WO2017159121A1

WO2017159121A1 - Valve timing control device for internal combustion engine and method for attaching valve timing control device

Info

Publication number: WO2017159121A1
Application number: PCT/JP2017/004329
Authority: WO
Inventors: 邦長初谷; 佐藤　健治; 厳典市野澤
Original assignee: 日立オートモティブシステムズ株式会社
Priority date: 2016-03-15
Filing date: 2017-02-07
Publication date: 2017-09-21
Also published as: CN108603422B; JPWO2017159121A1; CN108603422A; JP6685382B2; US20190085735A1

Abstract

The present invention is provided with: a housing 7 to which a rotational force is transmitted from a crankshaft; a vane rotor 8 which is provided inside the housing and has a cylindrical rotor 20 that is fastened and fixed to a camshaft 2 by a cam bolt 5; and a groove part 47 which is provided on a leading surface of a cylindrical part 23 of the rotor and has one lateral surface 47a located opposite to a fastening direction of the cam bolt. The lateral surface is formed so as to be inclined on the side opposite to the fastening direction of the cam bolt when compared to a first virtual plane S1 formed by connecting a rotary shaft center O of the vane rotor and an edge 47d of the lateral surface on the inner periphery side of the rotor. Accordingly, rotation of the vane rotor generated when fastening the vane rotor to the camshaft by the cam bolt can be arrested, while deformation due to the inhibition of rotation can also be reduced.

Description

Valve timing control device for internal combustion engine and method for mounting the valve timing control device

The present invention relates to a valve timing control device for an internal combustion engine that variably controls the opening and closing timing of an intake valve and an exhaust valve according to the engine operating state, and a method for mounting the valve timing control device.

As a conventional valve timing control device for an internal combustion engine, one described in Patent Document 1 below is known.

This valve timing control device includes a cylindrical housing to which a rotational force is transmitted from a crankshaft, and a vane rotor having a cylindrical rotor provided inside the housing and bolted to the camshaft by a cam bolt. ing.
And the opening / closing timing (valve timing) of the intake valve or the exhaust valve is variably controlled by changing the relative rotational phase of the vane rotor with respect to the housing.

Also, the valve timing control device has a plurality of rectangular grooves formed on the inner peripheral wall on the opposite side of the rotor camshaft. Each of the grooves is formed so that a protrusion of a holding tool that restricts the rotation of the rotor can be engaged when fastening the bolt, and each contact surface that contacts the protrusion is substantially in the radial direction of the rotor. It is formed in a planar shape along.

Even when the rotor tries to rotate in the bolt fastening direction by slidingly contacting the head of the cam bolt when the bolt is tightened, the rotational force at the time of the rotation is engaged in each groove portion. Since it is restrained by the projections of the holding tool, the rotation is restrained.

JP 10-317923 A

However, as described above, in the rotor, the rotational force generated at the time of bolt tightening is suppressed by each protrusion of the holding tool, while the rotation force is equivalent to the rotation force from each protrusion to the contact surface of each groove. Reaction force will act. This reaction force acts perpendicularly to each contact surface, and there is a possibility that the vane rotor is pushed outward by the reaction force and deformed in diameter.

The present invention has been devised in view of the above-described conventional technical problems, and suppresses the deformation associated with the rotation suppression while suppressing the rotation of the vane rotor when the vane rotor is bolted to the camshaft. It is an object of the present invention to provide an obtained valve timing control device and a mounting method of the valve timing control device.

The present invention includes a housing to which rotational force is transmitted from a crankshaft, a vane rotor provided inside the housing and having a cylindrical rotor fastened and fixed to the camshaft by cam bolts, and the rotor opposite to the camshaft. And a groove portion having one side surface opposite to the fastening direction of the cam bolt, and the one side surface is a rotation axis of the vane rotor and an inner circumferential end of the one side of the rotor. An end edge on the outer peripheral side of the one side surface is opposite to a fastening direction side of the cam bolt from a virtual surface formed by connecting the edge.

According to the present invention, it is possible to suppress deformation due to the rotation suppression while suppressing the rotation of the vane rotor when the vane rotor is bolted to the camshaft.

FIG. 5 is an overall configuration diagram showing the valve timing control device according to the first embodiment of the present invention, taken along line AA in FIG. 4. It is a disassembled perspective view of the valve timing control device. It is a perspective view of the valve timing control device. It is a front view of the valve timing control device showing the state in which the valve timing is controlled to the retard side, with the front plate removed. It is a front view of the valve timing control device showing the state in which the valve timing is controlled to the advance side, with the front plate removed. It is an enlarged view of the support line B part of FIG. It is a front view of the valve timing control device. It is a principal part enlarged view which shows the groove part of the vane rotor which concerns on this embodiment. It is a figure which shows the holding tool used when a valve timing control apparatus is assembled | attached to a cam shaft, Comprising: (A) is a front view of a holding tool, (B) is a side view of a holding tool. It is a figure which shows the 1st process at the time of attaching a valve timing control apparatus to a camshaft. It is a figure which shows the 2nd process and 3rd process at the time of attaching a valve timing control apparatus to a camshaft. It is the schematic which shows the rotational force which arises between a vane rotor and a holding tool in a 3rd process, and the reaction force of this rotational force with a vector. It is a principal part enlarged view which shows the groove part of the valve timing control apparatus which concerns on 2nd Embodiment of this invention.

Hereinafter, embodiments of a valve timing control device for an internal combustion engine according to the present invention will be described in detail with reference to the drawings. In each embodiment, the valve timing control device is applied to the intake valve side of the internal combustion engine.
[First Embodiment]
As shown in FIG. 1, the valve timing control device according to the present embodiment is provided so as to be rotatable relative to the sprocket 1 and a sprocket 1 that is rotationally driven via a timing chain by a crankshaft (not shown). A camshaft 2, a phase conversion mechanism 3 disposed between the sprocket 1 and the camshaft 2 for converting the relative rotational phases of the two 1 and 2, and the phase conversion mechanism 3 operated based on hydraulic supply / discharge. And a hydraulic circuit 4 to be operated.

The sprocket 1 is integrally formed with a housing body 11 to be described later, and integrally has a plurality of gear portions 1a around which the timing chain is wound.

The camshaft 2 is rotatably supported by a cylinder head (not shown) via a cam bearing, and opens an intake valve (not shown) against a spring force of a valve spring at a predetermined axial position on the outer peripheral surface. A plurality of drive cams having a cam profile of the shape are integrally provided, and a bolt hole 6 into which the cam bolt 5 is inserted and screwed is formed in the inner axial direction of the one end portion 2a.

The cam bolt 5 is formed on a hexagonal head portion 5a, a shaft portion 5c integrally provided at one end portion of the head portion 5a via a flange-shaped seat portion 5b, and an outer periphery of a tip portion of the shaft portion 5c. In the mounting operation process of the valve timing control device to be described later, the screw hole 5d is screwed into the bolt hole 6 by rotating in the clockwise direction in FIG. 7 (hereinafter referred to as the bolt fastening direction D). It comes to wear.

The bolt hole 6 is formed with a female screw part 6a into which the male screw part 5d of the cam bolt 5 is screwed on the bottom side, and a part on the opening side of the female screw part 6a is larger than the outer diameter of the shaft part 5c. An annular oil passage 27c, which is a part of a retarding passage 27 described later, is formed between the inner peripheral surface of the bolt hole 6 and the outer peripheral surface of the shaft portion 5c.

As shown in FIGS. 1 to 4, the phase conversion mechanism 3 is disposed on the one end 2a side of the camshaft 2, and is fixed to the housing 7 having an operation chamber therein and the one end 2a of the camshaft 2, A vane rotor 8 housed in a housing 7 so as to be relatively rotatable, four first to fourth shoes 15a to 15d integrally having the working chamber on an inner peripheral surface of a housing body 11 (to be described later) of the housing 7 and the vane rotor 8 There are provided four retard hydraulic chambers 9 which are partitioned by four vanes 21a to 21d, which will be described later, and an advanced hydraulic chamber 10 which is an advanced hydraulic chamber.

The housing 7 includes a substantially cylindrical housing body 11 having both axial ends open, a front plate 12 that closes the front end opening of the housing body 11, and a rear plate 13 that closes the rear end opening of the housing body 11. It is equipped with. The housing body 11, the front plate 12, and the rear plate 13 are fastened together by four bolts 14 penetrating through bolt insertion holes 16 and the like, which will be described later, and are integrally coupled.

The housing body 11 is integrally formed of a sintered metal material, and the sprocket 1 is integrally provided at a substantially central position in the axial direction of the outer periphery, and the four main bodies 11 are disposed at substantially equal intervals in the circumferential direction of the inner peripheral surface. First to fourth shoes 15a to 15d are integrally projected inward.

Each of these shoes 15a to 15d is formed in a substantially trapezoidal shape when viewed from the front, and is formed with a bolt insertion hole 16 through which each bolt 14 is inserted along the direction of the internal axis. Each of the shoes 15a to 15d has a seal groove formed at the tip portion along the axial direction of the housing body 11, and is substantially in sliding contact with the outer peripheral surface of the rotor 20 described later in each seal groove. A U-shaped sealing member 17 is accommodated.

Further, a positioning groove 11a having a U-shaped cross section is formed along the axial direction on the outer peripheral surface of the housing body 11 to be used for positioning the housing body 11 and the rear plate 13 in the circumferential direction.

The front plate 12 is formed in a disk shape by press-molding a metal plate, and a comparatively large-diameter through-hole 12a through which a cylindrical portion 23 of the rotor 20 described later is inserted with a predetermined gap is formed at the center position. .

Further, the front plate 12 is formed with four bolt holes 12b through which the respective bolts 14 are inserted at circumferentially equidistant positions on the outer peripheral side. A circular seating surface 12d on which the head portion 14a of each bolt 14 is seated is recessed in the vicinity of the hole edge on the outer end surface 12c side of each bolt hole 12b. As a result, when the housing 7 is fastened by the bolts 14, the heads 14a do not protrude forward from the outer end surface 12c.

Further, as shown in FIGS. 1 to 3, a pin 18 with an umbrella is press-fitted and fixed from the axial direction on the outer peripheral side of the outer end surface 12c of the front plate 12.

The pin 18 with an umbrella includes a pin main body 18a formed in a substantially columnar shape, and a disk-shaped umbrella portion 18b integrally provided at an end of the pin main body 18a opposite to the press-fitting side. Yes.

The pin main body 18a is configured to lock the second locking end 45c by winding a second locking end 45c of a spiral spring 45 described later on the outer peripheral surface.

The umbrella portion 18b has a diameter that covers almost the entire axial end surface of the second locking end portion 45c wound around the pin body 18a, whereby the second locking end portion 45c of the spiral spring 45 is provided. Is prevented from dropping from the pin body 18a to the front of the device.

As shown in FIGS. 1 and 2, the rear plate 13 is formed of a sintered metal material, and a support hole 13 a that rotatably supports the one end 2 a of the camshaft 2 is formed through the center. Four female screw holes 13b into which male screw parts 14c formed on the outer peripheral surface of the tip part of the shaft part 14b of each bolt 14 are screwed are formed at circumferentially equidistant positions on the outer peripheral side.

Further, as shown in FIG. 2, a columnar positioning that positions the housing main body 11 and the rear plate 13 in the rotational direction by engaging with the positioning groove 11 a of the housing main body 11 on the outer peripheral portion of the rear plate 13. The pin 19 is press-fitted and fixed.

The vane rotor 8 is integrally formed of, for example, a sintered metal material, and, as shown in FIGS. 1 to 4, a cylindrical rotor 20 fixed to the camshaft 2 by a cam bolt 5 and a circle on the outer peripheral surface of the rotor 20. It is mainly composed of four first to fourth vanes 21a to 21d protruding radially at substantially equal intervals in the circumferential direction.

As shown in FIG. 1, the rotor 20 has a bolt hole 20 a through which the shaft portion 5 c of the cam bolt 5 is inserted at a substantially central position. An annular passage 27d, which is a part of a retarding passage 27 described later, is partitioned between the inner peripheral surface of the rotor 20 and the outer peripheral surface of the shaft portion 5c.

Further, the rotor 20 has a circular seating surface 20c in which the seat 5b of the cam bolt 5 is seated at the center of the front end surface 20b on the front plate 12 side.

Furthermore, a circular concave fitting hole 20d is formed at the center of the rear end surface of the rotor 20 on the rear plate 13 side. The fitting hole 20d has an inner diameter that is slightly larger than the outer diameter of the tip of the one end portion 2a of the camshaft 2, and can be fitted to the one end portion 2a.

Also, as shown in FIG. 10, a pin hole 20e having a circular cross section is formed at a predetermined position on the outer peripheral side of the bottom surface of the fitting hole 20d. In addition, one end of a cylindrical pin member 22 is inserted and disposed in the pin hole 20e. The pin member 22 is interposed between the pin hole 20e and the pin groove 2b formed in the outer peripheral portion of the tip end surface 2a of the camshaft 2, so that the relative rotational position of the rotor 20 with respect to the camshaft 2 is achieved. Is to be positioned.

Furthermore, as shown in FIGS. 1 to 3, a cylindrical portion 23, which is an extending portion extending along the axial direction of the rotor 20, is projected from the front end surface 20 b of the rotor 20.

The cylindrical portion 23 is integrally formed with the rotor 20 by sintering and is formed in a substantially cylindrical shape having the same axis as the rotor 20. Further, the cylindrical portion 23 protrudes to the outside of the housing 7 through the through hole 12a of the front plate 12 so that the head portion 5a of the cam bolt 5 is accommodated therein.

Further, the cylindrical portion 23 is provided with a locking groove 24 which is a locking portion for locking a first locking end 45b of a spiral spring 45 described later. As shown in FIGS. 2 to 4, the locking groove 24 is formed in a rectangular shape extending in the axial direction from the distal end surface to the proximal end side at a predetermined position in the circumferential direction of the cylindrical portion 23. The locking groove 24 has a side surface 24a on the side where the first locking end 45b is locked, of a pair of opposing side surfaces facing each other along the circumferential direction of the cylindrical portion 23, and is formed in an arcuate shape. ing.

Furthermore, an annular groove 25 having a rectangular cross section is formed over substantially the entire circumferential direction at a substantially central position in the axial direction of the outer peripheral surface of the cylindrical portion 23. The annular groove 25 accommodates and holds a part of the inner peripheral side of the spiral spring 45 therein, thereby preventing the inner peripheral side of the spiral spring 45 from dropping from the apparatus.

As shown in FIGS. 2 and 4, each of the first to fourth vanes 21a to 21d is disposed between the shoes 15a to 15d, and in the seal groove formed on each arcuate outer peripheral surface. In addition, a substantially U-shaped seal member 26 slidably contacting the inner peripheral surface of the housing body 11 is accommodated.

In each vane 21a to 21d, the first vane 21a is formed with the maximum width, and the other three second to fourth vanes 21b to 21d are formed with the same width smaller than the first vane 21a. .

When the vane rotor 8 rotates in the maximum counterclockwise direction shown in FIG. 4, the first vane 21 a is in contact with the opposite side surface of the first shoe 15 a and the relative rotational position on the maximum retard angle side with respect to the housing 7 is restricted. Has been. When the vane rotor 8 rotates in the maximum clockwise direction shown in FIG. 4, the first vane 21 a comes into contact with the opposite side surface of the second shoe 15 b so that the relative rotation position on the maximum advance angle side is regulated. It has become.

The other vanes 21b to 21d other than the first vane 21a may be any shoe facing in the circumferential direction even when the first vane 21a is in contact with the first and

second shoes

15a and 15b. No contact with 15a to 15d. As a result, the contact accuracy between the first vane 21a and the first and

second shoes

15a, 15b is improved, and the supply speed of the hydraulic pressure to each of the retard and advance

hydraulic chambers

9 and 10 is increased, thereby causing the vane rotor 8 to move. The rotational responsiveness in the forward / reverse direction becomes higher.

Each retard hydraulic chamber 9 and each advance hydraulic chamber 10 communicate with the hydraulic circuit 4 via a retard communication hole 9a and an advance communication hole 10a formed in the rotor 20 along the radial direction. is doing.

The hydraulic circuit 4 supplies hydraulic oil to the retard and advance

hydraulic chambers

9 and 10, discharges the hydraulic oil in the retard and advance

hydraulic chambers

9 and 10, and the retard and advance hydraulic chambers. As shown in FIG. 1, each of the retarding passages 27 communicating with the retarding hydraulic chambers 9 through the retarding-side communication holes 9a, An advance oil passage 28 communicating with each advance hydraulic chamber 10 through the advance side communication hole 10a, and a supply passage 29 through which hydraulic oil for supplying to each retard and advance

hydraulic chamber

9, 10 flows. A drain passage 30 through which the hydraulic oil discharged from the respective retard and advance

hydraulic chambers

9 and 10 flows, a supply passage 29 for the retard and advance

passages

27 and 28 according to the operating state of the engine, and the like An electromagnetic switching valve 31 that is a hydraulic control valve that selectively switches the communication state of the drain passage 30 is mainly configured.

The retarding passage 27 includes a retarding passage portion 27a communicating with a passage port (not shown) of the electromagnetic switching valve 31, a retarding passage hole 27b formed through the camshaft 2 along the radial direction, and a bolt hole. 6 and the annular oil passage 27c formed between the inner peripheral surface of the cam bolt 5 and the outer peripheral surface of the shaft portion 5c, and between the inner peripheral surface of the rotor 20 and the outer peripheral surface of the shaft portion 5c. It is formed as a series of passages including an annular passage 27d communicating with the corner side communication hole 9a.

The advance passage 28 includes an advance passage portion 28a that communicates with a supply port (not shown) of the electromagnetic switching valve 31, an advance passage hole 28b that is formed through the cam shaft 2 along the radial direction, and a cam shaft. 2 and the rotor 20, and is formed as a series of passages provided with four axial oil holes 28c communicating with the respective advance side communication holes 10a.

The supply passage 29 has an upstream end communicating with an oil pan 33 via an oil strainer 32, and a downstream end communicating with a drain port (not shown) of the electromagnetic switching valve 31. The supply passage 29 has an oil pump 34 in the middle of the flow path, and the hydraulic oil sucked from the oil pan 33 by the oil pump 34 is discharged to the electromagnetic switching valve 31 side.

The drain passage 30 communicates with the passage port (not shown) of the electromagnetic switching valve 31 at the upstream end, and communicates with the oil pan 33 at the downstream end.

As shown in FIG. 1, the electromagnetic switching valve 31 is a three-position four-port switching valve, and is provided with a spool valve body outside the figure that is slidable in the axial direction within the valve body by an electronic controller outside the figure. Is moved in the front-rear direction so that the supply passage 29 and one of the

oil passages

27 and 28 communicate with one oil passage 27 (28) and at the same time the drain passage 30 and the other oil passage 28 (27) communicate with each other. Alternatively, the communication between the passages 27 to 30 is blocked.

The electronic controller includes information from various sensors such as a crank angle sensor, an air flow meter, an engine water temperature sensor, a throttle valve opening sensor, and a cam angle sensor that detects the current rotational phase of the camshaft 2 by an internal computer. A signal is input to detect the current engine operating state. Based on the detected engine operating state, an appropriate control pulse current is output to the electromagnetic coil of the electromagnetic switching valve 31 to control the movement position of the spool valve body, thereby switching the communication between the passages 27-30. It comes to control.

Also, between the first vane 21 a and the rear plate 13, a lock mechanism 35 that restrains the vane rotor 8 to the most retarded position with respect to the housing 7 is provided.

As shown in FIGS. 4 and 6, the lock mechanism 35 is slidably accommodated in a sliding hole 36 formed in the first vane 21a so as to penetrate along the axial direction. Then, a lock pin 37 provided so as to be movable forward and backward with respect to the rear plate 13 side and a small-diameter portion 37a (to be described later) of the lock pin 37 are engaged with each other by being engaged with a vane rotor. 8 is mainly composed of a lock hole 38 for locking 8 and an engagement / disengagement mechanism for engaging or releasing the small diameter portion 37a of the lock pin 37 with respect to the lock hole 38 in accordance with the starting state of the engine.

As shown in FIG. 6 in particular, the sliding hole 36 has an inner peripheral surface formed in a step diameter shape, and has a small diameter hole portion 36a on the rear plate 13 side and a large diameter hole portion 36b on the front plate 12 side. In addition, an annular first step portion 36c is formed between the small diameter hole portion 36a and the large diameter hole portion 36b.

The lock pin 37 has a small-diameter portion 37a on the rear plate 13 side (tip side) and a large-diameter hole. A large-diameter portion 37b on the front plate 12 side that is slidably accommodated in the portion 36b. An annular second step portion 37c is formed between the small diameter portion 37a and the large diameter portion 37b. On the rear end surface of the lock pin 37 on the front plate 12 side, a circular concave spring accommodating groove 37d is formed along the inner axial direction.

The lock hole 38 is disposed and formed at a predetermined position in the circumferential direction of the rear plate 13 such that the relative conversion angle between the housing 7 and the vane rotor 8 becomes the most advanced angle when the lock pin 37 is engaged.

The lock hole 38 has an inner diameter larger than the outer diameter of the small-diameter portion 37a of the lock pin 37, and an annular ring member 39 into which the small-diameter portion 37a of the lock pin 37 can be inserted into the inner peripheral surface. Is inserted. The ring member 39 is made of an abrasion-resistant material, and even when the inner peripheral surface repeatedly contacts the outer peripheral surface of the small-diameter portion 37a of the lock pin 37 as the lock pin 37 is engaged and disengaged, the wear or the like Is to be suppressed.

The engagement / disengagement mechanism is supplied into the coil spring 40, which is elastically mounted between the inner end surface of the front plate 12 and the bottom surface of the spring accommodating groove 37d of the lock pin 37, and constantly urges the lock pin 37 in the advance direction. The first and

second pressure chambers

41 and 42 move the lock pin 37 in the backward direction based on the hydraulic pressure.

When the vane rotor 8 rotates relative to the housing 7 at the maximum retarded angle position, the coil spring 40 moves the lock pin 37 forward by the spring force so that the tip of the small diameter portion 37a of the lock pin 37 is moved into the lock hole 38. The vane rotor 8 is locked with respect to the housing 7 by being engaged therewith.

The first pressure chamber 41 is an annular space defined between the first stepped portion 36c of the sliding hole 36 and the second stepped portion 37c of the lock pin 37, and is formed through the peripheral wall. It communicates with the retarded hydraulic chamber 9 separated by the first vane 21a through one oil passage 43 (see FIG. 4). Further, when hydraulic oil is supplied to the first pressure chamber 41, the hydraulic pressure of the hydraulic oil is applied to the second step portion 37 c of the lock pin 37 to urge the lock pin 37 in the backward direction. It is supposed to be.

The second pressure chamber 42 is formed as a cylindrical space having a smaller diameter than the small diameter portion 37a of the lock pin 37 on the bottom surface of the lock hole 38, and through a long groove-like second oil passage 44 formed in the peripheral wall. It communicates with the advance hydraulic chamber 10 separated by the first vane 21a (see FIG. 4). Further, when hydraulic oil is supplied to the second pressure chamber 42, the hydraulic pressure of the hydraulic oil is applied to the distal end surface of the lock pin 37 to urge the lock pin 37 in the backward direction. It has become.

Further, as shown in FIGS. 1 to 3 and 7, a spiral spring 45, which is a biasing member that biases the vane rotor 8 in the advance direction with respect to the housing 7, is provided on the outer end surface 12 c of the front plate 12. It has been.

The spiral spring 45 is formed by winding flat rectangular lines having a substantially rectangular cross section on substantially the same plane so that the surfaces in the longitudinal direction face each other, and gradually increases in diameter from the inner peripheral side to the outer peripheral side. A spiral spring main body 45a, a first locking end 45b in which one end portion on the inner peripheral side of the spiral spring main body 45a is bent radially inward, and a second end portion on the outer peripheral side of the spiral spring main body 45a in the radial direction And a second locking end portion 45c curved outwardly in a semicircular hook shape.

The spiral spring main body 45a has a part of the innermost peripheral portion on the first locking end portion 45b side accommodated in the annular groove 25 formed in the cylindrical portion 23, and a second locking end portion. The outermost peripheral portion on the 45c side is supported by a support pin 46 (see FIG. 3) that is press-fitted and fixed to the outer end surface 12c of the front plate 12. The support pin 46 supports the outermost peripheral portion of the spiral spring 45 so that the spiral spring 45 can perform a stable biasing operation between the housing 7 and the vane rotor 8, and the spiral spring 45 has a reduced diameter. When deformed in the direction, the torque generated between the contact position of the support pin 46 of the spiral spring 45 and the second locking end 45c is increased.

The first locking end portion 45 b is locked and fixed to one side surface 24 a of the locking groove 24 while being engaged with the locking groove 24 of the cylindrical portion 23. On the other hand, the second locking end portion 45c is locked and fixed to the outer peripheral surface of the pin body 18a of the pin 18 with the umbrella provided on the outer end surface 12c of the front plate 12.

With this configuration, the spiral spring 45 urges the vane rotor 8 in the advance direction with respect to the housing 7 as described above. This urging force positively rotates the vane rotor 8 to the advance side. It is not strong and is set to such an extent that it can be balanced with negative alternating torque (alternating torque that rotates the vane rotor 8 to the retard side) generated in the camshaft 2 during engine operation.

In other words, the phase conversion of the vane rotor 8 is performed only by the hydraulic pressure supplied to the respective retard and advance

hydraulic chambers

9 and 10, and the urging by the spiral spring 45 is used to maintain the phase of the vane rotor 8. It is an auxiliary one.

As shown in FIGS. 2 to 4, 7, and 8, the cylindrical portion 23 has a U-shape that is a tool engaging portion into which an engaging protrusion 54 of a holding tool 52 described later is engaged when fastening a bolt. Three groove portions 47 are provided at circumferentially equidistant positions.

As shown in FIG. 7, each groove 47 is a side surface 47 a that is a first contact surface provided on the side opposite to the bolt fastening direction D, and a second contact surface that faces the side surface 47 a. The other side surface 47b and the circular-arc-shaped bottom surface 47c which connects both

side surface

47a, 47b are provided.

As shown in FIG. 8, the one side surface 47a is formed by connecting the rotation axis O of the vane rotor 8 and the edge 47d on the inner peripheral side of the cylindrical portion 23 (rotor 20) of the one side surface 47a. In comparison with the bolt fastening direction D, it is formed in a flat shape that is inclined to the opposite side. In other words, the edge 47f on the outer peripheral side of the cylindrical portion 23 (the rotor 20) of the one side surface 47a is provided on the opposite side to the bolt fastening direction D with respect to the first virtual surface S1.

On the other hand, the other side surface 47b is compared with the second virtual surface S2 formed by connecting the rotation axis O of the vane rotor 8 and the edge 47e on the inner peripheral side of the cylindrical portion 23 (rotor 20) of the other side surface 47b. It is formed in a flat shape inclined in the bolt fastening direction D. In other words, the edge 47g on the outer peripheral side of the cylindrical portion 23 (rotor 20) on the other side surface 47b is provided on the bolt fastening direction D side with respect to the second virtual surface S2.

That is, each groove portion 47 is formed in a C shape in a front view in which the width (groove width) in the circumferential direction of the cylindrical portion 23 gradually increases from the inner peripheral side to the outer peripheral side of the cylindrical portion 23.

In addition, as shown in FIG. 10 in particular, each groove portion 47 is formed so that the groove depth is slightly shorter than the axial length of the cylindrical portion 23, and the bottom surface 47 c is slightly forward of the apparatus than the front end surface 20 b of the rotor 20. In other words, it is positioned closer to the distal end portion 23a of the cylindrical portion 23.

Further, the above-described locking groove 24 is configured such that the formation position of the cylindrical portion 23 in the circumferential direction is determined based on the relative relationship with each groove portion 47.

That is, as shown in FIG. 8, the locking groove 24 is disposed between specific

adjacent groove portions

47, 47 in the circumferential direction of the cylindrical portion 23. 23 is slightly deviated in the direction opposite to the bolt fastening direction D from the intermediate position P0 between both

groove portions

47, 47 in the circumferential direction.
[Attaching method of valve timing control device]
The valve timing control device is fastened and attached to the camshaft 2 by the cam bolt 5 as described above. In this fastening operation, a hexagon wrench 51 (see FIG. 11) which is a general bolt fastening tool having a fitting portion 51a fitted to the hexagonal head 5a of the cam bolt 5 at the end, and the hexagon wrench 51 And a holding tool 52 for holding the vane rotor 8 when performing the fastening operation.

As shown in FIGS. 9A and 9B, the holding tool 52 is integrally formed of a metal material, and has a cylindrical base portion 53 and three engagement members protruding from one end surface in the axial direction of the base portion 53. It is comprised from the entrance protrusion 54 and the holding part 55 extended from the outer peripheral surface of the base 53.

The base 53 is formed to have substantially the same diameter as the cylindrical portion 23 of the vane rotor 8, and an insertion hole 53 a that is a hole through which a hexagon wrench 51 that engages with the head 5 a of the cam bolt 5 can be inserted. Yes.

As shown in FIG. 9A, each engaging protrusion 54 is arranged at a substantially equal interval in the circumferential direction of the base 53 and is formed in a shape corresponding to each groove 47 of the cylindrical portion 23. It is possible to engage with each groove 47.

That is, the engaging protrusion 54 is formed in a substantially fan shape when viewed from the front. The engaging protrusion 54 is formed on the first locking surface 54 a facing the one side surface 47 a of the groove portion 47 and the other side surface 47 b of the groove portion 47 when engaging with the groove portion 47. And an opposing second locking surface 54b.

Next, the operation of attaching the valve timing control device to the camshaft 2 will be described step by step with reference to FIGS.

First, as a first step, as shown in FIG. 10, the valve timing control device in a state where members other than the spiral spring 45 are assembled in advance is inserted into the camshaft 2 from the axial direction. The fitting hole 20d of the rotor 20 is fitted to the one end 2a of the two.

At this time, the vane rotor 8 is restrained to the most retarded position with respect to the housing 7 by the lock pin 37 engaging with the lock hole 38, and the pin member 22 is positioned in the circumferential direction with respect to the camshaft 2. It has come to be.

Next, as a second step, after inserting the cam bolt 5 into the bolt hole 6 of the camshaft 2, as shown in FIG. 11, the engaging projections 54 of the holding tool 52 are arranged in the cylinder direction along the axial direction of the cam bolt 5. It is made to engage in each groove part 47 of the part 23 from an axial direction.

Subsequently, as a third step, the fitting portion 51a at the tip of the hexagon wrench 51 is inserted into the insertion hole 53a of the holding tool 52 and fitted into the head portion 5a of the cam bolt 5, and then the holding portion of the holding tool 52 is held. The hexagon wrench 51 is rotated in the bolt fastening direction D while gripping 55.

At this time, as shown in FIG. 12, the vane rotor 8 tries to rotate in the bolt fastening direction D by being brought into sliding contact with the seat portion 5b of the rotating cam bolt 5 and being rotated by the seat portion 5b. However, the first locking surface 54 a of each engaging protrusion 54 of the holding tool 52 fixed by gripping is in contact with one side surface 47 a of each groove portion 47, so that the rotation is suppressed. As a result, a large shearing force does not act on the outer peripheral surface of the pin member 22 interposed between the vane rotor 8 and the camshaft 2 or the outer peripheral surface of the lock pin 37 engaged in the lock hole 38. Therefore, the deformation of the

pins

22 and 37 can be suppressed.

Then, after the male screw portion 5d of the cam bolt 5 is completely screwed into the female screw portion 6a of the bolt hole 6, as a fourth step, the spiral spring 45 is attached to the outer end surface 12c side of the front plate 12, thereby providing a valve timing control device. The mounting operation for the camshaft 2 is completed.

In addition, when removing a valve timing control apparatus from the camshaft 2, removal work is performed by the process reverse to the attachment work process mentioned above. In this case, the second locking surface 54b of each engaging projection 54 of the holding tool 52 abuts against the other side surface 47a of each groove portion 47 so that the cam bolt 5 of the vane rotor 8 is loosened (the direction opposite to the bolt fastening direction D). ) Is suppressed. As a result, deformation of the pin member 22 and the lock pin 37 can be suppressed even when the valve timing control device is removed.
[Effects of this embodiment]
From the above-described configuration, according to the valve timing control device of the present embodiment, the electronic controller (not shown) appropriately passes a control current through the coil of the electromagnetic switching valve 31 according to the operating state of the engine. The communication state of ~ 30 is switched. Then, based on the switching of the communication state, the relative hydraulic phase of the vane rotor 8 with respect to the housing 7 (sprocket 1) is changed as shown in FIG. 4 by changing the hydraulic relationship between each retarded hydraulic chamber 9 and each advanced hydraulic chamber 10. The valve timing of the engine is changed by being converted into the most retarded phase shown and the most advanced phase shown in FIG.

Further, in the valve timing control device of the present embodiment, during the engine operation, the communication of the passages 27 to 30 is blocked by the electromagnetic switching valve 31 to operate inside the retard hydraulic chamber 9 and the advance hydraulic chamber 10, respectively. By maintaining the state in which the oil is supplied, the valve timing of the engine can be maintained at a desired phase.

In particular, in this embodiment, since the spiral spring 45 that biases the vane rotor 8 in the advance direction with respect to the housing 7 is provided, the negative force generated in the camshaft 2 during engine operation by the spring force of the spiral spring 45 is provided. Since the balance with the alternating torque can be easily taken, the valve timing can be easily and accurately maintained.

Further, in the present embodiment, since the spiral spring 45 is used as the biasing member provided for this phase maintenance, the axial length is remarkably shortened compared with the case where a torsion spring or the like is used. Can be made compact.

And in this embodiment, it was made to suppress the deformation | transformation of the vane rotor 8 at the time of the attachment operation | work to the cam shaft 2 of a valve timing control apparatus.

In the valve timing control apparatus as shown in the present embodiment, the engaging protrusions 54 of the holding tool 52 are engaged with the groove portions 47 of the vane rotor 8 to suppress the rotation of the vane rotor 8 when the bolts are tightened. 12, the rotational force F1 of the vane rotor 8 is suppressed by the first locking surfaces 54a of the respective engaging protrusions 54, and at the same time, a reaction force (load) F2 equivalent to the rotational force F1 is applied to each groove portion 47. Acting on one side surface 47a.

At this time, if the reaction force F2 has a vector component in the direction of the outer diameter of the vane rotor 8, the vane rotor 8 may be deformed to expand in the outer direction by the reaction force F2, but in this embodiment, as described above. Since the one side surface 47a of each groove portion 47 is formed so as to be inclined in the direction opposite to the bolt fastening direction D as compared with the first virtual surface S1, the reaction force F2 is a vector component F2 in the inner diameter direction of the vane rotor 8. _{With the rad} , the vane rotor 8 acts so as to be restrained inwardly with respect to each side surface 47a.

This prevents the vane rotor 8 from being expanded outwardly based on the reaction force F2 when the bolt is fastened, so that the diameter expansion deformation of the vane rotor 8 can be effectively suppressed.

Therefore, according to the present embodiment, it is possible to suppress the deformation of the vane rotor 8 when the rotation of the vane rotor 8 is suppressed while suppressing the rotation of the vane rotor 8 when the vane rotor 8 is bolted to the camshaft 2.

In addition, the above-mentioned effect is the valve timing control of this embodiment in which each groove part 47 is formed in the comparatively thin (low-rigidity) cylindrical part 23 used for latching of the spiral spring 45 in the vane rotor 8. It is particularly useful in the device.

When the strength of the cylindrical portion 23 is concerned, the cylindrical portion 23 is formed thick to improve the strength, or the cylindrical portion 23 is formed of another member having high rigidity. However, the former has a problem of an increase in the weight of the apparatus due to the thickening of the cylindrical portion 23, and the latter has a problem that the assembling work becomes complicated due to an increase in the number of parts.

On the other hand, in the present embodiment, the rotor 20 and the cylindrical portion 23 are integrally formed, and the reaction force F2 is received by devising the action direction of the reaction force F2. The deformation of the cylindrical portion 23 based on the reaction force F2 can be suppressed without increasing the weight or the number of parts.

In the present embodiment, the locking groove 24 that is locked by the first locking end 45b of the spiral spring 45 is provided in a portion that does not interfere with each circumferential groove 47 of the cylindrical portion 23, so that the bolt During the fastening operation, the problem that the locking groove 24 interferes with the holding tool 52 does not occur, and the workability related to the bolt fastening is not impaired.

Furthermore, in this embodiment, the disposition position P1 of the locking groove 24 is set on the opposite side to the bolt fastening direction D from the circumferential intermediate position P0 between the two

specific groove portions

47, 47 in the cylindrical portion 23. It was biased in the direction. As a result, as shown in FIG. 12, of the

meat portions

23 b and 23 c between the

specific groove portions

47 and 47 of the cylinder portion 23, the side that receives the reaction force F <b> 2 from the engaging protrusion 54 of the holding tool 52 (the bolt fastening direction). Since the cross-sectional area of the meat portion 23b on the (D side) is ensured widely, the strength of the vane rotor 8 against the reaction force F2 does not greatly decrease. As a result, even if the locking groove 24 is provided, it can sufficiently counter the reaction force F2.

Further, in the present embodiment, the other side surface 47b of each of the groove portions 47 is formed in a flat shape that is inclined in the bolt fastening direction D as compared with the second virtual surface S2, so that a failure occurs in the valve timing control device. in such case be removed from the cam shaft 2 Te, the reaction force F4 of the rotational force F3 generated in the vane rotor 8 with the loosening operation of the cam bolt 5 is allowed to have an inner diameter direction of the vector component F4 _rad of the vane rotor 8. Thereby, since the reaction force F4 acts so as to be restrained inward with respect to the cylindrical portion 23, the diameter expansion deformation of the vane rotor 8 can be suppressed even when the cam bolt 5 is removed.

Furthermore, in the present embodiment, each groove 47 is formed to have a groove depth such that the bottom surface 47c is closer to the tip 23a of the cylindrical portion 23 than the front end surface 20b of the rotor 20, and therefore each groove 47 is a rotor. 20 does not reach the inside of the groove 20, and the formability of each groove 47 is good.

In the present embodiment, since the bottom surface 47c of each groove 47 is formed in an arc shape, the stress concentration on a specific part of the cylinder 23 when the reaction force F2 is applied to the cylinder 23 at the time of bolt fastening. Therefore, deformation of the cylindrical portion 23 can be further suppressed.
[Second Embodiment]
FIG. 13 shows a second embodiment of the present invention. The basic configuration is the same as that of the first embodiment, but the shape of the other side surface 47b of each groove 47 is changed.

Basically, the valve timing control device is not a device that is repeatedly attached to and detached from the camshaft 2, but a device that maintains its state for a long period of time once it is attached. Further, the rotational force F3 generated in the vane rotor 8 when the cam bolt 5 is removed tends to be smaller than the rotational force F1 generated in the vane rotor 8 when the bolt is fastened.

In view of these circumstances, in this embodiment, the other side surface 47b of each groove portion 47 is formed in a planar shape that is inclined to the opposite side to the bolt fastening direction D as compared with the second virtual surface S2.

Thereby, when the cam bolt 5 is loosened, the vane rotor 8 may be slightly deformed in the diameter-expanding direction, but the groove width of the groove portion 47 (in the circumferential direction of the cylindrical portion 23) is larger than that of the valve timing control device of the first embodiment. The length of the cylindrical portion 23 is narrowed, and a wide cross-sectional area of the cylindrical portion 23 can be secured. Therefore, the strength of the cylindrical portion 23 can be improved. As a result, the deformation of the vane rotor 8 at the time of bolt fastening can be further suppressed.

Other functions and effects are the same as those in the first embodiment.

The present invention is not limited to the configuration of each of the embodiments described above, and the configuration can be changed without departing from the spirit of the invention.

For example, in each of the embodiments described above, each groove portion 47 is provided in the cylindrical portion 23 of the rotor 20, but it is also possible to eliminate the cylindrical portion 23 and provide each groove portion 47 in the front end surface 20b of the rotor 20.

In each of the above embodiments, the cylindrical portion 23 is provided on the front end surface 20 b of the rotor 20, and the engaging protrusions 54 of the holding tool 52 are engaged with the groove portions 47 formed on the front end surface of the cylindrical portion 23. Thus, the rotation of the vane rotor 8 is suppressed. However, the cylindrical portion 23 is abolished, a plurality of protrusions are provided on the front end surface 20b of the rotor 20, and the engaging protrusions 54 of the holding tool 52 are inserted between the protrusions. The rotation of the vane rotor 8 may be suppressed by locking one side surface formed on the bolt fastening direction D side of each protrusion to the first locking surface 54a of the insertion protrusion 54.

As a valve timing control device for an internal combustion engine and a method for mounting the valve timing control device based on the embodiments described above, for example, the following modes can be considered.

In one embodiment, a valve timing control device for an internal combustion engine includes a housing to which a rotational force is transmitted from a crankshaft, and a cylindrical rotor provided inside the housing and fastened and fixed to the camshaft by a cam bolt. A vane rotor, and a groove portion provided on an end surface of the rotor opposite to the camshaft and having a side surface opposite to a fastening direction of the cam bolt, and the one side surface includes a rotation axis of the vane rotor and the The edge on the outer peripheral side of the one side surface is on the opposite side to the fastening direction of the cam bolt than the imaginary surface formed by connecting the inner peripheral edge of the rotor on the one side surface.

In a preferred aspect of the valve timing control device of the internal combustion engine, the vane rotor is provided at an end opposite to the camshaft, and has a cylindrical tube portion extending to the outside of the housing, and the groove portion is , Provided in the cylindrical portion.

In another preferred aspect, in any one of the aspects of the valve timing control device of the internal combustion engine, one end is locked to the cylindrical part and the other end is between the cylindrical part and the housing. A biasing member that is locked to the housing and biases the vane rotor to one side in the rotational direction with respect to the housing is provided, and a plurality of the groove portions are provided along a circumferential direction of the cylindrical portion. The valve timing of the internal combustion engine is characterized in that a locking groove for locking one end of the urging member is formed in a portion of the cylindrical portion between a specific pair of adjacent groove portions. Control device.

In still another preferred aspect, in any one of the aspects of the valve timing control device for the internal combustion engine, the locking groove is more than a circumferential intermediate position between the specific pair of adjacent groove portions in the cylindrical portion. It is biased to the opposite side with respect to the fastening direction of the cam bolt.

In still another preferred aspect, in any one of the aspects of the valve timing control device of the internal combustion engine, the groove portion has another side surface provided to face the one side surface, and the other side surface is formed of the vane rotor. The edge on the outer peripheral side of the one side surface is in the fastening direction of the cam bolt, rather than the virtual surface formed by connecting the rotation axis and the edge on the inner peripheral side of the cylindrical portion on the other side surface.

In still another preferred aspect, in any one of the aspects of the valve timing control device of the internal combustion engine, the groove portion has another side surface provided to face the one side surface, and the other side surface is formed of the vane rotor. The edge on the outer peripheral side of the one side surface is on the opposite side of the fastening direction of the cam bolt from the virtual surface formed by connecting the rotation axis and the edge on the inner peripheral side of the cylindrical portion on the other side surface. .

According to still another preferred aspect, in any one of the aspects of the valve timing control device of the internal combustion engine, the bottom surface of the groove portion is disposed at a position closer to the cylindrical portion than an end surface of the rotor on the side opposite to the cam shaft. ing.

In still another preferred aspect, in any one of the aspects of the valve timing control device of the internal combustion engine, the bottom surface of the groove is formed in an arcuate shape.

In still another preferred aspect, in any one of the aspects of the valve timing control device of the internal combustion engine, the biasing member is a spiral spring.

In still another preferred aspect, in any of the aspects of the valve timing control device for the internal combustion engine, the cylindrical portion is integrally formed with the rotor by sintering.

In another aspect of the valve timing control device for an internal combustion engine, a rotational force is transmitted from a crankshaft, a housing having a working chamber therein, a housing provided inside the housing, and fastened and fixed to the camshaft by a cam bolt. A cylindrical rotor, a vane rotor provided on an outer peripheral side of the rotor and having a vane that divides the working chamber into a retarded working chamber and an advanced working chamber, and an end of the rotor opposite to the camshaft An extending portion extending to the outside of the housing, and one end portion of the extending portion being locked to the extending portion, the other end portion being locked to the housing, and the vane rotor to the housing A biasing member that biases one side in the rotational direction, and a holding tool that is provided at the tip of the extending portion and restricts the rotation of the rotor when the cam bolt is fastened. A groove portion having one abutment surface, wherein the first abutment surface is formed such that a vector of a load received from the holding tool when regulating the rotation of the rotor has a component in the rotor inner diameter direction. Has been.

In a preferred embodiment of the valve timing control device for an internal combustion engine as seen from another viewpoint, a plurality of the groove portions are provided along a circumferential direction of the extension portion, and the adjacent one of the extension portions is adjacent to the extension portion. A locking groove for locking one end of the urging member is formed at a portion between the pair of grooves.

In another preferred embodiment, in any one of the aspects of the valve timing control device for an internal combustion engine as viewed from another viewpoint, the locking groove is a circumferential direction between the specific pair of adjacent groove portions in the extending portion. It is biased to the opposite side to the fastening direction of the cam bolt from the center position.

In still another preferred aspect, in any one of the aspects of the valve timing control device for an internal combustion engine as seen from another viewpoint, the extending portion is integrally formed with the rotor by sintering.

Further, from another point of view, the valve timing control device for an internal combustion engine is provided with a housing having a working chamber therein, in which rotational force is transmitted from the crankshaft, and is fastened and fixed to the camshaft by cam bolts A cylindrical rotor, a vane rotor provided on an outer peripheral side of the rotor and having a vane that divides the working chamber into a retarded working chamber and an advanced working chamber, and an end surface of the rotor opposite to the camshaft A projection portion provided on the cam bolt, the projection portion having one side surface at a portion on a fastening direction side of the cam bolt, and the one side surface is a rotation axis of the vane rotor and the rotor inner peripheral side. Compared to a virtual surface formed by connecting the end edges of the cam bolt, the cam bolt is inclined to the opposite side to the fastening direction of the cam bolt.

Further, from another viewpoint, a method for mounting a valve timing control device for an internal combustion engine includes a housing in which a rotational force is transmitted from a crankshaft and having a working chamber therein, and a camshaft provided by a cam bolt. And a vane rotor provided on the outer peripheral side of the rotor and having a vane that separates the working chamber into a retarded working chamber and an advanced working chamber, and opposite to the camshaft of the rotor A tool engaging portion having one side surface provided on an end surface on the side and opposed to a direction opposite to a direction in which the cam bolt is fastened, wherein the one side surface is a rotating shaft of the vane rotor and the rotor on the one side surface. The internal combustion engine valve is inclined to the opposite side to the fastening direction of the cam bolt in comparison with a virtual plane formed by connecting the inner peripheral edge of the cam bolt. A method for attaching a timing control device, comprising: a step of bringing an end face of the rotor into contact with an end face of the camshaft; an engaging protrusion engageable with the tool engaging portion; and a fastening tool for fastening the cam bolt. A step of engaging a holding tool having a possible hole portion into the tool engaging portion, and a step of inserting the fastening tool into the hole portion of the holding tool and fastening the cam bolt with the fastening tool. Have.

Claims

A housing to which rotational force is transmitted from the crankshaft;
A vane rotor provided inside the housing and having a cylindrical rotor fastened and fixed to the camshaft by a cam bolt;
A groove portion provided on an end surface of the rotor opposite to the cam shaft, and having a side surface opposite to a fastening direction of the cam bolt;
With
The one side is connected to the cam bolt by an outer peripheral edge of the one side surface than a virtual surface formed by connecting the rotation axis of the vane rotor and the inner peripheral edge of the one side rotor. A valve timing control device for an internal combustion engine, wherein the valve timing control device is on the opposite side to the fastening direction.
The valve timing control apparatus for an internal combustion engine according to claim 1,
The vane rotor is provided at an end opposite to the camshaft and has a cylindrical tube portion extending to the outside of the housing,
The valve timing control device for an internal combustion engine, wherein the groove portion is provided in the cylindrical portion.
The valve timing control device for an internal combustion engine according to claim 2,
Between the tube portion and the housing, one end portion is locked to the tube portion, and the other end portion is locked to the housing, and the vane rotor is attached to one side in the rotation direction with respect to the housing. A biasing member is provided,
A plurality of the groove portions are provided along the circumferential direction of the cylindrical portion,
A valve timing control for an internal combustion engine, wherein a locking groove for locking one end of the urging member is formed in a portion of the cylindrical portion between a pair of specific adjacent groove portions. apparatus.
The valve timing control apparatus for an internal combustion engine according to claim 3,
The internal combustion engine, wherein the locking groove is biased to an opposite side to a fastening direction of the cam bolt with respect to a circumferential intermediate position between the specific pair of adjacent groove portions in the cylindrical portion. Valve timing control device.
The valve timing control device for an internal combustion engine according to claim 2,
The groove portion has another side surface provided to face the one side surface,
The outer side edge of the other side surface is connected to the rotation axis of the vane rotor and the inner peripheral side edge of the cylindrical portion of the other side surface. A valve timing control device for an internal combustion engine, characterized by being in the fastening direction of
The valve timing control device for an internal combustion engine according to claim 2,
The groove portion has another side surface provided to face the one side surface,
The outer side edge of the other side surface is connected to the rotation axis of the vane rotor and the inner peripheral side edge of the cylindrical portion of the other side surface. A valve timing control device for an internal combustion engine, wherein the valve timing control device is on the opposite side to the fastening direction.
The valve timing control device for an internal combustion engine according to claim 2,
The valve timing control device for an internal combustion engine, wherein the cylindrical portion is integrally formed with the rotor by sintering.
A housing in which a rotational force is transmitted from the crankshaft and has a working chamber inside;
A cylindrical rotor provided inside the housing and fastened and fixed to the camshaft by a cam bolt, and a vane provided on the outer peripheral side of the rotor and separating the working chamber into a retarded working chamber and an advanced working chamber. A vane rotor having,
An extended portion provided at an end of the rotor opposite to the camshaft and extending to the outside of the housing;
One end portion is locked to the extending portion, the other end portion is locked to the housing, and a biasing member that biases the vane rotor to one side in the rotational direction with respect to the housing;
A groove portion having a first abutting surface that is provided at a distal end portion of the extending portion and abuts with a holding tool that regulates rotation of the rotor when the cam bolt is fastened;
With
The first contact surface is formed so that a vector of a load received from the holding tool when regulating the rotation of the rotor has a component in an inner diameter direction of the rotor. Valve timing control device.
A housing in which a rotational force is transmitted from the crankshaft and has a working chamber inside;
A cylindrical rotor provided inside the housing and fastened and fixed to the camshaft by a cam bolt, and a vane provided on the outer peripheral side of the rotor and separating the working chamber into a retarded working chamber and an advanced working chamber. A vane rotor having,
A protrusion provided on the end surface of the rotor opposite to the camshaft;
With
The protrusion has one side surface at a portion on the fastening direction side of the cam bolt,
The one side surface is inclined to the side opposite to the fastening direction of the cam bolt as compared with a virtual surface formed by connecting the rotation axis of the vane rotor and the edge on the inner peripheral side of the rotor. An internal combustion engine valve timing control device.
A housing in which a rotational force is transmitted from the crankshaft and has a working chamber inside;
A cylindrical rotor provided inside the housing and fastened and fixed to the camshaft by a cam bolt, and a vane provided on the outer peripheral side of the rotor and separating the working chamber into a retarded working chamber and an advanced working chamber. A vane rotor having,
A tool engagement portion provided on an end surface of the rotor opposite to the camshaft and having one side surface facing a direction opposite to a direction of fastening the cam bolt;
With
The one side surface is inclined to the opposite side to the fastening direction of the cam bolt, compared to a virtual surface formed by connecting the rotating shaft of the vane rotor and the inner peripheral edge of the rotor on the one side surface. An internal combustion engine valve timing control device mounting method comprising:
Contacting the end face of the rotor with the end face of the camshaft;
A step of engaging a holding tool having an engagement protrusion capable of being engaged with the tool engagement portion and a hole portion through which a fastening tool for fastening the cam bolt is inserted into the tool engagement portion;
Inserting the fastening tool through the hole of the holding tool, and fastening the cam bolt with the fastening tool while restricting rotation of the holding tool;
A method for mounting a valve timing control device for an internal combustion engine, comprising: