JPH11311109A - Valve on-off timing controller - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent any increment in the manufacturing cost of a valve on-off timing controller and the malfumctioning of a locking member from occurring by making any shearing load so as not to act on a lock pin when locking by a locking member. SOLUTION: A locking member which is stored in rotary shafts (a camshaft and an inner rotor 20) or rotation transmitting member (an outer rotor and so on), and when in the specified relative phase between the rotary shaft 20 and the rotation transmitting member 39, and holds the relative phase between the rotary shaft 20 and the rotation transmitting member 30 by way of engaging with these elements 30 and 20 in the circumferential direction is composed of installing a piston part 81a being fitted in a storage hole to be formed in the rotary shaft or the rotation transmitting member and shiftable in the storage hole according to pressure in a pressure chamber to be formed in a bottom part of the storage hole, a regulating part 81b being connected to this piston part and being fitted in a circumferential clearance part 61 lying between a first stage part 25 of an outer circumference of the rotary shaft and a second stage part 23 of an inner circumference of the rotation transmitting member according to a movement of a piston part and capable of regulating a rotation to the other side in the circumferential direction to the rotation transmitting member 30 of the rotary shaft.

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 timing of opening or closing an intake valve or an exhaust valve in a valve train of an internal combustion engine.

[0002]

2. Description of the Related Art As one type of valve opening / closing timing control device of this type, a valve opening / closing rotary shaft (camshaft and an internal rotor integrally provided therewith) which is rotatably mounted on a cylinder head of an internal combustion engine. Formed between the rotation shaft and the rotation transmission member, the rotation transmission member being externally rotatably rotatable within a predetermined range and transmitting rotation power from a crankshaft, a vane attached to the rotation shaft, and the rotation transmission member. A fluid pressure chamber divided into an advance chamber and a retard chamber by the vane, a first fluid passage for supplying and discharging fluid to the advance chamber, and a fluid supply and exhaust to the retard chamber. A second fluid passage, a retraction hole formed in the rotation transmitting member and accommodating therein a lock pin spring-biased toward the rotation shaft, a rotation hole formed in the rotation shaft, and the rotation transmission member. The evacuation hole has a relative phase of a predetermined phase. A receiving hole which the head of the lock pin when the synchronization is fitted, there is one having a third fluid passage for supplying and discharging fluid into the receiving hole, for example, JP-1-
No. 92504 and Japanese Utility Model Laid-Open No. 2-50105.

[0003]

In the valve timing control devices disclosed in the above publications, the relative phase between the rotating shaft and the rotation transmitting member is maintained by fitting the head of the lock pin into the receiving hole. When the lock pin is fitted into the receiving hole, a shear load is applied to the lock pin at the boundary between the portion accommodated in the evacuation hole and the head, and the shear load is repeatedly generated by the fluctuating torque applied to the camshaft. Works.
For this reason, the lock pin and the receiving hole require heat treatment such as carburizing and quenching to secure the strength enough to withstand the shear load, and there is a problem that the manufacturing cost of the valve timing control apparatus is increased. .

Further, as described above, since a repeated shearing load acts on the lock pin, the inner peripheral surface of the evacuation hole is worn and deformed by the shearing load, so that the sliding of the lock pin is hindered and the lock pin is prevented from sliding. There was a risk of malfunction.

Accordingly, the present invention provides a valve timing control apparatus in which a shearing load does not act on a lock pin when locking by a lock member, thereby increasing the manufacturing cost of the valve timing control apparatus and operating the lock member. The problem is to prevent the occurrence of defects.

[0006]

Means for Solving the Problems The technical means of the present invention taken to solve the above problems is a rotating shaft for opening and closing a valve rotatably mounted on a cylinder head of an internal combustion engine, and a rotating shaft for the valve. A rotation transmitting member which is provided so as to be relatively rotatable in a predetermined range, a vane provided on one of the rotation shaft or the rotation transmission member, and a vane formed between the rotation shaft and the rotation transmission member and advanced by the vane. A fluid pressure chamber divided into a chamber for horn and a chamber for retard, a first fluid passage for supplying / discharging the fluid to the advance chamber, and a second fluid passage for supplying / discharging the fluid to the retard chamber And the rotation shaft or the rotation shaft that is housed in the rotation shaft or the rotation transmission member and circumferentially engages with the rotation transmission member or the rotation shaft at a predetermined relative phase between the rotation shaft and the rotation transmission member. A lock member for maintaining a relative phase with the rotation transmitting member. In the valve timing control apparatus used to control the opening / closing timing of an intake valve or an exhaust valve of an internal combustion engine, rotation of the rotating shaft to one side in a circumferential direction with respect to the rotation transmitting member is formed on the rotating shaft. The stopper portion is restricted by being brought into contact with the rotation transmitting member, and a first step portion directed to the other side in the circumferential direction is provided on the outer periphery of the rotation shaft, and on the inner periphery of the rotation transmission member. A second step portion which is directed to one side in the circumferential direction so as to face the first step portion and forms a predetermined circumferential gap with the first step portion when the stopper portion comes into contact with the first step portion; A piston that is fitted into a receiving hole formed in the rotation shaft or the rotation transmitting member and that can move in the receiving hole according to the pressure of a pressure chamber formed in the bottom of the receiving hole; The piston connected to the part Is moved that a structure in which a said regulation capable regulating unit rotation of the relative rotation transmission member to the other circumferential side of said rotary shaft fitted into the circumferential gap in accordance with the.

According to the above-described means, the relative phase between the rotation shaft and the rotation transmitting member is set by inserting the regulating portion of the lock member into the circumferential gap between the first step portion and the second step portion. Will be retained. At this time, the restricting portion is pinched in the circumferential direction between the first step portion and the second step portion, and does not receive a shear load. Deformation and wear are prevented from occurring on the inner periphery of the accommodation hole that accommodates the portion.

In the above means, the lock member is housed in the rotation transmitting member, and the cylindrical piston portion is axially movable in a housing hole formed in the rotation transmitting member in the axial direction. The restricting portion is connected to the piston portion via a connecting portion extending in the radial direction, and is axially moved in accordance with the movement of the piston portion. It is desirable to be able to move. Further, the rotation shaft includes a cam shaft rotatably supported by the cylinder head, and an internal rotor integrally provided at a tip end of the cam shaft, and the rotation transmitting member accommodates the internal rotor. An outer rotor, a front plate, and a rear plate, wherein the first step portion and the second step portion are formed on an outer periphery of the inner rotor and an inner periphery of the outer rotor, respectively, and the accommodation hole is formed. Preferably, the lock member is accommodated in the external rotor.

In the above means, the vane is integrally provided so as to extend in a radial direction from an outer periphery of the rotary shaft, and the stopper portion is provided at a radially inner end of the vane on one side in a circumferential direction. It is desirable to be protruded.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a valve timing control apparatus according to the present invention will be described below with reference to the drawings.

The valve timing control apparatus shown in FIGS. 1 and 2 is integrally assembled with a camshaft 10 rotatably supported by a cylinder head 70 of an internal combustion engine and a tip end thereof (left end in FIG. 1). A rotation shaft for opening and closing a valve, which is provided with an internal rotor 20 attached thereto, and an outer rotor 30, a front plate 40, a rear plate 50, and a rear plate 50 which are externally rotatable relative to the camshaft 10 and the internal rotor 20 within a predetermined range. Timing sprocket 5 provided integrally on the outer periphery
1, four vanes 20 a integrally provided on the outer periphery of the inner rotor 20, and a lock mechanism (phase holding mechanism) 80 attached to the outer rotor 30. As is well known, the timing sprocket 51 is configured to transmit rotational power clockwise in FIG. 2 from a crankshaft (not shown) via a crank sprocket and a timing chain.

The camshaft 10 has a well-known cam (not shown) for opening and closing the intake valve, and has therein a retard passage 11 and an advance passage 12 extending in the axial direction of the camshaft 10.
Is provided. The advance passage 12 is provided in the camshaft 10.
The connecting port 91b of the control valve 90 is formed in a mounting hole for the mounting bolt 16 provided in the camshaft 10 and passes through the radial passage 13 and the annular groove 14 provided in the camshaft 10 and the connecting passage 72 provided in the cylinder head 70. It is connected to the. The retard passage 11 is connected to the connection port 91 a of the control valve 90 via the annular groove 15 provided in the camshaft 10 and the connection passage 71 provided in the cylinder head 70.

The control valve 90 is capable of moving a spool 91 inserted in the housing movably in the axial direction to the left in FIG. 1 against a spring 93 by supplying a current to a solenoid 92. When energized, the supply port 91c connected to the oil pump P driven by the internal combustion engine communicates with the connection port 91a, and the connection port 91b communicates with the discharge port 91d. The connection port 91a communicates with the discharge port 91d while communicating with the discharge port 91b. For this reason, when the solenoid 92 of the control valve 90 is not energized, hydraulic oil is supplied to the retard passage 11, and when the solenoid 92 is energized, hydraulic oil is supplied to the advance passage 12. Is used to control the duty.

In the present embodiment, the internal rotor 20 is formed of a resin material, and is integrally fixed to the camshaft 10 by a single mounting bolt 16.
Each of the vanes 20a is integrally provided on the outer periphery thereof. Further, when the relative phase between the camshaft 10 and the internal rotor 20 and the external rotor 30 is synchronized at a predetermined phase (maximum retard position), which will be described later, the internal rotor 20 moves to the inner periphery of a protrusion 31 of the external rotor 30 which will be described later. The first step 25 (see FIG. 4), which is radially expanded so as to form a circumferential gap 61 between the formed second step 33 and the opposing surface 25 a, and each vane 20 a A passage 23 communicating the advance passage 12 and each advance chamber R2 so as to supply and discharge the working oil from the advance passage 12 to the divided advance chamber R1, and a side facing the tip end surface of the camshaft 10. An annular groove 21 formed on one end face of the annular groove 21 and communicating with the retard passage 11, four passages 22 extending from the annular groove 21 to the other end face side in the axial direction, and a retard chamber R 2 partitioned by the vanes 20 a. The hydraulic oil is supplied from the retard passage 11 to the annular groove 21 and And a passage 24 communicating the respective retarded angle chamber R2 and the passages 22 to supply and discharge through the road 22. The first step 25 is formed so that the opposing surface 25a faces the advance side (clockwise in FIG. 2).
As shown in the figure, the axial rear plate 50 of the first step 25
On the side, a notch 26 is formed on the retard side (counterclockwise in FIG. 2).

The outer rotor 30 is formed of a resin material in the present embodiment, and is mounted on the outer periphery of the inner rotor 20 so as to be relatively rotatable within a predetermined range. 50 are joined and integrally connected by four connecting bolts (not shown) penetrating through holes 32. In addition, the external rotor 3
On the inner circumference of the projection 0, four protrusions 31 are formed at predetermined intervals in the circumferential direction so as to protrude radially inward.
The inner peripheral surface of the internal rotor 20 is
The outer rotor 30 is rotatably supported by the inner rotor 20 in such a configuration that the outer rotor 30 is in sliding contact with the outer peripheral surface of the outer rotor 30 in a liquid-tight manner. It is formed in the direction. The first inner surface of the internal rotor 20 is
The second step portion 33 with which the step portion 25 slides is formed so as to be enlarged in the radial direction. The accommodation hole 34 is formed to open to the rear plate 50 side in the axial direction and to open to the second step portion 33 side in the radial direction, and the second hole is formed in the bottom of the accommodation hole 34 on the front plate 40 side. A hydraulic hole 34 a penetrating in the axial direction toward the front plate 40 is formed at a position radially outwardly separated from the step portion 33. The opening of the hydraulic hole 34a on the front plate 40 side is
And the opening end of the hydraulic hole 34a on the front plate 40 side is adjacent to the fluid pressure chamber R0 via the communication groove 35 formed in the surface of the projection 31 of the external rotor 30 facing the front plate 40 side. Is connected to the advance chamber R1.

Each vane 20a is provided integrally with the outer periphery of the inner rotor 20 as described above, and
0, each protrusion 31 of the outer rotor 30 and the inner rotor 20.
And a fluid pressure chamber R0 formed between the front plate 40 and the rear plate 50 is formed by an advance chamber R1 and a retard chamber R1.
2 and the stopper portions 20b, 20 of one vane (upper vane in FIG. 2) 20a are provided on the circumferential end faces of the pair of protrusions 31 formed on the outer rotor 30 so as to face each other.
Due to the contact of c, the phase (the relative rotation amount) adjusted by the valve timing control device is limited. In the present embodiment, the stopper 20b,
20c is formed at the base (radial inner end) of one vane 20a located at the top of FIG.
The outer diameter Rs of the stopper portions 20b and 20c is the maximum outer diameter of the sliding outer diameter R1 <Rs <the vane 20a of the internal rotor 20 extending in the circumferential direction from the base of one vane 20a located at the top of FIG. It is set as follows. Recesses 31a and 31b are formed on the opposing circumferential end surfaces of the pair of protrusions 31 with which the stopper portions 20b and 20c abut, respectively, and the outer diameter of the recesses 31a and 31b> the sliding of the inner rotor 20. It is set to be the dynamic outer diameter R1. Accordingly, in the present embodiment, the vane 20a can be reduced in thickness only to a minimum (rigidity with respect to the oil pressure in the fluid pressure chamber R0) without receiving an impact load during the above-described phase limitation. Thus, the number of vanes can be increased, and a large conversion torque and a large conversion angle can be secured.

As shown in FIG. 3, the lock member 81 is assembled in the accommodation hole 34 so as to be movable in the axial direction.
A piston portion 81 which is slidably fitted in the hydraulic hole 34a in the axial direction to form the pressure chamber 60 at the open end of the hydraulic hole 34a.
a and a restricting portion 81b connected to the piston portion 81a via a connecting portion 81c so as to protrude in the axial direction parallel to the piston portion 81a. The lock member 81 is constantly urged toward the pressure chamber 60 by a spring 82 having one end locked to the rear plate 50, and the hydraulic oil in the pressure chamber 60 is supplied by supplying hydraulic oil to the pressure chamber 60. This allows the spring to move toward the rear plate 50 against the spring 82. The restricting portion 81b can be fitted into the circumferential gap 61 formed between the first step portion 25 and the second step portion 33 in the maximum retarded state shown in FIG. 2 in which the stopper portion 20b contacts the concave portion 31a. The lock member 81 (piston portion 81a) moves toward the rear plate 50 by the oil pressure of the pressure chamber 60 as described above, and retreats from the circumferential gap 61. It is supposed to. When the restricting portion 81b is retracted, the internal rotor 20 is not hindered by the notch 26 from rotating toward the advance angle with respect to the external rotor 30 by the restricting portion 81b.
The inner rotor 20 is rotatable with respect to the outer rotor 30 up to the maximum advancing state in contact with the inner rotor 20.

In the valve opening / closing timing control device of the present embodiment configured as described above, the internal combustion engine is started and the predetermined hydraulic pressure is supplied to each of the advance chamber R1 and each of the retard chamber R2 in the intermediate phase. Balance state (the pressing force by the advance hydraulic pressure in each advance chamber R1 is the pressing force by the retard hydraulic pressure in each retard chamber R2, and the hydraulic pressure is transmitted through the rotation transmission path from the external rotor 30 to the internal rotor 20). (In a state in which the chamber R0 and the vane 20a are interposed and the sum of the force in the retard direction acting on the internal rotor 20 and the camshaft 10 is always balanced) according to the operating state of the internal combustion engine. And the control valve 9
By increasing the duty ratio of the current supplied to the solenoid 92 of 0, hydraulic oil is supplied to the advance chambers R1 through the advance passages 12 and 23, and at the same time, the passage oil is supplied from the retard chambers R2 to the passages R2. 24, 22 and retard passage 11 and control valve 9
0 and the like, the inner rotor 20 and each vane 20a are connected to the outer rotor 30, both plates 40, 5
Relative to 0 etc. on the advance side (clockwise in FIG. 2),
The relative rotation amount (maximum advance angle amount) is limited by the contact of the stopper portion 20c with the concave portion 31b. Further, by reducing the duty ratio of the current supplied to the solenoid 92 of the control valve 90, the retard passage 11 and each passage 2
Hydraulic oil is supplied to each of the retard chambers R2 through the chambers 2 and 24, and each passage 23 and the advance passage 12
When the hydraulic oil is discharged through the control valve 90 and the like, the inner rotor 20 and each vane 20a rotate relative to the outer rotor 30, the two plates 40, 50, and the like in the retarded direction (counterclockwise in FIG. 2). As shown in FIG. 2, the relative rotation amount (maximum retardation amount) is limited by the stopper portion 20b abutting on the concave portion 31a. During this phase conversion control (except during the maximum retarded state), a hydraulic pressure higher than the set pressure (a hydraulic pressure lower than the predetermined hydraulic pressure) is supplied to the pressure chamber 60 through the communication groove 35, and the piston portion 81a The (lock member 81) moves against the spring 82, and the regulating portion 81b
Are retracted from the circumferential gap 60 into the accommodation hole 34, and the lock by the lock member 81 is released.

When the internal combustion engine is stopped, the operation of the oil pump P is stopped, the supply of the hydraulic oil to the fluid pressure chamber R0 is stopped, and the control valve 90 is turned off. Thus, the pressing force by the advance hydraulic pressure in the advance chamber R1 and the pressing force by the retard hydraulic pressure in the retard chamber R2 do not act on the vane 60, and the internal rotor 20 and the cam shaft 10 It is rotated to the maximum retarded state by the force in the retard direction. In this maximum retarded state, the circumferential gap 6
The restricting portion 81b is fitted in the inner rotor 20 and the relative phase between the inner rotor 20 and the outer rotor 30 is held (locked).

In this locked state, even if the internal combustion engine is started and the oil pump P is driven, a predetermined time after the start of the internal combustion engine, that is, the oil pressure in the fluid pressure chamber R0 rises and the vane 20a is driven by the oil pressure. And the internal rotor 20 will rotate in the retarded and advanced directions with respect to the external rotor 30 due to the fluctuating torque acting on the camshaft 10. However, at this time, the regulating portion 81b is fitted into the circumferential gap 61, and the rotation of the camshaft 10 and the internal rotor 20 with respect to the external rotor 30 in the retard direction and the advance direction is prevented by the stopper portion 20b. You. Accordingly, it is possible to prevent a sound generated when the vane 20a comes into contact with the end wall of the fluid pressure chamber R0 when the internal combustion engine is started.

In the present embodiment, at the time of the above-described locking, the restricting portion 81b is pinched between the first step portion 25 and the second step portion 33, and a shear load is applied to the lock member 81 as in the conventional device. Does not work. In general, since the compressive load is high with respect to the shear strength, it is not necessary to perform a heat treatment such as carburizing and quenching on the lock member 81 to improve the strength in the present embodiment. Therefore, according to the present embodiment, it is possible to reduce the manufacturing cost of the valve timing control apparatus. Also,
In the present embodiment, the regulating portion 81b and the circumferential gap 6
Even if there is a backlash in the circumferential direction, the lock member 81 does not move in the circumferential direction by the amount of the backlash but the backlash is absorbed by the rotation of the lock member 81 about the axis of the piston portion 81a. You. For this reason, the hydraulic hole 3
No load is applied to the sliding surface 4a, and the sliding in the hydraulic hole 34a of the piston portion 81a is smoothly maintained.
Therefore, the first step portion 25, the second step portion 33, and the regulating portion 8
It is not necessary to make 1b high precision, and it is possible to reduce machining by molding, and it is possible to reduce the manufacturing cost of the valve timing control apparatus. In addition, since the lock member 81 is assembled in the accommodation hole 34 in the axial direction, the assembly can be performed in the same direction, and the productivity can be improved.

In the above embodiment, one vane 2
The present invention has been implemented in a valve opening / closing timing control device in which the maximum advance amount is limited by the abutment of the stopper portion 20c of 0a against the concave portion 31b. The present invention can be similarly applied to a valve opening / closing timing control device in which the hydraulic pressure of the chamber R2 is controlled so that the stopper portion is restricted before coming into contact with the concave portion 31b. In this case, the stopper 20c and the recess 31b become unnecessary. Further, in the above-described embodiment, the present invention is applied to the valve opening / closing timing control device mounted on the intake camshaft 10, but the present invention is applied to the valve opening / closing timing control device mounted on the exhaust camshaft. Can be similarly implemented.

[0023]

As described above, according to the present invention, the restricting portion of the lock member is fitted into the circumferential gap between the first step portion and the second step portion, thereby transmitting the rotation to the rotating shaft. Since the relative phase of the members is maintained, the regulating portion is clamped in the circumferential direction between the first step portion and the second step portion during this holding, and does not receive a shear load. For this reason, processing for improving the shear strength is not required, and the manufacturing cost of the valve timing control apparatus can be reduced. In addition, deformation and wear occur in the inner circumference of the housing hole that houses the piston portion. Is prevented,
The operation reliability of the valve timing control device can be improved.

[Brief description of the drawings]

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

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a perspective view of a lock member according to the first embodiment shown in FIG.

FIG. 4 is a perspective view showing a first step portion of the internal rotor according to the first embodiment shown in FIG. 1;

[Explanation of symbols]

 Reference Signs List 10 camshaft (rotating shaft) 11 retard passage (second fluid passage) 12 advance passage (second fluid passage) 20 internal rotor (rotating shaft) 20a vane 20b stopper portion 23 passage (first fluid passage) 24 passage ( 2nd fluid passage) 25 1st step part 30 External rotor (rotation transmission member) 31 Projection 33 2nd step part 34 Housing hole 34a Hydraulic hole 40 Front plate (rotation transmission member) 50 Rear plate (rotation transmission member) 81 Lock Member 81a Piston portion 81b Restriction portion 81c Connecting portion 82 Spring R0 Fluid pressure chamber R1 Advance chamber R2 Delay chamber

Claims (4)

[Claims] A rotating shaft for opening and closing a valve rotatably mounted on a cylinder head of an internal combustion engine; a rotation transmitting member externally rotatable relative to the rotating shaft within a predetermined range; and the rotating shaft or the rotating shaft. A vane provided on one of the transmission members,
A fluid pressure chamber formed between the rotation shaft and the rotation transmitting member and divided into an advance chamber and a retard chamber by the vane; and a first fluid for supplying and discharging fluid to and from the advance chamber. Aisle and
A second fluid passage for supplying / discharging fluid to / from the retard chamber, the rotation transmitting member or the rotation transmitting member being contained in the rotation shaft or the rotation transmission member at a predetermined relative phase between the rotation shaft and the rotation transmission member; A lock member that is engaged with the rotation shaft in a circumferential direction to maintain a relative phase between the rotation shaft and the rotation transmitting member, and is used to control opening / closing timing of an intake valve or an exhaust valve of the internal combustion engine. The rotation of the rotary shaft to one side in the circumferential direction with respect to the rotation transmitting member is restricted by a stopper formed on the rotary shaft abutting on the rotation transmitting member. A first step portion directed to the other side in the circumferential direction is provided on the outer periphery of the rotating shaft, and the stopper is directed to one side in the circumferential direction on the inner periphery of the rotation transmitting member so as to face the first step portion. At the time of contact of the part A second step portion that forms a predetermined circumferential gap between the step portion and the step portion is provided, and the lock member is fitted into a receiving hole formed in the rotation shaft or the rotation transmitting member and formed at the bottom of the receiving hole. A piston that is movable in the housing hole in accordance with the pressure of the pressure chamber, and is connected to the piston and fits into the circumferential gap according to the movement of the piston to rotate the rotation shaft. A valve opening / closing timing control device, comprising: a regulating portion capable of regulating rotation of the transmission member to the other side in the circumferential direction. 2. The lock member is housed in the rotation transmitting member, and the cylindrical piston portion is axially movable in a housing hole formed in the rotation transmission member in the axial direction, and is provided in the pressure chamber. The restricting portion is connected to the piston portion via a connecting portion extending in a radial direction, and is movable in the axial direction in accordance with the movement of the piston portion, while being spring-biased and fitted. The valve opening / closing timing control device according to claim 1, wherein: 3. The rotating shaft comprises a camshaft rotatably supported by the cylinder head and an internal rotor integrally provided at a tip end of the camshaft. Housing the outer rotor,
A front plate and a rear plate, wherein the first step portion and the second step portion are formed on an outer periphery of the inner rotor and an inner periphery of the outer rotor, respectively, and wherein the housing hole is formed; The valve timing control apparatus according to claim 2, wherein the lock member is housed in a rotor. 4. The vane is integrally provided so as to extend radially from an outer periphery of the rotating shaft, and the stopper portion is provided at a radially inner end of the vane so as to protrude to one side in a circumferential direction. The valve opening / closing timing control device according to claim 1, wherein: