JP4645561B2 - Valve timing control device - Google Patents

Description

  The present invention relates to a valve opening / closing timing control device for controlling the opening / closing timing of intake and exhaust valves of an internal combustion engine.

  In recent years, a valve opening / closing timing control device that can change the opening / closing timing of an intake valve or an exhaust valve in accordance with the operating state of an internal combustion engine is attached to one end of a camshaft.

  An internal combustion engine that transmits engine rotational power from a crankshaft to a camshaft by a power transmission means such as a timing belt or a timing chain, as described in Patent Document 1, for example, as one type of valve opening / closing timing control device of this type. In an engine, a rotor member assembled with a plurality of vanes extending in the radial direction is fixed to the camshaft side, and the timing pulley fitted coaxially to the rotor member is fluidized in a circular shape on its inner periphery. There is a vane type valve opening / closing timing control device that forms a chamber and is engaged with a fluid pressure chamber as a piston.

In the above system, the fluid pressure of the working fluid is applied to the first pressure chamber or the second pressure chamber of the fluid pressure chamber partitioned by the vanes according to the operating state of the internal combustion engine, and the relative pressure is generated between the camshaft and the timing pulley. Valve opening / closing control is performed by changing the phase. Specifically, the rotor member (17) having a plurality of vanes (18) extending in the radial direction and the rotor member (17) are included, and the vanes (18) are respectively fitted between the rotor member (17). As described above, the first pressure of the fluid pressure chamber formed by the vane (18) is composed of a housing member (19) in which a plurality of fluid pressure chambers on which the working fluids for advance and retard act are formed in a circular shape. The main passage (27) extending in the axial direction of the camshaft and the branch passage (13) extending radially from the main passage (27) are provided in at least one of the chamber (30) and the second pressure chamber (31). And a working fluid is led out through the fluid passage.
JP-A-9-151711

  In general, when the engine is operated at low speed, the amount of working fluid discharged from the oil pump is small, so compared to when operating at medium and high speed, the amount of working fluid supplied to the fluid pressure chamber is small. The pressure acting on the fluid pressure chamber is small. Further, the rotational force when starting the rotation of the rotor relative to the housing (hereinafter referred to as initial starting torque) is larger than the rotational force when further rotating the rotor that is rotating relative to the housing relative to the housing. For this reason, an area where the vane in the fluid pressure chamber receives a force from the working fluid (hereinafter referred to as a pressure receiving area of the vane) is set so that an initial starting torque can be ensured when the engine is operated at a low speed.

  In the apparatus described in Patent Document 1, the pressure receiving area of the vane is constant. That is, the volume of the fluid pressure chamber required for rotating the rotor by a unit angle is constant. For this reason, the amount of working fluid required to rotate the rotor by a unit angle is constant.

  When the engine is operated at medium and high speeds, the amount of working fluid supplied is large, so that the pressure acting on the fluid pressure chamber is large and the rotational force of the rotor is sufficiently secured. However, since the amount of working fluid required to rotate the rotor at a unit angle is constant, the time required to rotate the rotor at a unit angle during operation at medium and high speeds of the engine is It depends on the supply amount. In particular, when the engine is operated at a high speed, the camshaft is also rotating at a high speed. Therefore, it is required to further improve the response speed of the valve timing control apparatus.

  The present invention has been made in view of the above-described prior art, and it is an object of the present invention to provide a technique for further improving the response speed of the valve opening / closing timing control device in a state where the internal combustion engine is at a high speed and the amount of working fluid supplied is large. And

In order to solve the above-mentioned problems, the technical means taken in the present invention are, as described in claim 1, a housing member that rotates integrally with one of a crankshaft and a camshaft of an internal combustion engine, and the housing A rotor member that is assembled to the member so as to be rotatable relative to the housing member, and rotates integrally with the other of the camshaft and the crankshaft, and a fluid pressure chamber formed between the housing member and the rotor member And is provided so as to rotate integrally with the rotor member, and is slidably contacted with a wall surface in the large diameter direction of the fluid pressure chamber and supplied to the fluid pressure chamber so as to rotate the rotor member relative to the housing member. A valve opening / closing timing control device comprising a vane that slides between an initial position and an operating position by a working fluid, wherein the radius of the wall surface is: As serial state of the initial position is larger than the state of the working position, the wall includes a starting portion the vane abuts in the initial position, from the vane abuts in the operating position the start part An end point portion having a small radius, and a connection portion that connects the starting point portion and the end point portion and gradually decreases in radius from the starting point portion toward the end point portion .

Alternatively, in order to solve the above-described problem, the technical means taken in the present invention includes a housing member that rotates integrally with one of a crankshaft and a camshaft of an internal combustion engine, and A rotor member that is assembled to the housing member so as to be rotatable relative to the housing member, and rotates integrally with the other of the camshaft and the crankshaft; and a fluid pressure formed between the housing member and the rotor member And a fluid pressure chamber provided to rotate integrally with the rotor member, in sliding contact with the wall surface in the large diameter direction of the fluid pressure chamber, and to rotate the rotor member relative to the housing member. A valve opening / closing timing control device comprising: a vane that slides between an initial position and an operating position by a supplied working fluid; The wall surface includes a starting point where the vane abuts at the initial position, and the vane is between the initial position and the operating position so that the initial position is larger than the operating position. And an intermediate portion having a radius smaller than that of the starting portion, and a connecting portion connecting the starting portion and the intermediate portion and having a radius gradually decreasing from the starting portion toward the intermediate portion .

Preferably, as described in claim 3 , the rotor member may include a groove portion that supports the vane movably in the radial direction of the wall surface.

According to the first and second aspects of the present invention, the radius of the large-diameter wall surface of the fluid pressure chamber is larger in the vane initial position than in the vane operating position. In this structure, as the vane moves from the initial position to the operating position, an area where the vane in the fluid pressure chamber receives a force from the working fluid (hereinafter referred to as a pressure receiving area of the vane) decreases. That is, as the vane moves from the initial position to the operating position, the volume of the fluid pressure chamber necessary for rotating the rotor member by a unit angle decreases.

  Therefore, under the same supply amount of the working fluid per unit time, the hydraulic pressure chamber is filled with the working fluid in a shorter time than the conventional structure, and the rotor member rotates with a smaller amount of the working fluid. To do.

  Therefore, in a state where the internal combustion engine is at a high speed and the supply amount of the working fluid is large, after the vane starts to move from the initial position, the rotor member rotates relative to the housing member in a shorter time, and the valve opening / closing timing The response speed of the control device is further improved.

Further, according to the first and second aspects of the present invention, when the rotor member rotates, the vane moves smoothly along the wall surface, and the valve opening / closing timing control device operates smoothly.

According to the invention described in claim 3 , when the rotor member rotates, the vane smoothly follows the change in the radius of the wall surface, and the valve opening / closing timing control device operates smoothly.

  Hereinafter, an embodiment of a valve timing control apparatus according to the present invention will be described with reference to the drawings.

  A valve timing control apparatus 1 shown in FIGS. 1 to 3 includes a camshaft 10 that is rotatably supported by a cylinder head 100 of an internal combustion engine, and a rotor 20 that is integrally assembled at the tip of the camshaft 10. It has a rotor member 2 for opening and closing the valve. Further, the valve timing control device 1 includes a housing member 3 including a housing 30, a front plate 50, and a rear plate 51 that are assembled so as to be able to rotate relative to the rotor 20 within a predetermined range. A timing sprocket 31 is integrally formed on the outer periphery of the housing 30. Furthermore, a torsion spring 60 assembled between the rotor 20 and the front plate 50, five vanes 70 assembled to the rotor 20, a lock key 80 assembled to the housing 30, and the like are provided.

 As is well known, rotational power is transmitted to the timing sprocket 31 from the crankshaft 110 via a crank sprocket (not shown) and the timing chain 120 in the clockwise direction shown as the camshaft rotation direction in FIG. In this embodiment, as an example, a configuration in which the rotation power of the crankshaft 110 of the internal combustion engine is transmitted to the timing sprocket 31 of the housing 30 via the timing chain 120 will be described, but the present invention is not limited thereto. It is not a thing. For example, as another configuration, a belt member may be used instead of the timing chain 120, and the timing sprocket 31 may be replaced with a pulley.

 The camshaft 10 has a known cam (not shown) that opens and closes an intake valve (not shown), and a retard oil passage (hydraulic circuit) 11 extending in the axial direction of the camshaft 10 is provided inside the camshaft 10. An advance oil passage (hydraulic circuit) 12 is provided. The retard oil passage 11 is connected to the second connection port 202 of the switching valve 200 through the radial passage 71 provided in the camshaft 10 and the annular groove 13 and the connection passage 15 provided in the cylinder head 100. The advance oil passage 12 is connected to the first connection port 201 of the switching valve 200 through the radial passage 72 provided in the camshaft 10 and the annular groove 14 and the connection passage 16 provided in the cylinder head 100.

 The switching valve 200 is a known valve that moves the spool 204 against a spring (not shown) by energizing the solenoid 203. When energized, the supply port 206 connected to the oil pump 205 driven by the internal combustion engine communicates with the first connection port 201 and the second connection port 202 communicates with the discharge port 207 as shown in FIG. It is configured. When the power is not supplied, the supply port 206 communicates with the second connection port 202, and the first connection port 201 communicates with the discharge port 207. For this reason, when the switching valve 200 is energized, hydraulic oil (hydraulic pressure) is supplied to the advance angle oil passage 12, and when the switching valve 200 is not energized, hydraulic oil (hydraulic pressure) as a working fluid is supplied to the retard angle oil passage 11. Yes. The switching valve 200 is duty-controlled to change the ratio between energization and non-energization per unit time. For example, when the duty ratio is controlled at 50%, the first and second ports 201 and 202 and the supply and discharge ports 206 and 207 are not in communication with each other.

 The rotor 20 is integrally fixed to the camshaft 10 by a single mounting bolt 95 through a through hole formed in the shaft center thereof, thereby constituting the rotor member 2. The rotor 20 is formed with five vane grooves 21 (in FIG. 2, only one number is attached) and one lock groove 22. A vane 70 is attached to the vane groove 21 so as to be movable in the radial direction of the rotor 20. As shown in FIG. 1, a vane spring 73 is disposed between the bottom of the vane groove 21 and the lower surface of the vane 70. Accordingly, the vane 70 is urged outward in the radial direction of the rotor 20, and moves in the radial direction of the rotor 20 in the vane groove 21 against the urging force of the vane spring 73. When the relative positions of the camshaft 10 and the rotor 20 and the housing 30 are synchronized at a predetermined phase (the most advanced angle position), a lock key is inserted into the lock groove 22 by a predetermined amount as shown in FIG. 80 is arranged.

 The rotor 20 includes five retard oil passages 23 and four advance oil passages 24 and one advance oil passage / lock oil passage 28 extending in the radial direction. The retarding oil passage 23 is communicated with the retarding oil passage 11 via a retarding oil passage 25 (in FIG. 2, only one part is given a number) provided in the axial direction. The retard oil passage 11 communicates with the connection passage 15 of the cylinder head 100 via the radial passage 71 of the camshaft 10 and the annular groove 13. The advance oil passage 24 and the advance oil passage / lock oil passage 28 communicate with the advance oil passage 12 via an advance oil passage 26 (only one is numbered in FIG. 2) provided in the axial direction. Has been. The advance oil passage 12 communicates with the connection passage 16 of the cylinder head 100 via the radial passage 72 of the camshaft 10 and the annular groove 14.

 The housing member 3 is configured such that a front plate 50 and a rear plate 51 are joined to both sides in the axial direction of the housing 30 and are integrally assembled by six connecting bolts 90. The housing member 3 is assembled to the outer periphery of the rotor 20 so as to be relatively rotatable in a predetermined angle range.

 The torsion spring 60 is attached with one end locked to the front plate 50 and the other end locked to the rotor 20, and the rotor 20 is advanced with respect to the housing 30, the front plate 50, and the rear plate 51 (FIG. 2). (Clockwise). Therefore, the response of the operation of the rotor 20 toward the advance side is improved.

 A timing sprocket 31 is integrally formed on the outer periphery of the housing 30. Five convex portions 33 are formed on the inner periphery of the housing 30. The inner peripheral surfaces of these convex portions 33 are in contact with the outer peripheral surface of the rotor 20, and the housing 30 is rotatably supported by the rotor 20. A certain projecting portion 33 is formed with a retracting groove 34 for storing the lock key 80, and a receiving hole 35 for communicating with the retracting groove 34 and for urging the lock key 80 radially inward. .

  The vane 70 advances a fluid pressure chamber R0 (only one number is attached in FIG. 2) formed between the housing 30 and the rotor 20 and between the convex portions 33 adjacent to each other in the circumferential direction of the housing 30. It is partitioned into a chamber R1 and a retarded oil chamber R2. On the most retarded angle side, relative rotation is restricted at a position where the vane 70 contacts the circumferential side surface 33a of the convex portion 33 (an initial position of the vane 70), and on the most advanced angle side, it is indicated by a two-dot chain line in FIG. Thus, the vane 70 is regulated at a position where the vane 70 contacts the other side surface 33b in the circumferential direction of the convex portion 33 (an operating position of the vane 70). At the most retarded angle side, the lock key 80 enters the lock groove 22 to restrict relative rotation of the rotor 20 and the housing 30.

  The large-diameter wall surface 40 in the fluid pressure chamber R <b> 0 (indicated by a number in one place in FIG. 2) is in sliding contact with the vane 70 assembled to the rotor 20. The wall surface 40 has a starting point portion 41, an end point portion 42, and a connecting portion 43. The starting point portion 41 contacts the vane 70 at the initial position. The end point portion 42 has a radius smaller than the radius of the starting point portion 41 with the vane 70 in contact with the operating position. The connecting portion 43 is provided between the starting point portion 41 and the ending point portion 42 of the wall surface 40, and connects the starting point portion 41 and the ending point portion 42. The radius of the connecting portion 43 gradually decreases from the starting point portion 41 toward the ending point portion 42. The wall surface 40 of the fluid pressure chamber R0 is formed so that its radius changes small with respect to the rotation direction of the camshaft 10 (shown in FIG. 2).

 The operation of the valve timing control apparatus 1 of the present embodiment configured as described above will be described with reference to FIGS.

  When the internal combustion engine is stopped, the oil pump 205 is stopped and the switching valve 200 is in a non-energized state, so hydraulic fluid (hydraulic pressure) is not supplied to the fluid pressure chamber R0. At this time, as shown in FIG. 2, the lock key 80 is immersed in the lock groove 22 of the rotor 20, and the relative rotation between the rotor 20 and the housing 30 is restricted. Even when the internal combustion engine is started and the oil pump 205 is driven, the oil pump 205 is supplied while the duty ratio for energizing the switching valve 200 is small (the ratio of the energization time to the non-energization time per unit time is small). Since the hydraulic fluid (hydraulic pressure) is only supplied to the retard oil chamber R2 through the connection passage 15 and the retard oil passages 11, 25 and 23, the valve opening / closing timing control device 1 is maintained in the locked state. At this time, the vane 70 assembled to the rotor 20 is in the initial position, and is in contact with the starting point portion 41 of the wall surface 40 of the fluid pressure chamber R0 as shown in FIG.

 If the valve opening / closing timing requires an advance angle depending on the operating conditions of the internal combustion engine, the duty ratio for energizing the switching valve 200 is increased, and the position of the spool 204 is switched. The hydraulic oil (hydraulic pressure) supplied from the oil pump 205 is supplied to the advance oil chamber R1 through the connection passage 16 and the advance oil passages 12, 26 and 24. At the same time, the hydraulic oil (hydraulic pressure) is supplied to the lock groove 22 through the advance oil passage / lock oil passage 28 and introduced into the distal end portion 80 a of the lock key 80. As a result, hydraulic pressure is applied to the distal end portion 80a of the lock key 80, the lock key 80 retreats from the lock groove 22, and the housing 30 and the rotor 20 can be rotated relative to each other. On the other hand, the hydraulic oil (hydraulic pressure) in the retarded oil chamber R2 is discharged from the discharge port 207 of the switching valve 200 through the retarded oil passages 23, 25 and 11 and the connection passage 15, and is shown in FIG. As shown, the rotor 20 begins to rotate relative to the housing 30 toward the advance side. As the rotor 20 rotates, the vane 70 assembled to the rotor 20 moves along the wall surface 40 of the fluid pressure chamber R0 from the starting point portion 41 to the end point portion 42 via the connecting portion 43. During this time, the vane 70 moves in the radial direction against the urging force of the vane spring 73 in the vane groove 21 to smoothly follow the change in the radius of the wall surface 40, so that the rotor 20 smoothly moves relative to the housing 30. Rotate to. As shown in FIG. 3C, when the vane 70 comes into contact with the other side surface 33 b of the convex portion 33 of the housing 30, the relative rotation of the rotor 20 relative to the housing 30 toward the advance side is restricted. In FIG.3 (c), the vane 70 exists in an operation position and is contact | abutting with the end point part 42 among the wall surfaces 40 of the fluid pressure chamber R0.

  As described above, in the wall surface 40 of the fluid pressure chamber R 0 that is in sliding contact with the vane 70, the radius of the end point portion 42 is smaller than the radius of the start point portion 41, and the radius of the connection portion 43 is from the start point portion 41 toward the end point portion 42. Decrease gradually. According to this structure, as the vane 70 moves from the initial position to the operating position, an area where the vane 70 in the fluid pressure chamber R0 receives a force from the working fluid (hereinafter referred to as a pressure receiving area of the vane 70) decreases. That is, as the vane 70 moves from the initial position to the operating position, the volume of the fluid pressure chamber R0 necessary for rotating the rotor 20 by a unit angle decreases. For this reason, compared with the conventional structure (indicated by a two-dot chain line in FIGS. 3A to 3C) where the radius of the wall surface 40 is constant under the same supply amount of the working fluid per unit time. The fluid pressure chamber R0 is filled with the working fluid in a shorter time, and the rotor 20 rotates with a smaller amount of the working fluid. Therefore, in a state where the internal combustion engine is at a high speed and the supply amount of the working fluid is large, after the vane 70 starts to move from the initial position, the rotor 20 rotates relative to the housing 30 in a shorter time, and the valve is opened and closed. The response speed of the timing control device 1 is further improved.

  Further, in the wall surface 40 of the fluid pressure chamber R0, the connecting portion 43 that connects the starting point portion 41 and the ending point portion 42 is formed so that the radius gradually decreases from the starting point portion 41 toward the ending point portion 42. When the rotor 20 rotates with respect to the housing 30, the vane 70 moves smoothly along the wall surface 40 from the start point 41 to the end point 42. Thereby, the valve opening / closing timing control apparatus 1 operates smoothly.

 Next, in the state shown in FIG. 3 (c), when the valve opening / closing timing needs to be retarded depending on the operating conditions of the internal combustion engine, the duty ratio for energizing the switching valve 200 is reduced and the position of the spool 204 is switched. . The hydraulic oil (hydraulic pressure) supplied from the oil pump 205 is supplied to the retarded oil chamber R2 through the connection passage 15 and the retarded oil passages 11, 25 and 23. On the other hand, the hydraulic oil (hydraulic pressure) in the advance oil chamber R1 is discharged from the discharge port 207 of the switching valve 200 through the advance oil passages 24, 26 and 12 and the connection passage 16, and FIG. As shown in FIG. 3, the rotor 20 starts to rotate relative to the housing 30 toward the retarded angle side. As the rotor 20 rotates, the vane 70 assembled to the rotor 20 moves from the end point portion 42 to the starting point portion 41 via the connection portion 43 along the wall surface 40 of the fluid pressure chamber R0. As shown in FIG. 3A, when the vane 70 comes into contact with the one side surface 33 a of the convex portion 33 of the housing 30, the relative rotation of the rotor 20 with respect to the housing 30 toward the retard side is restricted. When hydraulic oil (hydraulic pressure) is discharged from the lock groove 22, the lock key 80 movably disposed in the housing 30 is immersed in the lock groove 22, and the relative rotation between the housing 30 and the rotor 20 is restricted. The

  In the above description, the example in which the radius of the wall surface 40 of the fluid pressure chamber R0 changes stepwise between the two portions (the start point portion 41 and the end point portion 42) is shown, but the present invention is not limited to this. For example, as shown in FIG. 4, an intermediate portion 44 having a radius smaller than the radius of the starting point portion 41 and larger than the radius of the end point portion 42 can be provided on the wall surface 40 of the fluid pressure chamber R0. Thereby, the volume of the fluid pressure chamber R0 required for rotating the rotor 20 by a unit angle can be changed more finely according to the rotational position of the rotor 20 with respect to the housing 30, and the response speed of the valve timing control device 1 can be changed. This is a more preferable structure for further improvement of the above. Further, in the wall surface 40, between the starting point portion 41 and the intermediate portion 44, a connecting portion 45 that connects the starting point portion 41 and the intermediate portion 44 and gradually decreases in radius from the starting point portion 41 toward the intermediate portion 44 is provided. It is also possible to provide a connecting portion 46 between the intermediate portion 44 and the end point portion 42 so that the intermediate portion 44 and the end point portion 42 are connected and the radius gradually decreases from the intermediate portion 44 toward the end point portion 42. By providing these connection portions 45 and 46, when the rotor 20 rotates with respect to the housing 30, the vane 70 smoothly moves from the start point portion 41 along the wall surface 40 to the end point portion 42 via the intermediate portion 44. It moves and the smooth operation of the valve timing control device 1 is realized.

  In the above description, the wall surface 40 of the fluid pressure chamber R0 changes in a stepwise manner between two portions (starting point portion 41 and ending point portion 42) with respect to the rotation direction of the camshaft 10 (shown in FIG. 2). However, the present invention is not limited to this. For example, as shown in FIG. 5, a structure in which the wall surface 40 of the fluid pressure chamber R <b> 0 is tapered between the start point portion 41 and the end point portion 42 and the radius of the wall surface 40 continuously changes is also possible. . In this case, when the rotor 20 rotates with respect to the housing 30, the vane 70 moves smoothly along the wall surface 40 from the starting point portion 41 to the end point portion 42 via the connecting portion 43, and the valve opening / closing timing control device 1. Smooth operation is realized. Further, the volume of the fluid pressure chamber R0 required to rotate the rotor 20 by a unit angle can be changed more finely according to the rotational position of the rotor 20 with respect to the housing 30, and the response speed of the valve timing control device 1 can be changed. This is a more preferable structure for further improvement.

The figure which shows the structure of the valve timing control apparatus 1 which concerns on this invention (sectional drawing which follows the II line | wire in FIG. 2). II-II view in FIG. FIG. 3 is a transition diagram during operation of the valve opening / closing timing control device 1 (cross-sectional view taken along line III-III in FIG. 1). The figure which shows other embodiment of the wall surface 40 in the fluid pressure chamber R0 (sectional drawing in alignment with the III-III line in FIG. 1). The figure which shows other embodiment of the wall surface 40 in the fluid pressure chamber R0 (sectional drawing in alignment with the III-III line in FIG. 1).

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Valve opening / closing timing control apparatus 2 Rotor member 3 Housing member 10 Cam shaft 21 Vane groove (groove part)
40 walls
41 Starting Point 42 Ending Point 43 Connecting Portion 44 Intermediate Portion 45 Connecting Portion 46 Connecting Portion 70 Vane 110 Crankshaft R0 Fluid Pressure Chamber

Claims (3)

A housing member that rotates integrally with one of the crankshaft and camshaft of the internal combustion engine;
A rotor member that is assembled to the housing member so as to be rotatable relative to the housing member, and rotates integrally with the other of the camshaft and the crankshaft;
A fluid pressure chamber formed between the housing member and the rotor member;
Provided to rotate integrally with the rotor member, and is slidably contacted with the wall surface in the large diameter direction of the fluid pressure chamber and supplied to the fluid pressure chamber to rotate the rotor member relative to the housing member. A vane that slides between an initial position and an operating position by a working fluid;
In the valve timing control device comprising:
The radius of the wall surface is such that the state of the initial position is larger than the state of the operating position ,
The wall surface connects a starting point portion where the vane abuts at the initial position, an end point portion where the vane abuts at the operating position and has a radius smaller than the starting point portion, and the starting point portion and the end point portion. A valve opening / closing timing control device comprising: a connecting portion having a radius that gradually decreases from the starting portion toward the end portion . A housing member that rotates integrally with one of the crankshaft and camshaft of the internal combustion engine;
A rotor member that is assembled to the housing member so as to be rotatable relative to the housing member, and rotates integrally with the other of the camshaft and the crankshaft;
A fluid pressure chamber formed between the housing member and the rotor member;
Provided to rotate integrally with the rotor member, and is slidably contacted with the wall surface in the large diameter direction of the fluid pressure chamber and supplied to the fluid pressure chamber to rotate the rotor member relative to the housing member. A vane that slides between an initial position and an operating position by a working fluid;
In the valve timing control device comprising:
The radius of the wall surface is such that the state of the initial position is larger than the state of the operating position ,
The wall surface includes a starting point portion where the vane abuts at the initial position, an intermediate portion where the vane abuts between the initial position and the operating position, and has a smaller radius than the starting point portion, the starting point portion, and the A valve opening / closing timing control device comprising: a connecting portion connected to an intermediate portion, and having a radius that gradually decreases from the starting portion toward the intermediate portion . The rotor member, the valve timing control apparatus according to claim 1 or 2, characterized in that it comprises a groove for movably supporting the vanes in a radial direction of the wall surface.

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