JP5379669B2 - Variable valve operating device for internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve timing control device in which miniaturization of the device can be realized by shortening a length in the direction of a rotating shaft of the device. <P>SOLUTION: A phase conversion mechanism 4 includes: an annular member 19 connected to a housing 5; an electric motor 12 energized through brushes 23a and 23b; and a reduction gear 8 decelerating the forward/reverse torque of the electric motor to transmit it to a cam shaft 2. In the reduction gear, a second ball bearing 33 and a roller 34 are arranged in the substantially same direction as the radial direction of a needle bearing 28 rotatably supporting an eccentric shaft 30 to a cam bolt 10, so that the length in the direction of the shaft of the device is shortened, miniaturizing the entire device. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a variable valve operating apparatus for an internal combustion engine that variably controls, for example, an opening / closing timing and a lift amount of an intake valve or an exhaust valve of the internal combustion engine using a variable mechanism using an electric motor.

  Recently, a valve timing control device which is one of variable valve operating devices of an internal combustion engine has been provided which improves control response and controllability by driving an electric motor.

  For example, a valve timing control device described in Patent Document 1 below decelerates drive rotation of an electric motor by a planetary speed reduction mechanism, and sets a relative rotation phase between a sprocket and a camshaft to which rotational force is transmitted from a crankshaft. By changing, the opening / closing timing of the engine valve is variably controlled according to the engine operating state.

  The planetary speed reduction mechanism is configured by a planetary gear that performs planetary rotational movement by a planetary carrier that converts rotational movement into planetary rotational movement, and a thick sun gear that meshes with the planetary gear, and the planetary carrier includes the planetary gear and the sun gear. The sun gear is supported by two ball bearings provided in parallel at different positions in the direction of the rotation axis from the meshing portion.

JP 2009-185785 A

  However, in the valve timing control device described in Patent Document 1, the two ball bearings that support the planet carrier with respect to the sun gear are arranged at different positions in the rotation axis direction. The entire apparatus becomes longer in the direction of the rotation axis, and the apparatus must be enlarged.

The variable valve operating apparatus according to the present invention includes, inter alia, an electric motor whose rotational state is controlled in accordance with a control signal, and a rotational force transmitted from the output shaft of the electric motor, which is eccentric with respect to the rotation center of the output shaft. The cylindrical eccentric shaft portion, the inner peripheral mesh portion provided on the inner periphery of the first member, and the first shaft member perform planetary movement while meshing with the inner peripheral mesh portion by rotation of the eccentric shaft portion. A planetary meshing portion for rotating the second member relative to one member; a cylindrical portion formed integrally with the second member and having a bolt for fixing to another member inserted therein; A first bearing portion disposed at least partially on an inner peripheral side of a position where the inner peripheral meshing portion and the planetary meshing portion mesh, and interposed between the outer periphery of the cylindrical portion and the inner periphery of the eccentric shaft portion; With
The planetary meshing portion is provided on a second bearing portion provided on an outer periphery of the eccentric shaft portion, and is rotatably provided at a predetermined circumferential position on the outer periphery of the second bearing portion, so that the rotation of the second bearing portion is performed. A plurality of rollers whose meshing positions with the inner circumferential meshing portion move in the circumferential direction, and a cage that allows radial movement of each of the rollers and restricts circumferential movement,
The axial center position of the second bearing portion is arranged so as to overlap the first bearing portion and the roller in a radial direction at a predetermined axial position of the cylindrical portion .

  According to the present invention, the length of the apparatus in the direction of the rotation axis can be shortened by using the speed reduction mechanism having a unique structure, and as a result, the apparatus can be miniaturized.

It is a longitudinal section of one embodiment of a valve timing control device concerning the present invention. It is a principal part expanded sectional view of the main structural members in this embodiment. It is the sectional view on the AA line of FIG. It is the BB sectional view taken on the line of FIG. It is a disassembled perspective view of the cover member and 1st oil seal which are provided to this embodiment. It is CC sectional view taken on the line of FIG.

Hereinafter, an embodiment in which a variable valve operating apparatus for an internal combustion engine according to the present invention is applied to a valve timing control apparatus that varies the opening / closing timing of an engine valve will be described with reference to the drawings. In each of the embodiments, the present invention is applied to the valve operating device on the intake side of the internal combustion engine, but can also be applied to the valve operating device on the exhaust side.
[First Embodiment]
As shown in FIGS. 1 to 6, the valve timing control device is rotatably supported on a timing sprocket 1 that is a driving rotating body that is rotationally driven by a crankshaft of an internal combustion engine and a cylinder head via a bearing 44. A camshaft 2 that is rotated by the rotational force transmitted from the timing sprocket 1; a cover member 3 that is disposed at a front position of the timing sprocket 1 and is fixed to a chain cover 40 that is a fixing portion by a bolt; A phase changing mechanism 4 is provided between the timing sprocket 1 and the camshaft 2 and is a variable mechanism that changes the relative rotational phases of the both 1 and 2 according to the engine operating state.

  The timing sprocket 1 is integrally formed of an iron-based metal, and the inner peripheral surface is integrally provided on the outer periphery of the sprocket body 1a and the annular sprocket body 1a having a stepped diameter. And a gear portion 1b that receives the rotational force from the crankshaft via the timing chain 42. The timing sprocket 1 is interposed between a circular groove 1c formed on the inner peripheral side of the sprocket body 1a and an outer periphery of a thick flange portion 2a provided integrally with the front end portion of the camshaft 2. It is rotatably supported on the camshaft 2 by a third ball bearing 43 that is a third bearing.

  An annular protrusion 1b is integrally formed on the outer peripheral edge of the front end portion of the sprocket body 1a. At the front end of the sprocket body 1a, there is an annular member 19 that is coaxially positioned on the inner peripheral side of the annular protrusion 1b and has inner teeth 19a that are wavy meshing portions formed on the inner periphery. The plate 6 is fastened together by bolts 7 from the axial direction. Further, as shown in FIG. 4, a stopper convex portion 1d, which is an arc-shaped engaging portion, is formed on a part of the inner peripheral surface of the sprocket body 1a up to a predetermined length range along the circumferential direction. .

  A cylindrical housing 5 protruding forward in a state of covering components of a speed reducer 8 and an electric motor 12 described later of the phase changing mechanism 4 is fixed to the outer periphery of the front end side of the plate 6 by bolts 11. .

  The housing 5 is integrally formed of iron-based metal and functions as a yoke. The housing 5 has an annular plate-shaped holding portion 5a integrally on the front end side, and the entire outer peripheral side including the holding portion 5a is The cover member 3 is disposed so as to be covered with a predetermined gap.

  The camshaft 2 has two drive cams per cylinder for opening an intake valve (not shown) on the outer periphery, and a driven member 9 that is a driven rotating body at the front end portion is coupled from the axial direction by a cam bolt 10. Has been. Further, as shown in FIG. 4, the flange portion 2a of the camshaft 2 is formed with a stopper concave groove 2b, which is a locking portion into which the stopper convex portion 1d of the sprocket body 1a is engaged, along the circumferential direction. Has been. The stopper concave groove 2b is formed in an arc shape having a predetermined length in the circumferential direction, and both end edges of the stopper convex portion 1d rotated in this length range abut against the circumferential opposite edges 2c and 2d, respectively. Accordingly, the relative rotational position of the camshaft 2 on the maximum advance angle side or the maximum retard angle side with respect to the timing sprocket 1 is regulated. The stopper mechanism is constituted by the stopper convex portions 1d and the stopper concave groove 2b.

  The cam bolt 10 is integrally formed with the flange-like seating surface portion 10c at the end of the head portion 10a on the shaft portion 10b side, and is formed on the outer periphery of the shaft portion 10b from the end portion of the camshaft 2 to the inner axial direction. A male screw portion that is screwed onto the female screw portion is formed.

  The driven member 9 is integrally formed of an iron-based metal material, and as shown in FIG. 2, a disc portion 9a formed on the front end side and a cylindrical cylindrical portion 9b formed integrally on the rear end side. It consists of and.

  The disc portion 9a is integrally provided with an annular step protrusion 9c having substantially the same outer diameter as that of the flange portion 2a of the camshaft 2 at a substantially central position in the radial direction of the rear end surface. The outer peripheral surface of the step protrusion 9c and the flange The outer peripheral surface of the part 2a is inserted into the inner periphery of the inner ring 43a of the third ball bearing 43 while facing each other. This facilitates the shaft core operation between the camshaft 2 and the driven member 9 during assembly. The outer ring 43b of the third ball bearing 43 is press-fitted and fixed to the inner peripheral surface of the circular groove 1c of the sprocket body 1a.

  Further, as shown in FIGS. 1 to 3, a retainer 41 that holds a plurality of rollers 34 to be described later is integrally provided on the outer peripheral portion of the disk portion 9 a. The cage 41 is formed to protrude from the outer peripheral portion of the disc portion 9a in the same direction as the cylindrical portion 9b, and has a plurality of elongated protrusion portions 41a having predetermined gaps at substantially equal intervals in the circumferential direction. Is formed by.

  As shown in FIG. 1, the cylindrical portion 9 b has a through hole 9 d through which the shaft portion 10 b of the cam bolt 10 is inserted, and a first needle described later as a first bearing on the outer peripheral side. A bearing 30 is provided.

  As shown in FIGS. 1 and 5, the cover member 3 is integrally formed of a relatively thick synthetic resin material, and a cover body 3 a swelled in a cup shape, and a rear end portion of the cover body 3 a And a bracket 3b integrally provided on the outer periphery.

  The cover main body 3a is disposed so as to cover the front end side of the phase changing mechanism 4, that is, to cover substantially the entire rear end side from the axial holding portion 5b of the housing 5 with a predetermined gap. On the other hand, the bracket 3b is formed in a substantially annular shape, and bolt insertion holes 3f are formed through the six boss portions.

  Further, as shown in FIG. 1, the cover member 3 has the bracket 3b fixed to the chain cover 40 via a plurality of bolts 47, and is attached to the inner peripheral surface of the front end portion 3c of the cover body 3a. Inner and outer double slip rings 48a and 48b are embedded and fixed with their inner end faces exposed. Further, at the upper end portion, there is provided a connector portion 49 in which a connector terminal 49a connected to the slip rings 48a, 48b via a conductive member is fixed. The connector terminal 49a is energized or de-energized from a battery power source (not shown) via the control unit 21.

  A large-diameter first oil seal 50, which is a seal member, is interposed between the inner peripheral surface on the rear end side of the cover body 3a and the outer peripheral surface of the housing 5, as shown in FIG. It is disguised. The first oil seal 50 is formed in a substantially U-shaped cross section, a core metal is embedded in the synthetic rubber base material, and an annular base 50a on the outer peripheral side is formed at the rear end of the cover member 3a. It is fitted and fixed in a circular groove 3d formed on the inner peripheral surface of the part. Further, a seal surface 50b that comes into contact with the outer peripheral surface of the housing 5 is integrally formed on the inner peripheral side of the annular base portion 50a.

  The phase changing mechanism 4 includes an electric motor 12 that is an actuator disposed substantially coaxially on the front end side of the camshaft 2, and the speed reducer 8 that reduces the rotational speed of the electric motor 12 and transmits it to the camshaft 2. And is composed of.

  As shown in FIGS. 1 and 2, the electric motor 12 is a brushed DC motor, the housing 5 being a yoke that rotates integrally with the timing sprocket 1, and the housing 5 is rotatable inside the housing 5. A motor shaft 13 that is an output shaft, a pair of semicircular permanent magnets 14 and 15 fixed to the inner peripheral surface of the housing 5, and a stator fixed to the inner bottom surface side of the housing holding portion 5a. 16.

  The motor shaft 13 is formed in a cylindrical shape and functions as an armature, and an iron core rotor 17 having a plurality of poles is fixed to the outer periphery at a substantially central position in the axial direction. An electromagnetic coil 18 is wound. A commutator 20 is press-fitted and fixed to the outer periphery of the front end portion of the large-diameter rotating shaft 17, and the electromagnetic coil 18 is divided into each segment divided into the same number as the number of poles of the iron core rotor 17a. It is connected.

  As shown in FIG. 6, the stator 16 includes an annular plate-shaped resin holder 22 fixed to the inner bottom wall of the holding portion 5a by four screws 22a, the resin holder 22 and the holding portion 5a. Two first brushes 23a and 23b in the circumferential direction that are arranged in an axial direction so that each tip surface is slidably contacted with the pair of slip rings 48a and 48b and inward on the inner peripheral side of the resin holder 22 The second brushes 24a and 24b, which are held so as to freely move back and forth and whose arcuate tip end is in sliding contact with the outer peripheral surface of the commutator 20, are mainly configured.

  The first brushes 23a, 23b and the second brushes 24a, 24b are connected to each other by pigtail harnesses 25a, 25b. Each is biased toward the commutator 20.

  The motor shaft 13 is a needle bearing 28 which is a first bearing on the outer peripheral surface of the shaft portion 10b on the head 10a side of the cam bolt 10 and a bearing which is disposed on a side portion in the axial direction of the needle bearing 28. A ball bearing 35 is rotatably supported. A cylindrical eccentric shaft portion 30 constituting a part of the speed reducer 8 is integrally provided at the rear end portion of the motor shaft 13 on the camshaft 2 side.

  The first needle bearing 28 includes a cylindrical retainer 28a that is press-fitted into the inner peripheral surface of the eccentric shaft portion 30, and a needle roller 28b that is a plurality of rolling elements rotatably held inside the retainer 28a. It is configured. The needle roller 28 b rolls on the outer peripheral surface of the cylindrical portion 9 b of the driven member 9.

  In the fourth ball bearing 35, the inner ring 35 a is fixed in a sandwiched state between the front end edge of the cylindrical portion 9 b of the driven member 9 and the seat surface portion 10 c of the cam bolt 10, while the outer ring 35 b is fixed inside the motor shaft 13. Axial positioning is supported between a step formed on the periphery and a snap ring 36 which is a retaining ring.

  In addition, a friction member is provided between the outer peripheral surface of the motor shaft 13 (eccentric shaft portion 30) and the inner peripheral surface of the plate 6 to prevent leakage of lubricating oil from the inside of the speed reducer 8 into the electric motor 12. A second oil seal 32 is provided. The second oil seal 32 is configured to give a frictional resistance against the rotation of the motor shaft 13 by the inner peripheral portion being in elastic contact with the outer peripheral surface of the motor shaft 13.

  The control unit 21 detects the current engine operating state based on information signals from various sensors such as a crank angle sensor, an air flow meter, a water temperature sensor, an accelerator opening sensor, and the like, and performs engine control. The electromagnetic coil 18 is energized to control the rotation of the motor shaft 13 and the relative rotation phase of the camshaft 2 with respect to the timing sprocket 1 is controlled via the speed reducer 8.

  As shown in FIGS. 1 and 2, the speed reducer 8 includes the eccentric shaft portion 30 that performs an eccentric rotational motion, and a second ball bearing 33 that is a second bearing provided on the outer periphery of the eccentric shaft portion 30. The roller 34 provided on the outer periphery of the second ball bearing 33, the retainer 41 that allows the roller 34 to move in the radial direction while retaining the roller 34 in the rolling direction, and the retainer 41 integrated with the retainer 41. The driven member 9 is mainly composed of.

  In the eccentric shaft portion 30, the axis Y of the cam surface formed on the outer peripheral surface is slightly eccentric in the radial direction from the axis X of the motor shaft 13. The second ball bearing 33 and the roller 34 are configured as a planetary meshing portion.

  The second ball bearing 33 is formed in a large diameter, and is disposed so as to be substantially overlapped at the radial position of the first needle bearing 28, and the inner ring 33 a is disposed on the outer peripheral surface of the eccentric shaft portion 30. While being press-fitted and fixed, the roller 34 is always in contact with the outer peripheral surface of the outer ring 33b. Further, an annular gap C is formed on the outer peripheral side of the outer ring 33b, and the entire second ball bearing 33 can be moved in the radial direction along with the eccentric rotation of the eccentric shaft portion 30 by this gap C. It is possible.

  Each of the rollers 34 is fitted in the inner teeth 19a of the annular member 19 while moving in the radial direction along with the eccentric movement of the second ball bearing 33, and is guided in the circumferential direction by the protrusion 41a of the retainer 41. While swinging in the radial direction.

  Lubricating oil is supplied into the speed reducer 8 by lubricating oil supplying means. As shown in FIG. 1, the lubricating oil supply means is formed inside a bearing 44 of the cylinder head, and supplies an oil supply passage 47 for supplying lubricating oil from a main oil gallery outside the figure, and the camshaft 2. The oil supply hole 48 is formed in the direction of the inner axis of the oil supply passage 47 and communicates with the oil supply passage 47 via a groove groove. The oil supply hole 48 is formed to penetrate the oil supply hole 48 in the direction of the inner axis of the driven member 9. The small-diameter oil supply hole 45 opened at the other end in the vicinity of the first needle bearing 28 and the second ball bearing 33 and the three large-diameter unillustrated holes formed in the driven member 9 are also shown. And an oil discharge hole.

  Hereinafter, the operation of this embodiment will be described. First, when the crankshaft of the engine is rotationally driven, the timing sprocket 1 is rotated via the timing chain 42, and the rotational force is transmitted via the housing 5, the annular member 19 and the plate 6. Thus, the electric motor 12 rotates synchronously. On the other hand, the rotational force of the annular member 19 is transmitted from the roller 34 to the camshaft 2 via the retainer 41 and the driven member 9. As a result, the cam of the camshaft 2 opens and closes the intake valve.

  Then, during a predetermined engine operation after the engine is started, the electromagnetic coil 17 of the electric motor 12 is energized from the control unit 21 via the slip rings 48a and 48b. As a result, the motor shaft 13 is rotationally driven, and the rotational force obtained by reducing the rotational force is transmitted to the camshaft 2 via the speed reducer 8.

  That is, when the eccentric shaft portion 30 rotates eccentrically with the rotation of the motor shaft 13, each roller 34 is guided in the radial direction by the protrusion 41 a of the retainer 41 for each rotation of the motor shaft 13. It moves while rolling over one internal tooth 19a and moving to another adjacent internal tooth 19a, and rolling in the circumferential direction while repeating this. The rotational force is transmitted to the driven member 9 while the rotation of the motor shaft 13 is decelerated by the rolling contact of the rollers 34. The reduction ratio at this time can be arbitrarily set according to the number of the rollers 34 or the like.

  As a result, the camshaft 2 rotates relative to the timing sprocket 1 in the forward and reverse directions and the relative rotational phase is converted, so that the opening / closing timing of the intake valve is controlled to be advanced or retarded.

  The maximum position restriction (angular position restriction) of the forward and reverse relative rotation of the camshaft 2 with respect to the timing sprocket 1 is that each side surface of the stopper convex portion 1d is one of the opposing surfaces 2c and 2d of the stopper concave groove 2b. This is done by contacting one side.

  That is, the driven member 9 rotates in the same direction as the rotation direction of the timing sprocket 1 as the eccentric shaft portion 30 rotates eccentrically, so that one side surface of the stopper convex portion 1d is one side of the stopper groove 2b. Further rotation in the same direction is restricted by abutting against the opposite surface 1c. As a result, the relative rotation phase of the camshaft 2 with respect to the timing sprocket 1 is changed to the maximum on the advance side.

  On the other hand, when the driven member 9 rotates in the direction opposite to the rotation direction of the timing sprocket 1, the other side surface of the stopper convex portion 1d abuts against the opposite surface 2d on the other side of the stopper concave groove 2b and further in the same direction. Rotation is regulated. As a result, the relative rotation phase of the camshaft 2 with respect to the timing sprocket 1 is changed to the maximum on the retard side.

  As a result, the opening / closing timing of the intake valve is converted to the maximum on the advance side or the retard side, and the fuel efficiency and output of the engine can be improved.

  Thus, in this embodiment, the relative rotational position of the camshaft 2 can be reliably regulated by the stopper mechanism of the stopper convex portion 1d and the stopper concave groove 2b.

  In the present embodiment, the first needle bearing 28 and the second ball bearing 33 of the speed reducer 8 are disposed at substantially the same radial position, and in particular, the annular member is disposed at the same radial position as the first needle bearing 28. Since 19 and the roller 34 are disposed, the length of the apparatus in the axial direction can be sufficiently shortened. As a result, the apparatus can be reduced in size and weight.

  In addition, since the structure of the speed reducer 8 is simplified, manufacturing work and assembly work are facilitated, and these costs can be sufficiently reduced.

  Further, since the first needle bearing 28 is disposed on the radially inner peripheral side of the position where the tooth surface of the inner tooth 19a of the annular member 19 and the roller 34 mesh with each other, the first needle bearing 28 acts radially inward from the annular member 19 side. A large load can be received by the first needle bearing 28. For this reason, a bending moment due to the load hardly acts on the motor shaft 13. Therefore, the motor shaft 13 can always rotate smoothly.

  Further, since the lubricating oil is forcibly supplied into the reduction gear 8 from the oil supply hole 45, the lubricity of each part of the reduction gear 8 is improved, and the gap between the inner teeth 19a and the roller 34 is improved. Lubricating oil is supplied to the first needle bearing 28 and the second ball bearing 33, and the lubricity between the rollers 28b and 34 and the balls is improved, so that the reduction gear 8 always performs smooth phase conversion. Needless to say, since this lubricating oil exhibits a buffering function, it is possible to more effectively suppress the occurrence of the hitting sound.

  In particular, during the driving of the engine, the lubricating oil pumped from the oil pump is constantly supplied and immersed through the lubricating oil supply means, so that the occurrence of oil film breakage of each rolling element can be suppressed. Thereby, the initial driving load of the electric motor 12 can be sufficiently reduced, and the control response of the valve timing can be improved and the energy consumption can be reduced.

  The lubricating oil discharged from the inside of the speed reducer 8 through the oil discharge holes adheres to the third ball bearing 43 due to centrifugal force and also adheres to the gear portions 1b of the timing sprocket 1. Thus, these parts are lubricated efficiently. Thereafter, the gears 1 b are scattered outward by the rotational centrifugal force, and the scattered lubricating oil adheres to the outer peripheral surface of the rear end side of the housing 5 and comes into contact with the seal surface 50 b of the first oil seal 50. For this reason, generation | occurrence | production of the abrasion of the seal surface 50b accompanying rotation of the housing 5 is suppressed, and durability of the 1st oil seal 50 can be improved.

  Furthermore, since the motor shaft 13 and the eccentric shaft portion 30 are supported by the cam bolt 10 via the first needle bearing 28 and the fourth ball bearing 35, it is not necessary to provide a separate support shaft, and the number of parts can be reduced. Since the camshaft 2 is directly coupled to the camshaft 2 from the axial direction, the camshaft 2 is prevented from falling in the radial direction and high coaxiality is obtained.

  Further, since the speed reducer 8 and the electric motor 12 can be integrated by the housing 5 and can also be integrated with the timing sprocket 1 through the sprocket main body 1a, as shown in FIG. Can be unitized. Therefore, it is possible to reduce the size in the radial direction in addition to the axial direction of the apparatus and to facilitate product management.

  Furthermore, since the cover member 3 is formed of a synthetic resin material, the overall weight of the engine can be reduced, and the slip rings 48a and 48b and the connector terminals 49a can be provided integrally. Manufacturing work is facilitated.

  Further, since the second oil seal 32 imparts frictional resistance to the motor shaft 13, it absorbs the alternating torque generated in the camshaft 2 by the spring force of the valve spring and the like, thereby suppressing the load on the electric motor 12. can do.

  Further, by integrating the motor shaft 13 and the eccentric shaft portion 30, the number of parts can be reduced as compared with the case where the motor shaft 13 and the eccentric shaft portion 30 are divided, and the assembling and manufacturing operations are facilitated. Can be achieved.

  The present invention is not limited to the above-described embodiment. For example, the variable valve operating device can be applied to a variable mechanism that makes the lift amount and operating angle of an engine valve variable in addition to the valve spring control device. .

The technical ideas of the invention other than the claims ascertained from the embodiment will be described below.
[Claim a] The variable valve operating apparatus for an internal combustion engine according to claim 2,
The variable valve operating apparatus for an internal combustion engine, wherein the first bearing portion is formed by a needle bearing.
[Claim b] In the variable valve operating apparatus for an internal combustion engine according to claim a,
A variable valve operating apparatus for an internal combustion engine, comprising a ball bearing disposed adjacent to the needle bearing and restricting the movement of the eccentric shaft portion and the driven rotor in the rotational axis direction.
[Claim c] A variable valve operating apparatus for an internal combustion engine according to claim b,
In the ball bearing, an inner ring is clamped and fixed in the rotation axis direction by the driven rotator and a cam bolt for fixing the driven rotator to the camshaft, and an outer ring is a stepped portion formed on the inner periphery of the eccentric shaft portion. A variable valve operating apparatus for an internal combustion engine, wherein the variable valve operating apparatus is arranged and held between the retaining ring and the retaining ring.
[Claim d] In the variable valve operating apparatus for an internal combustion engine according to claim 2,
The planetary meshing part is
A second bearing portion provided on the outer periphery of the eccentric shaft portion;
A plurality of rollers provided on the outer periphery of the second bearing portion so as to be rotatable at a predetermined interval position in the circumferential direction, and a meshing portion with the annular member is moved in the circumferential direction by the rotation of the second bearing portion;
A cage that allows radial movement of each roller and restricts circumferential movement;
A variable valve operating apparatus for an internal combustion engine, wherein the retainer is fixed to a driven rotor.
(Claim e) In the variable valve operating apparatus for an internal combustion engine according to claim d,
The variable valve operating apparatus for an internal combustion engine, wherein the roller, the first bearing portion, and the second bearing portion are all disposed at substantially the same position in the rotation axis direction.

According to this invention, the arrangement position of the roller and the arrangement position of the first and second bearing portions are substantially the same at a predetermined position in the axial direction, so that the axial length of the apparatus can be shortened. This makes it possible to reduce the size.
[Claim f] The variable valve operating apparatus for an internal combustion engine according to claim e,
The variable valve operating apparatus for an internal combustion engine, wherein the second bearing portion is constituted by a ball bearing.
[Claim g] In the variable valve operating apparatus for an internal combustion engine according to claim d,
A variable valve operating apparatus for an internal combustion engine, comprising a friction member that imparts rotational resistance to the eccentric shaft portion when an alternating torque is applied to the cage from the camshaft.

This friction member can suppress transmission of alternating torque generated in the camshaft to the eccentric shaft portion.
(Claim h) In the variable valve operating apparatus for an internal combustion engine according to claim d,
A seal member that gives rotational resistance to the eccentric shaft portion is elastically contacted between the outer periphery of the eccentric shaft portion and the drive rotating body, and the electric motor, the annular member, and the planetary meshing portion by the seal member. A variable valve operating apparatus for an internal combustion engine, wherein the lubricating oil is separated from each other in a liquid-tight manner and lubricating oil is supplied only to the meshing side of the annular member and the planetary meshing portion.
[Claim i] In the variable valve operating apparatus for an internal combustion engine according to claim 2,
A variable valve operating apparatus for an internal combustion engine, wherein a third bearing portion is provided between the drive rotator and the driven rotator, and a part of a camshaft is inserted into the third bearing.
(Claim j) In the variable valve operating apparatus for an internal combustion engine according to claim i,
The variable valve operating apparatus for an internal combustion engine, wherein the third bearing is constituted by a ball bearing.
[Claim k] The variable valve operating apparatus for an internal combustion engine according to claim j,
An internal combustion engine characterized in that the driven rotating body and the camshaft are fixed by a cam bolt in a state where both the driven rotating body and the camshaft are inserted into an inner peripheral surface of an inner ring of the third ball bearing. Variable valve gear.

According to the present invention, the inner ring facilitates the alignment operation of the driven rotor and the camshaft.
[Claim 1] In the variable valve operating apparatus for an internal combustion engine according to claim 2,
A variable valve operating apparatus for an internal combustion engine, comprising a stopper mechanism for restricting a maximum relative rotational position between the drive rotating body and the camshaft.
[Claim m] In the variable valve operating apparatus for an internal combustion engine according to claim l,
The stopper mechanism is provided at an engagement portion provided at an end portion of the camshaft and an end portion on the camshaft side of the drive rotating body, and is locked to the engagement portion at a predetermined forward / reverse rotation position. A variable valve operating apparatus for an internal combustion engine, characterized by comprising a locking portion.
(Claim n) In the variable valve operating apparatus for an internal combustion engine according to claim m,
A variable valve operating apparatus for an internal combustion engine, wherein the driven rotating body and the camshaft are connected and fixed in the axial direction by a cam bolt.

1. Timing sprocket (rotating drive)
2 ... camshaft 3 ... cover member 3a ... cover body 4 ... phase change mechanism 5 ... housing 6 ... plate 8 ... speed reducer 9 ... driven member (driven rotating body)
DESCRIPTION OF SYMBOLS 10 ... Cam bolt 12 ... Electric motor 13 ... Motor shaft 17 ... Iron core rotor 18 ... Electromagnetic coil 19 ... Ring member 19a ... Internal tooth 23a, 23b ... Brush 24a, 24b ... Brush 28 ... 1st needle bearing (bearing part)
30 ... Eccentric shaft portion 32 ... Second oil seal 33 ... Second ball bearing 34 ... Roller 35 ... Fourth ball bearing 43 ... Third ball bearing 45 ... Oil supply hole 46 ... Oil discharge holes 48a, 48b ... Slip ring 50 ... 1st oil seal

Claims (4)

A variable valve operating apparatus for an internal combustion engine that changes an operating characteristic of an engine valve biased in a closing direction by a valve spring by changing a relative rotational position of a second member with respect to the first member,
An electric motor whose rotation state is controlled according to a control signal;
A rotational force is transmitted from the output shaft of the electric motor, and a cylindrical eccentric shaft portion that is eccentric with respect to the rotation center of the output shaft;
An inner periphery meshing portion provided on an inner periphery of the first member;
A planetary meshing portion for rotating the second member relative to the first member by performing planetary movement while meshing with the inner circumferential meshing portion by rotation of the eccentric shaft portion;
A cylindrical portion formed integrally with the second member and having a bolt for fixing to another member inserted therein;
At least a portion is disposed on the inner peripheral side of the position where the inner peripheral meshing portion and the planetary meshing portion mesh with each other in the rotation axis direction, and is interposed between the outer periphery of the cylindrical portion and the inner periphery of the eccentric shaft portion. 1 bearing part;
With
The planetary meshing portion is provided on a second bearing portion provided on an outer periphery of the eccentric shaft portion, and is rotatably provided at a predetermined circumferential position on the outer periphery of the second bearing portion, so that the rotation of the second bearing portion is performed. A plurality of rollers whose meshing positions with the inner circumferential meshing portion move in the circumferential direction, and a cage that allows radial movement of each of the rollers and restricts circumferential movement,
The internal combustion engine is characterized in that the axial center position of the second bearing portion is arranged to overlap the first bearing portion and the roller in a radial direction at a predetermined axial position of the cylindrical portion. Variable valve device. The variable valve operating apparatus for an internal combustion engine according to claim 1,
The variable valve operating apparatus for an internal combustion engine, wherein the first bearing portion is formed by a needle bearing. The variable valve operating apparatus for an internal combustion engine according to claim 2,
A variable valve operating apparatus for an internal combustion engine, comprising a ball bearing disposed adjacent to the needle bearing and restricting the movement of the eccentric shaft portion and the driven rotor in the rotational axis direction. The variable valve operating apparatus for an internal combustion engine according to claim 3,
The ball bearing has an inner ring sandwiched and fixed from the rotation axis direction by the second member and the bolt for fixing the second member, and an outer ring formed on the inner periphery of the eccentric shaft portion and a retaining ring. The variable valve operating apparatus for an internal combustion engine, wherein the variable valve operating apparatus is held between the two.

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