JP2022036329A - Valve timing control device of internal combustion engine - Google Patents

Abstract

To provide a valve timing control device of an internal combustion engine which can suppress the wobbling of a vane rotor.SOLUTION: In a valve timing control device, first and second vanes V1, V2 out of first to fourth vanes V1 to V4 are protruded from first and second large-diameter parts 31, 32 which are formed at a rotor main body 30 of a vane rotor 3. Then, the first and second large-diameter parts 31, 32 are arranged in a first operation chamber A1 and a second operation chamber A2 which are formed between first to fourth shoes S1 to S4 of a housing 2 in a circumferential direction, and constantly cover a first lock hole H1 and a second lock hole H2. As above, pressure-receiving faces of the first and second vanes V1, V2 can be thereby constituted while including the first and second large-diameter parts 31, 32. By this constitution, the torque of the vane rotor 3 is enhanced, and the wobbling of the vane rotor 3 which is generated by alternate torque can be suppressed.SELECTED DRAWING: Figure 3

Description

The present invention relates to a valve timing control device for an internal combustion engine.

As a conventional valve timing control device, for example, the one described in the following Patent Document 1 is known.

In this valve timing control device, one pair of vanes out of four vanes is formed so as to project on the outer peripheral side of a pair of large diameter portions having a diameter larger than that of the rotor body, and one pair of four shoes. Each shoe is configured to be in sliding contact with the pair of large diameter portions.

International Publication No. 2016/185918

The conventional valve timing control device has a configuration in which the pair of shoes is in sliding contact with the pair of large diameter portions from the radial direction. Therefore, the volume between the pair of vanes and the pair of shoes becomes small, a sufficient pressure receiving area cannot be secured, and the vane rotor flutters due to the alternating torque input via the camshaft. Was difficult to control.

The present invention has been devised in view of the actual situation of the valve timing control device of the conventional internal combustion engine, and an object of the present invention is to provide a valve timing control device of an internal combustion engine capable of suppressing fluttering of a vane rotor. There is.

As one aspect of the present invention, a plurality of lock holes (first lock hole and second lock hole) protruding outward in the radial direction from the rotor body of the vane rotor and provided in the housing over the entire range of relative rotation of the vane rotor with respect to the housing. ), A plurality of working chambers (first working chamber and second working chamber) formed between the circumferential directions of the plurality of shoes provided in the housing are formed by the plurality of large diameter portions (first large diameter portion and second large diameter portion). 2 It is located in the working chamber).

According to the present invention, the fluttering of the vane rotor can be suppressed.

It is an exploded perspective view of the valve timing control device of the internal combustion engine which concerns on 1st Embodiment of this invention. It is a vertical sectional view of the valve timing control device shown in FIG. FIG. 2 is a cross-sectional view taken along the line AA of FIG. 2, showing a locked state in an intermediate phase. FIG. 2 is a cross-sectional view taken along the line AA of FIG. 2, showing the most retarded angle state. FIG. 2 is a cross-sectional view taken along the line AA of FIG. 2 and shows a state of maximum advance angle. FIG. 5 is a cross-sectional view taken along the line CC of FIG. 5 and is a diagram showing a state of a lock pin in a state of maximum advance angle. It is a cross-sectional view corresponding to the line CC of FIG. 5, and is the figure which showed the state of the lock pin when it rotated slightly to the retard side from the state of FIG. It is a cross-sectional view corresponding to the line CC of FIG. 5, and is the figure which showed the state of the lock pin when it is further rotated to the retard side from the state of FIG. It is a cross-sectional view corresponding to the line CC of FIG. 5, and is the figure which showed the state of the lock pin when it was rotated further to the retard side from the state of FIG. 8 and became the intermediate phase. FIG. 3 is a cross-sectional view taken along the line BB of FIG. 3, showing a state in which the lock pins are completely engaged in the intermediate phase. It is a figure corresponding to FIG. 3 which concerns on 2nd Embodiment of this invention. It is a figure corresponding to FIG. 4 which concerns on 2nd Embodiment of this invention. It is a figure corresponding to FIG. 5 which concerns on 2nd Embodiment of this invention.

Hereinafter, embodiments of the valve timing control device for an internal combustion engine according to the present invention will be described with reference to the drawings. In the following embodiment, the device is applied to the valve timing control device on the exhaust side, but of course, it can also be applied to the valve timing control device on the intake side.

[First Embodiment]
1 to 10 show a first embodiment of a valve timing control device for an internal combustion engine according to the present invention. In the description of the embodiment, for convenience, the left side of FIG. 2 will be referred to as “front” and the right side will be referred to as “rear”. Further, the direction along the rotation axis Z of FIG. 2 will be described as "axial direction", the direction orthogonal to the rotation axis Z will be described as "diametrical direction", and the direction around the rotation axis Z will be described as "circumferential direction".

(Valve timing control device configuration)
FIG. 1 shows an exploded perspective view of a valve timing control device for an internal combustion engine according to the first embodiment of the present invention. FIG. 2 shows a cross-sectional view of the valve timing control device shown in FIG. 1 cut along the rotation center axis of the camshaft, to which a hydraulic circuit is added.

As shown in FIGS. 1 and 2, the valve timing control device includes a sprocket 22 that is rotationally driven by a rotational force of a crankshaft (not shown), and a camshaft 1 that is rotatably provided with respect to the sprocket 22. Be intervened during. Then, this valve timing control device controls the operation with the hydraulic pressure supplied and discharged by the first hydraulic circuit 51 described later, so that the relative rotation phase between the crankshaft and the camshaft 1 that rotate synchronously with the sprocket 22 is set. Convert. Specifically, the valve timing control device is provided integrally with the sprocket 22, and has relative rotation toward the inner peripheral side of the housing 2 having the first to fourth shoes S1 to S4 protruding toward the inner peripheral side. A vane rotor 3 having first to fourth vanes V1 to V4 that are possibly accommodated and project to the outer peripheral side is provided.

Further, between the housing 2 and the vane rotor 3, one end is fixed to the housing 2 and the other end is fixed to the vane rotor 3 to urge the vane rotor 3 to the advance angle side, which is a spiral spring. A spring 23 is provided. That is, the spiral spring 23 has a retard angle transmitted via the camshaft 1 immediately before the engine stops when the hydraulic pressure does not act on any of the operating chambers (advanced chamber Ad and retarded chamber Re described later). The vane rotor 3 is urged to the advance side against the rotational force in the direction (so-called alternating torque).

The camshaft 1 is rotatably supported by a bearing portion provided on a cylinder head (not shown), and opens an exhaust valve (not shown) via a drive cam (not shown). Further, the front end portion of the camshaft 1 is provided with a rotor connecting portion 1a that faces the inner peripheral side of the rear end portion of the rotor main body 30 and is used for connection with the vane rotor 3. Inside the rotor connecting portion 1a, a female threaded portion 1b into which a cam bolt 4 for fastening the vane rotor 3 is screwed is formed along the axial direction.

The housing 2 has a cylindrical housing body 20 that opens at both ends in the axial direction, a front plate 21 as a first side portion (first plate-shaped member) that closes an opening on the front end side of the housing body 20, and a housing. It has a sprocket 22 that constitutes a rear plate as a second side portion (second plate-shaped member) that closes an opening on the rear end side of the main body 20. The housing body 20, the front plate 21, and the sprocket 22 are jointly fastened and fixed by a plurality of bolts, the first to fourth bolts B1 to B4.

In this embodiment, the housing 2 has an embodiment in which both the front and rear sides are open, but the housing 2 does not necessarily have to be open on both the front and back sides. In other words, the housing 2 may have, for example, a housing body 20 formed in a bottomed cylindrical shape and having only one of the front plate 21 and the sprocket 22.

The housing body 20 is integrally formed of a sintered metal material, and the first to fourth shoes S1 to S4 are integrally provided at positions at substantially equal intervals in the circumferential direction so as to project inward. ing. The first to fourth shoes S1 to S4 have a substantially trapezoidal shape in a plan view, and inside the relatively wide first to fourth root portions S11, S21, S31, and S41 formed on the outer peripheral side, the first to fourth shoes S1 to S4 have a trapezoidal shape. The first to fourth bolt holes S13, S23, S33, and S43 through which the shaft portions of the first to fourth bolts B1 to B4 pass are formed along the axial direction.

Further, the relatively narrow first to fourth tip portions S12, S22, S32, and S42 formed on the inner peripheral side of the first to fourth shoes S1 to S4 are cross-sectionally opened inward in the radial direction. A seal groove having a substantially rectangular surface is formed along the axial direction. A shoe-side seal member 24 having a substantially prismatic shape is mounted in the seal groove.

The front plate 21 has a disk shape made of a predetermined metal material, and a front rotor through hole 211 through which the rotor main body 30 penetrates is formed at a substantially central position. Here, the front rotor through hole 211 is set to have a slightly larger diameter than the front boss portion 304 protruding from the front end portion of the rotor main body 30. As a result, the front side boss portion 304 of the vane rotor 3 housed inside the housing 2 faces the outside through the front side rotor through hole 211. Further, in the region on the outer peripheral side of the front rotor through hole 211 in the front plate 21, the first to fourth bolts B1 to B4 are located at positions corresponding to the first to fourth bolt holes S13, S23, S33, and S43. Four first to fourth bolt through holes 212a to 212d through which the shaft portion penetrates are formed.

The sprocket 22 is integrally formed of a boiled metal material, and has a sprocket body 25 formed in a substantially disk shape and a plurality of tooth portions 26 protruding from the outer peripheral side of the rear end portion of the sprocket body 25. And have. A timing chain (not shown) is wound around the tooth portion 26, cooperates with the crankshaft (not shown) via the timing chain, and rotates synchronously with the crankshaft.

The sprocket body 25 is formed at a substantially central position with a rear rotor through hole 251 through which the rear boss portion 305 of the rotor body 30 penetrates. Here, the rear-side rotor through hole 251 is set to have a slightly larger diameter than the rear-side boss portion 305 protruding from the rear end portion of the rotor main body 30. As a result, the rear side boss portion 305 of the vane rotor 3 housed inside the housing 2 faces the outside through the rear side rotor through hole 251. Further, in the region on the outer peripheral side of the rear rotor through hole 251 in the sprocket body 25, the first to fourth bolts B1 to B4 are located at positions corresponding to the first to fourth bolt holes S13, S23, S33, and S43. Female screw holes 252a to 252d are formed in which the male screw portions mesh with each other.

Further, a first lock hole H1 and a second lock hole H2 to which the first and second lock pins 611 and 621, which will be described later, can be engaged are formed on the inner surface (front end surface) of the sprocket body 25. The first lock hole H1 is formed in a long groove shape extending along the circumferential direction. The second lock hole H2 is arranged concentrically with the first lock hole H1 and is formed in a substantially circular shape in a plan view.

The vane rotor 3 is integrally formed of a predetermined metal material, and is integrally provided with the rotor main body 30 formed in a substantially cylindrical shape in the central portion and the rotor main body 30 so as to project radially toward the outer peripheral side of the rotor main body 30. It has the first to fourth vanes V1 to V4 and the like. Further, on the outer peripheral side of the rotor main body 30, a pair of large-diameter portions 31 and a second large-diameter portion 32, which are a pair of large-diameter portions protruding outward in the radial direction, face each other with the rotation axis Z of the vane rotor 3 interposed therebetween. They are arranged point-symmetrically. That is, the second large diameter portion 32 is arranged on the opposite side of the first large diameter portion 31 with the rotation shaft Z of the vane rotor 3 interposed therebetween.

The rotor main body 30 has a substantially bottomed cylindrical shape that opens toward the front, and has a tubular portion 301 for supplying and discharging each hydraulic pressure by the first and second hydraulic circuits 51 and 52, which will be described later, and the tubular portion. It is provided so as to close the rear end side of the 301, and has an end wall 302 for fastening the vane rotor 3 with the cam bolt 4. Further, on the rear end side of the end wall 302, a cylindrical camshaft receiving portion 303 that can be fitted to the rotor connecting portion 1a of the camshaft 1 is formed with an opening.

The tubular portion 301 is formed with a retard side oil hole 301a and an advance angle side oil hole 301b at positions on both sides in the circumferential direction sandwiching the first to fourth vanes V1 to V4. That is, the passage constituent member 6 described later is inserted into the inner peripheral side of the tubular portion 301, and the oil passages 511, 512 and the oil holes 301a, 302b described later are formed inside the passage constituent member 6. The hydraulic oil is supplied and discharged to the retard chamber Re or the advance chamber Ad, which will be described later, via the above. Further, the depth of the tubular portion 301 is set sufficiently large with respect to the insertion amount of the passage constituent member 6, and the head of the cam bolt 4 is located between the end wall 302 and the tip of the passage constituent member 6 in the axial direction. A bolt accommodating space 33 capable of accommodating the portion 4a is defined.

The end wall 302 has a substantially flat shape, and a cam bolt hole 302a through which the shaft portion 4b of the cam bolt 4 penetrates is formed through at a substantially central position along the axial direction. That is, the vane rotor 3 is fastened to the end of the camshaft 1 by seating the head portion 4a of the cambolt 4 penetrating the cambolt hole 302a on the front end surface of the end wall 302.

The first to fourth vanes V1 to V4 are arranged in the first to fourth operating chambers A1 to A4 (see FIGS. 3 to 5) formed between the circumferential directions of the first to fourth shoes S1 to S4, respectively. To. Further, at the tips of the first to fourth vanes V1 to V4, similar to the first to fourth shoes S1 to S4, a seal groove having a substantially rectangular cross section that opens outward in the radial direction is along the axial direction. Is formed. A vane-side seal member 27 having a substantially prismatic shape is mounted in the seal groove.

Here, the supply and discharge of the hydraulic oil to the retard chamber Re and the advance chamber Ad is performed via the first hydraulic circuit 51. The first hydraulic circuit 51 includes a retard side oil passage 511 and an advance angle side oil passage 512 provided in the passage component 6 inserted inside the rotor main body 30 (cylindrical portion 301) of the vane rotor 3. It has a retard side oil hole 301a and an advance angle side oil hole 301b that communicate the retard angle side oil passage 511 and the advance angle side oil passage 512 with the retard angle chamber Re and the advance angle chamber Ad. That is, in the first hydraulic circuit 51, one of the retard side oil passage 511 and the advance angle side oil passage 512 is connected to the discharge passage 54 of the oil pump 53 via the first electromagnetic valve 513. , The other oil passages 511 and 512 are connected to the drain passage 55.

The retard angle side oil passage 511 includes a retard angle side connection passage 511a provided along the internal axial direction of the passage constituent member 6 and an annular groove 511b provided on the outer periphery of the front end portion of the retard angle side connection passage 511a. It communicates with the retard side oil hole 301a through the oil hole 301a. Similarly, the advance angle side oil passage 512 includes the advance angle side connection passage 512a provided in parallel with the retard angle side connection passage 511a along the internal axial direction of the passage constituent member 6, and the advance angle side connection passage 512a. It communicates with the advance angle side oil hole 301b through the annular groove 512b provided on the outer periphery of the front end portion of the above.

The first solenoid valve 513 is a proportional control valve having 4 ports and 3 positions, and is based on a control signal from an electronic control unit (ECU) (not shown) that is output based on the detection results of various mounted sensors. The connection between the oil passages 511 and 512 and the passages 54 and 55 is selectively switched and controlled. As a result, hydraulic oil is selectively supplied from the discharge passage 54 of the oil pump 53 to the retard chamber Re or the advance chamber Ad via one oil passage 511, 512, and the other oil passage 511, 512. The hydraulic oil in the retard chamber Re or the advance chamber Ad is discharged from the drain passage 55 through the drain passage 55.

Further, the first and second large diameter portions 31 and 32 have a pair of locking mechanisms that hold the relative rotation phase of the vane rotor 3 with respect to the housing 2 (sprocket 22) in a predetermined intermediate phase (position shown in FIG. 3). Certain first and second lock mechanisms 61 and 62 are provided. The "predetermined intermediate phase" is an arbitrary circumferential position between the rotation position on the latest retard side (position shown in FIG. 4) and the rotation position on the most advanced angle side (position shown in FIG. 5). It means that it can be arbitrarily changed according to the specifications of the valve timing control device.

The first lock mechanism 61 includes a first lock pin 611 corresponding to a first lock member that can engage with the first lock hole H1, and a first spring 612 that urges the first lock pin 611 toward the sprocket 22 side. , Equipped with. The first lock pin 611 has a substantially bottomed cylindrical shape, is slidably accommodated in the first accommodating hole 310 penetrating the first large diameter portion 31 in the axial direction, and is slidably accommodated in the first accommodating hole 310 so as to advance toward the sprocket 22 side. 1 Engage with the lock hole H1. The first spring 612 is precompressed between the first lock pin 611 and the front plate 21, and the urging force based on this precompression urges the first lock pin 611 toward the sprocket 22 side.

Similar to the first lock mechanism 61, the second lock mechanism 62 has a second lock pin 621 corresponding to a second lock member that can engage with the second lock hole H2, and the second lock pin 621 on the sprocket 22 side. It is provided with a second spring 622 that urges the sprocket. The second lock pin 621 has a substantially bottomed cylindrical shape, is slidably accommodated in the second accommodating hole 320 penetrating the second large diameter portion 32 in the axial direction, and advances to the sprocket 22 side. 2 Engage with the lock hole H2. The second spring 622 is precompressed between the second lock pin 621 and the front plate 21, and the urging force based on this precompression urges the second lock pin 621 toward the sprocket 22 side.

As described above, in the first and second lock mechanisms 61 and 62, when the first and second lock holes H1 and H2 and the first and second lock pins 611 and 621 coincide with each other in the circumferential direction, the first and second lock mechanisms 61 and 62, respectively. 2 The tips of the first and second lock pins 611 and 621 are pushed into the first and second lock holes H1 and H2 based on the urging force of the springs 612 and 622. As a result, a so-called locked state is established in which the relative rotation between the housing 2 and the vane rotor 3 is restricted.

Here, the first and second lock mechanisms 61 and 62 are operated and controlled through the second hydraulic circuit 52 as shown in FIG. The second hydraulic circuit 52 operates on the supply passage 521 branched from the discharge passage 54 of the oil pump 53, the discharge passage 522 communicating with the drain passage 55, and the first and second lock holes H1 and H2. It has a supply / discharge passage 523 for supplying / discharging oil. That is, in the second hydraulic circuit 52, the connection between the supply / discharge passage 523 and one of the supply passage 521 and the discharge passage 522 is selectively switched via the second solenoid valve 524.

The supply / discharge passage 523 includes an axial oil passage 6a provided inside the passage component 6 and first and second radial oil passages 6b and 6c formed through the tubular portion 301 of the rotor main body 30. It has a bolt accommodating space 33 that communicates the first and second radial oil passages 6b and 6c with the axial oil passage 6a. One end of the axial oil passage 6a is connected to the second solenoid valve 524, and the other end faces the bolt accommodating space 33. One end of the first and second radial oil passages 6b and 6c faces the bolt accommodating space 33, and the other end is connected to the first and second lock holes H1 and H2.

In this way, hydraulic oil is supplied to the first and second lock holes H1 and H2 via the supply / discharge passage 523, and the hydraulic pressure acts on the tips of the first and second lock pins 611 and 621. By this hydraulic pressure, the first and second lock pins 611 and 621 are pushed away. As a result, the first and second lock pins 611 and 621 are separated from the first and second lock holes H1 and H2, and the locked state is released.

FIG. 3 is a cross-sectional view of the valve timing control device cut along the line AA of FIG. 2, showing a locked state in an intermediate phase. FIG. 4 is a cross-sectional view of the valve timing control device cut along the line AA of FIG. 2, and shows a diagram showing the most retarded angle state. FIG. 5 is a cross-sectional view of the valve timing control device cut along the line AA of FIG. 2, and is a view showing the maximum advance angle state.

As shown in FIGS. 3 to 5, the housing 2 has a cylindrical housing body 20 having both ends open in the axial direction, a front plate (not shown) that closes an opening on the front end side of the housing body 20, and a housing. It has a sprocket 22 that closes the opening on the rear end side of the main body 20. The housing main body 20 is provided with the first to fourth shoes S1 to S4, which are four shoes protruding toward the inner peripheral side, integrally with the housing main body 20 at substantially equal intervals in the circumferential direction. .. The first to fourth shoes S1 to S4 have a substantially trapezoidal shape in a plan view and are relatively wide. The first to fourth bolt holes S13 on the first to fourth root portions S11, S21, S31, and S41, respectively. , S23, S33, S43 are formed. Further, seal grooves that open inward in the radial direction are formed in the first to fourth tip portions S12, S22, S32, and S42 of the first to fourth shoes S1 to S4. A shoe-side seal member 24 is arranged in the seal groove. That is, the shoe-side sealing member 24 is in sliding contact with the outer peripheral surface of the rotor body 30 of the vane rotor 3, so that the first to fourth operating chambers A1 to A4 are liquidtightly defined between the shoes S1 to S4. To.

Further, a first notch S14 recessed inward is formed at the circumferential end of the first shoe S1 on the fourth shoe S4 side in the first tip S12. The first notch portion S14 is set to the radial width WR2 corresponding to the radial width WR1 of the first large diameter portion 31. Then, of the ends of the first shoe S1 on the fourth shoe S4 side, the remaining portion on the first root portion S11 side excluding the first notch portion S14 is the first contact surface with the first vane V1. The vane contact surface S15 is formed. The first vane contact surface S15 is provided so as to overlap the first bolt hole S13 in the circumferential direction. Further, the first corner radius R1 formed between the first vane contact surface S15 and the inner peripheral surface of the housing body 20 is formed by the first tip portion S12 and the first root portion S11 in the first notch portion S14. It is set to be smaller than the second corner radius R2 formed between them.

Due to such a configuration, only the first vane V1 abuts on the first shoe S1, and the first large diameter portion 31 does not abut. In other words, in a state where the first vane V1 is in contact with the first shoe S1, a first gap C1 is formed by the first notch S14 between the first shoe S1 and the first large diameter portion 31 in the circumferential direction. It is supposed to be done. That is, the retarded angle chamber Re at the most advanced angle phase in the first operating chamber A1 is defined by the first gap C1.

Similarly, a second notch S24 recessed inward is formed at the circumferential end of the second shoe S2 on the third shoe S3 side in the second tip S22. The second notch portion S24 is set to the radial direction WR4 corresponding to the radial direction width WR3 of the second large diameter portion 32. Then, of the ends of the second shoe S2 on the third shoe S3 side, the remaining portion on the second root portion S21 side excluding the second notch portion S24 is the second contact surface with the second vane V2. The vane contact surface S25 is formed. The second vane contact surface S25 is provided so as to overlap the second bolt hole S23 in the circumferential direction. Further, the first corner radius R1 formed between the second vane contact surface S25 and the inner peripheral surface of the housing body 20 is formed by the second tip portion S22 and the second root portion S21 in the second notch portion S24. It is set to be smaller than the second corner radius R2 formed between them.

Due to this configuration, only the second vane V2 abuts on the second shoe S2, and the second large diameter portion 32 does not abut. In other words, in a state where the second vane V2 is in contact with the second shoe S2, a second gap C2 is formed by the second notch S24 between the second shoe S2 and the second large diameter portion 32 in the circumferential direction. It is supposed to be done. That is, the advance angle chamber Ad at the latest retardation phase in the second operating chamber A2 is defined by the second gap C2.

Further, on one side of the vane rotor 3 in the rotation direction of the first root portion S11 of the first shoe S1, that is, at the end portion on the advance angle side, a built-up portion S16 that bulges in a stepped manner toward the advance angle side is provided. ing. A positioning recess S17 used for positioning the housing body 20 and the sprocket 22 is formed on the outer peripheral side of the built-up portion S16 so as to open outward in the radial direction. The positioning recess S17 has a groove shape having a constant width across flats along the radial direction, and the housing body 20 and the sprocket 22 have a press-fitting engagement with the positioning pin 28 provided on the inner surface of the sprocket 22. For relative positioning.

In the vane rotor 3, the first to fourth vanes V1 to V4, which are four vanes protruding radially, are integrally formed on the outer peripheral side of the rotor main body 30 formed in a substantially cylindrical shape. The first to fourth vanes V1 to V4 have a circumferential width from the first to fourth tip portions S12, S22, S32, and S42 sides toward the first to fourth root portions S11, S21, S31, and S41, respectively. It is formed in a nearly trapezoidal shape in a plan view, which gradually narrows. Further, at the tips of the first to fourth vanes V1 to V4, similar to the first to fourth shoes S1 to S4, a seal groove having a substantially rectangular cross section that opens outward in the radial direction is provided along the axial direction. Is formed. A vane-side seal member 34 having a substantially prismatic shape is installed in the seal groove. That is, when the vane-side sealing member 27 is in sliding contact with the inner peripheral surface of the housing body 20, the first to fourth actuating chambers A1 to A4 are liquidtight as the retarded angle chamber Re and the advance angle chamber Ad, which will be described later, respectively. It is partitioned.

Of the 1st to 4th vanes V1 to V4, the 1st and 2nd vanes V1 and V2 have the first and second large diameters protruding from the outer peripheral side of the rotor main body 30 in a constant region in the circumferential direction. It extends radially outward from the outer peripheral side of the portions 31 and 32. On the other hand, the third and fourth vanes V3 and V4 extend directly outward in the radial direction from the outer peripheral side of the rotor main body 30 corresponding to the small diameter portion. The circumferential width of the first and second vanes V1 and V2 is set to be larger than the circumferential width of the third and fourth vanes V3 and V4.

Further, the first vane V1 corresponds to one end of the vane rotor 3 in the rotational direction from the center position of the circumferential width of the first large diameter portion 31 in the first large diameter portion 31 (1st shoe S1 side ( It is placed unevenly at the end (advanced side). In other words, a series of first planes V10 that are continuous in the radial direction over the circumferential end surface of the first vane V1 on the first shoe S1 side and the circumferential end surface of the first large diameter portion 31 on the first shoe S1 side. Is formed. On the other hand, the second vane V2 is on the second shoe S2 side corresponding to the other end of the vane rotor 3 in the rotational direction from the center position of the circumferential width of the second large diameter portion 32 in the second large diameter portion 32. It is unevenly arranged at the end (on the retard side). In other words, a series of second planes V20 that are continuous in the radial direction over the circumferential end surface of the second vane V2 on the second shoe S2 side and the circumferential end surface of the second large diameter portion 32 on the second shoe S1 side. Is formed. In this way, the first and second vanes V1 and V2 extending from the first and second large diameter portions 31 and 32 are circumferentially within the region of the circumferential width of the first and second large diameter portions 31 and 32, respectively. They are arranged unevenly toward each other in the direction.

The first and second large diameter portions 31 and 32 are set to a circumferential width smaller than the circumferential width of the first and second operating chambers A1 and A2, respectively, from the latest retard angle position shown in FIG. Relative rotation of the vane rotor 3 to the most advanced angle position shown in FIG. 4 is possible. Further, the first and second large diameter portions 31 and 32 have a radial width of about ½ of the radial width of the first to fourth shoes S1 to S4 (first to fourth operating chambers A1 to A4). It is set. The first large-diameter portion 31 is accommodated and arranged between the first shoe S1 and the fourth shoe S4 in the circumferential direction, that is, in the circumferential region of the first operating chamber A1, and the first large-diameter portion 31 is accommodated and arranged in the entire area of the relative rotation of the vane rotor 3. 1 The lock hole H1 is always covered. On the other hand, the second large-diameter portion 32 is accommodated and arranged between the second shoe S2 and the third shoe S3 in the circumferential direction, that is, in the circumferential region of the second operating chamber A2, and is accommodated and arranged in the entire area of the relative rotation of the vane rotor 3. 2 The lock hole H2 is always covered.

Upon relative rotation of the vane rotor 3 with respect to the housing 2, the shoe-side sealing member 24 provided on the first to fourth shoes S1 to S4 is in sliding contact with the outer peripheral surface of the rotor main body 30 to form the first to fourth vanes V1 to V4. The provided vane-side sealing member 34 is in sliding contact with the inner peripheral surface of the housing body 20. As a result, the space between the first to fourth shoes S1 to S4 in the circumferential direction is the retard angle operating chamber (hereinafter, abbreviated as "retarded chamber") Re and the advance angle operating chamber (hereinafter, "advanced chamber"). It is abbreviated as) Ad and is partitioned liquidtly. Then, the valve timing control device is operated and controlled by selectively supplying hydraulic oil from the first hydraulic circuit 51 to the retard chamber Re or the advance chamber Ad.

Inside the tubular portion 301 of the rotor main body 30, the first to fourth root portions S11, S21, which are located substantially in the center in the axial direction and are on the retarded chamber Re side of the first to fourth vanes V1 to V4, At the circumferential positions adjacent to S31 and S41, four retard angle side oil holes 301a that can communicate with each retard angle chamber Re are formed through along the radial direction. As a result, hydraulic oil is supplied and discharged to each retard angle chamber Re via each retard angle side oil hole 301a.

Similarly, inside the tubular portion 301 of the rotor main body 30, the first to fourth root portions S11 on the advancing chamber Ad side of the first to fourth vanes V1 to V4 are located substantially at the center in the axial direction. , S21, S31, and S41 are adjacent to each other in the circumferential direction, and four advance angle side oil holes 301b that can communicate with each advance angle chamber Ad are formed through along the radial direction. As a result, hydraulic oil is supplied and discharged to each advance chamber Ad via each advance side oil hole 301b.

Further, the bolt accommodating space 33 and the first lock hole H1 are communicated between the first advance angle side oil hole 301b and the first retard angle side oil hole 301a in the circumferential direction, and the first lock hole H1 is communicated with the first lock hole H1 via the supply / discharge passage 523. The first radial oil passage 6b used for supplying and discharging hydraulic oil to the lock hole H1 is formed to penetrate substantially in the radial direction. Similarly, between the circumferential direction of the second advance angle side oil hole 301b and the second retard angle side oil hole 301a, the bolt accommodating space 33 and the second lock hole H2 are communicated with each other via the supply / discharge passage 523. The second radial oil passage 6c used for supplying and discharging the hydraulic oil to the second lock hole H2 is formed to penetrate substantially in the radial direction. As a result, hydraulic oil is supplied to the first and second lock holes H1 and H2 via the first and second radial oil passages 6b and 6c, respectively, and the locked state is released.

The inner surface of the sprocket 22 is a circumferential position that opens into the first and second operating chambers A1 and A2, respectively, and is inside more than 1/2 of the radial width of the first and second operating chambers A1 and A2. First and second lock holes H1 and H2 are formed at radial positions on the peripheral side. The first lock hole H1 has a slightly elongated groove shape in a plan view, and the bottom surface is formed in a two-step step shape descending from the advance angle side to the retard angle side. The second lock hole H2 has a substantially circular shape in a plan view and is provided on a concentric circle with the first lock hole H1. It is formed in a staircase pattern. Then, in the valve timing control device according to the present embodiment, the vane rotor 3 is moved to the retard side by the alternating torque from the most advanced phase shown in FIG. 4, and becomes the intermediate phase shown in FIG. The second lock pins 611 and 621 engage with the first and second lock holes H1 and H2, respectively, and the rotation of the vane rotor 3 is restricted.

FIG. 6 is an enlarged cross-sectional view of a main part of the valve timing control device cut along the line CC of FIG. 5, and shows the states of the first and second lock pins 611 and 621 in the maximum advance angle state. The figure is shown. FIG. 7 shows a diagram showing the states of the first and second lock pins 611 and 621 when rotated slightly to the retard side from the state of FIG. FIG. 8 shows a diagram showing the states of the first and second lock pins 611 and 621 when rotated further to the retard side from the state of FIG. 7. FIG. 9 shows a diagram showing the states of the first and second lock pins 611 and 621 when the state of FIG. 8 is further rotated to the retard side and the intermediate phase is reached. FIG. 10 is an enlarged cross-sectional view of a main part of the valve timing control device cut along the line BB of FIG. 3, in which the first and second lock pins 611 and 621 are completely engaged in the intermediate phase. Is shown in the figure.

As shown in FIGS. 6 to 10, the first and second lock pins 611 and 621 have the first and second accommodating holes 310, which are provided in the first and second large diameter portions 31 and 32 of the vane rotor 3, respectively. It is housed in the 320 so as to be slidable along the axial direction. The first and second lock pins 611 and 621 are urged toward the sprocket 22 side based on the urging forces of the first and second springs 612 and 622 seated on the front plate 21, respectively.

The first lock hole H1 is formed in a long groove shape slightly extending along the rotation direction of the vane rotor 3, and is formed in a stepped shape descending in two steps in the circumferential direction toward the retard angle side. That is, the first lock hole H1 is a first bottom surface H11a one step down from the inner side surface 220 with the inner side surface 220 of the sprocket 22 as the uppermost step, and a lowermost step further down one step from the first bottom surface H11a. It has two bottom surfaces H12a.

The first bottom surface H11a is set sufficiently smaller than the area of the tip surface (end surface of the first engaging portion 611b) of the first lock pin 611, and the tip surface (first engaging portion 611b) of the first lock pin 611 is set. Only a part of the end face) is configured to be abuttable. Further, on the side edge of the first bottom surface H11a on the advance angle side, a first side edge H11b that rises vertically from the first bottom surface H11a to the inner side surface 220 of the sprocket 22 is formed.

On the other hand, the second bottom surface H12a extends slightly along the circumferential direction and is set to be larger than the area of the tip surface (end surface of the first engaging portion 611b) of the first lock pin 611, and the first lock pin 611 has a second bottom surface H12a. The entire tip surface (end surface of the first engaging portion 611b) is configured to be abuttable. Further, on the side edge of the second bottom surface H12a on the advance angle side, a second side edge H12b that rises vertically from the second bottom surface H12a to the first bottom surface H11a is formed, and at the same time, a retard side edge of the second bottom surface H12a is formed. A third side edge H12c that rises vertically from the second bottom surface H12a to the inner side surface 220 of the sprocket 22 is formed on the side edge. As shown in FIG. 10, the circumferential width WP1 of the second bottom surface H12a is set to be larger than the circumferential width WP2 of the tip surface (end surface of the first engaging portion 611b) of the first lock pin 611. .. That is, in a state where the tip surface of the first lock pin 611 (the end surface of the first engaging portion 611b) is in contact with the second bottom surface H12a, the tip surface of the first lock pin 611 is placed between the tip surface and the second side edge H12b. The first circumferential gap CX1, which is a sufficiently large circumferential gap of about 1/2 of (the end surface of the first engaging portion 611b), is formed.

Similarly, the second lock hole H2 is formed in a substantially circular shape in a plan view (see FIG. 5), and is formed in a stepped shape that descends in two steps in the circumferential direction toward the retard side. That is, the second lock hole H2 is a first bottom surface H21a one step down from the inner side surface 220 with the inner side surface 220 of the sprocket 22 as the uppermost step, and a lowermost step further down one step from the first bottom surface H21a. It has two bottom surfaces H22a.

The first bottom surface H21a is set sufficiently smaller than the area of the tip surface (end surface of the second engaging portion 621b) of the second lock pin 621, and the tip surface of the second lock pin 621 (second engaging portion 621b) is set. Only a part of the end face) is configured to be abuttable. Further, on the side edge of the first bottom surface H21a on the advance angle side, a first side edge H21b that rises vertically from the first bottom surface H21a to the inner side surface 220 of the sprocket 22 is formed.

On the other hand, the second bottom surface H22a has a circular shape in a plan view, and is set to have substantially the same shape and area as the tip surface of the second lock pin 621 (the end surface of the second engaging portion 621b). The entire tip surface (end surface of the second engaging portion 621b) is configured to be abuttable. Further, on the side edge of the second bottom surface H22a on the advance angle side, a second side edge H22b that rises vertically from the second bottom surface H22a to the first bottom surface H21a is formed, and at the same time, on the retard side of the second bottom surface H22a. A third side edge H22c that rises vertically from the second bottom surface H22a to the inner side surface 220 of the sprocket 22 is formed on the side edge. Then, as shown in FIG. 10, the circumferential width WP3 of the second bottom surface H22a is set to be substantially the same as the circumferential width WP4 of the tip surface (end surface of the first engaging portion 611b) of the first lock pin 611. There is. That is, in a state where the tip surface of the first lock pin 611 (the end surface of the first engaging portion 611b) is in contact with the second bottom surface H22a, there is a slight circumferential gap between the first lock pin 611 and the third side edge H22c. A two-circumferential gap CX2 is formed.

Hydraulic oil is introduced into the first and second lock holes H1 and H2 via the second hydraulic circuit 52, and the hydraulic pressure of the hydraulic oil is the first described later in the first and second lock pins 611 and 621. , Acts on the second step portions 611c and 621c. As a result, the first and second lock pins 611 and 621 retract against the urging forces of the first and second springs 612 and 622, respectively, and separate from the first and second lock holes H1 and H2. The locked state by the first and second lock pins 611 and 621 is released.

The first lock pin 611 has a large diameter first pin body 611a that slides in the first accommodation hole 310, and the first pin body 611a is reduced in diameter via a first step portion 611c on the tip end side. It is provided and has a small-diameter first engaging portion 611b for engaging with the first lock hole H1. Specifically, the first pin body 611a has a cylindrical shape having a constant outer diameter in the axial direction, the front end side facing the front plate 21 is open, and the rear end side facing the sprocket 22 is closed. Further, a first spring accommodating portion 611d is formed on the inner peripheral side of the first pin main body 611a, and the first spring 612 is accommodated in the first spring accommodating portion 611d. The first engaging portion 611b has a substantially columnar shape, and its outer diameter is set to be smaller than that of the first pin main body 611a and smaller than the inner diameter of the first lock hole H1 (second bottom surface H12a). Then, when the vane rotor 3 rotates from the most advanced phase to the retard side, as shown in FIGS. 6 to 10, the first engaging portion 611b is the first and second bottom surfaces H11a of the first lock hole H1. , H12a is gradually contacted, and finally the outer peripheral surface of the first engaging portion 611b is in contact with the third side edge H12c, thereby restricting further movement of the vane rotor 3 to the retard side. Further, the first step portion 611c functions as a pressure receiving surface for receiving the hydraulic pressure of the hydraulic oil introduced into the first lock hole H1. That is, when the hydraulic pressure acts on the first step portion 611c, the first lock pin 611 retracts against the urging force of the first spring 612, and the first engaging portion 611b disengages from the first lock hole H1. ..

Similarly, the second lock pin 621 is contracted via a large-diameter second pin main body 621a that slides in the second accommodating hole 320 and a second step portion 621c on the tip end side of the second pin main body 621a. It has a small diameter second engaging portion 621b provided in a diameter shape and used for engaging with the second lock hole H2. Specifically, the second pin main body 621a has a cylindrical shape having a constant outer diameter in the axial direction, and an opening is formed on the front end side facing the front plate 21. Further, a second spring accommodating portion 621d is formed on the inner peripheral side of the second pin main body 621a, and the second spring 622 is accommodated in the second spring accommodating portion 621d. The second engaging portion 621b has a substantially columnar shape, and its outer diameter is set to be smaller than that of the second pin main body 621a and smaller than the inner diameter of the second lock hole H2 (second bottom surface H22a). Then, when the vane rotor 3 rotates from the most advanced angle position to the retard angle side, as shown in FIGS. 6 to 10, the second engaging portion 621b is the first and second bottom surfaces of the second lock hole H2. The outer peripheral surface of the second engaging portion 621b finally abuts on the third side edge H22c by gradually abutting on H21a and H22a, thereby restricting further movement of the vane rotor 3 to the retard side. .. Further, the second step portion 621c functions as a pressure receiving surface for receiving the hydraulic pressure of the hydraulic oil introduced into the second lock hole H2. That is, when hydraulic pressure acts on the second step portion 621c, the second lock pin 621 retracts against the urging force of the second spring 622, and the second engaging portion 621b separates from the second lock hole H2. do.

(Operation control of valve timing control device)
Hereinafter, the operation control of the valve timing control device according to the present embodiment will be described with reference to FIGS. 3 to 10.

In the valve timing control device according to the present embodiment, when the ignition is turned off and the engine is stopped, a control current is energized from an ECU (not shown) to the first solenoid valve 513 immediately before the engine is completely stopped. As a result, in the first solenoid valve 513, one of the retard side oil passage 511 or the advance angle side oil passage 512 is communicated with the discharge passage 54 of the oil pump 53, and the other of the oil passages 51 and 512 is connected to the drain passage 55. To communicate with. In this way, the ECU detects the relative rotation position of the vane rotor 3 based on the information of various sensors, and supplies the hydraulic oil to either the retard chamber Re or the advance chamber Ad based on this, thereby causing the vane rotor 3 to work. , As shown in FIG. 3, rotation control is performed up to a predetermined intermediate phase between the most advanced phase and the latest retard phase.

At the same time, a control current is applied to the second solenoid valve 524 from an ECU (not shown), and the supply / discharge passage 523 and the discharge passage 522 communicate with each other. As a result, the hydraulic oil in the first and second lock holes H1 and H2 is discharged from the discharge passage 522 to the oil pan 56 through the drain passage 55 through the supply / discharge passage 523, and the first and second lock holes H1. , The pressure inside H2 becomes low. As a result, as shown in FIG. 10, the first and second lock pins 611 and 621 are urged toward the sprocket 22 by the urging force of the first and second springs 622, and the first and second lock holes H1 are respectively. , H2 will be engaged.

In this state, the outer peripheral surface of the first engaging portion 611b of the first lock pin 611 comes into contact with the third side edge H12c of the first lock hole H1, so that the movement of the vane rotor 3 to the retard side is restricted. .. Further, the outer peripheral surface of the second engaging portion 621b of the second lock pin 621 comes into contact with the second side edge H22b of the second lock hole H2, so that the movement of the vane rotor 3 to the advance angle side is restricted. As a result, the vane rotor 3 is held in a predetermined intermediate phase as shown in FIG.

On the other hand, as described above, when the ignition is turned off when the engine is stopped, the vane rotor 3 does not return to the intermediate phase, but stops in the state of the maximum advance phase as shown in FIGS. 5 and 6, for example. I may end up doing it. In this case, it operates as follows when the engine is restarted.

That is, when the ignition is turned on from the state of the maximum advance phase as shown in FIG. 6 and the cranking is started, at the initial stage of this cranking, the valve spring of the exhaust valve is referred to the camshaft 1. The positive and negative alternating torque generated by the spring force is input. Then, when a positive torque of the alternating torque is input, the vane rotor 3 slightly rotates to the retard side, and as shown in FIG. 7, the first lock pin is based on the urging force of the first spring 612. 611 advances, and the first engaging portion 611b of the first lock pin 611 comes into contact with the first bottom surface H11a of the first lock hole H1. Subsequently, when a negative torque of the alternating torque is input and a torque on the advance side acts on the vane rotor 3, the outer peripheral surface of the first engaging portion 611b of the first lock pin 611 becomes the first lock hole H1. It abuts on the first side edge H11b of the bottom surface H11a, and the movement of the vane rotor 3 on the advance side is restricted (see FIG. 7).

After that, a positive torque is input again, and the torque on the retard side acts on the vane rotor 3, so that the vane rotor 3 further rotates to the retard side. Then, as shown in FIG. 8, the first lock pin 611 further advances based on the urging force of the first spring 612, and the first engaging portion 611b of the first lock pin 611 locks first. It abuts on the second bottom surface H12a of the hole H1. Subsequently, when a negative torque is input again, the outer peripheral surface of the first engaging portion 611b of the first lock pin 611 comes into contact with the second side edge H12b of the second bottom surface H12a of the first lock hole H1 and the vane rotor. The movement on the advance side of 3 is restricted (see FIG. 8). As described above, in the valve timing control device according to the present embodiment, the first engaging portion 611b of the first lock pin 611 engages with the first lock hole H1 in a so-called ratchet manner, so that the vane rotor 3 is on the advance side. The vane rotor 3 gradually rotates to the retard side while restricting the movement of the vane rotor 3.

Subsequently, when a positive torque is input again and a torque on the retard side acts on the vane rotor 3, as shown in FIG. 9, the end surface of the first engaging portion 611b of the first lock pin 611 is on the second bottom surface H12a. Slides to move to an intermediate position in the circumferential direction on the second bottom surface H12a. At the same time, the second lock pin 621 advances based on the urging force of the second spring 622, and the second engaging portion 621b of the second lock pin 621 comes into contact with the first bottom surface H21a of the second lock hole H2. Subsequently, when a negative torque is input again, the outer peripheral surface of the second engaging portion 621b of the second lock pin 621 abuts on the first side edge H21b of the first bottom surface H21a of the second lock hole H2, and the vane rotor The movement on the advance side of 3 is restricted (see FIG. 9).

After that, a positive torque is input again, and the torque on the retard side acts on the vane rotor 3, so that the vane rotor 3 further rotates to the retard side. Then, as shown in FIG. 10, the end surface of the first engaging portion 611b of the first lock pin 611 slides on the second bottom surface H12a and slides on the third side edge H12c of the second bottom surface H12a. Contact. At the same time, the second lock pin 621 further advances based on the urging force of the second spring 622, and the second engaging portion 621b of the second lock pin 621 comes into contact with the second bottom surface H22a of the second lock hole H2. Along with this, the outer peripheral surface of the second engaging portion 621b of the second lock pin 621 comes into contact with the second side edge H22b of the second bottom surface H22a of the second lock hole H2 (see FIG. 10). In this way, also for the second lock pin 621, the second engaging portion 621b engages with the second lock hole H2 in a so-called ratchet manner, thereby restricting the movement of the vane rotor 3 on the advance side while restricting the movement of the vane rotor 3 on the advance side. 3 further rotates to the retard side.

Finally, the first engaging portion 611b abuts on the third side edge H12c of the second bottom surface H12a, and the second engaging portion 621b abuts on the second side edge H22b of the second bottom surface H22a. The lock pins 611 and 621 are stretched in the circumferential direction, and the rotation of the vane rotor 3 is restricted. As a result, the vane rotor 3 is held in an intermediate phase as shown in FIG. 3, that is, a predetermined intermediate phase between the latest retard phase shown in FIG. 4 and the most advanced phase shown in FIG. ..

(Action and effect of this embodiment)
In the conventional valve timing control device, the first and second large diameter portions 31, 32 are configured to overlap (oppose) the second and fourth shoes S2 and S4 in the radial direction. In other words, the second and fourth shoes S2 and S4 are configured to be in sliding contact with the first and second large diameter portions 31, 32. Therefore, the pressure receiving areas of the first and third vanes V1 and V3 facing each advance chamber Ad are reduced by the thickness (diametrical dimension) of the first and second large diameter portions 31 and 32. It was difficult to suppress the fluttering of the vane rotor 3 caused by the alternating torque input via the camshaft 1.

On the other hand, the valve timing control device for the internal combustion engine according to the present embodiment can solve the problem of the conventional valve timing control device by achieving the following effects.

The valve timing control device for an internal combustion engine according to the present embodiment has a cylindrical portion (housing body 20) formed in a tubular shape and a first side portion that closes one end side of the tubular portion (housing body 20) in the axial direction. (Front plate 21), a second side portion (sprocket 22) that closes the other end side of the tubular portion (housing body 20) in the axial direction, and a radial inside from the inner peripheral side of the tubular portion (housing body 20). A plurality of shoes (first to fourth shoes S1 to S4) including the first shoe S1 and the second shoe S2 protruding toward the cylinder, and a plurality of shoes (first to fourth shoes) adjacent to each other in the circumferential direction in the tubular portion 301. The first operating chamber A1 and the second operating chamber A2 formed between S1 to S4) and the first operating chamber A1 provided on the first side portion (front plate 21) or the second side portion (sprocket 22). A housing 2 having a first lock hole H1 and a second lock hole H2 that open axially toward the second operating chamber A2 and rotating in synchronization with the crankshaft of an internal combustion engine, and a cylindrical portion (a tubular portion). A vane rotor that is rotatably arranged on the inner peripheral side of the housing body 20) and rotates integrally with the camshaft 1, is fixed to the camshaft 1, and has a plurality of shoes (first to fourth shoes S1 to S4). The rotor body 30 is slidably contacted with the rotor body 30, and is arranged within the range of the first operating chamber A1 and the second operating chamber A2. 1 First accommodating hole that opens axially in the first large diameter portion 31 and the second large diameter portion 32 that cover the lock hole H1 and the second lock hole H2, and the first large diameter portion 31 and the second large diameter portion 32. The first vane V1 and the first vane V1 and the second accommodating hole 320 projecting radially outward from the outer peripheral side of the first large diameter portion 31 and the second large diameter portion 32 to separate the first operating chamber A1 and the second operating chamber A2. A vane rotor 3 having a second vane V2, and a first lock hole H1 and a first lock hole H1 and a first lock hole H1 and a second are movably accommodated inside the first accommodating hole 310 and the second accommodating hole 320 and at a predetermined rotation position of the vane rotor 3 with respect to the housing 2. 2 A first lock member (first lock pin 611) and a second lock member (second lock pin 621) to be inserted into the lock hole H2 are provided.

As described above, in the present embodiment, the first and second large diameter portions 31, 32 are arranged in the circumferential direction of the first and second operating chambers A1 and A2. That is, the first and second large diameter portions 31, 32 are configured to overlap (oppose) the shoes S1 to S4 defining the first and second operating chambers A1 and A2 in the circumferential direction. In other words, in the relative rotation range of the vane rotor 3, each shoe S1 to S4 is configured to radially overlap (oppose) the outer peripheral surface of the rotor body 30 which is a small diameter portion of the vane rotor 3. ing.

According to the above configuration, it is possible to configure the pressure receiving surfaces of the first and second vanes V1 and V2 including the first and second large diameter portions 31 and 32. That is, as compared with the conventional valve timing control device in which the first and second large diameter portions 31 and 32 are arranged so as to face each shoe S1 to S4 in the radial direction, the first and second vanes V1 and V2 The pressure receiving area (radial width) can be expanded. As a result, the torque of the vane rotor 3 generated based on the hydraulic pressure acting on the first and second vanes V1 and V2 is increased, and the fluttering of the vane rotor 3 generated by the alternating torque can be suppressed.

In other words, the pressure receiving surfaces of the first and second vanes V1 and V2 including the first and second large diameter portions 31 and 32 can be configured, so that the pressure receiving surface is higher than that of the conventional valve timing control device. The housing 2 and the vane rotor 3 can be miniaturized by the volume of the first and second operating chambers A1 and A2 increased by the pressure receiving surface. As a result, the valve timing control device can be miniaturized, and the mountability on a vehicle or engine can be improved.

Further, in the present embodiment, the first side portion and the second side portion are the first plate-shaped member (front plate 21) and the second plate-shaped member (front plate 21) provided separately from the tubular portion (housing body 20). The first shoe S1 is a sprocket 22), and the first shoe S1 is a first bolt B1 for fastening a tubular portion (housing body 20) to a first plate-shaped member (front plate 21) and a second plate-shaped member (sprocket 22). Has a first bolt hole S13 through which the first vane V1 abuts, and the contact surface (first vane contact surface S15) of the first shoe S1 with which the first vane V1 abuts overlaps with the first bolt hole S13 in the circumferential direction.

As described above, in the present embodiment, the first vane contact surface S15 is configured to overlap with the first bolt hole S13 in the circumferential direction. In other words, the first shoe S1 is formed with the first vane contact surface S15 at a position where the rigidity is increased by the first bolt B1. Therefore, it is possible to suppress the generation of a moment due to the contact (collision) of the first vane V1 in the first shoe S1. As a result, it is possible to suppress a problem that the front plate 21 and the sprocket 22 provided separately from the housing main body 20 are out of phase.

Further, in the present embodiment, when the vane rotor 3 rotates to one side in the circumferential direction with respect to the housing 2, the first vane V1 comes into contact with the first shoe S1, and the first large diameter portion 31 comes into contact with the first shoe S1. Do not abut.

For example, when the first vane V1 comes into contact with the tip end side of the first shoe S1, a rotational moment around the first bolt B1 is generated in the first shoe S1. As a result, the phase of the housing body 20 may shift with respect to the front plate 21 and the sprocket 22 formed separately from the housing body 20.

Therefore, in the present embodiment, the first vane V1 is in contact with the first shoe S1, and the first large diameter portion 31 is not in contact with the first shoe S1. In other words, with respect to the housing 2, in the vane rotor 3, only the first vane V1 on the tip side is located on the radial outer side of the first shoe S1 on the first root portion S11 side, that is, the fastening point by the first bolt B1. It will come into contact with a position close to. In this way, by bringing the first vane V1 into contact with the position close to the fastening point by the first bolt B1, the housing body 20 is opposed to the front plate 21 and the sprocket 22 provided separately from the housing body 20. It is possible to suppress the problem that the phase of the is out of phase.

Further, in the present embodiment, there is a gap (first gap C1) between the first large diameter portion 31 and the first shoe S1 in a state where the first vane V1 and the first shoe S1 are in contact with each other.

As described above, in the present embodiment, the first gap C1 is formed between the first large diameter portion 31 and the first shoe S1 when the first vane V1 and the first shoe S1 are in contact with each other. Has been done. As a result, only the first vane V1 on the tip side of the vane rotor 3 comes into contact with the first root portion S11 side located on the radial outer side of the first shoe S1, that is, the position close to the fastening point by the first bolt B1. become. In this way, by bringing the first vane V1 into contact with the position close to the fastening point by the first bolt B1, the housing body 20 is opposed to the front plate 21 and the sprocket 22 provided separately from the housing body 20. It is possible to suppress the problem that the phase of the is out of phase.

Further, in the present embodiment, the second large diameter portion 32 and the second vane V2 are arranged on opposite sides of the first large diameter portion 31 and the first vane V1 with the rotation shaft Z of the vane rotor 3 interposed therebetween. There is.

As described above, in the present embodiment, the first large diameter portion 31 and the first vane V1 and the second large diameter portion 32 and the second vane V2 are arranged so as to be symmetrical with respect to the rotation axis Z. As a result, the rotational balance of the vane rotor 3 is improved, and the valve timing control device is smoothly operated.

Further, in the present embodiment, the first vane V1 is arranged on one end side in the rotation direction of the vane rotor 3 with respect to the center position of the circumferential width of the first large diameter portion 31, and the second vane V2 has the second large diameter. It is arranged on the other end side of the vane rotor 3 in the rotational direction from the center position of the circumferential width of the portion 32.

When the first and second vanes V1 and V2 are arranged at intermediate positions in the circumferential direction of the first and second large diameter portions 31, 32, respectively, the shoes S1 to S4 are extended in the circumferential direction to obtain the maximum. It is necessary to bring the first and second vanes V1 and V2 into contact with each other in the advance phase or the latest retard phase. In this case, the extension of the shoes S1 to S4 in the circumferential direction increases the weight of the housing 2, which may lead to an increase in the weight of the valve timing control device.

Therefore, in the present embodiment, the first vane V1 is eccentrically arranged on one end side in the rotation direction, and the second vane V2 is eccentrically arranged on the other end side in the rotation direction. As a result, when the vane rotor 3 rotates, the first vane V1 rotates to the first shoe S1 when the vane rotor 3 rotates to one end side in the rotation direction, and the second vane rotor 3 rotates to the other end side in the rotation direction. The vane V2 easily comes into contact with the first shoe S1. As a result, it is possible to suppress the extension of each shoe S1 to S4, and it is possible to suppress the weight increase of the valve timing control device.

In the present embodiment, the first vane V1 is arranged at one end of the vane rotor 3 in the first large diameter portion 31 in the rotation direction, and the second vane V2 is arranged in the rotation direction of the vane rotor 3 in the second large diameter portion 32. Although the one arranged at the other end of the above is illustrated, the present invention is not limited to this. That is, if the first vane V1 is unevenly arranged on one end side in the rotation direction of the vane rotor 3 and the second vane V2 is unevenly arranged on the other end side in the rotation direction of the vane rotor 3, the valve timing control device described above. The action and effect of the present embodiment such as suppression of weight increase can be exhibited, and the specific arrangement of the first and second vanes V1 and V2 can be arbitrarily changed.

Further, in the present embodiment, the first vane V1 is arranged at one end of the vane rotor 3 in the rotational direction in the circumferential direction of the first large diameter portion 31, and the second vane V2 is the circumference of the second large diameter portion 32. In the direction, it is arranged at the other end of the vane rotor 3 in the rotation direction.

As described above, in the present embodiment, the first and second vanes V1 are arranged in the first and second large diameter portions 31 and 32 most deviatedly in the rotation direction (circumferential direction) of the vane rotor 3. As a result, the extension of each shoe S1 to S4 can be minimized, and the weight increase of the valve timing control device can be suppressed more effectively.

Further, in the present embodiment, the circumferential end surface of the first vane V1 on the first shoe S1 side and the circumferential end surface of the first large diameter portion 31 on the first shoe S1 side are a series of radial ends. The circumferential end surface of the second vane V2 on the second shoe S2 side and the circumferential end surface of the second large diameter portion 32 on the second shoe S2 side having one plane V10 are a series of radial ends. It has two planes V20.

As described above, in the present embodiment, the contact surfaces of the first and second vanes V1 and V2 with respect to the first and second shoes S1 and S2 are formed flat as the first and second planes V10 and V20. ing. As a result, the contact area of the first and second vanes V1 and V2 with respect to the first and second shoes S1 and S2 is expanded, the input load on the first and second vanes V1 and V2 can be reduced, and the valve can be valved. The durability of the timing control device can be improved.

Further, in the present embodiment, the second vane V2 comes into contact with the second shoe S2 when the vane rotor 3 rotates to the other side in the circumferential direction with respect to the housing 2.

As described above, in the present embodiment, the second vane V2 comes into contact with the second shoe S1 when the vane rotor 3 rotates on the other end side in the circumferential direction. In other words, different vanes V1 and V2 are in contact with each other in the most advanced phase and the latest retard phase. As a result, the load input to each vane V1 and V2 can be dispersed, and metal fatigue in the vane rotor 3 can be reduced. As a result, the durability of the valve timing control device can be improved.

Further, since it is not necessary to expand and form only one vane in order to counter the load by the above load distribution, the weight of the vane rotor 3 can be reduced and the rotational balance can be improved.

Further, in the present embodiment, the first corner radius R1 formed at the boundary between the first root portion S11 and the inner peripheral side of the tubular portion (housing body 20) is the first root portion S11 and the first tip portion. It is smaller than the second corner radius R2 formed at the boundary with S12.

As described above, in the present embodiment, since the first corner radius R1 is formed to be relatively smaller than the second corner radius R2, the contact area of the first vane V1 that abuts on the first shoe S1 is determined. It is possible to secure a larger size. As a result, the load bearing capacity of the vane rotor 3 can be improved, and the durability of the valve timing control device can be improved.

Further, in the present embodiment, the housing 2 further has a third operating chamber A3 formed between a plurality of shoes S1 to S4 adjacent to each other in the circumferential direction in the tubular portion (housing body 20), and the vane rotor 3 has a vane rotor 3. A third vane V3 that protrudes radially outward from the outer peripheral surface of the rotor body 30 and separates the third operating chamber A3 is further provided, and the circumferential width of the first vane V1 is larger than the circumferential width of the third vane V3. Largely set, the third vane V3 does not abut on the plurality of shoes S1 to S4.

As described above, in the present embodiment, the third vane V3 does not abut on the shoes S1 to S4, so that the first vane V3 abuts on the shoes S1 to S4 (specifically, "shoe S1"). It is necessary to secure the strength of vane V1. Therefore, in the present embodiment, since the circumferential width of the first vane V1 is set to be larger than the circumferential width of the third vane V3, the strength of the first vane V1 is secured and the durability of the vane rotor 3 is ensured. Can be improved.

Further, the valve timing control device for the internal combustion engine according to the present embodiment has a tubular portion (housing body 20) formed in a tubular shape and a tubular portion (housing body 20) protruding inward in the radial direction from the inner peripheral side. The housing 2 has a plurality of shoes (first to fourth shoes S1 to S4) and rotates in synchronization with the crankshaft of the internal combustion engine, and the tubular portion (housing body 20) rotates relative to the inner peripheral side. A vane rotor that is possibly arranged and rotates integrally with the camshaft 1, a rotor body 30 fixed to the camshaft 1, and a plurality of large diameter portions (first, first) protruding radially outward from the rotor body 30. 2 large diameter portions 31, 32) and a plurality of large diameter portions (first and second large diameter portions 31, 32) projecting radially outward from the outer peripheral side, and the inner peripheral side of the tubular portion (housing body 20). A vane rotor 3 having a plurality of vanes (first to fourth vanes V1 to V4) in sliding contact with the vane, and a plurality of locks arranged in a plurality of large diameter portions (first and second large diameter portions 31, 32). 1. The second lock holes H1 and H2 are provided, and the plurality of large diameter portions (first and second large diameter portions 31, 32) are provided between the circumferential directions of the plurality of shoes (first to fourth shoes S1 to S4). It is arranged in a plurality of operating chambers (first to fourth operating chambers A1 to A4) formed in the above, and constantly covers a plurality of lock holes (first and second lock holes H1 and H2).

As described above, in the present embodiment, the first and second large diameter portions 31, 32 are arranged in the first and second operating chambers A1 and A2, and constantly cover the first and second lock holes H1 and H2. It is composed. That is, the first and second large diameter portions 31, 32 are configured to overlap (oppose) the shoes S1 to S4 defining the first and second operating chambers A1 and A2 in the circumferential direction. In other words, in the relative rotation range of the vane rotor 3, each shoe S1 to S4 is configured to radially overlap (oppose) the outer peripheral surface of the rotor body 30 which is a small diameter portion of the vane rotor 3. ing.

According to the above configuration, it is possible to configure the pressure receiving surfaces of the first and second vanes V1 and V2 including the first and second large diameter portions 31 and 32. That is, as compared with the conventional valve timing control device in which the first and second large diameter portions 31 and 32 are arranged so as to face each shoe S1 to S4 in the radial direction, the first and second vanes V1 and V2 The pressure receiving area (radial width) can be expanded. As a result, the torque of the vane rotor 3 generated based on the hydraulic pressure acting on the first and second vanes V1 and V2 is increased, and the fluttering of the vane rotor 3 generated by the alternating torque can be suppressed.

In other words, the pressure receiving surfaces of the first and second vanes V1 and V2 including the first and second large diameter portions 31 and 32 can be configured, so that the pressure receiving surface is higher than that of the conventional valve timing control device. The housing 2 and the vane rotor 3 can be miniaturized by the volume of the first and second operating chambers A1 and A2 increased by the pressure receiving surface. As a result, the valve timing control device can be miniaturized, and the mountability on a vehicle or engine can be improved.

Further, in the present embodiment, at least a part of the plurality of vanes (first to fourth vanes V1 to V4) is in contact with the plurality of shoes (first to fourth shoes S1 to S4). The large diameter portions (first and second large diameter portions 31, 32) do not come into contact with the plurality of shoes (first to fourth shoes S1 to S4).

As described above, in the present embodiment, at least a part of the vanes (first and second vanes V1 and V2) of the first to fourth vanes V1 to V4 are in contact with the first and second shoes S1 and S2. Therefore, the first and second large diameter portions 31 and 32 are configured so as not to come into contact with the first and second shoes S1 and S2. In other words, with respect to the housing 2, only the first and second vanes V1 and V2 provided on the tip side of the vane rotor 3 are close to the fastening points by the first and second bolts B1 and B2. 2 The shoes S1 and S2 come into contact with the first and second root portions S11 and S21. As a result, the moments generated in the first and second shoes S1 and S2 due to the contact between the first and second vanes V1 and V2 are reduced, and the phase of the housing body 20 is shifted with respect to the front plate 21 and the sprocket 22. It is possible to suppress the trouble that ends up.

Further, in the present embodiment, the plurality of large diameter portions have a pair of large diameter portions (first and second large diameter portions 31, 32) provided with the rotation shaft Z of the vane rotor 3 interposed therebetween. A pair of vanes (1st and 2nd vanes V1, V2) extending from a pair of large diameter portions (1st and 2nd large diameter portions 31, 32) is a pair of large diameter portions (1st and 2nd large diameter portions). Within the region of the circumferential width of the diameter portions 31, 32), they are arranged unevenly toward each other in the circumferential direction.

As described above, in the present embodiment, the first and second vanes V1 and V2 extending from the first and second large diameter portions 31 and 32 are the regions having the circumferential width of the first and second large diameter portions 31 and 32. Within, they are arranged unevenly toward the side closer to each other in the circumferential direction. Therefore, when the vane rotor 3 is rotated, the first vane V1 abuts on the first shoe S1 when the vane rotor 3 is rotated to one side, and the second vane V2 is the first shoe when the vane rotor 3 is rotated to the other side. It becomes easy to come into contact with S1. As a result, as described above, the extension of each shoe S1 to S4 in the circumferential direction is suppressed, and the weight increase of the valve timing control device can be suppressed.

[Second Embodiment]
11 to 13 show a second embodiment of the valve timing control device for an internal combustion engine according to the present invention, and the arrangement of the first and second vanes V1 and V2 according to the first embodiment is changed. Since the basic configuration other than the changes is the same as that of the first embodiment, the same configurations as those of the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

11 to 13 are vertical cross-sectional views of the valve timing control device according to the second embodiment of the present invention, FIG. 11 shows a locked state in an intermediate phase, and FIG. 12 shows a most retarded angle state. FIG. 13 is a diagram showing the maximum advance angle state.

As shown in FIGS. 11 to 13, in the valve timing control device according to the present embodiment, the first and second vanes V1 and V2 are located at intermediate positions in the circumferential direction of the first and second large diameter portions 31, 32, respectively. Is located in. Specifically, the first and second vanes V1 and V2 are formed so as to project radially outward from the substantially central position in the circumferential direction of the first and second large diameter portions 31, 32, respectively.

Further, with the arrangement of the first and second vanes V1 and V2, the first root portion S11 of the first shoe S1 that comes into contact with the first vane V1 in the maximum advance angle phase shown in FIG. 13 is the first operating chamber A1. It is formed so as to extend toward the side. Specifically, the first root portion S11 has a constant radial width corresponding to the radial width of the first vane V1 in the entire circumferential direction, and when the vane rotor 3 rotates to the advance angle side, It is provided so as to overlap the first large diameter portion 31 in the radial direction. Then, the circumferential end surface of the first root portion S11 on the first operating chamber A1 side is in contact with the circumferential end surface of the first vane V1 on the first shoe S1 side over the entire radial direction, and the first vane contact surface S15. To configure.

Here, the radial width WR5 of the first root portion S11 is set to be slightly smaller than the radial width WR6 of the first vane V1. That is, for example, as shown in FIG. 11, in a state where the first root portion S11 and the first large diameter portion 31 overlap each other in the radial direction, between the first root portion S11 and the first large diameter portion 31 in the radial direction. , The first radial gap CR1 is formed. In other words, with the first root portion S11 and the first large diameter portion 31 overlapping in the radial direction, the retard angle chamber Re is not divided into the first shoe concubine SR1 and the first vane concubine VR1, and the first shoe The concubine SR1 and the first vane concubine VR1 are configured to be able to communicate with each other through the first radial clearance CR1.

Further, the circumferential width WP5 of the first root portion S11 extending toward the first operating chamber A1 is wider than the circumferential width WP6 of the first large diameter portion end portion 311 extending toward the first shoe S1 side from the first vane V1. It is set slightly larger. That is, in the maximum advance angle phase shown in FIG. 13, a predetermined first circumferential gap CP1 is formed between the circumferential direction of the first tip portion S12 of the first shoe S1 and the first large diameter portion 31. It has become.

Further, in the present embodiment, the build-up portion S16 according to the first embodiment is abolished, and the positioning recess S17 provided in the build-up portion S16 is provided on the outer peripheral side of the first root portion S11. .. As a result, the first shoe S1 does not bulge on both sides in the circumferential direction, and the configuration of the first shoe S1 is simplified. Further, by preventing the first shoe S1 from bulging on both sides in the circumferential direction, the first shoe S1 is also made smaller and lighter.

Further, in the first large diameter portion 31 of the first large diameter portion 31, the retard angle chamber Re and the retard angle side oil passage 511 are provided at substantially the center position in the circumferential direction at one end portion 311 of the first large diameter portion extending toward the first shoe S1. The retard side oil hole 301a that communicates is formed along the radial direction. Then, the hydraulic oil guided to the retard angle chamber Re through the retard angle side oil hole 301a is bifurcated through the first radial gap CR1 as shown by an arrow F in FIG. 13, for example, in the first shoe. It is guided to both the concubine SR1 and the first vane concubine VR1.

Further, in the first large diameter portion 31, the first vane V1 and the first accommodating hole 310 are provided so as to overlap each other in the radial direction. In other words, the first vane V1 is formed so as to project on the outer peripheral side of the first accommodating hole 310. As a result, the advance angle chamber Ad and the advance chamber Ad and the first accommodating hole 310 are compared with the case where the first accommodating hole 310 is unevenly arranged in the one end portion 311 of the first large diameter portion or the other end portion 312 of the first large diameter portion. The distance to the retarded chamber Re, that is, the sealing allowance SL1 of the first accommodating hole 310 is configured to be relatively large.

Similar to the first root portion S11, the second root portion S21 of the second shoe S2 that abuts on the second vane V2 in the most retarded phase shown in FIG. 12 is formed so as to extend toward the second operating chamber A2 side. Has been done. Specifically, the second root portion S21 has a constant radial width corresponding to the radial width of the second vane V2 in the entire circumferential direction, and when the vane rotor 3 rotates to the retard side, It is provided so as to overlap the second large diameter portion 32 in the radial direction. Then, the circumferential end surface of the second root portion S21 on the second operating chamber A2 side abuts on the circumferential end surface of the second vane V2 on the second shoe S2 side over the entire radial direction, and the second vane contact surface S25. To configure.

Here, the radial width WR7 of the second root portion S21 is set to be slightly smaller than the radial width WR8 of the second vane V2. That is, for example, as shown in FIG. 12, in a state where the second root portion S21 and the second large diameter portion 32 overlap each other in the radial direction, between the second root portion S21 and the second large diameter portion 32 in the radial direction. , The second radial gap CR2 is formed. In other words, with the second root portion S21 and the second large diameter portion 32 overlapping in the radial direction, the advance chamber Ad is not divided into the second shoe concubine SR2 and the second vane concubine VR2, and the second shoe The concubine SR2 and the second vane concubine VR2 are configured to be able to communicate with each other through the second radial clearance CR2.

Further, the circumferential width WP7 of the second root portion S21 extending to the second operating chamber A2 side is the other end portion of the second large diameter portion extending toward the second shoe S2 side from the second vane V2 in the second large diameter portion 32. It is set slightly larger than the circumferential width WP8 of 322. That is, in the latest retard angle phase shown in FIG. 12, a predetermined second circumferential gap CP2 is formed between the circumferential direction of the second tip portion S22 of the second shoe S2 and the second large diameter portion 32. It has become.

Further, in the second large diameter portion 32, the second vane V2 and the second accommodating hole 320 are provided so as to overlap each other in the radial direction. In other words, the second vane V2 is formed so as to project on the outer peripheral side of the second accommodating hole 320. As a result, the advance angle chamber Ad and the advance chamber Ad and the second accommodating hole 320 are arranged from the second accommodating hole 320 as compared with the case where the second accommodating hole 320 is unevenly arranged at the one end portion 321 of the second large diameter portion or the other end portion 322 of the second large diameter portion. The distance to the retarded chamber Re, that is, the sealing allowance SL2 of the second accommodating hole 320 is configured to be relatively large.

As described above, in the valve timing control device for the internal combustion engine according to the present embodiment, the first vane V1 is at an intermediate position in the circumferential direction of the first large diameter portion 31, and is in the radial direction of the first accommodating hole 310. The first shoe S1 provided on the outside is provided on the radial outer side of the first tip portion S12 that is in sliding contact with the rotor main body 30 and the first tip portion S12, and is provided on the outer side in the radial direction and is in contact with the first vane V1. And have.

As described above, in the present embodiment, the first vane V1 is provided at an intermediate position in the circumferential direction of the first large diameter portion 31. As a result, the rotational balance of the vane rotor 3 is improved, and the valve timing control device is smoothly operated.

Further, in the present embodiment, the first vane V1 is provided on the radial outer side of the first accommodating hole 310. As a result, the advance angle chamber Ad and the advance chamber Ad and the first accommodating hole 310 are compared with the case where the first accommodating hole 310 is unevenly arranged in the one end portion 311 of the first large diameter portion or the other end portion 312 of the first large diameter portion. It is possible to extend the distance to the retarded chamber Re, that is, the sealing allowance SL1 of the first accommodating hole 310. As a result, leakage of hydraulic oil generated between the first accommodating hole 310 and the advance angle chamber Ad and the retard angle chamber Re can be suppressed.

In the present embodiment, as an example of arranging the first vane V1 at the circumferential intermediate position of the first large diameter portion 31, the first vane V1 is arranged at substantially the center position in the circumferential direction of the first large diameter portion 31. The thing was illustrated and explained. However, the "intermediate position in the circumferential direction" in the present invention means an arbitrary circumferential position except for the "one end and the other end in the circumferential direction" as exemplified in the first embodiment. , It is not limited to the "center position in the circumferential direction".

Further, in the present embodiment, the first side portion and the second side portion are the first plate-shaped member (front plate 21) and the second plate-shaped member (front plate 21) provided separately from the tubular portion (housing body 20). The first shoe S1 is a sprocket 22), and the first shoe S1 is a first bolt B1 for fastening a tubular portion (housing body 20) to a first plate-shaped member (front plate 21) and a second plate-shaped member (sprocket 22). Has a first bolt hole S13 through which the first bolt hole S13 penetrates, and the first root portion S11 overlaps with the first large diameter portion 31 in the radial direction in a state of being in contact with the first vane V1.

As described above, in the present embodiment, the first root portion S11 and the first large diameter portion 31 overlap in the radial direction in a state where the first root portion S11 of the first shoe S1 and the first vane V1 are in contact with each other. It is composed. With such a configuration, it is possible to bring only the first vane V1 into contact with the first shoe S1. That is, only the first vane V1 comes into contact with the first shoe S1 at a position close to the fastening point by the first bolt B1. In this way, by bringing the first vane V1 into contact with the position close to the fastening point by the first bolt B1, the housing body 20 is opposed to the front plate 21 and the sprocket 22 provided separately from the housing body 20. It is possible to suppress the problem that the phase of the is out of phase.

Further, in the present embodiment, the first root portion S11 has a gap (first radial gap CR1) between the first large diameter portion 31 and the first large diameter portion 31 in a state of being in contact with the first vane V1. The first large diameter portion 31 is a first supply oil passage (sliding angle side oil hole 301a) communicating with a first retard angle operating chamber (sliding angle chamber Re) defined by the first shoe S1 and the first vane V1. Have.

As described above, in the present embodiment, in a state where the first root portion S11 of the first shoe S1 and the first vane V1 are in contact with each other, between the first root portion S11 and the first large diameter portion 31 in the radial direction. The configuration is such that the first radial gap CR1 is formed. With such a configuration, the retard angle chamber Re is not divided into the first shoe side chamber SR1 and the first vane side chamber VR1, and the first shoe side chamber SR1 and the first vane side chamber VR1 are communicated with each other by the first radial clearance CR1. It becomes possible to do. As a result, the hydraulic oil introduced into the retard angle chamber Re from the retard angle side oil hole 301a is supplied to both the first shoe side chamber SR1 and the first vane side chamber VR1 through the first radial clearance CR1. It can be used for smooth operation of the valve timing control device.

The present invention is not limited to the configuration of the above-described embodiment, and can be freely changed according to the specifications and costs of the applicable object as long as the above-mentioned functions and effects of the present invention can be exhibited.

As the valve timing control device for the internal combustion engine based on the embodiment described above, for example, the one described below can be considered.

That is, in one aspect of the internal combustion engine valve timing control device, the tubular portion has a tubular portion, a first side portion that closes one end side of the tubular portion in the axial direction, and the tubular portion. In the tubular portion, a second side portion that closes the other end side in the axial direction of the portion, a plurality of shoes including a first shoe and a second shoe that project radially inward from the inner peripheral side of the tubular portion, and the tubular portion. A first operating chamber and a second operating chamber formed between the plurality of shoes adjacent to each other in the circumferential direction, and the first operating chamber and the second operating chamber provided on the first side portion or the second side portion. A housing that has a first lock hole and a second lock hole that open axially toward the working chamber and rotates in synchronization with the crankshaft of an internal combustion engine, and a relative rotation toward the inner peripheral side of the tubular portion. A vane rotor that is possibly arranged and rotates integrally with the camshaft, and is within the range of the rotor main body fixed to the camshaft and in which the plurality of shoes are in sliding contact, and the first operating chamber and the second operating chamber. A first large-diameter portion and a second large-diameter portion that are arranged, project radially outward from the rotor body, and cover the first lock hole and the second lock hole over the entire relative rotation range between the housing and the vane rotor. The diameters of the first accommodating hole and the second accommodating hole that open in the axial direction in the first large-diameter portion and the second large-diameter portion, and the outer peripheral side of the first large-diameter portion and the second large-diameter portion. A vane rotor having a first vane and a second vane that project outward in the direction and separate the first operating chamber and the second operating chamber, and movably accommodated inside the first accommodating hole and the second accommodating hole. The vane rotor is provided with a first lock hole and a first lock member and a second lock member inserted into the second lock hole at a predetermined rotation position of the vane rotor with respect to the housing.

In a preferred embodiment of the valve timing control device for an internal combustion engine, the first side portion and the second side portion are a first plate-shaped member and a second plate-shaped member provided separately from the cylindrical portion. The first shoe has a first bolt hole through which a first bolt for fastening the cylindrical portion, the first plate-shaped member, and the second plate-shaped member penetrates, and the first vane hits the first shoe. The contact surface of the first shoe in contact overlaps with the first bolt hole in the circumferential direction.

In another preferred embodiment, in any of the aspects of the valve timing control device of the internal combustion engine, when the vane rotor rotates to one side in the circumferential direction with respect to the housing, the first vane corresponds to the first shoe. The first large diameter portion is in contact with the first shoe and does not come into contact with the first shoe.

In yet another preferred embodiment, in any one of the aspects of the valve timing control device of the internal combustion engine, the first large diameter portion and the first shoe are in contact with the first vane and the first shoe. There is a gap between them.

In yet another preferred embodiment, in any of the aspects of the valve timing control device of the internal combustion engine, the second large diameter portion and the second vane are relative to the first large diameter portion and the first vane. It is arranged on the opposite side of the rotation axis of the vane rotor.

In yet another preferred embodiment, in any of the aspects of the valve timing control device of the internal combustion engine, the first vane is one end of the vane rotor in the rotational direction rather than the center position of the circumferential width of the first large diameter portion. The second vane is arranged on the side, and the second vane is arranged on the other end side in the rotational direction of the vane rotor from the central position of the circumferential width of the second large diameter portion.

In yet another preferred embodiment, in any of the aspects of the valve timing control device of the internal combustion engine, the first vane is arranged at one end of the vane rotor in the rotational direction in the circumferential direction of the first large diameter portion. The second vane is arranged at the other end of the vane rotor in the rotational direction in the circumferential direction of the second large diameter portion.

In yet another preferred embodiment, in any of the aspects of the valve timing control device of the internal combustion engine, the circumferential end surface of the first vane on the first shoe side and the first shoe side of the first large diameter portion. The circumferential end face of the above has a series of first planes continuous in the radial direction, and the circumferential end face of the second vane on the second shoe side and the second shoe side of the second large diameter portion. The circumferential end face has a series of second planes continuous in the radial direction.

In yet another preferred embodiment, in any of the aspects of the valve timing control device of the internal combustion engine, the first vane is at an intermediate position in the circumferential direction of the first large diameter portion and the first accommodating hole. The first shoe is provided on the radial outer side of the rotor body, and the first shoe is provided on the radial outer side of the first tip portion and the first tip portion that is in sliding contact with the rotor body, and is in contact with the first vane. With a part.

In yet another preferred embodiment, in any one of the aspects of the valve timing control device of the internal combustion engine, the first side portion and the second side portion have a first plate shape provided separately from the tubular portion. A member and a second plate-shaped member, the first shoe has a first bolt hole through which a first bolt for fastening the tubular portion, the first plate-shaped member, and the second plate-shaped member penetrates. The first root portion is in contact with the first vane and overlaps with the first large diameter portion in the radial direction.

In yet another preferred embodiment, in any one of the aspects of the valve timing control device of the internal combustion engine, the first root portion is in contact with the first vane in the radial direction with the first large diameter portion. With a gap between them, the first large diameter portion has a first supply oil passage that communicates with a first retard angle operating chamber defined by the first shoe and the first vane.

In yet another preferred embodiment, in any of the aspects of the valve timing controller of the internal combustion engine, the second shoe is the second shoe when the vane rotor rotates to the other side in the circumferential direction with respect to the housing. Contact with.

In yet another preferred embodiment, in any of the aspects of the valve timing control device of the internal combustion engine, the first shoe has a first tip portion that is in sliding contact with the rotor body and a radial outer side of the first tip portion. The first corner radius formed in the boundary portion between the first root portion and the inner peripheral side of the tubular portion is provided with a first root portion that abuts on the first vane. It is smaller than the second corner radius formed at the boundary between the first root portion and the first tip portion.

In yet another preferred embodiment, in any of the aspects of the valve timing control device of the internal combustion engine, the housing is formed between the plurality of shoes adjacent to each other in the circumferential direction in the cylindrical portion. The vane rotor further has a third vane that protrudes radially outward from the outer peripheral surface of the rotor body and separates the third operating chamber, and the circumferential width of the first vane is the third. It is set to be larger than the circumferential width of the vane, and the third vane does not abut on the plurality of shoes.

From another point of view, the valve timing control device for an internal combustion engine based on the above-described embodiment has, as one aspect, a cylindrical portion formed in a cylindrical shape and a radial inner side from the inner peripheral side of the tubular portion. A housing that has a plurality of shoes protruding toward the inside and rotates in synchronization with the crankshaft of an internal combustion engine, and a vane rotor that is rotatably arranged on the inner peripheral side of the cylindrical portion and rotates integrally with the camshaft. The rotor body is fixed to the camshaft, a plurality of large diameter portions projecting radially outward from the rotor body, and the tubular shape protruding radially outward from the outer peripheral side of the plurality of large diameter portions. A vane rotor having a plurality of vanes that are in sliding contact with the inner peripheral side of the portion, a plurality of lock members arranged in the plurality of large diameter portions, and the plurality of lock members provided in the housing and the plurality of lock members can be engaged with each other. A plurality of lock holes are provided, and the plurality of large diameter portions are arranged in a plurality of operating chambers formed between the circumferential directions of the plurality of shoes, and constantly cover the plurality of lock holes.

In a preferred embodiment of the valve timing control device for an internal combustion engine, the plurality of large diameter portions are in contact with the plurality of shoes while at least a part of the plurality of vanes is in contact with the plurality of shoes. do not do.

In another preferred embodiment, in any of the embodiments of the valve timing control device of the internal combustion engine, the plurality of large diameter portions have a pair of large diameter portions provided so as to sandwich the rotation shaft of the vane rotor. The pair of vanes extending from the pair of large diameter portions are arranged unevenly toward each other in the circumferential direction within the region of the circumferential width of the pair of large diameter portions.

1 ... camshaft, 2 ... housing, 20 ... housing body (cylindrical part), 21 ... front plate (first side part), 22 ... sprocket (second side part), H1 ... first lock hole, H2 ... first 2 lock hole, 3 ... vane rotor, 30 ... rotor body, 31 ... first large diameter part, 32 ... second large diameter part, 310 ... first accommodating hole, 320 ... second accommodating hole, 611 ... first lock pin ( 1st lock member), 621 ... 2nd lock pin (2nd lock member), S1 to S4 ... 1st to 4th shoes (multiple shoes), V1 to V4 ... 1st to 4th vanes (multiple vanes) , A1 ... 1st working chamber, A2 ... 2nd working chamber,

Claims (17)

A tubular portion formed in a tubular shape, a first side portion that closes one end side of the tubular portion in the axial direction, a second side portion that closes the other end side of the tubular portion in the axial direction, and the cylinder. The first operation formed between a plurality of shoes including a first shoe and a second shoe protruding radially inward from the inner peripheral side of the shaped portion and the plurality of shoes adjacent to the circumferential portion in the tubular portion. A first lock hole and a second lock provided in the first side portion or the second side portion of the chamber and the second working chamber and opening axially toward the first working chamber and the second working chamber. A housing that has holes and rotates in synchronization with the crankshaft of an internal combustion engine,
A vane rotor that is rotatably arranged on the inner peripheral side of the tubular portion and rotates integrally with the camshaft. The rotor body is fixed to the camshaft and the plurality of shoes are slidably contacted, and the first operation. Arranged within the range of the chamber and the second working chamber, it projects radially outward from the rotor body and covers the first lock hole and the second lock hole over the entire relative rotation range between the housing and the vane rotor. The first large-diameter portion and the second large-diameter portion, the first accommodating hole and the second accommodating hole that open in the axial direction in the first large-diameter portion and the second large-diameter portion, the first large-diameter portion, and the first large-diameter portion. A vane rotor having a first vane and a second vane projecting radially outward from the outer peripheral side of the second large diameter portion and separating the first operating chamber and the second operating chamber.
A first lock member that is movably accommodated inside the first accommodating hole and the second accommodating hole and is inserted into the first lock hole and the second lock hole at a predetermined rotation position of the vane rotor with respect to the housing. And the second lock member,
A valve timing control device for an internal combustion engine, which is characterized by being equipped with. In the valve timing control device for an internal combustion engine according to claim 1.
The first side portion and the second side portion are a first plate-shaped member and a second plate-shaped member provided separately from the tubular portion.
The first shoe has a first bolt hole through which a first bolt for fastening the cylindrical portion, the first plate-shaped member, and the second plate-shaped member penetrates.
A valve timing control device for an internal combustion engine, wherein the contact surface of the first shoe with which the first vane abuts overlaps with the first bolt hole in the circumferential direction. In the valve timing control device for an internal combustion engine according to claim 2.
When the vane rotor rotates to one side in the circumferential direction with respect to the housing, the first vane abuts on the first shoe, and the first large diameter portion does not abut on the first shoe. Valve timing control device for internal combustion engines. In the valve timing control device for an internal combustion engine according to claim 3.
A valve timing control device for an internal combustion engine, characterized in that there is a gap between the first large diameter portion and the first shoe in a state where the first vane and the first shoe are in contact with each other. In the valve timing control device for an internal combustion engine according to claim 1.
The internal combustion engine is characterized in that the second large-diameter portion and the second vane are arranged on opposite sides of the first large-diameter portion and the first vane with the rotation shaft of the vane rotor interposed therebetween. Valve timing control device. In the valve timing control device for an internal combustion engine according to claim 5.
The first vane is arranged on one end side in the rotational direction of the vane rotor with respect to the central position of the circumferential width of the first large diameter portion.
The valve timing control device for an internal combustion engine is characterized in that the second vane is arranged on the other end side in the rotational direction of the vane rotor with respect to the central position of the circumferential width of the second large diameter portion. In the valve timing control device for an internal combustion engine according to claim 6.
The first vane is arranged at one end of the vane rotor in the rotational direction in the circumferential direction of the first large diameter portion.
The valve timing control device for an internal combustion engine is characterized in that the second vane is arranged at the other end of the vane rotor in the rotational direction in the circumferential direction of the second large diameter portion. In the valve timing control device for an internal combustion engine according to claim 7.
The circumferential end face of the first vane on the first shoe side and the circumferential end face of the first large diameter portion on the first shoe side have a series of first planes continuous in the radial direction.
The circumferential end surface of the second vane on the second shoe side and the circumferential end surface of the second large diameter portion on the second shoe side are characterized by having a series of second planes continuous in the radial direction. Valve timing control device for internal combustion engine. In the valve timing control device for an internal combustion engine according to claim 1.
The first vane is provided at an intermediate position in the circumferential direction of the first large-diameter portion and outside the radial direction of the first accommodating hole.
The first shoe is characterized by having a first tip portion that is in sliding contact with the rotor body and a first root portion that is provided radially outside the first tip portion and is in contact with the first vane. Valve timing control device for internal combustion engine. In the valve timing control device for an internal combustion engine according to claim 9.
The first side portion and the second side portion are a first plate-shaped member and a second plate-shaped member provided separately from the tubular portion.
The first shoe has a first bolt hole through which a first bolt for fastening the cylindrical portion, the first plate-shaped member, and the second plate-shaped member penetrates.
A valve timing control device for an internal combustion engine, wherein the first root portion overlaps with the first large diameter portion in the radial direction in a state of being in contact with the first vane. In the valve timing control device for an internal combustion engine according to claim 10.
The first root portion has a gap in the radial direction with the first large diameter portion in a state of being in contact with the first vane.
The valve timing control device for an internal combustion engine, characterized in that the first large diameter portion has a first supply oil passage communicating with a first retard angle operating chamber defined by the first shoe and the first vane. .. In the valve timing control device for an internal combustion engine according to claim 1.
The second vane is a valve timing control device for an internal combustion engine, characterized in that the vane rotor comes into contact with the second shoe when the vane rotor rotates to the other side in the circumferential direction with respect to the housing. In the valve timing control device for an internal combustion engine according to claim 1.
The first shoe has a first tip portion that is in sliding contact with the rotor body, and a first root portion that is provided radially outside the first tip portion and is in contact with the first vane.
The first corner radius formed at the boundary between the first root portion and the inner peripheral side of the tubular portion is the second corner formed at the boundary portion between the first root portion and the first tip portion. A valve timing control device for an internal combustion engine, which is characterized by being smaller than R. In the valve timing control device for an internal combustion engine according to claim 1.
The housing further comprises a third working chamber formed between the plurality of shoes adjacent to each other in the circumferential direction in the cylindrical portion.
The vane rotor further has a third vane that protrudes radially outward from the outer peripheral surface of the rotor body and separates the third working chamber.
The circumferential width of the first vane is set to be larger than the circumferential width of the third vane.
The third vane is a valve timing control device for an internal combustion engine, characterized in that it does not come into contact with the plurality of shoes. A housing having a cylindrical portion formed in a tubular shape and a plurality of shoes protruding radially inward from the inner peripheral side of the tubular portion, and rotating in synchronization with the crankshaft of an internal combustion engine.
A vane rotor that is rotatably arranged on the inner peripheral side of the cylindrical portion and rotates integrally with the camshaft, and has a rotor body fixed to the camshaft and a plurality of vanes that project radially outward from the rotor body. A vane rotor having a large-diameter portion, and a plurality of vanes protruding outward in the radial direction from the outer peripheral side of the plurality of large-diameter portions and in sliding contact with the inner peripheral side of the tubular portion.
A plurality of lock members arranged in the plurality of large diameter portions, and
A plurality of lock holes provided in the housing and to which the plurality of lock members can engage,
Equipped with
The plurality of large-diameter portions are arranged in a plurality of operating chambers formed between the plurality of shoe circumferential directions, and constantly cover the plurality of lock holes. A valve timing control device for an internal combustion engine. .. In the valve timing control device for an internal combustion engine according to claim 15.
A valve timing control device for an internal combustion engine, characterized in that at least a part of the plurality of vanes is in contact with the plurality of shoes, and the plurality of large diameter portions are not in contact with the plurality of shoes. .. In the valve timing control device for an internal combustion engine according to claim 16.
The plurality of large diameter portions have a pair of large diameter portions provided so as to sandwich the rotation shaft of the vane rotor.
The pair of vanes extending from the pair of large diameter portions are characterized in that they are arranged unevenly toward each other in the circumferential direction within the region of the circumferential width of the pair of large diameter portions. Valve timing control device for internal combustion engine.

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