WO2010026645A1 - 自動車用エンジンにおけるカムシャフト位相可変装置 - Google Patents
自動車用エンジンにおけるカムシャフト位相可変装置 Download PDFInfo
- Publication number
- WO2010026645A1 WO2010026645A1 PCT/JP2008/066082 JP2008066082W WO2010026645A1 WO 2010026645 A1 WO2010026645 A1 WO 2010026645A1 JP 2008066082 W JP2008066082 W JP 2008066082W WO 2010026645 A1 WO2010026645 A1 WO 2010026645A1
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- rotator
- eccentric
- control
- rotating body
- rotation
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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
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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
- F01L1/352—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 includes a rotating operation force applying means for rotating a rotating drum arranged coaxially with the camshaft in either the forward or reverse direction, and the rotational phases of the crankshaft and the camshaft are adjusted according to the rotating direction.
- This is a technology of a phase variable device in an automobile engine that changes the opening / closing timing of a valve by changing it to either an advance angle direction or a retard angle direction.
- Patent Document 1 As this type of conventional technology, there is a valve timing control device shown in Patent Document 1 below.
- the assembly angle of the camshaft 1 with respect to the drive plate 2 driven by driving force from the crankshaft of the engine is set to the advance direction (rotation direction of the drive plate 2) or retard direction (drive plate).
- 2 is a device that changes the opening / closing timing of a valve of an internal combustion engine that is opened and closed by a cam.
- the spacer 8 and the lever shaft 13 are integrally fixed, and the drive plate 2 is assembled so as to be rotatable relative to the spacer 8.
- One end of a link arm 14 is rotatably attached to the three levers 12 of the lever shaft 13, and a movable operation member 11 rotatably attached to the other end of the link arm 14 is provided on the front surface of the drive plate 2. It slides on the substantially radial guide groove 10 in the radial direction.
- a guide plate 24 (rotating drum) is disposed so as to be rotatable relative to the camshaft 1 (lever shaft 13) and the drive plate 2.
- a ball 22 is rotatably held between a recess 21 provided on the front surface of the movable operation member 11 and a spiral groove 28 (spiral guide) provided on the rear surface of the guide plate 24.
- the movable operation member 11 is moved radially inward or outward on the substantially radial guide groove 10 by the ball 22 rolling along the spiral groove 28 according to the relative rotation direction of the guide plate 24 with respect to the drive plate 2. Slide towards.
- the guide plate 24 is rotated relatively to the retard side with respect to the drive plate 2 by the braking force of the first electromagnetic brake 26, and is operated by the following planetary gear mechanism 25 (reverse rotation mechanism) operated by the second electromagnetic brake 27. Rotate relative to the drive plate 2 toward the advance side.
- the planetary gear mechanism 25 (reverse rotation mechanism) is provided with a sun gear 30 on the rear surface of the braking flange 34 and the front surface of the guide plate that are assembled to be rotatable relative to the camshaft 1 (lever shaft 13) in front of the guide plate 24. And a plurality of planetary gears 33 that are rotatably supported with respect to the carrier plate 32 fixed to the lever shaft 13 and mesh between the sun gear 30 and the ring gear 31. ing.
- the brake flange 34 is braked by the second electromagnetic brake 27, the guide plate 24 rotates the planetary gear 33 to accelerate the ring gear 31 in the advance direction, and the guide plate 24 rotates relative to the drive plate 2 in the advance direction. Move.
- Patent Document 1 rotates the guide plate 24 relative to the drive plate 2 by a pair of electromagnetic brakes (26, 27) and a planetary gear mechanism 25 (reverse rotation mechanism), and the relative rotation direction thereof.
- This is a device for changing the assembly angle of the camshaft 1 and the crankshaft (drive plate 2) according to the above.
- the apparatus of Patent Document 1 has a problem in that the manufacturing unit price of the reverse rotation mechanism of the rotating drum (guide plate 24) becomes high and the operation noise increases. That is, since the planetary gear mechanism 25 employs a large number of gears including the sun gear 30, the ring gear 31, and the plurality of planetary gears 33, there is a problem in that the manufacturing unit cost increases when molding a large number of teeth with high accuracy. there were. On the other hand, the gear generates a rattling sound when the meshing tooth portions collide during operation. Accordingly, the planetary gear mechanism 25 has a problem in that the operation noise becomes loud when the valve timing is changed by employing a large number of gears.
- the inventor of the present application has a low manufacturing unit price and a quiet operation sound when changing the valve timing, and includes a reverse rotation mechanism for a rotating drum (guide plate 24).
- Invented the phase-variable device in No. 1 and filed a patent application international application number: PCT / JP2008 / 57857, title of the invention: phase-variable device in an automobile engine, hereinafter referred to as “prior application 1”).
- the reverse rotation mechanism of the rotary drum in the prior application 1 is attached so as to be rotatable relative to the center shaft 42 integrated with the camshaft 40 and is braked by the first and second electromagnetic clutches (44, 60), respectively.
- the first and second control rotators (45, 57) are provided, and the second intermediate rotator 56 cannot rotate relative to the center shaft 42 between the first and second control rotators (45, 57). It is fixed in the state.
- the second control rotator 57 has a curved second guide groove 62 that decreases in diameter along the advance direction (the clockwise direction when viewed from the second electromagnetic clutch 60 side, which is the rotation direction of the drive rotator 71).
- the first control rotator 45 is provided on a surface facing the second intermediate rotator 56, and the first control rotator 45 has a curvilinear shape whose diameter decreases along a retarded direction (a counterclockwise direction opposite to the rotation of the drive rotator 71).
- the first guide groove 61 is provided on the surface facing the second intermediate rotator 56, and the second intermediate rotator 56 includes a substantially radial guide groove 63 penetrating in the central axis direction.
- a slide pin 64 is inserted into each guide (61-63) and is slidable along the direction of each guide groove.
- the slide pin 64 moves along the second guide groove 62 and the substantially radial guide groove 63.
- the first control rotor 45 rotates relative to the second intermediate rotor 56 in the advance direction by receiving the torque in the advance direction from the slide pin 64 in which the first guide groove 61 moves inward.
- the assembly angle of the camshaft 40 (center shaft 42) with respect to the shaft (drive rotating body 41) is changed to the advance side.
- the first control rotator 45 rotates relative to the intermediate rotator 56 in the retard direction to change the assembly angle to the retard side.
- the reverse rotation mechanism of the first control rotating body 45 has a simple shape in which each rotating body (56, 57), slide pin 64, and each guide groove (61 to 63) are based on a circle. Is easy, and the manufacturing cost is reduced. Since the slide pin 64 is silently displaced while being always in sliding contact with the respective guide grooves (61 to 63), the operation sound when changing the valve timing is quiet.
- the assembling angle of the camshaft 40 with respect to the crankshaft (drive rotating body 41) can increase the displacement width by increasing the length of the first guide groove 61 in the circumferential direction.
- the advance torque received from the slide pin 64 that slides inward along the first guide groove 61 by the first control rotator 45 increases the length of the first guide groove 61 in the circumferential direction.
- the first guide groove 61 becomes smaller with an increase in the inclination of the first guide groove 61 with respect to the substantially radial guide groove 63 (increase in friction).
- the reverse rotation mechanism of the first control rotator 45 (rotary drum) maintains the rotational torque of the first rotator 45 given by the braking of the second control rotator 57, and further sets the camshaft 40 to the crankshaft. It is desirable to make the displacement angle of the angle of attachment as large as possible.
- the present invention maintains the advantages of the prior application 1 (inexpensive manufacturing cost and quietness), and further, the crankshaft and the camshaft without reducing the rotational torque of the first control rotor by the second control rotor.
- An engine phase variable device having a reverse rotation mechanism of a rotary drum capable of increasing the displacement width of the assembly angle is provided.
- a phase varying device for an engine includes a drive rotating body that is rotationally driven by a crankshaft, a first intermediate rotating body integrated with a camshaft, and a rotating operation force applying means.
- the first control rotator that receives the rotation torque from the first control rotator is disposed on the same rotation center axis so as to be rotatable relative to each other, and the relative rotation direction of the first control rotator with respect to the first intermediate rotator and the drive rotator
- the turning operation force applying means is configured to perform the first control rotation with respect to the first intermediate rotator and the drive rotator.
- a coupling means for coupling the first and second eccentric rotation mechanisms so as to be capable of relative rotation, and the first control rotation body and the second control rotation body are either When one is rotated, the other is relatively rotated.
- the first control rotating body rotates integrally with the first intermediate rotating body integrated with the camshaft and the driving rotating body that receives the driving force from the crankshaft.
- the first control rotator receives a braking force from the first braking means
- the first control rotator rotates relative to the drive rotator and the first intermediate rotator in the retarding direction
- the second control rotator is rotated by the second braking means.
- the brake When the brake is braked, it rotates relative to the drive rotating body and the first intermediate rotating body in the advance direction, contrary to the first braking means.
- the phase angle of the first intermediate rotator (camshaft side) with respect to the drive rotator (crankshaft side) is an advance direction (rotation direction of the drive rotator below) according to the relative rotation direction of the first control rotator. Same) or retarded direction (the direction opposite to the rotation direction of the drive rotator, hereinafter the same).
- the first eccentric rotating mechanism rotates together with the first control rotating body, and the second control rotating body and the second eccentric rotating mechanism are moved to the first control rotating body and the camshaft by the second braking means. Both rotate relative to the integrated second intermediate rotating body.
- the connecting means displaces the substantially radial guide groove of the second rotating body in the radial direction and rotates the other in the opposite direction. That is, when the first control rotator brakes the second control rotator, the first control rotator is rotated by the first and second eccentric rotation mechanisms in the opposite direction to the time of braking by the first braking means.
- the connection means includes an eccentric point from the rotation center axis of the connection means and the first eccentric rotation mechanism, an eccentric point of the connection means and the second eccentric rotation mechanism, and an eccentric point and rotation of the first eccentric rotation mechanism.
- the displacement width of the camshaft assembly angle with respect to the crankshaft can be increased by making the substantially radial guide groove longer or by increasing the reciprocating rotation range of the first and second eccentric rotation mechanisms. .
- Each control rotator, second intermediate rotator, each eccentric rotation mechanism, and connecting means have a simple configuration based on a circle, and therefore are easy to process. Further, when changing the phase angle between the drive rotator and the first intermediate rotator, the connecting means is gently displaced while always slidingly contacting each guide groove.
- the first eccentric rotation mechanism includes a first eccentric circular hole formed in the first control rotor.
- a first ring member engaged with the outer periphery of the first eccentric circular hole so as to be in sliding contact with the inner periphery of the first eccentric circular hole, and the second eccentric rotation mechanism is formed on the second control rotating body.
- Two eccentric circular holes and a second ring member engaged with the outer periphery of the second eccentric circular hole so as to be in sliding contact with the inner periphery of the second eccentric circular hole, and the connecting means are formed on the first and second ring members, respectively.
- the centers of the second ring members were respectively arranged with the extending line of the substantially radial guide groove interposed therebetween.
- the first and second ring members rotate eccentrically around the rotation center axis of each control rotator together with the first and second control rotators, and slide in the first and second eccentric circular holes. To do. When one of the first and second control rotators is braked, the ring member of the braked control rotator slides in the eccentric circular hole and swings the connecting member along the substantially radial guide groove. Then, the other control rotator is rotated in the reverse direction via the other connected ring member.
- the first and second control rotators are each of a first ring member (first eccentric circular hole) and a second ring member (second eccentric circular hole) that slide in circular holes that rotate eccentrically in opposite directions.
- the eccentric points rotate in the reverse direction smoothly by performing the same operation as the connecting portion of the four-bar linkage mechanism by the connecting member that displaces the substantially radial guide groove.
- the ring member, the eccentric circular hole, and the connecting member based on a circle are easy to process and operate quietly.
- the first eccentric circular hole extends from the rotation center axis of the first control rotating body.
- the amount of eccentricity reaching the central axis was made larger than the amount of eccentricity reaching the central axis of the second eccentric circular hole from the rotation central axis of the second control rotator.
- the eccentric amount of the first ring member (the distance from the central axis of the first ring member to the rotation central axis of the first control rotating body, hereinafter the same) is the eccentric amount of the second ring member. (The distance from the central axis of the second ring member to the rotational central axis of the second control rotator, hereinafter the same), and the movement distance of the center of the first ring member when the second ring member rotates It is larger than the moving distance of the center of the second ring member. Therefore, the phase varying device according to claim 3 applies the reverse rotation torque of the same magnitude as the first braking means to the first control rotating body while reducing the braking torque of the second control rotating body by the second braking means. Therefore, the relative rotation speed of the first control rotator coincides with the advance direction and the retard direction.
- Claim 4 is the engine phase variable device according to claim 2 or 3, wherein at least one of the first and second ring members is a C-shaped ring member.
- the C-shaped cutout portion serves as an escape portion from the center shaft, so that the eccentric amount of the first ring member and the second ring member can be increased. I can do it.
- the substantially radial guide has a length capable of rotating 360 ° or more within the second eccentric circular hole of the second ring member. A groove was formed.
- the rotation operation force applying means of the first control rotator reduces the relative rotation torque of the first control rotator based on the braking of the second control rotator.
- the displacement width of the assembly angle between the crankshaft and the camshaft can be increased without making it.
- the rotating operation force applying means is formed with the component parts based on a circle, it can be manufactured easily and inexpensively, and the operation sound when changing the phase angle is reduced.
- the second braking means that is arranged on the inner side of the first braking means and is concerned about lack of braking torque is equivalent to the first braking means.
- the braking performance can be demonstrated.
- the degree of freedom in setting the eccentric amount of the first ring and the second ring is improved, the displacement width of the assembly angle of the crankshaft and the camshaft is further increased. it can.
- the assembly angle of the crankshaft and the camshaft can be changed in both the advance direction or the retard direction by one control rotating body and one braking means.
- the other braking means can be provided with a fail-safe function that can change the assembly angle of the crankshaft and the camshaft.
- FIG. 1 is an exploded perspective view of a phase varying device in an automobile engine according to a first embodiment of the present invention as viewed from the front
- FIG. 2 is a front view of the device
- FIG. 3 is an axial sectional view of the device.
- 2 is a cross-sectional view taken along the line AA in FIG. 2
- FIG. 4 is a cross-sectional view taken along the radial direction of the device before the phase displacement, in which (a) is a cross-sectional view taken along BB in FIG. 3 is a cross-sectional view taken along the line CC in FIG. 3,
- FIG. 5C is a cross-sectional view taken along the line DD in FIG. 3, FIG.
- FIG. 5 is a view showing a state after the phase displacement of each cross-sectional view in FIG.
- FIG. 3 is a radial cross-sectional view of the same device before displacement, in which (a) is a cross-sectional view taken along line EE in FIG. 3, (b) is a cross-sectional view taken along line FF in FIG. 3 is a cross-sectional view taken along the line GG in FIG. 3, FIG. 7 is a view showing a state after the phase displacement of each cross-sectional view in FIG. 6, and FIG. 8 is a diagram showing the first ring member and the first eccentricity in the second embodiment of the phase varying device.
- GG sectional view of FIG. 3, showing a circular hole 3A is a cross-sectional view taken along line EE of FIG.
- FIG. 3 showing the second ring member and the second eccentric circular hole in the third embodiment of the phase varying device
- FIG. 3B is the first ring member in the third embodiment
- FIG. 4 is a sectional view taken along the line GG of FIG. 3 showing the first eccentric circular hole.
- the engine phase varying device shown in the embodiment is used in a form assembled and integrated with the engine, and 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 engine load and the rotational speed.
- the configuration of the device of the first embodiment will be described with reference to FIGS. 1 to 7.
- the device of the first embodiment (for convenience of explanation, the direction of a second electromagnetic clutch 90 described later is the front side, and the direction of the sprocket 71a is the rear side. ) Is fixed to a driving rotator 71 that rotates by receiving a driving force from a crankshaft (not shown) of the engine and a camshaft (not shown), and supports the driving rotator 71 in a relatively rotatable state.
- the outer peripheral surface is supported, and the first control rotating body 74 that rotates relative to the center shaft 72 in a non-contact state is fixed to an engine case (not shown).
- a first electromagnetic clutch 75 for braking the rotation of the body 74 are provided on the same rotational axis L1.
- the first control rotator 74 is provided with an eccentric circular cam 76 (see FIGS. 3 and 4 (a)) that rotates integrally around the central axis L1 on the rear surface.
- the intermediate rotating body 73 includes a cam guide 77 that engages with the eccentric circular cam 76 on the front surface, and reciprocally swings in a direction orthogonal to the central axis L1 and the wall surface direction of the cam guide 77 when the eccentric circular cam 76 rotates.
- the center shaft 72 is integrated with the hole 72a in a state in which the hole 72a cannot rotate relative to the tip of a camshaft (not shown).
- the drive rotator 71 is configured by a sprocket 71 a and a drive cylinder 71 b being coupled by a plurality of coupling pins 78.
- the drive rotator 71 is supported in a state in which the hole 71c of the sprocket 71a is rotatable relative to a cylindrical portion 72c provided behind the flange 72b of the center shaft 72.
- the drive cylinder 71b is formed in a bottomed cylinder shape, and a pair of curved guide grooves 79 provided in a substantially circumferential direction around the rotation center axis L1 is formed in the bottom portion of the drive cylinder 71b.
- the guide groove 79 has a guide groove 79a that decreases in diameter in the rotation direction D1 (clockwise direction when viewed from the front of the apparatus, the same applies hereinafter) of the drive rotator 71, and a rotation center axis.
- the guide groove 79b is formed symmetrically with the guide groove 79a.
- the direction in which the guide groove 79a decreases in diameter may be a counterclockwise D2 direction to be described later.
- the first intermediate rotating body 73 is a pair of wall surfaces that are formed in a disc shape and perpendicular to the central axis L1, and includes a cam guide 77 that engages with an eccentric circular cam 76 on the front surface.
- the bottom surface of the cam guide 77 is provided with an elongated hole 80 that extends in a direction orthogonal to the wall surface of the cam guide 77 and the central axis L1 and penetrates in the direction of the central axis L1.
- the first intermediate rotating body 73 is fixed in a state in which it cannot rotate relative to the center shaft 72 when the long hole 80 is engaged with the flat engagement surface 72 d, and the long hole 80 is fixed by the center shaft 72. Is slidably supported in the extending direction.
- the first intermediate rotator 73, the first control rotator 74, and the eccentric circular cam 76 are disposed inside the drive cylinder 71b.
- the first control rotator 74 includes a through-hole 74a through which the cylindrical portion 72e of the center shaft 72 is inserted in a non-contact state.
- the eccentric circular cam 76 integrally formed on the rear surface of the first control rotator 74 has its center axis L2 eccentric from the rotation center axis L1 by a distance d0.
- the first control rotator 74 is formed in a disk shape, and is supported by a step inner peripheral surface 71d of the drive cylinder 71b with which the outer peripheral surface 74b is substantially inscribed.
- the first control rotator 74 is supported by the drive cylinder 71b without the through-hole 74a always contacting the cylindrical portion 72e of the center shaft 72.
- the eccentric circular cam 76 receives a force from the cam guide 77 in a direction orthogonal to the rotation center axis L1.
- the first control rotator 74 moves in a direction orthogonal to L1, and the outer peripheral surface 74b comes into contact with the inner peripheral surface 71d of the rotating cylinder 71b.
- the phase varying device of the first embodiment has a self-locking function that prevents the frictional force of the contact surface from causing the phase angle deviation due to the disturbance. Since the through-hole 74a has a sufficient gap with the cylindrical portion 72e of the center shaft 72, even if the first control rotator 74 moves in the direction perpendicular to L1 during self-locking, the through-hole 74a does not move to the cylindrical portion 72e. There is no contact. Therefore, the self-locking function acts reliably between the outer peripheral surface 74b and the inner peripheral surface 71d.
- the outer shape of the eccentric circular cam 76 is not limited to the circular shape as in the present embodiment, but may be a cam shape having a special peripheral edge.
- the first intermediate rotating body 73 includes a pair of shaft-like members 81 protruding rearward from the pair of engaging holes 73a.
- the shaft-like member 81 is formed by inserting a thin round shaft 81a inside a hollow thick round shaft 81b.
- the thin round shaft 81a at the front end is engaged with the engagement hole 73a, and the hollow thick round shaft 81b at the rear end is a pair of guide grooves (79a, 79b) that are substantially circumferential grooves formed in the drive cylinder 71b. Engage in a displaceable state.
- a first electromagnetic clutch 75 having a friction material 82 disposed on the rear surface is disposed in front of the first control rotator 74.
- the electromagnetic clutch 75 energizes the coil 75a, and the suction surface 74c of the first control rotator 74 is placed on the suction surface 74c. By making sliding contact with the friction material 82, the rotation of the first control rotating body 74 is braked.
- the holder 89 and the second electromagnetic clutch 90 are respectively disposed.
- the members 83 to 90 together with the first electromagnetic clutch 90 constitute the turning operation force applying means of claim 1 of the present application.
- the first control rotating body 74 is formed in a bottomed cylindrical shape, and has a step-shaped first eccentric circular hole 74d whose center axis L2 is eccentric from the rotation center axis L1 by a distance d1 on the front surface of the bottom.
- the first ring member 83 is slidably engaged with the eccentric circular hole 74d.
- the first ring member 83 includes a first engagement hole 83a that opens to the front surface.
- the second intermediate rotator 84 includes a square hole 84a at the center, and a substantially radial guide groove 84b extending in the radial direction of the second intermediate rotator 84 on the outer side thereof.
- the second intermediate rotating body 84 is fixed to the center shaft 72 in a non-rotatable state by engaging the square holes 84a with the second flat engaging surfaces (72f, 72g) of the center shaft 72, respectively.
- the second control rotator 87 is supported in a state in which the small cylindrical portion 72h at the tip of the center shaft 72 is inserted into a circular hole 87a formed in the center and is rotatable with respect to the center shaft 72.
- the second control rotator 87 is provided with a step-shaped eccentric circular hole 87b on the rear surface whose central axis L3 is eccentric from the rotation central axis L1 by a distance d1 in the same manner as the first eccentric circular hole 74d.
- the second ring member 86 is slidably engaged with the eccentric circular hole 87b.
- the second ring member 86 includes a second engagement hole 86a that opens to the rear surface.
- the shaft-shaped member 85 is configured by inserting a hollow thick circular shaft 85b at the center of the thin circular shaft 85a. Both ends of the thin round shaft 85a are slidably engaged with the first and second engagement holes (83a, 86a), and the hollow round shaft 85b is second along the substantially radial guide groove 84b.
- the intermediate rotating body 84 engages in a displaceable state in the radial direction.
- the first and second ring members (83, 86) have substantially central diameters (R2, L3) perpendicular to the rotation center axis L1 of the first and second control rotators (74, 87).
- the first and second eccentric circular holes (74d, 87b) are arranged so that the extension line L4 of the direction guide groove 84b is sandwiched therebetween and arranged substantially symmetrically about the extension line L4.
- the shim 88 is disposed in the stepped circular hole 87c on the front surface of the second control rotating body 87, and the holder 89 is inserted into the small cylindrical portion 72h of the center shaft 72 protruding forward from the circular hole 87a.
- the components from the holder 89 to the drive cylinder 71b are fixed by inserting bolts (not shown) into the central holes from the front and screwing them onto the camshaft (not shown).
- the second electromagnetic clutch 90 is disposed so as to face the front surface of the second control rotor 87 in a state of being fixed to an engine case (not shown).
- the second electromagnetic clutch 90 energizes the coil 90 a, brakes the rotation of the second control rotator 87 by attracting the suction surface 87 d on the front surface of the second control rotator 87 and slidingly contacting the friction material 91. To do.
- the adsorption surface 87d of the second control rotator is magnetized when the first electromagnetic clutch 75 is operated and the operation may become unstable if the second control rotator 87 is disposed inside the coil 75a. As shown in FIG. 3, it is desirable to arrange the first control rotator 74 flush with the suction surface 74c.
- the shaft-like members (81, 85) may be configured to have a bearing, for example, and may roll inside the groove when the guide groove 79 and the substantially radial guide groove 84b are displaced.
- the shaped members (81, 85) may be replaced with balls. In that case, the frictional resistance at the time of displacement of the shaft-like members (81, 85) is reduced and the displacement becomes easy, and the power consumption of each electromagnetic clutch is reduced.
- the second intermediate rotator 84 be formed of a nonmagnetic material.
- the second intermediate rotator 84 is formed of a magnetic body, a magnetic force for attracting one of the control rotators (74, 87) is transmitted to the other control rotator via the second intermediate rotator 84, The problem of being sucked together can be solved.
- the second control rotator 87 is braked by the second electromagnetic clutch 90.
- the first and second ring members (83, 86) are displaced from the state shown in FIG. 6 to FIG. That is, the second control rotator 87 causes a rotation delay with respect to the second intermediate rotator 84 and the first control rotator 74, and in the retard direction (counterclockwise D2 direction when viewed from the front of the apparatus, the same applies hereinafter). Relative rotation.
- the shaft-shaped member 85 is radially inward along the substantially radial guide groove 84b as the second ring member 86 slides in the direction D1 in the second eccentric circular hole 87b (FIG. 6 ( b) (D3 direction).
- the first ring member 83 slides in the first eccentric circular hole 74d in the D2 direction while passing the D1 to the first control rotating body 74.
- a relative rotational torque in the direction is applied.
- the first control rotator 74 rotates relative to the second intermediate rotator 84 and the second control rotator 87 in the advance direction (D1 direction).
- the first control rotator 74 rotates relative to the first intermediate rotator 73 and the drive rotator 71 in the advance direction D1, and is an eccentric circle integrated with the first control rotator 74 shown in FIG.
- the cam 76 rotates eccentrically around the central axis L1 in the clockwise direction D1.
- the eccentric circular cam 76 rotates eccentrically while sliding with the inner peripheral surface of the cam guide 77, the first intermediate rotating body 73 and the shaft-shaped member 81 are moved in the direction D3 in FIG. Descend.
- the first intermediate rotating body 73 rotates relative to the driving rotating body 71 in the D1 direction by being displaced in the D1 direction along the guide grooves (79a, 79b) when the shaft-like member 81 is lowered.
- the state is displaced from FIG. 4 to FIG.
- the phase angle of the camshaft (not shown) that rotates synchronously with the first intermediate rotator 73 is changed to the advance direction (D1 direction) with respect to the phase angle of the drive rotator 71 driven by the crankshaft. Is done.
- the first control rotator 74 is braked by the first electromagnetic clutch 75.
- the eccentric circular cam 76 integrated with the braked first control rotator 74 is relatively rotated in the counterclockwise direction D2 with respect to the drive rotator 71 and the first intermediate rotator 73.
- the intermediate rotating body 73 and the shaft-like member 81 are raised in the direction D4 in FIG.
- the first intermediate rotator 73 rotates in the D2 direction relative to the drive rotator 71 by being displaced in the D2 direction along the guide groove 79 when the shaft-like member 81 is lifted.
- the amount is equally d1.
- the amount of eccentricity d2 from the rotation center axis L1 of the first control rotating body 74 to the center axis L2 ′ of the first eccentric circular hole 92 (first ring member 93) is The eccentric amount d1 of the second eccentric circular hole 87b (second ring member 86) shown in FIG.
- the first ring member 93 has a center axis L2 ′ sandwiched between the extension line L4 (see FIG. 6B) of the substantially radial guide groove 84b together with the center axis L3 of the second ring member 86. Arranged in the eccentric circular hole 92.
- the configuration of the second embodiment is the same as that of the first embodiment except for the first eccentric circular hole 92 and the first ring member 93.
- the eccentric amount d2 of the first ring member 93 in FIG. 8 is larger than the eccentric amount d1 of the second ring member 86 in FIG.
- the central axis L2 ′ (eccentric point) of the first ring member 93 that relatively rotates about the torque radius is larger than the central axis L3 (eccentric point) of the second ring member 86 that also rotates about the rotational center axis L1.
- the relative rotational torque applied to the first control rotator 74 can be increased. Even the second braking means for which the shortage of torque is a concern can exhibit braking performance equivalent to that of the first braking means. Further, a smaller second electromagnetic clutch 90 can be arranged inside the first electromagnetic clutch 75, and the phase variable device can be formed compactly.
- the first and second ring members (83, 86), which were circular in the first embodiment, are provided with cutout portions, and the first and second C-shapes shown in FIG.
- the ring members (94, 95) are used.
- the notch of the first ring member formed in a C-shape serves as a relief portion for the center shaft 72, and therefore the eccentric amount d3 of the first and second ring members (94, 95) is further increased.
- the relative rotational torque generated in the first control rotor 74 by the second electromagnetic clutch 90 can be further increased.
- the formation range of the notch part in a 1st and 2nd ring member (94,95) shall be less than 180 degrees of the whole.
- the second ring member 83 of the first and second embodiments rotates 360 ° or more in the second eccentric circular hole 87b by making the length of the substantially radial guide groove 84 sufficiently long.
- the shaft-shaped member 85 reciprocates from one end to the other end of the substantially radial guide groove when the second control rotator 87 rotates 360 °
- the first control rotator 74 moves to the drive rotator 71.
- it relatively rotates in both the advance direction and the retard direction.
- the second ring member 86 is configured to be able to rotate 360 ° or more in the second eccentric circular hole.
- the first ring member (83, 93) is the first one. It is also possible to adopt a configuration in which the inside of one knitted circular hole can be rotated by 360 ° or more. In that case, the outer diameter of the eccentric circular cam 76 is formed such that the cam guide 77 can rotate 360 °. In such a configuration, since the shaft-like member 81 reciprocates both ends of the substantially radial guide groove 79 when the first control rotator 74 rotates 360 °, the crankshaft is driven only by the first electromagnetic clutch 75.
- the camshaft assembly angle can be changed to both the advance side and the retard side. That is, even if one of the first and second electromagnetic clutches (75, 90) fails, the non-failed electromagnetic clutch is operated and the assembly angle of the crankshaft and the camshaft is retarded from the advance side. It is possible to change both sides (fail-safe function).
- FIG. 3 is a cross-sectional view taken along the line AA of FIG.
- FIG. 3 is a radial cross-sectional view of the device before phase displacement
- (a) is a cross-sectional view taken along line BB in FIG. 3
- (b) is a cross-sectional view taken along line CC in FIG. 3
- (c) is a cross-sectional view.
- FIG. 4 is a DD cross-sectional view of FIG. 3. It is a figure which shows the state after the phase displacement of each sectional drawing of FIG. FIG.
- FIG. 3 is a radial cross-sectional view of the device before phase displacement, (a) is a cross-sectional view taken along line EE in FIG. 3, (b) is a cross-sectional view taken along line FF in FIG. 3, and (c) is a cross-sectional view.
- FIG. 4 is a GG sectional view of FIG. 3. It is a figure which shows the state after the phase displacement of each sectional drawing of FIG.
- FIG. 6 is a cross-sectional view taken along the line GG in FIG. 3 showing the first ring member and the first eccentric circular hole in the second embodiment of the phase varying device.
- 3A is a cross-sectional view taken along the line EE of FIG.
- FIG. 3 showing the second ring member and the second eccentric circular hole in the third embodiment of the phase varying device
- FIG. 3B is the first ring member in the third embodiment
- FIG. 4 is a sectional view taken along the line GG in FIG. 3 showing a first eccentric circular hole.
- Second electromagnetic clutch (second braking means) L1 rotation center axis L2, L2 ′ first eccentric circular hole and central axis of the first ring member L3 second eccentric circular hole and central axis of the second ring member L4 extension line of substantially radial guide groove d1, d3 first And the eccentric amount of the second eccentric circular hole d2 the eccentric amount of the first eccentric circular hole D1 advance angle direction (
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Abstract
Description
72 センターシャフト(カムシャフトと一体の部材)
73 第一中間回転体
74 第一制御回転体
74d 第一偏心円孔(第一偏心回動機構)
75 第一電磁クラッチ(第一の制動手段)
83,93,95 第一リング部材(第一偏心回動機構)
83a 第一係合孔(連結手段)
84 第二中間回転体
84b 略径方向ガイド溝
85 軸状部材(連結手段)
86,94 第二リング部材(第二偏心回動機構)
86a 第二係合孔(連結手段)
87 第二制御回転体
87b 第二偏心円孔(第二偏心回動機構)
90 第二電磁クラッチ(第二の制動手段)
L1 回動中心軸
L2,L2’ 第一偏心円孔と第一リング部材の中心軸
L3 第二偏心円孔と第二リング部材の中心軸
L4 略径方向ガイド溝の延伸線
d1,d3 第一及び第二偏心円孔の偏心量
d2 第一偏心円孔の偏心量
D1 進角方向(駆動回転体の回動方向)
D2 遅角方向(駆動回転体の回動方向と逆方向)
Claims (5)
- クランクシャフトによって回転駆動する駆動回転体と、カムシャフトに一体化
された第一中間回転体と、回動操作力付与手段から回動トルクを受ける第一制御回転体を互いに相対回動可能に同一の回動中心軸上に配置し、前記第一中間回転体と駆動回転体に対する第一制御回転体の相対回動方向に応じて前記カムシャフトと駆動回転体の位相角を変更するエンジンの位相可変装置において、
前記回動操作力付与手段は、
前記第一中間回転体と駆動回転体に対して前記第一制御回転体を相対回動させる第一の制動手段と、
前記カムシャフトに一体化され、その半径方向に延伸すると共に軸方向に貫通する略径方向ガイド溝を有する第二中間回転体と、
前記第一制御回転体と第二中間回転体に対して同軸かつ相対回動可能に配置され、第二の制動手段によって相対回動する第二制御回転体と、
第一制御回転体と連動して前記回動中心軸周辺を偏心回動する、第一の偏心回動機構と、
第二制御回転体と連動して前記回動中心軸周辺を偏心回動する、第二の偏心回動機構と、
前記略径方向ガイド溝と変位可能な状態で係合し、前記第一及び第二の偏心回動機構を相対回動可能に連結する連結手段と、
を備えたことを特徴とするエンジンの位相可変装置。 - 前記第一偏心回動機構は、前記第一制御回転体に形成された第一偏心円孔と、その外周が前記第一偏心円孔の内周と摺接可能な状態で係合する第一リング部材を備え、
前記第二偏心回動機構は、前記第二制御回転体に形成された第二偏心円孔と、その外周が前記第二偏心円孔の内周と摺接可能な状態で係合する第二リング部材を備え、
前記連結手段は、第一及び第二リング部材にそれぞれ形成された第一及び第二係合孔と、前記略径方向ガイド溝を貫通し、その両端が前記第一及び第二係合孔にそれぞれ挿入される連結部材を備え、
前記第一リング部材と第二リング部材の中心は、前記略径方向ガイド溝の延伸線を間に挟んでそれぞれ配置されたことを特徴とする、請求項1記載のエンジンの位相可変装置。 - 前記第一偏心円孔は、第一制御回転体の回動中心軸から第一偏心円孔の中心軸に至る偏心量が、前記第二制御回転体の回動中心軸から第二偏心円孔の中心軸に至る偏心量よりも大きく形成されたことを特徴とする、請求項2記載のエンジンの位相可変装置。
- 前記第一及び第二リング部材のうち少なくとも一つは、C型形状のリング部材であることを特徴とする、請求項2または3に記載のエンジンの位相可変装置
- 前記略径方向ガイド溝は、前記第二リング部材が第二偏心円孔内を360°以上回転可能な長さに形成されたことを特徴とする請求項2から4のうちいずれかに記載のエンジンの位相可変装置。
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP08810137.3A EP2320036B1 (en) | 2008-09-05 | 2008-09-05 | Cam shaft phase variable device in engine for automobile |
CN2008801309763A CN102144077B (zh) | 2008-09-05 | 2008-09-05 | 汽车用发动机中的凸轮轴相位可变装置 |
KR1020117005179A KR101236276B1 (ko) | 2008-09-05 | 2008-09-05 | 자동차용 엔진에 있어서의 캠샤프트 위상 가변 장치 |
US13/062,351 US8613266B2 (en) | 2008-09-05 | 2008-09-05 | Cam shaft phase variable device in engine for automobile |
PCT/JP2008/066082 WO2010026645A1 (ja) | 2008-09-05 | 2008-09-05 | 自動車用エンジンにおけるカムシャフト位相可変装置 |
JP2010527628A JP5307145B2 (ja) | 2008-09-05 | 2008-09-05 | 自動車用エンジンにおけるカムシャフト位相可変装置 |
HK11112488.1A HK1158288A1 (en) | 2008-09-05 | 2011-11-18 | Cam shaft phase variable device in engine for automobile |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2008/066082 WO2010026645A1 (ja) | 2008-09-05 | 2008-09-05 | 自動車用エンジンにおけるカムシャフト位相可変装置 |
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WO2010026645A1 true WO2010026645A1 (ja) | 2010-03-11 |
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Application Number | Title | Priority Date | Filing Date |
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PCT/JP2008/066082 WO2010026645A1 (ja) | 2008-09-05 | 2008-09-05 | 自動車用エンジンにおけるカムシャフト位相可変装置 |
Country Status (7)
Country | Link |
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US (1) | US8613266B2 (ja) |
EP (1) | EP2320036B1 (ja) |
JP (1) | JP5307145B2 (ja) |
KR (1) | KR101236276B1 (ja) |
CN (1) | CN102144077B (ja) |
HK (1) | HK1158288A1 (ja) |
WO (1) | WO2010026645A1 (ja) |
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EP2589766A1 (en) * | 2010-07-02 | 2013-05-08 | Nittan Valve Co., Ltd. | Engine phase varying device and controller for same |
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JP5616440B2 (ja) * | 2010-05-18 | 2014-10-29 | 日鍛バルブ株式会社 | エンジンの位相可変装置 |
EP2573336A1 (en) * | 2010-05-18 | 2013-03-27 | Nittan Valve Co., Ltd. | Phase variable device for engine |
EP2573336A4 (en) * | 2010-05-18 | 2013-12-18 | Nittan Valva | PHASE VARYING DEVICE FOR MOTOR |
EP2589766A4 (en) * | 2010-07-02 | 2014-07-23 | Nittan Valva | DEVICE FOR MOTOR PHASE VARIATION AND CONTROL AND FOR THIS |
EP2589766A1 (en) * | 2010-07-02 | 2013-05-08 | Nittan Valve Co., Ltd. | Engine phase varying device and controller for same |
EP2628910A1 (en) * | 2010-10-12 | 2013-08-21 | Nittan Valve Co., Ltd. | Phase variable device of engine |
CN103140653A (zh) * | 2010-10-12 | 2013-06-05 | 日锻汽门株式会社 | 发动机的相位可变装置 |
US8726867B2 (en) | 2010-10-12 | 2014-05-20 | Nittan Valve Co., Ltd. | Phase varying apparatus for automobile engine technical |
JP5600748B2 (ja) * | 2010-10-12 | 2014-10-01 | 日鍛バルブ株式会社 | エンジンの位相可変装置 |
WO2012049727A1 (ja) * | 2010-10-12 | 2012-04-19 | 日鍛バルブ株式会社 | エンジンの位相可変装置 |
EP2628910A4 (en) * | 2010-10-12 | 2014-11-12 | Nittan Valva | PHASE REVERSIBLE DEVICE FOR A MOTOR |
WO2013024513A1 (ja) | 2011-08-12 | 2013-02-21 | 日鍛バルブ株式会社 | 自動車用エンジンの位相可変装置 |
EP2743465A4 (en) * | 2011-08-12 | 2015-04-29 | Nittan Valva | VARIABLE PHASE DEVICE OF AN AUTOMOBILE ENGINE |
US9032925B2 (en) | 2011-08-12 | 2015-05-19 | Nittan Valve Co., Ltd. | Phase varying apparatus for automobile engine |
Also Published As
Publication number | Publication date |
---|---|
HK1158288A1 (en) | 2012-07-13 |
JP5307145B2 (ja) | 2013-10-02 |
KR20110059607A (ko) | 2011-06-02 |
JPWO2010026645A1 (ja) | 2012-01-26 |
KR101236276B1 (ko) | 2013-02-22 |
EP2320036A4 (en) | 2012-03-28 |
US20110192365A1 (en) | 2011-08-11 |
US8613266B2 (en) | 2013-12-24 |
EP2320036A1 (en) | 2011-05-11 |
CN102144077B (zh) | 2013-02-13 |
CN102144077A (zh) | 2011-08-03 |
EP2320036B1 (en) | 2013-07-03 |
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