JP2002004815A - Valve action timing control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve the conventional problem that a machining process accompanying a machining process, such as drilling machining, is entirely unnecessary when feed and discharge passages are formed. SOLUTION: A rotor member 20 rotating in a housing member 30 comprises a main rotor 21 rotatably assembled to a shoe part 31a, and a cylindrical subrotor 23 coupled to the main rotor and rotatably assembled to an annular bearing part situated at the housing member 30. A feed and discharge passage for working oil and extending to and from a spark advance oil chamber R1 consists of an annular recess 21c formed in the main rotor 21 by a molding die, a recess part for communication 21d formed in the main rotor 21 by a molding die and causing communication of the outer peripheral part of the annular recess 21c with the spark advance oil chamber R1, and recessed grooves for communicating 23a and 23b formed in the subrotor 23 by a mold die and radially externally communicating with an annular passage D, formed in the outer peripheral part of the annular recess 21c by the subrotor 23, and internally communicating radially with the inner hole of the subrotor 23.

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 (valve timing control device for an internal combustion engine) used for controlling the timing of opening and closing an intake valve or an exhaust valve in a valve train of an internal combustion engine.

[0002]

2. Description of the Related Art A drive shaft of an internal combustion engine (crankshaft of an engine) is known as one type of such a valve timing control apparatus.
A housing member that is provided in a driving force transmission system that transmits driving force to a driven shaft (cam shaft) that opens and closes an intake valve or an exhaust valve of an internal combustion engine, and that rotates integrally with the drive shaft or the driven shaft. An advancing oil chamber and a retarding oil chamber are formed in the housing member at the vane portion, and are integrally rotated with the driven shaft or the drive shaft. And a hydraulic circuit for controlling supply and discharge of hydraulic oil to the advance oil chamber and the retard oil chamber, for example, as disclosed in JP-A-2000-2103. ing.

[0003]

In the valve timing control apparatus disclosed in the above publication, the supply / discharge passage of hydraulic oil to the advance oil chamber or the retard oil chamber is formed by machining such as drilling. A formed communication hole (for example, a drilled hole drilled from the outer periphery to the inner periphery of the rotor member) is provided, and a problem (increase in cost, etc.) due to machining is inevitable. Further, the supply of hydraulic oil to the annular bearing portion provided on the housing member is not actively performed, and there is room for improvement in the reliability and durability of the device.

[0004]

SUMMARY OF THE INVENTION The present invention is directed to a driving force transmission system for transmitting driving force from a driving shaft of an internal combustion engine to a driven shaft for opening and closing an intake valve or an exhaust valve of the internal combustion engine. And a housing member rotatable integrally with the drive shaft or the driven shaft, and an advancing oil inside the housing member at a vane portion which is rotatably assembled to a shoe portion provided on the housing member. And a rotor member that forms a chamber and a retard oil chamber and rotates integrally with the driven shaft or the drive shaft, and controls supply and discharge of hydraulic oil to the advance oil chamber and the retard oil chamber. In the valve timing control apparatus provided with a hydraulic circuit for, the rotor member,
As a configuration including a main rotor rotatably mounted on the shoe portion, and a cylindrical subrotor provided on one side of the main rotor and rotatably mounted on an annular bearing portion provided on the housing member, An annular recess formed by a molding die on one side inner peripheral portion of the main rotor, and an outer peripheral portion of the annular recess formed by a molding die on one side intermediate portion of the main rotor, the advance oil chamber or the A communicating recess formed to communicate with the retarding oil chamber, and a radially extending outer peripheral portion of the annular recess formed by a molding die on the other side of the sub rotor and radially outwardly communicating with an annular passage formed by the sub rotor; A communication groove for communicating hydraulic fluid to the advance oil chamber or the retard oil chamber is formed by a communication concave groove communicating with an inner hole of the sub-rotor inwardly of the sub-rotor (the invention according to claim 1). Specially There is. In this case, it is desirable that the other end of the annular bearing portion provided on the housing member is exposed to the annular passage (the invention according to claim 2).

[0005]

In the valve opening / closing timing control device according to the present invention (the invention according to claim 1), an annular recess formed in one inner peripheral portion of the main rotor by a molding die, A communicating recess formed at one intermediate portion by a molding die to communicate an outer peripheral portion of the annular recess to the advance oil chamber or the retard oil chamber; and a diameter formed by a molding die on the other side of the sub rotor. A communication groove extending radially outwardly to an outer peripheral portion of the annular recess and communicating with an inner hole of the sub rotor radially inward and radially inwardly to the advancing oil. A supply / discharge passage of hydraulic oil to / from the chamber or the retard oil chamber is formed. For this reason, when forming the supply / discharge passage, machining such as drilling is not required at all, and problems associated with machining (cost increase, etc.) can be solved.

Further, in the valve timing control apparatus according to the present invention (the invention according to claim 2), in addition to the above-described structure, the other end of the annular bearing provided on the housing member is exposed to the annular passage. As a matter of course, it is possible to positively supply hydraulic oil from the entire circumference of the annular passage to the entire circumference of the annular bearing portion, and it is possible to lubricate the annular bearing portion. The performance can be improved, and the reliability and durability of the device can be improved.

[0007]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the drawings. The valve timing control apparatus according to the present invention shown in FIGS. 1 to 14 includes a rotor member 20 integrally attached to the tip of a camshaft 10 (driven shaft), and a relative rotation of the rotor member 20 within a predetermined range. A torsion spring S interposed between the housing member 30 and the rotor member 20 to urge the rotor member 20 to the advance angle side with respect to the housing member 30; A stopper mechanism A for defining the most retarded phase and the most advanced phase of the member 20, a lock mechanism B for regulating the relative rotation of the housing member 30 and the rotor member 20 at the most retarded phase, and an advance angle to be described later A hydraulic circuit C is provided for controlling the supply and discharge of hydraulic oil to and from the oil chamber R1 and the retard oil chamber R2, and for controlling locking and unlocking of the lock mechanism B.

The camshaft 10 is an intake valve (not shown).
The cam has a well-known cam (not shown) that opens and closes, and is rotatably supported by a cylinder head 40 of the internal combustion engine, and includes therein an advance passage 11 and a retard passage that extend in the axial direction of the camshaft 10. 12 are provided. Advance angle passage 11
Is a radial passage 13, an annular passage 14, and a connection passage P1.
Through the connection port 101 of the switching valve 100. The retard passage 12 is connected to the connection port 102 of the switching valve 100 via the radial passage 15, the annular passage 16, and the connection passage P2. The radial passage 1
The annular passage 16 is formed between the camshaft 10 and the stepped portion of the cylinder head 40.

The switching valve 100 constitutes a hydraulic circuit C with an oil pump 110, an oil reservoir 120, and the like, and energizes a solenoid 103 (controlled by an unillustrated energization control device according to the operating state of the internal combustion engine). 1), the spool 104 can be moved to the left in FIG. 1 against the spring 105. In a non-energized state, the supply port 106 connected to the oil pump 110 driven by the internal combustion engine communicates with the connection port 102. Along with
The supply port 106 and the discharge port 107 are cut off from the connection ports 101 and 102 so that the connection port 101 communicates with the discharge port 107 connected to the oil reservoir 120 and when the first set current is supplied. As described above, the supply port 106 communicates with the connection port 101 and the connection port 102 communicates with the discharge port 107 when the second set current is larger than the first set current.

Therefore, when the solenoid 103 is not energized, hydraulic oil is supplied from the oil pump 110 to the retard passage 12, and oil is supplied from the advance passage 11 to the oil reservoir 120.
When the first set current is supplied, the hydraulic oil is accumulated in the advance passage 11 and the retard passage 12, and when the second set current is supplied, the oil is supplied from the oil pump 110 to the advance passage 11. The hydraulic oil is supplied and the hydraulic oil is discharged from the retard passage 12 to the oil reservoir 120.

The rotor member 20 is made of a sintered metal and has a stepped portion made of a sintered metal integrally assembled via a connecting sleeve 22 behind (to the right in FIG. 1) the main rotor 21. Each of the rotors 21 and 23 and the coupling sleeve 22, which is constituted by a cylindrical sub-rotor 23, is integrally fixed to a front end of the camshaft 10 by a bolt 50, and has a front end closed by a head of the bolt 50.
Is connected to an advance passage 11 provided in the camshaft 10.

As shown in FIGS. 1, 4 to 6, and 8, the main rotor 21 has a hub portion 21a to which the connecting sleeve 22 and the sub rotor 23 are coaxially mounted, and a radially outer portion from the hub portion 21a. 4 to define four advanced oil chambers R1 and retarded oil chambers R2 in the housing member 30.
Each of the vanes 21b is provided with a seal member 24 for sealing between the advance oil chamber R1 and the retard oil chamber R2 at the radially outer end of each vane 21b.

On the rear side (one side) of the main rotor 21, as shown in FIGS. 4 and 8, annular recesses 21c and 4c are formed.
Linear communication recesses 21d and two arc communication recesses 21
e is formed, and the mounting hole 2 of the positioning pin 25 is formed.
1f is formed. The annular recess 21c is formed on the rear inner peripheral portion of the main rotor 21 by a main rotor molding die (a molding die used when molding the main rotor 21). Each linear communication recess 21d is provided with a main rotor 21.
The outer peripheral portion of the annular recess 21c is communicated with the advance oil chamber R1 by a main rotor molding die at a rear intermediate portion of the main body. Each of the arc-shaped communication recesses 21e is provided with an annular recess 21c.
Is formed by a main rotor molding die at an area where the groove is formed, and is formed deeper in the axial direction than the annular recess 21c (see FIG. 1).

As shown in FIG. 6, a second annular recess 21g is formed on the front side (the other side) of the main rotor 21. As shown in FIGS. 1, 5 and 8, four communication holes 21h extending in the radial direction are provided. The second annular recess 21g is a recess for accommodating a rear portion of the torsion spring S, is formed by a main rotor molding die, and has a rear end of the torsion spring S at a portion corresponding to one of the vane portions 21b. Sr (extending in the radial direction)
To reduce the axial dimension of the device. Each communication hole 21h is provided with the main rotor 2
After the molding of No. 1, it is drilled from the outer periphery by drilling, and communicates with the arcuate communication concave portion 21e at the radial inner end and communicates with the retard oil chamber R2 at the radial outer end.

On the other hand, the sub-rotor 23 has
As shown in FIGS. 7 and 9 to 11, a pair of communication concave grooves 23a and 23b, two communication holes 23c and an annular groove 23d are formed, and a free concave 23e and a lock concave 2 are formed.
3f is formed. One communication concave groove 23a is provided with a sub rotor forming die (sub rotor 23
Formed at the outer periphery of the annular recess 21c, and communicates with the annular passage D formed by the sub rotor 23 radially outward and radially inward. Advance passage 11 through the inner hole of sub rotor 23
Is in communication with As shown in FIG. 4, a positioning pin 25 is engaged with a part of the communication concave groove 23a, and the main rotor 21 and the sub rotor 23 are positioned in the circumferential direction.

The other communication concave groove 23b is
Is formed by a sub-rotor forming die on the front side and extends in the radial direction.
The inner diameter of the sub-rotor 23 communicates with the advance passage 11 at an inner diameter. Each communication hole 23c is formed by a sub-rotor forming die so as to penetrate the sub-rotor 23 in the axial direction, and communicates with the arc-shaped communication concave portion 21e of the main rotor 21 at the front end and communicates with the annular groove 23d at the rear end. are doing. The annular groove 23d is formed on the rear side of the sub-rotor 23 by a sub-rotor forming die, and
It communicates with 2.

The free recess 23e and the lock recess 23f are
It is formed on the front side of the sub rotor 23 by a sub rotor molding die. The free recess 23e extends in the circumferential direction and is formed in an arc shape, and the lock key 6 is provided in a state where relative rotation between the housing member 30 and the rotor member 20 is allowed.
One tip 61a is accommodated. A stopper surface 23e1 (see FIG. 10) for defining the most retarded phase by contact with the tip portion 61a of the lock key 61 is formed at one circumferential end of the free recess 23e.
A lock recess 23f is formed continuously along 3e1. The other end of the free recess 23e in the circumferential direction has the most advanced angle phase of the rotor member 20 with respect to the housing member 30.
Second stopper surface 23e2 for defining (maximum relative rotation amount)
(See FIG. 10) is formed to face the stopper surface 23e1.

The housing member 30 includes a housing body 3
1, a front plate 32, and a rear thin plate 33
, A rear thick plate 34, and four bolts 35 for integrally connecting the rear thick plate 34, and a sprocket 34a is integrally formed on the outer periphery of the rear thick plate 34. As is well known, the sprocket 34a is connected to a crankshaft (a drive shaft not shown) of the internal combustion engine via a timing chain (not shown), and is configured to transmit a driving force from the crankshaft. ing.

The housing body 31 has two pairs of four shoe portions 31a projecting radially inward.
A hub portion 21a of the main rotor 21 is supported at a radially inner end of 1a via a seal member 36 so as to be relatively rotatable. The front plate 32 and the rear thin plate 33
At the axially opposed end surfaces, the outer peripheral surface of the axial end surface of the hub portion 21a of the main rotor 21, the entire axial end surface of each vane portion 21b, and the entire axial end surface of each seal member 36 are slidably contacted. ing.

That is, the housing member 30 is formed by the housing body 31 and the front plate 32 so as to have a substantially bottomed cylindrical shape that opens rearward (to the right in FIG. 1) and accommodates the rotor member 20 therein. The rear thin plate 33 and the substantially flat rear thick plate 34 form a cover that covers the opening of the housing. As shown in FIG. 12, the rear thin plate 33 is formed in an annular shape and is sandwiched between the housing body 31 and the rear thick plate 34 to perform a sealing function. By forming a bead-shaped bend, the sealing property is improved.

As shown in FIGS. 1, 3, 7, 13, and 14, the rear thick plate 34 is opened on the front side and opened radially inward, and the opening on the front side is thinned to the rear side. A sub-rotor having an accommodation groove 34b closed by the plate 33 in the hub portion 34c and projecting from an opening of the housing member 30 at an inner periphery (annular bearing portion) of the hub portion 34c whose front end is exposed to the annular passage D. 23 is rotatably supported on the outer periphery. Further, a lock key 61 and a lock spring 62 which constantly urges the lock key 61 toward the bottom of the free recess 23e (inward in the radial direction of the rear thick plate 34) are provided in the housing groove 34b.
It is assembled so as to be able to rotate integrally with it. The accommodation groove 34
The radially outer end of b is opened through a through hole 34d (see FIGS. 1 and 3) to ensure rapid movement of the lock key 61 in the radial direction.

Sprocket 34 of rear thick plate 34
a, the accommodation groove 34b and the through hole 34d
4 are formed at the same time as the molding of
4f, 34g and 34h (see FIGS. 2 and 13) are also formed at the same time. As a result, the manufacturing cost can be reduced, and the size and weight of the device can be reduced. The holes 34e, 34f, 34g, and 34h are extracted so as to balance the rotation.

The lock key 61 is formed in a rectangular cross section, and has a length such that a radially inner tip portion 61a always projects toward the free recess 23e of the sub-rotor 23 (contacts a radially outer end of the accommodation groove 34b). Even if it moves radially outward until it touches,
a has a length protruding from the accommodation groove 34b), and a groove 61b is formed radially outward and opened to the front side and radially outward to accommodate a part of the lock spring 62.

As shown in FIGS. 1 and 7, the lock key 61 can receive the distal end portion 61a in the lock recess 23f so as to be immovable in the circumferential direction at the most retarded phase. When hydraulic oil is supplied from the advance passage 11 through 23b, the hydraulic oil is pushed radially outward against the lock spring 62, the tip portion 61a is retracted from the lock recess 23f, and the hydraulic oil passes through the communication concave groove 23b. When discharged into the advance passage 11,
The lock recess 23f is generated by the urging force of the lock spring 62.
, And the distal end portion 61a is fitted to and housed in the lock recess 23f.

In this embodiment constructed as described above, when the internal combustion engine is started, even if the necessary and sufficient hydraulic oil is not supplied from the oil pump 110 to the retard oil chamber R2, the oil in the retard oil chamber R2 is The torque in the retard direction due to the hydraulic pressure and the average fluctuation torque acting on the camshaft 10 cause the rotor member 20 to rotate relative to the housing member 30 to the retard side against the urging force of the torsion spring S. Therefore, at the time of starting the internal combustion engine, the relative rotation between the housing member 30 and the rotor member 20 is determined based on the most retarded phase (optimizing the overlap period in which the intake valve and the exhaust valve of the internal combustion engine are open at the same time. (Phase that improves startability)
, Is regulated by a lock mechanism B including a lock key 61, a lock recess 23f, a lock spring 62, and the like.

Therefore, even if a fluctuating torque (positive / negative reversing torque) acts on the camshaft 10 when driving the intake valve, the lock key 61 prevents the relative rotation of the rotor member 20 with respect to the housing member 30. Is not regulated, relative rotation vibration is not generated, and generation of a tapping sound due to the rotation vibration is prevented. If the switching valve 100 is in the non-energized state shown in FIG. 1 when the internal combustion engine is started, hydraulic oil is supplied from the oil pump 110 to the retard passage 12 via the switching valve 100, and is supplied to the retard oil chamber R2. The relative rotation between the rotor member 20 and the housing member 30 is also restricted by the oil pressure in the retard oil chamber R2 from the point in time when the hydraulic oil is supplied toward the oil reservoir R2.

In this state, when the solenoid 103 of the switching valve 100 is switched from the non-energized state to the energized state of the second set current, the supply port 106 is connected to the connection port 101.
And the connection port 102 is connected to the discharge port 1
The hydraulic fluid is supplied to the advance passage 11 and the hydraulic oil is discharged from the retard passage 12 to the oil reservoir 120. Therefore, hydraulic oil is supplied from the advance passage 11 to the lock recess 23 f through the communication recess groove 23 b of the sub rotor 23, and the communication recess groove 23 a, 23 b of the sub rotor 23 and the annular shape of the main rotor 21 from the advance passage 11. The advance oil chamber R passes through the recess 21c and each linear communication recess 21d.
Hydraulic oil is supplied to the retard oil passage R1, and the hydraulic oil is discharged from the retard oil chamber R2 to the retard passage 12 through the communication hole 21h of the main rotor 21, the arc-shaped communication recess 21e, the communication hole 23c of the sub rotor 23, and the annular groove 23d. .

Therefore, the operating oil supplied to the lock recess 23f causes the lock key 61 to lock the lock spring 6
4, the rotor member 20 is moved outward from the lock recess 23f to be moved and retracted, and the hydraulic oil supplied to the advance oil chamber R1 pushes the rotor member 20 counterclockwise in FIG. Relative to the housing member 30 from the most retarded phase toward the advanced side. The relative rotation of the rotor member 20 with respect to the housing member 30 is possible until the second stopper surface 23e2 formed on the sub rotor 23 comes into contact with the distal end portion 61a of the lock key 61.

When the solenoid 103 of the switching valve 100 is switched from the second set current energized state to the first set current energized state, the supply port 106 and the discharge port 10
7 is disconnected from the connection ports 101 and 102, and the hydraulic oil is stored in the advance passage 11 and the retard passage 12, so that the hydraulic oil is stored in the advance oil chamber R1 and the retard oil chamber R2. The housing member 30 of the rotor member 20
Is restricted.

When the solenoid 103 of the switching valve 100 is switched from the energized state of the first set current to the non-energized state, the supply port 106 communicates with the connection port 102 and the connection port 101 communicates with the discharge port 107. The hydraulic oil is supplied to the retard passage 12, and the hydraulic oil is discharged from the advance passage 11 to the oil reservoir 120. For this reason, the annular groove 23 of the sub rotor 23
Hydraulic oil is supplied to the retard oil chamber R2 through the communication hole d, the communication hole 23c, the arc-shaped communication recess 21e of the main rotor 21 and the communication hole 21h, and the straight communication recess 21d of the main rotor 21 is formed from the advance oil chamber R1 into the annular shape. Recess 21c and sub rotor 2
3 and the advancing passage 11 through the two communication concave grooves 23a and 23b.
Hydraulic oil is discharged.

Therefore, the rotor member 20 is pushed clockwise in FIG. 4 by the hydraulic oil supplied to the retard oil chamber R2, and rotates relative to the housing member 30 toward the retard side. The relative rotation of the rotor member 20 with respect to the housing member 30 is possible until the stopper surface 23e1 formed on the sub-rotor 23 abuts on the distal end portion 61a of the lock key 61.

As is apparent from the above description, in the present embodiment, the relative rotation of the rotor member 20 with respect to the housing member 30 is controlled by controlling the energization state of the solenoid 103 of the switching valve 100 when the internal combustion engine is driven. The phase can be adjusted to any phase in the range from the most retarded phase to the most advanced phase, and the valve opening / closing timing when the internal combustion engine is driven can be appropriately adjusted.

In the present embodiment, an annular recess 21c formed by a main rotor molding die in the rear inner peripheral portion of the main rotor 21 and a main rotor molding die formed in a rear intermediate portion of the main rotor 21. A linear communication recess 21d for communicating the outer peripheral portion of the annular recess 21c to the advance oil chamber R1; and a subrotor 23 formed at the front side of the subrotor 23 by a subrotor molding die and extending in the radial direction and extending to the outer periphery of the annular recess 21c. The advanced oil chamber R1 is formed by the communication concave grooves 23a and 23b communicating with the annular passage D formed radially outward and communicating with the inner hole of the sub-rotor 23 radially inward.
A supply / discharge passage for hydraulic oil to / from the pump is formed. For this reason, when forming the supply / discharge passage, machining such as drilling is not required at all, and problems associated with machining (cost increase, etc.) can be solved.

In the present embodiment, the inner periphery of the hub portion 34c (the annular bearing portion of the housing member 30) of the rear thick plate 34 is exposed at the front end to the annular passage D. Hub part 34 from the entire circumference of D
Hydraulic oil can be positively supplied to the entire inner periphery of the hub c, and the lubrication performance of the inner periphery (annular bearing portion) of the hub portion 34c can be improved, and the reliability and durability of the device can be improved. Can be improved.

In the present embodiment, the stopper mechanism A and the lock mechanism B are configured to include the lock key 61, the free recess 23e, the stopper surfaces 23e1, 23e2, the lock recess 23f, and the lock spring 62 described above. Stopper mechanism A is locked key 61, free recess 23
e, stopper surfaces 23e1, 23e2, etc.
The lock mechanism B is constituted by a lock key 61, a lock recess 23f, a lock spring 62, and the like), and these are provided on each hub portion of the housing member 30 and the rotor member 20. In other words, the stopper mechanism A and the lock mechanism B share the lock key 61, so that the stopper mechanism A and the lock mechanism B can be integrally configured. Therefore, the size and weight of the device can be reduced.

Therefore, the circumferential end surface of the shoe portion 31a of the housing member 30 and the vane portion 21b of the rotor member 20
There is no need to machine each of the circumferential end surfaces of the rotor member 20 and the vane portion 21b of the rotor member 20 and the housing member 3
The high shoe part 31a is not required to have high strength. Therefore, while reducing the production cost,
The thickness of the vane portion 21b of the rotor member 20 can be reduced, and the size and weight can be reduced.

Further, a stopper surface 23e1 for defining the most retarded phase is formed at one end in the circumferential direction of the free recess 23e by contact with the tip portion 61a of the lock key 61, and is continuously formed along the stopper surface 23e. Since the lock recess 23f is formed (the stopper surface 23e1 and the lock recess 23f are formed at one place of the sub rotor 23), the positional accuracy of the lock recess 23f with respect to the most retarded phase can be easily obtained with high accuracy. Therefore, the productivity of the device can be improved.

Further, the tip portion 61a of the lock key 61 always projects from the housing groove 34b, and the lock key 61 and the housing member 30 (the rear thin plate 33 and the rear thick plate 34) that slidably support the lock key 61. Can be implemented by providing a small gap allowing sliding, foreign matter hardly enters the gap, foreign matter can be prevented from being caught, and the operation reliability of the lock key 61 is improved. be able to.

Further, a second stopper surface 23e2 which defines the most advanced angle phase (maximum relative rotation amount) of the rotor member 20 with respect to the housing member 30 is provided at the other end in the circumferential direction of the free recess 23e opposite to the stopper surface 23e1. Since the free recess 23e is formed with high precision in the circumferential direction, the maximum relative rotation amount of the rotor member 20 with respect to the housing member 30 can be easily set with high precision.

Also, by changing the circumferential length of the free recess 23e provided in the sub-rotor 23, the maximum relative rotation amount can be set appropriately, so that a valve opening / closing timing control device suitable for various models is provided. 23 can be easily manufactured by replacing the other parts (the rotor member 20).
Components and Housing Member 3 Excluding Subrotor 23
0, etc.).

In the above-described embodiment, the present invention is applied to the valve opening / closing timing control device provided in the driving force transmission system of the camshaft 10 for opening and closing the intake valve. However, the present invention relates to the driving of the camshaft for opening and closing the exhaust valve. The present invention can be implemented in a similar manner or with appropriate changes to a valve opening / closing timing control device provided in the force transmission system. Further, in the above embodiment, the present invention was implemented when the rotor member 20 was configured to supply and discharge the working oil to and from the advance oil chamber R1. It can also be implemented when configuring the supply / discharge passage.

In the above embodiment, the present invention is applied to the valve timing control apparatus provided with the lock mechanism B. However, the present invention is applied not only to the valve timing control apparatus provided with another lock mechanism but also to the lock mechanism. The present invention can be similarly or appropriately modified to a valve opening / closing timing control device that does not include the above. In the above-described embodiment, the present invention is applied to the valve opening / closing timing control device including four advance oil chambers R1 and four retard oil chambers R2. It can be changed and is not limited to the above embodiment.

In the above embodiment, the rotor member 20 is mounted on the camshaft 10 side,
Although the present invention has been carried out by assembling the housing member 30 on the crankshaft side, the present invention has been made such that the rotor member is assembled on the crankshaft side and the housing member is assembled on the camshaft side. It is also possible to carry out.

[Brief description of the drawings]

FIG. 1 is a vertical sectional side view showing an embodiment of a valve timing control apparatus according to the present invention.

FIG. 2 is a front view of the valve timing control apparatus shown in FIG.

FIG. 3 is a rear view of the valve timing control apparatus shown in FIG. 1;

FIG. 4 is a sectional view taken along line 4-4 in FIG. 1;

FIG. 5 is a sectional view taken along line 5-5 in FIG. 1;

FIG. 6 is a sectional view taken along the line 6-6 in FIG. 1 omitting the sprocket shown in FIG. 1;

FIG. 7 is a sectional view taken along the line 7-7 in FIG. 1;

FIG. 8 is a rear view of the main rotor shown in FIG.

FIG. 9 in FIG. 10 in the sub-rotor shown in FIG. 1;
It is sectional drawing which followed the -9 line.

FIG. 10 is a front view of the sub-rotor shown in FIG.

FIG. 11 is a rear view of the sub-rotor shown in FIG.

FIG. 12 is a front view of the rear thin plate shown in FIG. 1;

FIG. 13 is a front view of the rear thick plate shown in FIG. 1;

14 is a vertical sectional side view of a main part of the rear thick plate shown in FIG. 13;

[Explanation of symbols]

10 camshaft (driven shaft), 11 advance passage, 12
Retard passage, 20: rotor member, 21: main rotor, 2
1b: vane portion, 21c: annular concave portion, 21d: communicating concave portion, 23: sub rotor, 23a, 23b: communicating concave groove, D
... annular passage, 30 ... housing member, 31a ... shoe portion, 33 ... rear thin plate, 34 ... rear thick plate, 34c ... hub portion (annular bearing portion), R1 ... advanced oil chamber,
R2: retard oil chamber, C: hydraulic circuit, 100: switching valve, 11
0: oil pump, 120: oil reservoir.

Claims (2)

[Claims] 1. A driving force transmission system for transmitting driving force from a driving shaft of an internal combustion engine to a driven shaft that opens and closes an intake valve or an exhaust valve of the internal combustion engine, and rotates integrally with the driving shaft or the driven shaft. A housing member to be mounted on the housing member and a shoe portion provided on the housing member so as to be relatively rotatable to form an advance oil chamber and a retard oil chamber in the housing member by a vane portion, wherein the driven shaft or the drive shaft is formed. And a rotor member that rotates integrally with the valve, and a valve opening / closing timing control device including a hydraulic circuit for controlling supply and discharge of hydraulic oil to the advance oil chamber and the retard oil chamber. The member is
As a configuration including a main rotor rotatably mounted on the shoe portion, and a cylindrical subrotor provided on one side of the main rotor and rotatably mounted on an annular bearing portion provided on the housing member, An annular recess formed by a molding die on one side inner peripheral portion of the main rotor, and an outer peripheral portion of the annular recess formed by a molding die on one side intermediate portion of the main rotor, the advance oil chamber or the A communicating recess formed to communicate with the retarding oil chamber, and a radially extending outer peripheral portion of the annular recess formed by a molding die on the other side of the sub rotor and radially outwardly communicating with an annular passage formed by the sub rotor; A valve opening / closing timing, wherein a communication concave groove communicating with an inner hole of the sub-rotor inside the sub-rotor forms a supply / discharge passage of hydraulic oil to the advance oil chamber or the retard oil chamber. control Location. 2. The valve timing control device according to claim 1, wherein the other end of the annular bearing portion provided on the housing member is exposed to the annular passage.