circular hole 13a to be engaged with the eccentric circular cam 12 of the center shaft 7, and has a pair of flat surfaces (23, 24) at both ends of the outer periphery.
  • the plane (23, 24) is substantially parallel to a straight line L2 (hereinafter the same; hereinafter, simply referred to as a straight line L2) connecting the camshaft center axis L0 and the cam center L1. It is pivotally mounted.
  • the lock plate 14 is formed in a disk shape as a whole and has a substantially rectangular holding groove 15 extending in the radial direction.
  • the lock plate 14 has a pair of constituent members (14a) equally divided by a pair of slits (25, 26) extending linearly from the short surfaces (15a, 15b) of the holding groove 15 toward the outer periphery of the lock plate 14. , 14b).
  • the flat surfaces (23, 24) of the lock plate bush 13 are held in contact with the long surfaces (15c, 15d) of the holding groove 15, respectively.
  • the lock plate 14 has a long surface (15c, 15d) of the holding groove 15 sandwiching the flat surface (23, 24) of the lock plate bush 13 and an outer peripheral surface (14c, 14d) of the cylindrical portion 20 of the drive cylinder 5.
  • the outer circumference of the eccentric circular cam 12 is further eccentric than the straight line L3 (hereinafter the same, hereinafter simply referred to as the straight line L3) perpendicular to the straight line L2 at the cam center L1 (the direction further decentered beyond L0 to L1). ) Is held in the holding groove 15 of the lock plate 14 via the lock plate bush 13.
  • the connection mechanism 16 includes a pair of connection pins (27, 27), a pair of first pin holes (28, 28) provided in the bottom 3b of the control rotator 3, and a component (14a) of the lock plate 14. , 14b) and second pin holes (29, 29) respectively.
  • the connecting pin 27 is fitted and fixed to one of the first pin hole 28 and the second pin hole 29, and is inserted in a state where a minute gap is defined between the other.
  • the lock plate 14 is pressed against the inner peripheral surface 20a of the cylindrical portion 20 of the drive cylinder 5 by the self-lock mechanism 11 described later when disturbance torque is generated, and is held so as not to be relatively rotatable.
  • the minute gap provided in either one of the first and second pin holes (27, 28) for inserting the continuous pin 27 has a lock plate 14 fixed to the first control rotator 3 due to a manufacturing error. It is provided to alleviate the phenomenon that it is difficult to be pressed against the surface 20a.
  • the lock plate 14 that is inscribed in the cylindrical portion 20 of the drive cylinder 5 while sandwiching the lock plate bush 13 is controlled to rotate by inserting the connecting pin 27 into the first and second pin holes (28, 29). It is integrated with the body 3 so that it cannot rotate relative to the body 3. As a result, the center shaft 7 (cam shaft 6) is integrated with the control rotating body 3 through the eccentric circular cam 12, the lock plate bush 13 and the lock plate 14 so as not to be relatively rotatable.
  • the camshaft 6 is integrated with the control rotator 3 that receives torque from the turning operation force applying means 9 and is relative to the drive rotator 2 in either the advance side D1 direction or the retard side D2 direction. Rotate. As a result, the assembly angle between the camshaft 6 and the drive rotator 2 (a crankshaft not shown) is changed, and the opening / closing timing of the valve is changed.
  • the first electromagnetic clutch 21 is fixed inside the engine (not shown) and disposed in front of the first control rotator 3.
  • the first control rotator 3 causes a rotation delay with respect to the drive rotator 2 rotating in the direction D1 by adsorbing the front surface 3e of the flange portion 3a to the friction material 21a of the first electromagnetic clutch 21.
  • the reverse rotation mechanism 22 brakes the circumferential groove 30 and the reduced diameter guide groove 31, the second control rotation body 32, the disk-shaped pin guide plate 33, and the second control rotation body 32 of the first control rotation body 3.
  • the second electromagnetic clutch 38, the first and second link pins (34, 35), and the ring member 36 are configured.
  • the second control rotator 32 is disposed inside the cylindrical portion 3b of the first control rotator 3, and is connected to the third cylindrical portion 7d of the center shaft 7 through a through-hole 32a provided around the central axis L0. It is rotatably supported. Further, the second control rotator 32 has a stepped eccentric circular hole 32b whose center O1 is eccentric from the camshaft central axis L0 on the rear side, and the ring member 36 is slidably rotatable in the eccentric circular hole 32b. Inscribed.
  • the disc-shaped pin guide plate 33 is disposed between the bottom 3c and the second control rotator 32 inside the cylindrical portion 3b of the first control rotator 3, and is centered through a through-hole 33a in the center. 7 is rotatably supported by the third cylindrical portion 7d.
  • the pin guide plate 33 includes a substantially radial groove 33b and a substantially radial guide groove 33c that extend in a substantially radial direction from a position not connected to the through-hole 33a.
  • the substantially radial groove 33 b is formed to penetrate from the vicinity of the through-hole 33 a to the outer peripheral edge at a position corresponding to the circumferential groove 30, and the substantially radial guide groove 33 c is formed at a position corresponding to the reduced diameter guide groove 31. It is formed in an oval shape to the vicinity of the outer peripheral edge.
  • the first link pin 34 is formed by a narrow round shaft 34a and a hollow thick round shaft 34b integrally engaged with the front end of the narrow round shaft 34a.
  • the hollow round shaft 34b is sandwiched from both sides by a substantially radial groove 33b, and the rear end of the thin round shaft 34a is inserted into the circumferential groove 30 and the holding groove 15 and into the mounting hole 5b of the drive cylinder 5. Fixed. Further, the narrow round shaft 34a moves at both ends of the circumferential groove 30 along the groove direction.
  • the second link pin 35 is formed by a first member 35c, a hollow first shaft 35d, a hollow second shaft 35e, and a hollow third shaft 35f, in which a thick circular shaft 35b is integrally formed at the rear end of the thin circular shaft 35a.
  • the hollow first shaft to the hollow third shaft (35d to 35f) are inserted into the thin circular shaft 35a in order toward the thick circular shaft 35b and are prevented from coming off backward.
  • the thick round shaft 35 b is inserted into the holding groove 15.
  • the hollow first shaft 35 d has an arc shape whose outer peripheral shape is along the reduced diameter guide groove 31. The hollow first shaft 35 d is held up and down by the reduced diameter guide groove 31 and moves along the reduced diameter guide groove 31.
  • the hollow second shaft 35e has a cylindrical shape, is held on both sides by the substantially radial guide groove 33c, and moves along the substantially radial guide groove 33c.
  • the hollow third shaft 35f has a cylindrical shape and is rotatably connected to the circular hole 36a of the ring member 36.
  • a holder 39 and a washer 40 having a circular hole (39a, 40a) in the center are disposed from the front at the tip of the third cylindrical portion 7d of the center shaft 7, and the holder 39, washer 40 and center shaft 7 are circular.
  • the bolts 37 inserted into the holes (39a, 40a) and the circular hole 7e are attached to the female screw hole 6a, thereby being fixed to the camshaft 6 so as not to be relatively rotatable.
  • the parts from the drive rotator 2 of FIG. 4 arranged on the outer periphery of the center shaft 7 to the second control rotator 2 are secured between the flange portion 6b of the camshaft 6 and the holder 39, and are secured.
  • a cover 70 is disposed in front of the bolt and the first and second electromagnetic clutches (21, 38).
  • the operation of changing the assembly angle between the camshaft 6 and the drive rotator 2 (crankshaft not shown) by the turning operation force applying means 9 will be described.
  • the first control rotator 3 is rotated integrally with the drive rotator 2 in the direction D1 (see FIG. 6C).
  • the center shaft 7 (camshaft 6) rotates together with the integrated first control rotator 3 in the direction D1. 2 causes a rotational delay in the direction D2.
  • the assembly angle of the camshaft 6 with respect to the drive rotator 2 (crankshaft not shown) is changed in the direction of the retard side D2, and the opening / closing timing of a valve not shown changes.
  • the hollow first shaft 35d of the second link pin 35 shown in FIG. 6 (c) moves in the direction D3 which is substantially clockwise in the reduced diameter guide groove 31, and the hollow second shaft shown in FIG. 6 (b).
  • the shaft 35e moves in the direction D4 in the substantially radial guide groove 33c toward the central axis L0
  • the hollow third shaft 35f in FIG. 6A is a sliding rotation torque in the circular hole 32b in the ring member 36. Is granted.
  • the fine round shaft 34a of the first link pin 34 moves in the circumferential direction groove 30 in the clockwise direction D1.
  • both ends (30a, 30b) of the circumferential groove 30 act as stoppers against which the moved fine round shaft 34a abuts.
  • the second control rotator 32 normally rotates in the direction D1 together with the drive rotator 2 (FIG. 6A).
  • the front surface 32c of the second control rotator 32 is adsorbed by the friction material 38a, causing a rotation delay in the direction D2 with respect to the first control rotator 3.
  • the ring member 36 in FIG. 6A slides and rotates in the eccentric circular hole 32b when the inscribed eccentric circular hole 32b rotates eccentrically in the direction D2.
  • the hollow second shaft 35e shown in FIG. 6B moves in the outer circumferential direction D5 along the substantially radial guide groove 33c together with the hollow third shaft 35f and the hollow first shaft 35d by the operation of the link member 36.
  • the first control rotating body 3 in FIG. 6C is a hollow first shaft that moves in the reduced-diameter groove 31 in the substantially counterclockwise direction D6, contrary to the operation of the first electromagnetic clutch 21.
  • the relative rotation torque in the advance side D1 direction is received from 35d via the diameter-reduced groove 31, and the relative rotation torque further rotates in the advance side D1 direction with respect to the drive rotating body 2 rotating in the D1 direction.
  • the assembly angle of the camshaft 6 with respect to the drive rotor 2 (a crankshaft not shown) is returned to the advance side D1, and the opening / closing timing of a valve (not shown) changes.
  • the assembly angle of the center shaft 7 (camshaft 6) and the drive rotator 2 (crankshaft not shown) is set so that the control rotator 3 is advanced with respect to the drive rotator 2 by the turning operation force applying means 9 as described above. It is determined by relative rotation in either the corner side D1 direction or the retard side D2 direction.
  • disturbance torque due to reaction is input to the camshaft 6 from a valve spring (not shown)
  • the assembly angle shifts between the camshaft 6 and the drive rotor 2 due to the disturbance torque Unexpected deviation occurs in the valve opening and closing timing.
  • the self-locking mechanism 11 of the present embodiment prevents the assembly angle from shifting by reversing the generation of the disturbance torque.
  • FIG. 7 shows the outer peripheral surface (14c, 14d) of the lock plate 14 and the drive cylinder 5 when a disturbance torque is generated in the cam shaft 6 (center shaft 7) in either the clockwise direction D1 or the counterclockwise direction D2. A force acting between the inner peripheral surface of the cylindrical portion 20 and a self-locking action are shown.
  • the eccentric circular cam 12 When the camshaft 6 and the center shaft 7 receive disturbance torque in the retarding side D2 direction or the advance side D1 direction, the eccentric circular cam 12 is eccentric so that the cam center L1 tends to rotate eccentrically around the camshaft center axis L0. A rotational torque is received in the direction D2 or D1.
  • the cam center axis L1 is decentered by a distance s from the camshaft center axis L0.
  • a straight line connecting L0 and L1 is L2
  • a straight line passing through L1 and perpendicular to L2 is L3.
  • the force (F1, F2) is transmitted from the lock plate bush 13 to the lock plate 14 via the planes (23, 24) in surface contact with each other and the long surfaces (15c, 15d) of the holding groove 15 on the straight line L3. Is done. Further, the force (F1, F2) is generated from the lock plate 14 to the inside of the cylindrical portion of the drive cylinder 5 at the intersection (P3, P4) between the straight line L3 and the outer peripheral surfaces (14c, 14d) of the lock plate constituent members (14a, 14b). It is transmitted to the peripheral surface 20a.
  • the straight lines passing through the intersections P3 and P4 and extending in the tangential direction of the outer peripheral surfaces (14c, 14d) of the lock plate are L4, the straight line orthogonal to L3 is L5, the straight line orthogonal to the straight line L4 is L6, and the straight line L4 And L5 and the slopes of the straight lines L3 and L6 are ⁇ 1 at the intersection P3, ⁇ 2 at the intersection P4 (hereinafter, ⁇ 1 and ⁇ 2 are referred to as friction angles), and the friction coefficient of the friction surface is ⁇ .
  • the forces that cause the assembly angle deviation between the body 2 and the camshaft 6 are represented by tangential forces F1 ⁇ sin ⁇ 1 and F2 ⁇ sin ⁇ 2 at the intersections P3 and P4, respectively.
  • the local frictional forces in the reverse direction that prevent sliding between the cylindrical inner peripheral surface 20a and the outer peripheral surfaces (14c, 14d) of the lock plate 14 are represented by ⁇ ⁇ F1 ⁇ cos ⁇ 1 and ⁇ ⁇ F2 ⁇ cos ⁇ 2, respectively.
  • the drive cylinder 5 and the lock plate 14 are held so as not to rotate relative to each other.
  • the lock plate bush 13 and the eccentric circular cam 12 (center shaft 7) are also held so as not to rotate relative to the drive cylinder 5.
  • the drive rotator 2 and the camshaft 6 are locked so that they cannot rotate relative to each other due to the generation of disturbance torque, and there is a misalignment between the camshaft 6 and the control rotator 2 (crankshaft). Does not occur.
  • the self-locking mechanism 41 of the second embodiment is different from the self-locking mechanism 11 of the first embodiment except that the shapes of the lock plate bush 42 and the lock plate 43 are different and include a spring member 44 (biasing means of claim 4). Have a common configuration.
  • the shape of the lock plate bush 42 of the second embodiment is the same as that of the lock plate bush 13 of the first embodiment, except that it has a ring shape in which no plane (23, 24) is provided.
  • the lock plate 43 of the second embodiment has the same shape as the lock plate 14 of the embodiment except that the slit 47 is formed larger than the slit 46 for mounting the spring member 44.
  • the ring-shaped lock plate bush 42 is attached to the eccentric circular cam 12 through a circular hole 42a.
  • the disc-shaped lock plate bush 42 has a substantially rectangular holding groove 45 extending in the radial direction.
  • the lock plate bushing 42 is a pair of constituent members equally divided by a pair of slits (46, 47) extending linearly from the short surfaces (45a, 45b) of the holding groove 45 toward the outer periphery of the lock plate 43. 43a, 43b).
  • the slit 46 has the same shape as the slit 25 of the lock plate 14 of the first embodiment, but the slit 47 is different from the slit 26 of the first embodiment because it is wider than the slit 46.
  • a spring member 44 is attached to the slit 47.
  • the spring member 44 has a shape in which return portions (44b, 44c) bent outward are provided at both ends of the arc-shaped convex portion 44a.
  • the width of the arc-shaped convex portion 44a is formed to be larger than the width of the slit 47.
  • the In the spring member 44 the arc-shaped convex portion 44a is fitted into the slit 47, and the return portions (44b, 44c) hold the outer peripheral surfaces (43c, 43d) of the constituent members (43a, 43b), thereby making the slit 47 wide.
  • a biasing force that pushes and expands in the direction is applied to the constituent members (43a, 43b).
  • the forces (F1, F2) transmitted from the cam center L1 of the eccentric circular cam 12 along the straight line L3 to the cylindrical inner peripheral surface 20a of the drive cylinder 5 due to the disturbance torque are the straight line L3 and the outer periphery of the lock plate bush 42.
  • the friction angle corresponding to ( ⁇ 1, ⁇ 2) of the first embodiment formed between a line extending in the tangential direction from the intersection (P7, P8) and a line orthogonal to the straight line L3 is set to the first embodiment.
  • a self-locking function by disturbance torque is constructed between the lock plate 43 and the cylindrical portion 20 of the drive cylinder 5. .
  • the urging means for pushing and expanding the slit 47 in the width direction may be the one shown in FIGS. 9A and 9B in addition to providing the spring member 44 as shown in FIG. That is, in FIG. 9A, notches (47a, 47b) that are notched in a tapered shape toward the camshaft central axis L0 direction are provided at the outer peripheral end of the slit 47, and the notches (47a 47b) is provided with a trapezoidal member 48a.
  • the trapezoidal member 48a has an attachment portion 48c of a spring member 48b having a shape corresponding to the spring member 44 on the outer peripheral side, receives a biasing force in the direction D7 from the attached spring member 48b toward the central axis L0, and is cut out ( The slit 47 is pushed and expanded by applying a force perpendicular to the surfaces 47a and 47b).
  • the slit 47 is expanded in the width direction by disposing the C-shaped leaf spring member 49 along the outer periphery of the lock plate constituent members (43a, 43b).
  • the lock plate constituent members (43a, 43b) are biased in the direction of narrowing the width of the lock plate.
  • the leaf spring member 49 is disposed so that the C-shaped opening corresponds to the slit 46 with respect to the lock plate constituent members (43a, 43b).
  • the leaf spring member 49 fixes the left half of FIG. 9B to the component member 43a, and the component member 43b to which the right half is attached receives an urging torque in a substantially D2 direction with respect to the component member 43a. What should I do?
  • the outer peripheral surfaces (43c, 43d) of the lock plate constituting members (43a, 43b) are urged toward the cylindrical portion inner peripheral surface 20a of the drive cylinder 5 by the leaf spring member 49.
  • a gap due to a manufacturing error or the like formed between the cylindrical portion inner peripheral surface 20a of the drive cylinder 5 and the outer peripheral surface (43c, 43d) of the lock plate 43 and between the lock plate bush 50 and the holding groove 45 is as follows. Since it is reduced by the urging force of the leaf spring member 49 and rattling is reduced, a reliable self-locking action occurs.
  • the lock plate bush is formed by lock plate bush constituent members (50a, 50b) equally divided by slits (50c, 50d) arranged on an extension line of the straight line L2. It may be configured.
  • the lock plate bush is divided, a gap due to a manufacturing error or the like formed between the inner peripheral surface 50e of the lock plate bush 50 and the outer periphery of the eccentric circular cam 12 is further reduced. A certain self-locking action occurs.
  • the biasing means such as the spring member 44 shown in FIGS. 8 and 9 is provided, rattling due to manufacturing error can be reduced by the biasing force, so that the eccentric circular cam 12, the lock plate bush (42, 50), the lock The dimensional accuracy of the plate 43 can be relaxed and manufactured at low cost.
  • the lock plate is formed in a substantially C shape (reference numeral 51) provided with a slit 53 that opens from the holding groove 52 to the outer peripheral surface 51a of the lock plate 51 only at one location.
  • the outer diameter of 51 in the left-right direction is slightly larger than the inner diameter of the inner peripheral surface 20a of the cylindrical portion 20, so that the inner peripheral surface 20a (the left-right d2 and d3 directions in FIG. 10). It may be assembled so as to always urge the force. In that case, the same effect can be obtained while omitting the spring members as shown in FIGS.
  • the self-locking mechanism 61 of the third embodiment the spring member 44 is omitted from the self-locking mechanism 40 of the second embodiment, and the shape of the lock plate bush 42 is changed to that of reference numeral 62.
  • the lock mechanism 41 has a common configuration.
  • the lock plate bush 62 has a pair of flat surfaces (62a, 62b) on the left and right sides, and a pair of parallel portions provided on a pair of stepped portions (62c, 62d) protruding outward from the flat surfaces (62a, 62b). Step surface (63, 64).
  • the lock plate bush 62 is attached to the eccentric circular cam 12 through the circular hole 62e so that the step surfaces (63, 64) are parallel to the straight line L2 extending from the cam shaft central axis L0 in the cam center L1 direction.
  • the step surfaces (63, 64) are formed so as to be arranged symmetrically with respect to the straight line L2 and eccentric from the cam center L1 by being attached to the eccentric circular cam 12. That is, the step surface (63, 64) is a flat surface (62a) in a region in a further eccentric direction (d1 direction from L0 to L1) from the intersection (C1, C2) of the straight line L3 and the flat surface (62a, 62b).
  • a straight line L7 connecting the centers of the planes 63 and 64 is substantially parallel to the straight line L3, and is orthogonal to the straight line L2 at an intersection C3 that is eccentric from the camshaft center axis L0 rather than the cam center L1.
  • the step surfaces (63, 64) are held by the long surfaces (45a, 45b) of the holding groove 45, respectively.
  • the long surfaces (45a, 45b) of the holding groove 45 are stepped surfaces (63, 63) that come into surface contact at positions eccentric from the cam center L1 of the eccentric circular cam 12. 64) through the left and right outward force (F3, F4) along the straight line L7. Further, the force (F3, F4) is generated at the intersection (P9, P10) between the straight line L7 and the outer peripheral surfaces (43c, 43d) of the lock plate constituent members (43a, 43b) from the lock plate 43 to the inner periphery of the cylindrical portion of the drive cylinder 5. It is transmitted to the surface 20 a and acts between the lock plate 43 and the cylindrical portion 20 of the drive cylinder 5.
  • the friction angle corresponding to ( ⁇ 1, ⁇ 2) of the first embodiment formed between the line extending in the tangential direction from the intersection (P9, P10) and the line orthogonal to the straight line L7 is set to the first embodiment.
  • a self-locking function by disturbance torque is constructed between the lock plate 43 and the cylindrical portion 20 of the drive cylinder 5. .
  • a minute gap is generated between the step surface (63, 64) and the holding surface 45 due to a manufacturing error or the like.
  • the step surfaces (63, 64) provided so as to contact the holding surface 45 at a position eccentric from the cam center axis L1 of the eccentric circular cam 12 are stepped as in the first embodiment. Compared with the case where the flat surfaces (23, 24) that are not present are held in the holding groove 15, the play due to the minute gap is reduced. That is, when a disturbance torque is generated in a state where there is a minute gap, the plane moves around the central axis L0 until it comes into contact with the holding surface, but the stepped surfaces (63, 64) which are eccentric from the cam center L1 have the holding grooves.
  • the distance between the contact point 45 and the rotation center is longer than the distance between the contact point 15 and the rotation center with the flat surface (23, 24) having no step, even if the gap amount is the same.
  • the amount of assembly angle deflection due to the gap amount can be reduced.
  • the backlash is reduced, thereby improving the pressing force to the cylindrical portion 20 of the lock plate 43 at the time of the occurrence of the disturbance and ensuring the self-locking function. I can do it.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
PCT/JP2010/058370 2010-05-18 2010-05-18 エンジンの位相可変装置 WO2011145175A1 (ja)

Priority Applications (6)

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CN2010800664074A CN102859126A (zh) 2010-05-18 2010-05-18 发动机的相位可变装置
PCT/JP2010/058370 WO2011145175A1 (ja) 2010-05-18 2010-05-18 エンジンの位相可変装置
US13/697,908 US20130125846A1 (en) 2010-05-18 2010-05-18 Variable cam phaser for automobile engine
JP2012515663A JP5616440B2 (ja) 2010-05-18 2010-05-18 エンジンの位相可変装置
KR1020127024883A KR20130072190A (ko) 2010-05-18 2010-05-18 엔진의 위상 가변 장치
EP10851739.2A EP2573336B1 (en) 2010-05-18 2010-05-18 Phase variable device for engine

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WO2013157110A1 (ja) * 2012-04-19 2013-10-24 日鍛バルブ株式会社 エンジンの位相可変装置
WO2014057530A1 (ja) 2012-10-09 2014-04-17 日鍛バルブ株式会社 自動車用エンジンの位相可変装置
US8726867B2 (en) 2010-10-12 2014-05-20 Nittan Valve Co., Ltd. Phase varying apparatus for automobile engine technical
WO2014109050A1 (ja) * 2013-01-11 2014-07-17 日鍛バルブ株式会社 自動車用エンジンの位相可変装置

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US20100256451A1 (en) 2007-08-27 2010-10-07 Aircraft Medical Limited Laryngoscope insertion section
CN108291481A (zh) * 2015-12-02 2018-07-17 博格华纳公司 分隔式排气增压涡轮增压器

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US8726867B2 (en) 2010-10-12 2014-05-20 Nittan Valve Co., Ltd. Phase varying apparatus for automobile engine technical
WO2013157110A1 (ja) * 2012-04-19 2013-10-24 日鍛バルブ株式会社 エンジンの位相可変装置
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JP6029691B2 (ja) * 2013-01-11 2016-11-24 日鍛バルブ株式会社 自動車用エンジンの位相可変装置

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JP5616440B2 (ja) 2014-10-29
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CN102859126A (zh) 2013-01-02
EP2573336A4 (en) 2013-12-18
EP2573336A1 (en) 2013-03-27
US20130125846A1 (en) 2013-05-23
EP2573336B1 (en) 2015-03-04

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