JP4329675B2 - Vane rotor manufacturing method and manufacturing apparatus - Google Patents

Description

  The present invention relates to a manufacturing method and a manufacturing apparatus for manufacturing a vane rotor used in a valve timing adjustment mechanism that adjusts the opening / closing timing of at least one of an intake valve and an exhaust valve of an internal combustion engine.

  As a valve timing adjustment mechanism using a vane rotor, for example, one described in Patent Document 1 is known. The valve timing adjustment mechanism disclosed in Patent Document 1 includes a vane rotor and a shoe housing having a storage chamber that rotatably and liquid-tightly stores the vane rotor, and an advance hydraulic chamber partitioned by the vane of the vane rotor; The vane rotor is rotated relative to the shoe housing by the hydraulic pressure with the retarded hydraulic chamber.

  By inserting such a valve timing adjusting mechanism into the transmission system of the driving force from the crankshaft that is the drive shaft of the internal combustion engine to the camshaft that drives the intake valve and / or the exhaust valve, the intake valve and / or Alternatively, the opening / closing timing of the exhaust valve can be appropriately changed according to the operating conditions.

Here, in Patent Document 1, in order to reduce leakage of hydraulic oil from the hydraulic chamber and facilitate assembly, the peripheral wall and one of the side walls of the shoe housing are integrally formed by aluminum die casting. At this time, with respect to the shape material of the shoe housing formed by this aluminum die casting, the inner wall surface of one side wall of the shape material is cut with respect to the outer wall surface of the peripheral wall of the shape material. With reference to the outer wall surface of the peripheral wall of the material or the inner wall surface of one side wall of the shaped material after cutting, the inner peripheral surface of the peripheral wall of the shaped material or the open end surface on the other side wall of the shaped material is cut. In this way, the processing accuracy of the processing surface of the shoe housing, such as the inner wall of the storage chamber and the opening end surface, which affects the sealing performance between the hydraulic chambers and the sliding wear between the members, is improved.
Japanese Patent Laid-Open No. 11-117717

  In a valve timing adjustment mechanism including a shoe housing and a vane rotor, in order to prevent a poor seal between the hydraulic chambers and the like, in addition to processing the shoe housing with high accuracy, the vane rotor accommodated in the accommodation chamber is also the same. It is necessary to process with high accuracy.

  Here, the vane rotor has a boss portion and a plurality of vane portions formed integrally with the boss portion so as to rise from the outer peripheral surface of the boss portion and extend in the radial direction. In the boss portion, a hole for fixing to either the crankshaft or the camshaft is formed in the center of the boss portion by cutting. For example, the vane rotor and the camshaft are fixed by inserting a bolt into the hole and screwing the bolt into one end of the camshaft.

  The cutting process described above is performed in a state where the vane rotor is chucked by the plurality of chuck claws of the chuck device. For this reason, the vane rotor receives a pressing force from the chuck pawl during the cutting of the central hole, and thus may be deformed by the pressing force. When the vane rotor is deformed, problems such as insufficient sealing between the hydraulic chambers and uneven wear of the vane rotor and the shoe housing occur.

  The present invention has been made in view of the above-described points, and an object of the present invention is to provide a method and an apparatus for manufacturing a vane rotor capable of suppressing deformation of the vane rotor when chucking the vane rotor for cutting. To do.

In order to achieve the above-described object, the vane rotor manufacturing method according to claim 1 includes a cutting step of forming a center hole penetrating the center of the columnar boss portion of the vane rotor by cutting,
At the time of the cutting process , the vane rotor is chucked by applying a pressing force to the vane rotor by at least three or more chuck claws having a tip portion formed in a bifurcated portion, and the tip portion chuck formed in the fork portion of the chuck claws. The position is set on the outer peripheral surface of the boss part, avoiding the plurality of vane parts defined by the rising start position,
Furthermore, at least three or more chucking claw end portion is formed in bifurcated, along with contact-spaced with respect to the vane rotor, so exert a pressing force to the vane rotor at the time of abutment, in the radial direction of the boss portion It moves linearly,
When the imaginary extension line extending to the vane rotor side along the moving direction of the chuck claw is drawn from the chuck position , the extension position of the tip part formed at the fork is around the central hole in the boss part. It is set so that it may be settled in the thickness range of a cylindrical part.

  The vane section defines a pressure chamber formed in the housing in which the vane rotor is accommodated, and is formed integrally with the boss section so as to rise from the outer peripheral surface of the columnar boss section and extend in the radial direction. The When such a vane rotor is chucked by a plurality of chuck claws, if the chuck position is hung, for example, on the rising start position of the vane part, the vane part may be inclined due to the pressing force from the chuck claws for chucking the vane rotor. , May be deformed to be twisted. When such deformation of the vane portion occurs, the sealing performance when partitioning the pressure chamber in the housing becomes insufficient.

  Therefore, in the manufacturing method according to the first aspect, the chuck position is set on the outer peripheral surface of the boss portion while avoiding the plurality of vane portions defined by the rising start position. Thereby, the deformation | transformation of a vane part as mentioned above can be suppressed.

Further , in the direction in which the pressing force from the chuck claw (the tip portion formed at the fork) acts, there is not a central hole formed by cutting, but a surrounding cylindrical portion. Thereby, in the boss | hub part which receives the pressing force from a chuck | zipper claw, the intensity | strength which resists a deformation | transformation by pressing force can be raised.

The vane rotor manufacturing method according to claim 2 is characterized in that the tip portion formed at the fork of the chuck claw has an R shape, and the R-shaped portion abuts on the vane rotor for chucking. When the vane rotor is chucked by the tip of the chuck claw, the chuck claw is further moved in order to apply a predetermined pressing force to the boss even after the tip contacts the boss. At this time, if the frictional resistance between the tip end portion of the chuck claw and the outer peripheral surface of the boss portion is large, the tip end portion of the chuck claw may be caught on the outer peripheral surface of the boss portion, and the boss portion may be deformed. In the manufacturing method according to claim 2 , since the tip of the chuck claw has an R shape in order to reduce the frictional resistance between the tip of the chuck claw and the outer peripheral surface of the boss, the tip of the chuck claw has an outer periphery of the boss. It becomes easy to slip on the surface, and deformation of the boss portion can be suppressed during chucking by the chuck claw.

Claims 3 to 4 relate to a manufacturing apparatus for manufacturing a vane rotor by the above-described method for manufacturing a vane rotor, and the operation and effect thereof are as described above, and thus the description thereof is omitted.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of a vane rotor manufacturing method and manufacturing apparatus according to the present invention will be described with reference to the drawings.

  First, a valve timing adjusting mechanism using a vane rotor to which the manufacturing method according to the present embodiment is applied will be described with reference to FIGS. 1 and 2. 1 and 2 are cross-sectional views of a valve timing adjusting mechanism whose cross section is a plane orthogonal to each other.

  A timing gear 1 shown in FIG. 1 has a gear train, and a driving force is transmitted from a crankshaft as a drive shaft of an engine (not shown) via a timing belt meshing with the gear train, and rotates in synchronization with the crankshaft. The camshaft 2 as a driven shaft receives driving force from the timing gear 1 and opens / closes at least one of an intake valve and an exhaust valve (not shown). The camshaft 2 can be rotated with a predetermined phase difference with respect to the timing gear 1 by a valve timing adjusting mechanism described below. The timing gear 1 and the camshaft 2 rotate clockwise as viewed from the direction of the arrow X shown in FIG. Hereinafter, this rotational direction is referred to as an advance direction.

  The timing gear 1 and the shoe housing 3 constitute a housing member as a driving side rotating body, and are fixed coaxially by a bolt 20. The shoe housing 3 is integrally formed with a peripheral wall 4 and a front plate 5 as one side wall. Note that the timing gear 1 constitutes the other side wall of the housing member.

  As shown in FIG. 2, the shoe housing 3 has shoes 3a, 3b, 3c formed in a trapezoidal shape at substantially equal intervals in the circumferential direction. Fan-like space portions 40 as storage chambers for storing the vanes 9a, 9b, 9c as the vane members are formed in the three gaps in the circumferential direction of the shoes 3a, 3b, 3c, respectively. The inner peripheral surface is formed in a circular arc shape in cross section. That is, as shown in FIG. 2, the vane rotor 9 has vanes 9a, 9b, 9c at substantially equal intervals in the circumferential direction, and these vanes 9a, 9b, 9c are rotatably accommodated in the above-described fan-shaped space. The

  As shown in FIG. 1, the vane rotor 9 and the bush 6 are integrally fixed to the camshaft 2 by bolts 21 to form a driven side rotating body. The bush 6 fixed integrally with the vane rotor 9 is fitted to the inner peripheral wall of the front plate 5 so as to be relatively rotatable. Further, a minute clearance is provided between the outer peripheral wall of the vane rotor 9 and the inner peripheral wall of the shoe housing 3, and the vane rotor 9 can rotate relative to the shoe housing 3. Seal members 16 urged by springs 17 are fitted to the outer peripheral walls of the vanes 9a, 9b, 9c and the outer peripheral wall of the boss portion 9d of the vane rotor 9, respectively, to prevent leakage of hydraulic oil between the hydraulic chambers. It is preventing.

  A retard hydraulic chamber 10 is formed between the shoe 3a and the vane 9a, a retard hydraulic chamber 11 is formed between the shoe 3b and the vane 9b, and a retard hydraulic chamber 12 is formed between the shoe 3c and the vane 9c. Is formed. Further, an advance hydraulic chamber 13 is formed between the shoe 3a and the vane 9b, an advance hydraulic chamber 14 is formed between the shoe 3b and the vane 9c, and an advance hydraulic chamber is formed between the shoe 3c and the vane 9a. A chamber 15 is formed.

  With the above configuration, the camshaft 2 and the vane rotor 9 can rotate relative to the timing gear 1 and the shoe housing 3 coaxially.

  As shown in FIGS. 1 and 2, the guide ring 19 is press-fitted and held on the inner wall of the vane 9 a that forms the accommodation hole 23, and the stopper piston 7 is inserted into the guide ring 19. Accordingly, the stopper piston 7 is accommodated in the vane 9 a so as to be slidable in the axial direction of the camshaft 2, and is biased toward the front plate 5 by the spring 8. The stopper piston 7 can be fitted into a stopper hole 22 formed in the front plate 5 by the urging force of the spring 8. Since the communication passage 24 formed in the timing gear 1 communicates with the accommodation hole 23 on the right side of the flange portion 7a and is released to the atmosphere, the movement of the stopper piston 7 is not hindered.

  The hydraulic chamber 37 on the left side of the flange portion 7a communicates with the retarded hydraulic chamber 10 via an oil passage (not shown). When hydraulic oil is supplied to the retarded hydraulic chamber 10, the stopper piston 7 comes out of the stopper hole 22 against the urging force of the spring 8. The hydraulic chamber 38 formed at the tip of the stopper piston 7 communicates with the advance hydraulic chamber 15 through an oil passage 39 shown in FIG. Therefore, when hydraulic oil is supplied to the advance hydraulic chamber 15, the stopper piston 7 comes out of the stopper hole 22 against the urging force of the spring 8.

  The positions of the stopper piston 7 and the stopper hole 22 are determined when the camshaft 2 is at the most retarded position with respect to the crankshaft, that is, when the vane rotor 9 is at the most retarded position with respect to the shoe housing 3. The piston 7 is set so as to fit into the stopper hole 22. The stopper piston 7 and the stopper hole 22 constitute a lock mechanism.

  As shown in FIGS. 1 and 2, the boss portion 9 d of the vane rotor 9 is provided with an oil passage 29 at a contact portion with the bush 6, and an oil passage 33 is provided at a contact portion with the camshaft 2. ing. The oil passages 29 and 33 are each formed in an arc shape. The oil passage 29 communicates with a hydraulic source or drain as driving means (not shown) via the oil passages 25 and 27. Furthermore, the oil passage 29 communicates with the retarded hydraulic chambers 10, 11, 12 through the oil passages 30, 31, 32, and communicates with the hydraulic chamber 37 through an oil passage (not shown).

  The oil passage 33 communicates with a hydraulic pressure source or drain as driving means (not shown) via the oil passage 26 and the oil passage 28. Further, the oil passage 33 communicates with the advance hydraulic chambers 13, 14, and 15 through oil passages 34, 35, and 36, and communicates with the hydraulic chamber 38 through the advance hydraulic chamber 15 and the oil passage 39.

  Next, the operation of the valve timing adjustment mechanism having the above-described configuration will be described. During normal operation of the engine, the stopper piston 7 has come out of the stopper hole 22 due to the hydraulic pressure of the hydraulic oil supplied to the retarded hydraulic chambers 10, 11, 12 and the advanced hydraulic chambers 13, 14, 15. On the other hand, the vane rotor 9 is relatively rotatable. Therefore, the phase difference of the camshaft 2 with respect to the crankshaft can be adjusted by controlling the hydraulic pressure applied to each hydraulic chamber.

  When the engine is stopped, the hydraulic oil is not supplied to the retarded hydraulic chambers 10, 11, 12, and the advanced hydraulic chambers 13, 14, 15, so that the vane rotor 9 is at the most retarded position shown in FIG. Stop. Since hydraulic oil is not supplied to the hydraulic chambers 37 and 38, the stopper piston 7 is fitted into the stopper hole 22 by the urging force of the spring 8.

  Even when the engine is restarted, the stopper piston 7 remains fitted in the stopper hole 22 until hydraulic oil is supplied to the retarded hydraulic chambers 10, 11, 12, and the advanced hydraulic chambers 13, 14, 15. The camshaft 2 is held at the most retarded position with respect to the crankshaft. As a result, the vane rotor 9 is locked to the front plate 5 until the hydraulic oil is supplied to each hydraulic chamber, so that the shoe housing 3 and the vane rotor 9 can be prevented from colliding with each other due to the fluctuation torque of the cam.

  Next, the manufacturing method and manufacturing apparatus of the vane rotor 9 used for the valve timing adjusting mechanism will be described. The shoe housing 3 is manufactured by a known manufacturing method as described in, for example, Japanese Patent Application Laid-Open No. 11-117717, and thus will not be particularly described.

  As shown in FIGS. 1 and 2, the vane rotor 9 includes a substantially cylindrical boss portion 9d and a plurality of boss portions 9d formed integrally with the boss portion 9d so as to rise from the outer peripheral surface and extend in the radial direction. And vanes 9a, 9b, 9c. The vane rotor 9 is formed by forming, for example, an aluminum die-cast material having shapes corresponding to the vanes 9a, 9b, 9c and the boss portion 9d, and an oil passage, a bolt hole, and the like are formed on the material. For example, it is manufactured by performing a cutting process. In addition to aluminum, the metal material of the vane rotor 9 can be iron, for example.

  When the base material is cut, the vane rotor 9 is chucked and fixed. A chuck device 50 for chucking the vane rotor 9 will be described with reference to FIGS. 3 and 4.

  As shown in FIGS. 3 and 4, the chuck device 50 includes three chuck claws 51, 52, and 53 that are arranged at approximately equal intervals around the vane rotor 9. At the tip of each chuck claw 51, 52, 53, two protrusions 51a, 51b divided into two are formed. These protrusions 51a and 51b abut against the boss 9b of the vane rotor 9 and press the outer surface thereof, whereby the vane rotor 9 is firmly held. Each of the chuck claws 51, 52, 53 can be made of, for example, chrome molybdenum steel and is preferably subjected to carburizing and quenching in order to improve wear resistance.

  The chuck device 50 includes a drive unit for each chuck claw 51, 52, 53 in order to bring the chuck claws 51, 52, 53 into contact with or away from the vane rotor 9d. This drive unit will be described with reference to FIG. 4 shows only the boss portion 9d as a work and only the chuck claw 51 as a chuck claw for easy understanding.

  The chuck claw 51 is fixed to the movable portion 54. The movable portion 54 has a built-in drive source such as a motor and moves linearly on the rail 55 using the drive force of the drive source. However, the drive source for moving the movable part 54 may be provided outside the movable part 54. Further, the chuck device 50 includes a pedestal 56 for temporarily fixing the vane rotor 9.

  When the vane rotor 9 is chucked by the chuck device 50, the chuck claws 51, 52, 53 are retracted to the separation positions away from the vane rotor 9, and the vane rotor 9 is temporarily fixed on the pedestal 56. After the vane rotor 9 is temporarily fixed, the protrusions 51a and 51b formed at the tips of the chuck claws 51, 52, and 53 are moved by the drive unit so as to contact the boss 9d of the vane rotor 9. After that, the drive unit generates a drive force so that each chuck claw 51, 52, 53 applies a predetermined pressing force to the boss portion 9d.

  When the vane rotor 9 is chucked by the chuck device 50 in this way, the end mill 60 (cutting machine) causes the bolt hole, the oil passage, and the seating surface that receives the bush 6 to the boss portion 9d by cutting. It is formed.

  Here, since the machining accuracy of the bolt holes and the seating surface greatly affects the sealing performance of each hydraulic chamber, the chuck device 50 holds the vane rotor 9 at a fixed position during the cutting by the end mill 60. There is a need. Therefore, when the vane rotor 9 is chucked by the chuck device 50, the vane rotor 9 receives a considerable pressing force from the protrusions 51a and 51b of the chuck claws 51, 52, and 53.

  In the present embodiment, the vane rotor 9 can be prevented from being deformed while receiving a pressing force from the projections 51a and 51b of the chuck claws 51, 52, and 53. For this purpose, first, as shown in FIG. 5, the chuck positions of the protrusions 51a, 51b formed at the tips of the chuck claws 51, 52, 53 are more than the rising start positions of the vanes 9a, 9b, 9c. The outer peripheral surface side was set. That is, the chuck position is set so as to be positioned on the outer peripheral surface of the boss portion 9d, avoiding the vanes 9a, 9b, and 9c defined by the rising start position.

  As shown in FIG. 2, when the oil passages 30 to 32 and 34 to 36 are formed in the vicinity of the rising start positions of the vanes 9a, 9b and 9c, the boss portion 9 is also avoided so as to avoid the oil passage formation positions. The chuck position is set by shifting in the circumferential direction or the axial direction.

  When the chuck position by the projections 51a, 51b formed at the tips of the chuck claws 51, 52, 53 is suspended from the rising position of the vanes 9a, 9b, 9c, the pressing force from the projections 51a, 51b is applied to the vanes 9Aa, 9b. , 9c may be applied unevenly to only a part or one side of the root. As a result, the vanes 9a, 9b, and 9c may be slightly deformed so as to be inclined or twisted. When such deformation of the vanes 9a, 9b, and 9c occurs, the sealing performance by the vanes 9a, 9b, and 9c becomes insufficient, such as leakage of hydraulic oil between the pressure chambers.

  Therefore, in order to suppress deformation of the vanes 9a, 9b, 9c when the vane rotor 9 is chucked, the chuck positions by the protrusions 51a, 51b of the chuck claws 51, 52, 53 are set to the vanes 9a, 9b, 9c as described above. This is set on the outer peripheral surface of the boss portion 9d.

  Further, as shown in FIG. 6, the chuck position by the projections 51 a and 51 b is obtained by drawing a virtual extension line extending from the chuck position along the movement direction of each chuck claw 51, 52 and 53. The extension line is set so as to be as much as possible within the thickness range of the cylindrical portion around the bolt hole formed at the center of the boss portion 9d.

  As a result, in the direction in which the pressing force from the protrusions 51a and 51b of the chuck claws 51, 52, and 53 acts, there is a cylindrical portion around the bolt hole formed by cutting. . Thereby, in the boss portion 9d that receives the pressing force from the protrusions 51a and 51b, the strength against the deformation due to the pressing force can be increased.

  In order to establish the above relationship for all chuck positions, as shown in FIG. 6, the distance between the protrusions 51a and 51b of the chuck claws 51, 52 and 53, that is, the width of the chuck claws 51, 52 and 53 is set. The radius may be set to be twice or more the radius R1 of the hole formed in the center of the boss portion 9d. However, since the vanes 9a, 9b, and 9c are located between the adjacent chuck claws 51, 52, and 53, the larger the difference between the inner diameter R1 and the outer diameter R2 of the boss portion 9d, the more the vanes 9a, 9b, and 9c are avoided. However, it becomes easy to satisfy the above-described relationship for all chuck positions.

  Note that the relationship that the extension line from the chuck position falls within the thickness range of the cylindrical portion does not have to be established for all chuck positions. If the above-described relationship is established for at least a part of the six chuck positions formed by the two protrusions formed at the tips of the three chuck claws 51, 52, and 53, respectively, This is because the deformation of the boss portion 9d is suppressed.

  Further, in order to suppress the deformation of the boss portion 9d, the protrusions 51a and 51b of the chuck claws 51, 52, and 53 have an R-shaped contact surface that contacts the boss portion 9d as shown in FIG. Is formed.

  When the boss portion 9d of the vane rotor 9 is chucked by the protrusions 51a and 51b of the chuck claws 51, 52 and 53, the protrusions 51a and 51b are brought into contact with the outer peripheral surface of the boss portion 9d, On the other hand, in order to apply a predetermined pressing force, a driving force for moving the chuck claws 51, 52, 53 is further applied. At this time, if the frictional resistance between the protrusions 51a, 51b of the chuck claws 51, 52, 53 and the outer peripheral surface of the boss part 9d is large, the protrusions 51a, 51b of the chuck claws 51, 52, 53 become the boss part 9d. There is a possibility that excessive stress concentrates and the boss portion 9d is deformed.

  Therefore, in order to reduce the frictional resistance between the protrusions 51a and 51b of the chuck claws 51, 52 and 53 and the outer peripheral surface of the boss 9d, the shape of the contact surface of the protrusions 51a and 51b of the chuck claws 51, 52 and 53 is reduced. The R shape. For this reason, the protrusions 51a and 51b of the chuck claws 51, 52, and 53 can easily slide on the outer peripheral surface of the boss portion 9d, and deformation of the boss portion 9d can be suppressed during chucking by the chuck claws 51, 52, and 53. .

  The preferred embodiments of the present invention have been described above, but the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention. .

  For example, in the above-described embodiment, the example in which the vane rotor 9 that is the workpiece is chucked using the three chuck claws 51, 52, and 53 has been described, but the number of chuck claws may be four or more.

  In the above-described embodiment, the vane rotor 9 includes the three vanes 9a, 9b, and 9c. However, the number of vanes may be two or four or more.

  In the above-described embodiment, the chuck claws 51, 52, 53 are arranged between the adjacent vanes 9a, 9b, 9c. For example, by increasing the length of the two protrusions, A part or all of the chuck claws may be arranged so that the vanes are accommodated in the space between the protrusions.

  In the above-described embodiment, the vane rotor 9 and the camshaft 2 are fixed by forming a hole for inserting the bolt 21 in the center of the boss portion 9d and screwing the bolt 21 into the tip of the camshaft 2. . However, as disclosed in, for example, Japanese Patent Application Laid-Open No. 2002-295209, a camshaft can be inserted into the boss portion of the vane rotor, and a nut is fastened to the tip of the camshaft inserted through the hole. The shaft and the vane rotor may be fixed.

  In the above-described embodiment, the shoe housing 3 rotates with the crankshaft, and the vane rotor 9 rotates with the camshaft 2. However, the vane rotor may rotate with the crankshaft, and the shoe housing may rotate with the camshaft.

  Furthermore, in the above-described embodiment, the boss portion has a substantially cylindrical shape having a hole in the center portion. However, the outer shape is not limited to a circle and may be a polygon.

It is sectional drawing of the valve timing adjustment mechanism using a vane rotor. It is sectional drawing of the valve timing adjustment mechanism which makes a cross section the plane orthogonal to the cross section in FIG. It is explanatory drawing which shows the positional relationship of the chuck | zipper claw of a chuck | zipper apparatus, and the vane rotor which is a workpiece | work. It is explanatory drawing for demonstrating a structure and action | operation of a chuck | zipper apparatus. It is explanatory drawing for demonstrating the chuck | zipper position when the projection part formed in the front-end | tip of each chuck | zipper claw avoids a vane and chucks the outer peripheral surface of a boss | hub part. Chuck position of each chuck claw protrusion when setting the chuck position so that the direction along the moving direction of the chuck claw from the chuck position is within the thickness range of the cylindrical part around the central hole in the boss part It is explanatory drawing which shows. It is explanatory drawing which shows the shape of protrusion part 51a, 51b of each chuck | zipper claw 51,52,53.

Explanation of symbols

9 Vane rotor 9a, 9b, 9c Vane 9d Boss part 50 Chuck device 51, 52, 53 Chuck claw 51a, 51b Protrusion part 60 End mill

Claims (4)

Provided in a driving force transmission system that transmits a driving force from a driving shaft of the internal combustion engine to a driven shaft that opens and closes at least one of an intake valve and an exhaust valve of the internal combustion engine, and the driven shaft is rotated with respect to the rotation of the driving shaft. A manufacturing method for manufacturing a vane rotor used in a valve timing adjustment mechanism that causes a phase difference in rotation of a shaft,
The vane rotor has a columnar boss portion, and a plurality of vane portions formed integrally with the boss portion so as to stand up from the outer peripheral surface of the boss portion and extend in the radial direction.
A cutting step of forming a central hole penetrating the center of the columnar boss portion by cutting,
At the time of the cutting process , the vane rotor is chucked by applying a pressing force to the vane rotor by at least three chuck claws each having a bifurcated tip portion, and the tip portions formed on the bifurcated portions of the chuck claws. The chuck position is set on the outer peripheral surface of the boss part, avoiding the plurality of vane parts defined by the rising start position,
Furthermore, at least three chuck claws said distal end portion is formed in the bifurcated, along with contact-spaced with respect to the vane rotor, so as to exert a pressing force to the vane rotor at the time of contact, of the boss portion It moves linearly in the radial direction, and the chuck position of the tip portion formed at the bifurcated portion is drawn with a virtual extension line extending from the chuck position to the vane rotor side along the movement direction of the chuck pawl. In this case, the extension line is set so as to be within the thickness range of the cylindrical portion around the central hole in the boss portion.   2. The method of manufacturing a vane rotor according to claim 1, wherein a tip end portion formed at a fork of the chuck claw has an R shape, and the R shape portion abuts on the vane rotor for chucking. Provided in a driving force transmission system that transmits a driving force from a driving shaft of the internal combustion engine to a driven shaft that opens and closes at least one of an intake valve and an exhaust valve of the internal combustion engine, and the driven shaft is rotated with respect to the rotation of the driving shaft. A manufacturing apparatus for manufacturing a vane rotor used in a valve timing adjusting mechanism that causes a phase difference in rotation of a shaft,
The vane rotor has a columnar boss portion, and a plurality of vane portions formed integrally with the boss portion so as to stand up from the outer peripheral surface of the boss portion and extend in the radial direction.
It has at least three or more chuck claws formed at the tip of the fork, and the chuck position of the tip formed at the fork of the chuck claws avoids the plurality of vanes defined by the rising start position. A chuck device set on the outer peripheral surface of the boss portion;
A cutting device that applies a pressing force to the vane rotor by a chuck claw of the chuck device, and forms a central hole through the center of the columnar boss portion by cutting in a state where the vane rotor is chucked. Prepared,
At least three chuck claws said distal end portion is formed in the bifurcated, along with contact-spaced with respect to the vane rotor, so as to exert a pressing force to the vane rotor at the time of contact, a radial direction of the boss portion be one which moves linearly in the chuck position of the tip portion formed in the bifurcated, if from the chuck position minus the extension of the virtual extending vane rotor side along the moving direction of the chuck jaws The vane rotor manufacturing apparatus, wherein the extension line is set to fall within a thickness range of a cylindrical portion around the central hole in the boss portion.   The vane rotor manufacturing apparatus according to claim 3, wherein a tip end portion formed at a fork of the chuck claw has an R shape, and the R shape portion abuts on the vane rotor for chucking.

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