JP2003120228A - Valve timing control device of internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve product quality by preventing the production of an abnormal sound, which is caused by the backlash of a link arm 14 in the valve timing control device of an internal combustion engine having a constitution for displacing one end side of the link arm 14 in the peripheral direction by sliding the other end radially as a mounting angle adjusting mechanism 4 for relatively displacing the mounting angle between a drive plate 2 to which rotation is transmitted from the internal combustion engine and a spacer 8, which is integral with a cam shaft 1. SOLUTION: In the valve timing control device of the internal combustion engine which is constituted such that when the link arm 14 of the mounting angle adjusting mechanism 4 is displaced along with the movement of the cylindrical section 14a in a radial direction so that the mounting angle between the cam shaft 1 and the drive plate 2 is relatively displaced, the link arm 14 is arranged so that it abuts on a guide plate 24 and the drive plate 2 slidably.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve timing control device for controlling the valve timing of at least one of an intake valve and an exhaust valve of an internal combustion engine according to operating conditions.

[0002]

2. Description of the Related Art Conventionally, a valve timing device for an internal combustion engine has a drive rotary member, which receives rotation from a drive shaft of the internal combustion engine, and a driven rotary member on the camshaft side, which are relative to each other by an assembly angle adjusting mechanism. By changing the assembling angle, the valve opening / closing timing is displaced to the retard side and the advance side.

In such a valve timing control device for an internal combustion engine, the applicant of the present application has found that the rotating portion at one end is driven and rotated as an assembly angle adjusting mechanism for changing the assembly angle between the driving rotor and the driven rotor. It is rotatably connected to one of the body and the driven rotary body, and the slide portion at the other end is connected to be slidable in the radial direction by a radial guide provided on the other of the drive rotary body and the driven rotary body. And a rotational position of the rotating portion is displaced in the circumferential direction as the slide portion is moved in the radial direction, so that the assembling angle of the driving rotary body and the driven rotary body is relatively displaced. The structured one was proposed earlier.

This conventional technique is disclosed in Japanese Patent Laid-Open No. 2001-4101.
No. 3 publication, a housing as a driving rotary body is supported rotatably on the outer periphery of a cam shaft as a driven rotary body, and a guide plate is coaxially provided so as to face the housing. There is. Then, one end of the link arm is rotatably connected to the axial center portion of the cam shaft, and a movable operation member provided at the other end of the link arm is connected to an intermediate portion of the housing so as to be slidable in the radial direction. At the same time, it is connected to a spiral guide provided on the end face of the guide plate so as to be displaced in the radial direction by the displacement in the circumferential direction.

Further, the guide plate is urged to rotate in a predetermined direction by a spiral spring, and an electromagnet can apply a braking force against the urging direction of the spiral spring. Therefore, when a braking force is applied to the guide plate by the electromagnet, the guide plate rotates relative to the housing, and the displacement of the spiral guide thereby displaces the movable operation member in the radial direction with respect to the housing, and the link arm rotates. The camshaft is pushed by the lever, and the relative assembly position of the housing and the camshaft is displaced.

[0006]

However, in the above-mentioned prior art, the link arm is supported by the intermediate portion of the movable operation member, and the housing (drive unit) is disposed in the axial front-rear direction with the link arm interposed therebetween. Since a space is interposed between the link arm and the rotating body) and the guide plate, a gap is inevitably created in the axial direction between the link arm and the support portions at both ends of the link arm, and the load is applied to the link arm. When was applied, the link arm would swing in the axial direction, causing rattling and abnormal noise.

The present invention has been made by paying attention to the above-mentioned conventional problems, and the relative assembly angles of the driving rotary body to which rotation is transmitted from the internal combustion engine and the driven rotary body on the camshaft side are relative to each other. In a valve timing control device of an internal combustion engine having a structure in which one end of a link arm is slid in the radial direction and the other end is displaced in the circumferential direction as a mounting angle adjusting mechanism for displacement, abnormal noise due to rattling of the link arm The purpose of this is to prevent the occurrence of noise, improve product quality, and further reduce costs and improve operation quality.

[0008]

In order to achieve the above object, a valve timing control device for an internal combustion engine according to the present invention has a drive rotor to which rotation is transmitted from a drive shaft of the internal combustion engine, and a coaxial drive with the drive rotor. And a driven rotary body formed of a cam shaft for driving at least one of an intake valve and an exhaust valve of the internal combustion engine or a separate member coupled to the shaft, and the driven rotary body and the drive rotary body. An assembly angle adjusting mechanism for rotating the assembly relative to each other, and an actuating device for operating the assembly angle adjusting mechanism. The assembly angle adjusting mechanism has a rotating portion at one end and a driven rotating body. A link arm that is rotatably connected to one of the body and a slide portion of the other end that is slidably connected in the radial direction by a radial guide provided on the other of the driving rotary body and the driven rotary body. Comprising the With the radial movement of the ride portion is configured such that the position of the rotating portion is assembling angle between circumferentially displaced by driving rotor and the driven rotor relative displacement,
The actuating device includes a guide plate that is disposed adjacent to the link arm and is rotatable coaxially with the driven rotor, and the guide plate has the slide portion in the radial direction in accordance with its rotation. In the valve timing control device for an internal combustion engine in which a spiral spiral guide to be displaced is formed, the link arm is slidably brought into contact with the guide plate and arranged.

According to a second aspect of the present invention, in the valve timing control device for an internal combustion engine according to the first aspect, the link arm is slidably held between the guide plate and the radial guide. It was used as a characteristic means.

According to a third aspect of the present invention, in the valve timing control device for an internal combustion engine according to the first or second aspect, a lubricating passage supply passage for supplying lubricating oil toward the spiral guide is formed, and the guide is provided. The spiral guide is arranged within the contact area between the plate and the link arm.

According to a fourth aspect of the present invention, in the valve timing control device for an internal combustion engine according to any of the first to third aspects, a spiral guide groove formed on an end face of the guide plate is used as the spiral guide. Provided on the slide portion of the link arm are a sphere moving along the spiral guide groove and an accommodation hole for accommodating the sphere, and the periphery of the accommodation hole on an end face of the link arm facing the guide plate. Is a means characterized in that a step portion is formed in a non-contact state with the guide plate.

[0012]

According to the invention described in claim 1, since the link arm slidably contacts the guide plate, the link arm is prevented from swinging in the axial direction. It is possible to prevent rattling and noise.

According to the second aspect of the invention, since the link arm is slidably held between the guide plate and the radial guide, the link arm is prevented from falling off the radial guide. Without the need for a separate means
The link arm will not fall out of the radial guide. Therefore, in addition to the effect of the invention described in claim 1, the effect that the number of parts can be reduced can be obtained.

According to the third aspect of the present invention, the lubricating oil is supplied to the spiral guide through the lubricating passage supply passage when the apparatus is operating. The lubricating oil smoothly slides between the spiral guide and the slide part of the link arm, and the lubricating oil is supplied to the part of the link arm that overlaps the spiral guide, so that the link arm and the guide plate slide. Is done smoothly. Therefore, in addition to the effects described in claim 1 and claim 2, the effect that the operation stability can be improved by smoothing the sliding of the link arm is achieved.

According to the fourth aspect of the present invention, since the periphery of the accommodation hole for accommodating the sphere moving along the spiral guide groove and the guide plate are not in contact with each other, the link arm and the guide plate are separated from each other. When relatively displaced, the peripheral edge of the accommodation hole and the edge of the spiral guide groove are not caught,
The operability can be improved. Therefore, in addition to the effects of the invention described in claims 1 to 3, there is an effect that the operability can be further improved.

[0016]

BEST MODE FOR CARRYING OUT THE INVENTION A valve timing control device for an internal combustion engine according to an embodiment of the present invention will be described with reference to the drawings. 1 is a cross-sectional view of a valve timing control device for an internal combustion engine according to an embodiment, FIG. 2 is an exploded perspective view of the device, FIGS. 3 and 4 are operation explanatory views of the main parts of the device, and FIG. FIG. 6 is an enlarged cross-sectional view of the main part, and FIG. 6 is a view seen from the direction of arrow D in FIG.

Although the valve timing control device for an internal combustion engine of the above-described embodiment is applied to the intake side of the internal combustion engine, it can be similarly applied to the exhaust side.

This valve timing control device is mainly composed of a camshaft 1, a drive plate 2, an assembly angle operating mechanism 4, an actuating device 15, a VTC cover 6 and a controller 7 shown in FIG. I am trying. To briefly explain these configurations, the camshaft 1 is
The operation of opening and closing the engine valve 71 on the intake side is performed.
The drive plate 2 is a member that rotates when the rotation is transmitted from the engine. The assembly angle operating mechanism 4 is a mechanism for arbitrarily changing the relative assembly angle between the cam shaft 1 and the drive plate 2. The actuating device 15 is a device for actuating the assembly angle operating mechanism 4. The VTC cover 6
Is mounted over the cylinder head (not shown) and the front end surface of the rocker cover, and is attached to the drive plate 2 and the assembly angle operation mechanism 4.
It is a cover that covers the front surface and the surrounding area. The controller 7 controls the operation of the operating device 15 according to the operating condition of the engine.

The above-mentioned components will be described in detail below. First, the camshaft 1 shown in FIG. 1 will be described. The camshaft 1 is rotatably supported by a cylinder head of an engine, and an intake valve driving cam 70 provided on the outer periphery of the engine causes the camshaft 1 to rotate. The engine valve 71 that opens and closes the intake port is opened and closed against the biasing force of the valve spring 73 that biases in the closing direction. A spacer 8 is fitted to the front end portion of the camshaft 1 (the left side is the front side in FIG. 1), and the spacer 8 has a larger diameter than the general portion of the camshaft 1f. The rotation is restricted by the pin 80. A plurality of oil supply holes 1r are formed through the camshaft 1 in the radial direction.

As shown in FIG. 2, the spacer 8 has a disk-shaped locking flange 8a, a circular tube-shaped circular tube portion 8b extending axially from the front end surface of the locking flange 8a, and the same locking. A shaft support portion 8d is formed on the front end surface of the flange 8a, which extends from the base end portion of the circular pipe portion 8b in three outer diameter directions and has a press-fitting hole 8c parallel to the axial direction. The shaft support portion 8d and the press-fitting holes 8c are arranged at intervals of 120 ° in the circumferential direction, as shown in FIG. Further, the spacer 8 has an oil supply hole 8r for supplying oil.
Are formed so as to penetrate in the radial direction.

The drive plate 2 has a through hole 2a at the center thereof.
Is formed into a disk shape and is rotatably assembled to the spacer 8 in a state where the axial displacement is restricted by the locking flange 8a. Further, the drive plate 2 is, as shown in FIG.
A timing sprocket 3 to which rotation is transmitted from the engine through a chain (not shown) is formed on the outer periphery of the rear portion. Further, three guide grooves 2g are formed in the outer diameter direction on the front end face by connecting the through hole 2a and the outer circumference. These guide grooves 2g are arranged at intervals of 120 ° in the circumferential direction, like the shaft supporting portion 3d. Further, an annular cover member 2c is fixed to the outer peripheral portion of the front end face by welding or press fitting.

In the present embodiment, the driven rotary body in the present invention is constituted by the cam shaft 1 and the spacer 8, and the drive rotary body is constituted by the drive plate 2 including the timing sprocket 3. The means for transmitting the rotation to the drive plate 2 is not limited to the chain described above, but may be other means such as a belt or a gear.

The assembling angle operation mechanism 4 includes the camshaft 1
It is arranged on the front end side of the drive plate 2 to change the relative assembly angle between the camshaft 1 and the drive plate 2. As shown in FIG. 2, this assembly angle operation mechanism 4
It has three link arms 14. Each link arm 14 is provided with a cylindrical portion 14a as a slide portion at the tip portion, and an arm portion 14b extending from the cylindrical portion 14a in the outer diameter direction is provided. A housing hole 14c is formed through the cylindrical portion 14a, while a rotation hole 14d as a rotation portion is formed through the base end of the arm portion 14b.

The link arms 14 are mounted rotatably around the pivot pin 81 by mounting the pivot hole 14d into the pivot pin 81 that is tightly press-fitted into the press-fit hole 8c of the spacer 8. ing. On the other hand, the cylindrical portion 14a of the link arm 14 is inserted into a guide groove 2g as a radial guide of the drive plate 2 and is attached to the drive plate 2 so as to be movable in the radial direction. When the link arm 14 is made rotatable about the rotation pin 81, the rotation pin 81 is integrally fixed to the link arm 14, and the rotation pin 81 is rotated with respect to the spacer 8. You may do it.

Therefore, in the assembly angle operation mechanism 4, when the cylindrical portion 14a receives an external force and is radially displaced along the guide groove 2g, the pivot pin 81 moves in the radial direction by the link action of the link arm 14. Since the cam shaft 1 is moved in the circumferential direction by an angle corresponding to the amount of displacement, the displacement of the rotating pin 81 causes the cam shaft 1 to rotate relative to the drive plate 2. 3 and 4 show the operation of the assembly angle operation mechanism 4, and as shown in FIG. 3, when the cylindrical portion 14a is arranged on the outer peripheral side of the drive plate 2 in the guide groove 2g, The pivot pin 81 at the base end is pulled to a position close to the guide groove 2g, and this position is the most retarded position in the present embodiment. On the other hand, as shown in FIG. 4, when the cylindrical portion 14a is arranged on the inner peripheral side of the drive plate 2 in the guide groove 2g, the rotating pin 81 is pushed in the circumferential direction to separate from the guide groove 2g. In this embodiment, this position is the most advanced position. In the present embodiment, the relative angle between the most retarded angle position shown in FIG. 3 and the most advanced angle position shown in FIG. 4 differs by approximately 30 degrees. It is dependent and is not limited to 30 degrees.

Cylindrical portion 1 in the assembly angle operating mechanism 4 described above.
The radial movement of 4a is performed by the actuating device 15, and the actuating device 15 includes an actuation conversion mechanism 40,
An acceleration / deceleration mechanism 41 is provided.

The operation converting mechanism 40 includes the link arm 1
4 is provided with a sphere 22 held by a cylindrical portion 14a and a guide plate 24 that is coaxially provided so as to face the front surface of the drive plate 2, and the guide plate 24 is rotated to rotate the cylindrical portion 14a of the link arm 14. This is a mechanism for converting into a radial displacement of. The configuration will be described below.

The guide plate 24 is supported on the outer circumference of the circular pipe portion 8b of the spacer 8 so as to be relatively rotatable via a metallic bush 23. Further, on the rear surface of the guide plate 24, a spiral guide groove 2 as a spiral guide which has a substantially semicircular cross section and is displaced in the radial direction along with the displacement in the circumferential direction.
8 is formed, and an oil supply hole 24r for supplying oil is formed in the middle portion in the radial direction so as to penetrate in the front-rear direction.

In the spiral guide groove 28, the sphere 22
Are engaged. That is, as shown in FIGS. 1 and 2, a disc-shaped support panel 22a, a coil spring 22b, a retainer 22c, and a ball 22 are provided in the accommodation hole 14c provided in the cylindrical portion 14a of the link arm 14. Are inserted in order. Further, the retainer 22c has a bowl-shaped support recess 22d for supporting the ball 22 in a protruding state at the front end thereof, and a flange 22f on the outer periphery of which the coil spring 22b is seated. Then, in the assembled state shown in FIG. 1, the coil spring 22b is shortened, the support panel 22a is pressed against the front surface of the drive plate 2, and the sphere 22 is pressed against the spiral guide groove 28 to engage in the vertical direction. Together, they can move relative to each other in the extending direction of the spiral guide groove 28. In addition, the spiral groove 28 is formed as shown in FIGS.
As shown in, the diameter is gradually reduced along the rotation direction R of the drive plate 2.

Therefore, in the operation converting mechanism 40, when the guide plate 24 rotates relative to the drive plate 2 in the rotation direction R in a state where the ball 22 is engaged with the spiral guide groove 28, the ball 22 is moved at this time. It moves radially outward along the spiral shape of the spiral guide groove 28, whereby the cylindrical portion 14a as the slide portion moves in the outer diameter direction shown in FIG. 3, and the rotating pin 81 connected to the link arm 14 is moved. Are attracted so as to approach the guide groove 2g, and the camshaft 1 moves in the retard direction.

On the contrary, when the guide plate 24 rotates relative to the drive plate 2 in the direction opposite to the rotation direction R from this state, the sphere 22 moves radially inward along the spiral shape of the spiral guide groove 28. As a result, the cylindrical portion 14a as the slide portion moves in the inner diameter direction shown in FIG. 4, and the rotating pin 81 connected to the link arm 14 is pushed in the direction away from the guide groove 2g. Move in the advance direction.

Further, the relative rotation of the guide plate 24 and the drive plate 2 is regulated by the assembly angle operation stopper 60 at the most retarded angle position and the most advanced angle position. The assembly angle operation stopper 60 includes a guide side member 61 and a drive side member 62. In the present embodiment, the guide side member 61 is provided at a position near the outer periphery of the rear surface of the guide plate 24.
It is made of a metal that is integrally molded with. In addition,
They may be integrally fixed by welding or bolts. On the other hand, the driving side member 62 has an elastic member 62b and a fastening member 62c. In the present embodiment, the elastic member 62b is formed in a rectangular parallelepiped shape using a rubber material or resin such as NBR type, fluorine type, acrylic type, etc., and has a through hole 62d in the center. Further, the fastening member 62c is a fixed shaft 62f press-fitted and fixed in a fitting hole 2n formed in the drive plate 2, and a substantially L-shaped cross section integrally provided at the base end of the fixed shaft 62f by welding or the like. And a pressing plate 62g having a shape. Then, the elastic member 62b
With the fixed shaft 62f inserted through the through hole 62d, the fixed shaft 62f is press-fitted into the fitting hole 2n to press the pressing plate 62g.
Due to this, the elastic member 62b is assembled in a state of being held down from the front side. The pressing member 62g includes an elastic member 62.
A flange 62h that holds down the side surface of b is provided to prevent the elastic member 62b from rotating and also prevent the elastic member 62b from being elastically deformed excessively.

In the assembly angle operation stopper 60 described above, at the most retarded position shown in FIG. 3, the guide side member 61 contacts the side surface of the drive side member 62 opposite to the rotation direction R. In contact with each other, the relative rotation between the guide plate 24 and the drive plate 2 is regulated. At this position, the sphere 22 arranged on the outermost peripheral side of the spiral guide groove 28 is the outer peripheral end of the spiral guide groove 28. It is a structure that does not reach the department. Therefore, the ball 22 does not collide with the outer peripheral end of the spiral guide groove 28. As a result, an excessive force does not act in the direction in which the ball 22 jumps out of the spiral guide groove 28, and the durability can be improved.

On the other hand, at the most advanced position shown in FIG. 4, the guide side member 61 abuts on the side surface on the rotation direction R side with respect to the drive side member 62, and the relative rotation between the guide plate 24 and the drive plate 2 is performed. It regulates movement, and at this position,
The sphere 2 arranged on the innermost side of the spiral guide groove 28
2 does not reach the inner peripheral end of the spiral guide groove 28. Therefore, the ball 22 does not collide with the inner peripheral end of the spiral guide groove 28. As described above, an excessive force does not act in the direction in which the ball 22 jumps out of the spiral guide groove 28, and the durability can be improved.

In the assembly of the assembly angle operation mechanism 4 and the operation conversion mechanism 40 described above, the rear surface of the link arm 14 slides on the bottom surface of the guide groove 2g as the radial guide of the drive plate 2 in the cylindrical portion 14a. And the shaft support portion 8d of the spacer 8 around the rotation hole 14d.
The assembly is slidably abutted on the front surface of the. On the other hand, the front surface of the link arm 14 is assembled so as to slidably contact the rear surface of the guide plate 24 at the arm portion 14b. As shown in the perspective views of FIG. 5 and FIG. 2 which are enlarged views of the C portion of FIG. 1, each link arm 14 has a step portion 14e formed gently near the boundary between the cylindrical portion 14a and the arm portion 14b. Then, on the front surface of the tip of the link arm 14, the periphery of the support hole 14c is guided by the guide plate 24.
It is separated from and is in a non-contact state. Also, the sphere 2
The retainer 22c that supports 2 is also formed such that the outer peripheral edge of the front end of the retainer 22c is not in contact with the guide plate 24 when the ball 22 is in contact with the spiral guide groove 28 of the guide plate 24. Further, a cover member 2c fixed to the drive plate 2 is disposed across the drive plate 2 and the guide plate 24 at an outer peripheral position of a portion to which the link arm 14 is assembled, and an inner periphery of the cover member 2c. A seal member 2s is provided between the guide plate 24 and a braking plate 36 which will be described later and is integrally provided on the outer periphery of the guide plate 24. As a result, the link arm 1
It is intended to prevent dust and the like from entering the sliding portion 4 and the sliding portion between the ball 22 and the spiral guide groove 28.

Next, the acceleration / deceleration mechanism 41, which is another structure of the actuating device 15, will be described in detail. The acceleration / deceleration mechanism 41 uses the guide plate 24 to drive the drive plate 2.
Acceleration and deceleration with respect to the guide plate 24
Moves in the direction of rotation R relative to the drive plate 2 (acceleration)
Or the guide plate 24 is moved (decelerated) in the direction opposite to the rotation direction R with respect to the drive plate 2, and the planetary gear mechanism 25, the first electromagnetic brake 26, and the second
And an electromagnetic brake 27.

The planetary gear mechanism 25 includes a sun gear 30, a ring gear 31, and a planetary gear 33 meshed with both gears 30, 31. As shown in FIGS. 1 and 2, the sun gear 30 is formed integrally with the inner periphery of the front side of the guide plate 24 rotatably supported by the spacer 8. The planetary gear 33 is rotatably supported by a carrier plate 32 fixed to the front end of the spacer 8. The ring gear 31 is formed on the inner circumference of an annular rotating body 34 that is rotatably supported outside the carrier plate 32. The carrier plate 32 is fitted to the front end portion of the spacer 8, and is fixed by being fastened to the camshaft 1 by passing the bolt 9 through the washer 37 with the front end surface of the washer 37 in contact therewith. A braking plate 35 having a braking surface 35b facing forward is screwed to the front end surface of the rotating body 34. Further, the braking surface 3 facing forward is also provided on the outer periphery of the guide plate 24 integrally formed with the sun gear 30.
A braking plate 36 having 6b is fixed by welding or fitting.

Therefore, in the planetary gear mechanism 25, if the planetary gear 33 revolves together with the carrier plate 32 without rotating, the sun gear 30 will operate when the first electromagnetic brake 26 and the second electromagnetic brake 27 are inactive.
And the ring gear 31 rotate at the same speed in the free state. If only the first electromagnetic brake 26 is braked from this state,
The guide plate 24 relatively rotates with respect to the carrier plate 32 (with respect to the camshaft 1) in the delay direction (the direction opposite to the R direction in FIGS. 3 and 4), and the drive plate 2 and the camshaft 1 move toward each other. The relative displacement is made in the advancing direction shown in. On the other hand, when only the second electromagnetic brake 27 is braked, a braking force is applied only to the ring gear 31, and the ring gear 31 rotates relative to the carrier plate 32 in the lagging direction, whereby the planetary gear 33 rotates and the planetary gear 33 rotates. The rotation accelerates the sun gear 30, the guide plate 24 is relatively rotated in the rotation direction R side with respect to the drive plate 2, and the drive plate 2 and the cam shaft 1 are relatively rotated in the retard direction shown in FIG. It will be.

The first electromagnetic brake 26 and the second electromagnetic brake 27 have the above-mentioned braking plates 36,
The inner and outer double layers are arranged so as to face the braking surfaces 36b and 35b of the pin 35, and the pins 26p and
It has circular pipe members 26r and 27r supported in a floating state in which only rotation is restricted by 7p. The circular pipe members 26r and 27r accommodate the coils 26c and 27c, and the friction material 2 is pressed against the braking surfaces 35b and 36b when the coils 26c and 27c are energized.
6b and 27b are attached. The friction material 26b,
Biasing means for pressing against the braking surfaces 35b and 36b may be provided on either or both of the 27b so that the braking force is removed when the coils 26c and 27c are energized. Also,
Each circular pipe member 26r, 27r and each braking plate 35,
36 is made of a magnetic material such as iron for forming a magnetic field when the coils 26c and 27c are energized. On the other hand, since the VTC cover 6 does not cause leakage of magnetic flux when energized, the VTC cover 6 also has friction members 26b and 27b.
Is a permanent magnet and brake plates 35, 36 when not energized
It is formed of a non-magnetic material such as aluminum in order to prevent sticking to the.

Further, in the planetary gear mechanism 25,
A planetary gear stopper 90 is provided between the brake plate 35 and the carrier plate 32, which are integrally provided with the ring gear 31. The planetary gear stopper 90 includes a stopper plate 91 protruding inward in the inner peripheral hole 35 c of the braking plate 35, and the stopper plate 9.
1 and a carrier side member 92 fixed to the carrier plate 32 so as to interfere with 1 in the circumferential direction. The carrier-side member 92 includes a metal base member 92b fitted and fixed in a fitting hole 32n formed in the carrier plate 32, and an arc-shaped NBR surrounding and fixed around the base member 92b. Elastic member 92d as a buffer member made of rubber material such as resin, fluorine, acrylic, or resin
And a cover member 92c made of resin or metal that covers the front surface and the inner peripheral surface of the elastic member 92d. Further, the cover member 92c is provided with a flange 92f that holds down the side surface of the elastic member 92d to prevent the elastic member 92d from rotating and prevent the elastic member 92d from being excessively elastically deformed. . The cover member 92c
The washer 92w is attached to the base member 92b in a state where the pin 92p protruding from the base member 92b penetrates to prevent the pin 92p from falling off. 6 is a view seen from the direction of arrow D in FIG. 1, in which the mounting rotation center of the base member 92b and the mounting rotation center of the cover member 92c are provided at different positions and serve as a stopper. When operating and receiving a load from the circumferential direction, both are prevented from rotating together.

Therefore, in the planetary gear mechanism 25, when the second electromagnetic brake 27 is braked,
By rotating the ring gear 31 relative to the carrier plate 32 in the lagging direction, the planetary gear 33 rotates, and the rotation of the planetary gear 33 accelerates the sun gear 30. At this time, the planetary gear 33 rotates and the carrier plate 32 rotates. When is rotated with respect to the ring gear 31 by a predetermined amount, its rotation is restricted by the planetary gear stopper 90. Therefore, the sun gear 30 is accelerated and displaced in the retard direction, and the guide plate 24 and the drive plate 2 are moved.
When the relative rotation with respect to the planetary gear 33 is restricted by the assembling angle operation stopper 60 described above, the reaction force thereof is
And the carrier plate 32 to the planetary gear stopper 90
Received by the planetary gear 33 and the ring gear 3
It will not be accepted by meshing with 1. As a result, the durability of gear meshing can be improved.

By the way, the operation conversion mechanism 40 described above is used.
Has a configuration in which the position of the cylindrical portion 14a of the link arm 14 is held and the relative assembly position of the drive plate 2 and the cam shaft 1 does not change. The configuration will be described.

The drive torque is transmitted from the drive plate 2 to the camshaft 1 via the link arm 14 and the spacer 8. However, the reaction force from the engine valve 71 (valve) is transmitted from the camshaft 1 to the link arm 14. Spring 7
The fluctuation torque (alternating torque) of the camshaft 1 due to the reaction force of 3) is input as the force F (see FIG. 4) in the direction connecting the pivot points of both ends of the link arm 14 from the rotating pin 81.

The cylindrical portion 14a of the link arm 14 is
Since the sphere 22 which is guided in the radial direction along the guide groove 2g as a radial guide and which projects from the cylindrical portion 14a to the front is engaged with the spiral guide groove 28, each link arm 14 is The force F input through the guide groove 2g is supported by the left and right walls of the guide groove 2g and the spiral guide groove 28 of the guide plate 24.

Therefore, the force F input to the link arm 14 is decomposed into two component forces FA and FB which are orthogonal to each other, and these component forces FA and FB are formed into the spiral guide groove 2.
The outer peripheral wall of 8 and the one wall of the guide groove 2g are received in a direction substantially orthogonal to each other, and the cylindrical portion 1 of the link arm 14 is received.
4a is prevented from moving along the guide groove 2g,
This prevents the link arm 14 from rotating. Therefore, the guide plate 24 is rotated by the braking force of each electromagnetic brake 26, 27, and the link arm 14 is rotated.
After being rotated to a predetermined position, basically, the position of the link arm 14 is maintained, that is, the rotational phase of the drive plate 2 and the camshaft 1 is maintained as it is, without continuously applying the braking force. be able to. In addition, the F
Is not limited to acting in the outer diameter direction as shown in FIG. 4, but may act in the opposite direction to that shown in the drawing. At this time, the component forces FA and FB are generated on the inner peripheral side of the spiral guide groove 28. With a wall
It is received in a direction substantially perpendicular to the other side of the guide groove 2g.

The operation of this embodiment will be described below. During engine startup and idle operation, the rotation phases of the crankshaft and the camshaft 1 are controlled to the most retarded side to stabilize engine rotation and improve fuel efficiency. To arrange the camshaft 1 at the most retarded position in this way, the controller 7 outputs a control signal for energizing the second electromagnetic brake 27.
As a result, the friction material 27b of the second electromagnetic brake 27 makes frictional contact with the braking plate 35, a braking force acts on the ring gear 31 of the planetary gear mechanism 25, and the sun gear 30 is rotated at an increased speed as the timing sprocket 3 rotates. It The speed-up rotation of the sun gear 30 causes the guide plate 24 to rotate in the rotational direction R side with respect to the drive plate 2, and the sphere 22 supported by the link arm 14 accordingly moves to the outer peripheral side of the spiral guide groove 28. Moving. This movement is caused by the guide side member 61 and the drive side member 6 of the assembly angle operation stopper 60.
2 is regulated at the most retarded position where it collides as shown in FIG. 3, and at this time, the camshaft 1 is arranged at the most retarded side assembly angle with respect to the drive plate 2.

Further, as described above, when the rotation of the ring gear 31 is braked by the second electromagnetic brake 27, the rotation is not regulated instantaneously but is allowed while allowing a predetermined amount of rotation. The rotation of the ring gear 31 is restricted by the planetary gear stopper 90 when the predetermined amount is reached. That is, the carrier side 92 provided on the carrier plate 32 collides with the end surface of the stopper plate 91, and the rotation is restricted. In this case, the accelerated rotation of the guide plate 24 provided with the sun gear 30 as described above causes the assembly angle stopper 6 to rotate.
When regulated by 0, the reaction force is input to the planetary gear mechanism 25, but this reaction force is transmitted from the carrier plate 32 to the braking plate 35 on the ring gear 31 side via the planetary gear stopper 90, and the respective gears No load is input to the meshing portion, and the durability of this meshing portion can be improved.

The second electromagnetic brake 27 is energized for a predetermined time (for example, 0.5 sec) set in advance.
However, thereafter, the most retarded state is held by the holding function of the operation conversion mechanism 40 described above. Also,
Basically, the control signal for arranging the above-mentioned most retarded angle position is output just before the stop of the engine, and at the time of starting thereafter, it is already at the most retarded angle position. It is preferable to output a control signal for controlling to the most retarded position also at the time of starting.

Next, when the engine shifts to the normal operation from the above-mentioned starting state and the controller 7 determines that the camshaft 1 is displaced in the advancing direction by the mounting angle, the controller 7 brakes the first brake 26. Output the control signal to operate. As a result, a braking force acts on the guide plate 24, the guide plate 24 rotates in the direction opposite to the rotation direction R with respect to the drive plate 2, and the assembly angle of the camshaft 1 is displaced to the advance side, whereby the engine is moved. Of high output.
The amount of displacement in the advance direction can be controlled to an arbitrary amount by feedback control by a sensor (not shown). Moreover, when the guide side member 61 and the drive side member 62 of the assembly angle operation stopper 60 collide as shown in FIG. 4 when displaced to the most advanced angle position, further displacement is restricted. Therefore, the cam shaft 1 is arranged at the most advanced angle with respect to the drive plate 2. Further, this state is maintained by the state maintaining function of the operation conversion mechanism 40 described above.
Further, when the rotation of the guide plate 24 is restricted, the planetary gear 33 rotates to rotate the ring gear 31 at an increased speed, but when the rotation amount reaches a predetermined amount, the rotation is restricted by the planetary gear stopper 90. Therefore, also in this case, the load is not input to the meshing portion of each gear, and the durability of this meshing portion can be improved.

Further, during the above-described operation, the lubricating oil passes through the inner periphery of the cam shaft 1 and the spacer 8 from the oil supply hole 1r which penetrates the cam shaft 1 from the engine (not shown) to pass through the spacer 8 The oil is supplied from the oil supply hole 8r toward the assembling angle operation mechanism 4 and the actuator 15, and further from the guide plate 24 through the oil supply hole 24r to the planetary gear mechanism 25.
The oil supply passage oil is formed by an alternate long and short dash line in FIG. In the middle of the oil supply path oil, the lubricating oil is supplied also to the spiral guide groove 28, and is further supplied to a portion of the link arm 14 which is arranged so as to overlap with the spiral guide groove 28. Therefore, the lubricating oil is supplied between the link arm 14 and the guide plate 24, and the link arm 14
Excellent in operability when is activated.

In the valve timing control system of the present embodiment, the guide plate 24 is appropriately accelerated and decelerated by the planetary gear mechanism 25 and the pair of electromagnetic brakes 26 and 27, and the acceleration and deceleration of the guide angle adjusts the assembly angle operating mechanism 4. Since the structure is such that the link arm 14 is driven and operated, each electromagnetic brake 26, 27 overcomes the operating resistance of the link arm 14 and the friction resistance of the power transmission path from each braking surface 35b, 36b to the link arm 14. It suffices to apply only the braking force. Therefore, the electromagnetic force required by each of the electromagnetic brakes 26, 27 is reduced, and the power consumption can be reduced.

Further, in the present embodiment, the link arm 14 is in slidable contact with the guide plate 24 and the drive plate 2 in front of and behind it.
Therefore, the link arm 14 does not swing in the front-rear direction, and it is possible to prevent the rattling of the link arm 14 and the generation of abnormal noise. In addition, although the link arm 14 is rotatably attached to the rotation pin 81,
The retainer is formed by the guide plate 24, and a retainer member such as a washer can be omitted.
As a result, the number of parts can be reduced and the cost can be reduced.

Further, in the present embodiment, the step portion 14e is formed in the link arm 14, and the end surface of the cylindrical portion 14a that slides in the radial direction is not in contact with the guide plate 24, and Retainer 22c housed in the housing hole 14c of the cylindrical portion 14a of the arm 14
Is also in a non-contact state with the guide plate 24. Therefore, when the link arm 14 rotates with respect to the guide plate 24, the corners of the outer peripheral edge of the link arm 14 and the peripheral edge of the accommodation hole 14c come into contact with the peripheral corners of the spiral guide groove 28. Therefore, it is possible to prevent the link arm 14 from being caught and causing a malfunction.

Further, in the present embodiment, since the spiral guide groove 28 is formed at the contact portion between the guide plate 24 and the link arm 14, the spiral guide groove 28 is formed at this contact portion. Lubricating oil is supplied via this, and the slidability and wear resistance of this contact portion can be improved.

The embodiment of the present invention has been described in detail above with reference to the drawings. However, the specific configuration is not limited to this embodiment, and changes in design within the scope not departing from the gist of the present invention. Even if it exists, it is included in the present invention. For example, in the embodiment, the link arm 14 is radially slidably connected to the outer peripheral side of the drive plate 2 as the drive rotating body and is rotatably connected to the inner peripheral side of the spacer 8 as the driven rotating body. However, conversely, it may be rotatably connected to the driving rotary member and slidably connected to the driven rotary member. Further, contrary to the embodiment, the driven rotor may be connected on the outer peripheral side and the drive rotor may be connected on the inner peripheral side.

As the link arm, the link arm 14 having the flat plate-shaped arm portion 14b is shown in the embodiment, but the shape of the link arm 14 is limited to the shape shown in the embodiment. Instead, it may be formed in another shape such as a rod shape. Further, as the slide portion of the link arm, in the embodiment, the cylindrical portion 14a is formed on the link arm 14, but the shape may be another shape such as a spherical shape, a cylindrical shape, a polygonal cylindrical shape, or a polygonal cylindrical shape. May be. Further, as the radial guide, the guide groove 2g is used to guide the guide in the embodiment, but it is sufficient to guide the guide in the radial direction, and one or a plurality of rail-shaped guides extending in the radial direction may be provided. Good. Further, although the spiral guide groove 28 is shown in the embodiment as a spiral guide for operating the slide portion of the link arm in the circumferential direction, it is also important that the spiral guide groove 28 is displaced in the circumferential direction along with the radial displacement. Any guide may be used, and a spiral rail-shaped member or the like may be used.

In the embodiment, the actuating device is provided with the planetary gear mechanism 25. However, the actuating device may be any device that can rotate the guide plate, such as a motor. Other devices such as a device for directly rotating the guide plate by the driving means may be used.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing a valve timing control device for an internal combustion engine according to an embodiment of the present invention.

FIG. 2 is an exploded perspective view showing a valve timing control device for an internal combustion engine according to an embodiment.

FIG. 3 is a cross-sectional view taken along the line AA of FIG. 1 showing the operation of the main part of the valve timing control device for the internal combustion engine of the embodiment.

FIG. 4 is a cross-sectional view taken along the line AA of FIG. 1 showing the operation of the main part of the valve timing control device for the internal combustion engine of the embodiment.

FIG. 5 is an enlarged cross-sectional view showing a main portion (C portion in FIG. 1) of the valve timing control device for the internal combustion engine according to the embodiment.

FIG. 6 is a view seen from the direction of arrow D in FIG. .

[Explanation of symbols]

1 camshaft 1r Oil supply hole 2 drive plate 2g guide groove 3 Timing sprocket 4 Assembly angle operation mechanism 6 VTC cover 7 controller 8 spacers 8r Oil supply hole 14 link arm 14a Cylindrical part (slide part) 14b Arm part 14c accommodation hole 14d Rotating hole (rotating part) 14e Step 15 Actuator 22 spheres 24 Guide plate 24r Oil supply hole 25 Planetary gear mechanism 26 First electromagnetic brake 27 Second electromagnetic brake 28 spiral guide groove 30 sun gear 31 ring gear 32 carrier plate 33 planetary gears 60 assembly angle operation stopper 90 Planetary gear stopper 91 Stopper plate 92 Carrier side member 92b base member 92c cover member 92d elastic member oil oil supply path

   ─────────────────────────────────────────────────── ─── Continued front page    F-term (reference) 3G018 AA05 AA06 AB02 AB07 AB16                       BA10 BA29 BA31 BA32 CA11                       DA20 DA70 DA71 EA02 EA04                       FA01 FA07 GA14 GA18 GA32                 3J030 EA13 EC02 EC07

Claims (4)

[Claims] 1. A drive rotating body to which rotation is transmitted from a drive shaft of an internal combustion engine, and a camshaft which is provided coaxially with the drive rotating body and drives at least one of an intake valve and an exhaust valve of the internal combustion engine. Alternatively, a driven rotating body formed of a separate member coupled to the shaft, an assembly angle adjusting mechanism for relatively rotating the driven rotating body and the drive rotating body, and operating the assembly angle adjusting mechanism. The assembly angle adjusting mechanism has a rotating portion at one end rotatably connected to one of a drive rotating body and a driven rotating body, and a slide portion at the other end drivingly rotates. A link arm slidably connected in a radial direction by a radial guide provided on the other of the body and the driven rotary body, and the position of the rotating portion is set in the circumferential direction along with the radial movement of the slide portion. Displaced to drive rotating body and driven rotation The operating device has a guide plate that is arranged adjacent to the link arm and is rotatable coaxially with the driven rotary body. In the valve timing control device for an internal combustion engine, wherein a spiral-shaped spiral guide that displaces the slide portion in the radial direction with the rotation of itself is formed, the link arm is slidable on the guide plate. A valve timing control device for an internal combustion engine, wherein the valve timing control device is placed in contact with each other. 2. The valve timing control device for an internal combustion engine according to claim 1, wherein the link arm is slidably held between the guide plate and the radial guide. Timing control device. 3. The valve timing control device for an internal combustion engine according to claim 1, wherein a lubrication passage supply passage for supplying lubricating oil toward the spiral guide is formed, and the guide plate and the link arm come into contact with each other. A bubble timing control device for an internal combustion engine, wherein a swirl guide is arranged within a range. 4. The valve timing control device for an internal combustion engine according to claim 1, wherein a spiral guide groove formed on an end face of the guide plate is provided as the spiral guide, and the link arm slides. A sphere that moves along the spiral guide groove, and a housing hole that houses the sphere, the end surface of the link arm facing the guide plate,
A valve timing control device for an internal combustion engine, wherein a step portion is formed so that a periphery of the accommodation hole is not in contact with the guide plate.