JP7207826B2 - valve timing adjuster - Google Patents

Description

The present invention relates to a valve timing adjusting device that adjusts the opening/closing timing of valves that are opened and closed by a crankshaft of an engine via a camshaft.

Conventionally, as described in Patent Document 1, for example, a valve in which an Oldham's coupling is interposed between a drive-side rotating body rotated by a crankshaft of an engine and a driven-side rotating body rotating integrally with a camshaft. Timing adjustment devices are known. The Oldham's coupling is composed of a guide groove provided on the drive-side rotor, a protrusion provided on the planetary rotor, and an Oldham intermediate body for eccentrically and rotationally synchronizing the guide groove and the protrusion. Two guide grooves are provided on the end face of the drive-side rotor at an angle of 180 degrees in the circumferential direction. Two protrusions are provided on the end surface of the planetary rotor at an angle of 180 degrees in the circumferential direction.

The Oldham's intermediate body is in the shape of an annular plate, and has a pair of engaging projections projecting from its outer peripheral edge and a pair of engaging recessed parts recessed from its inner peripheral edge. The engagement projection engages with the guide groove of the drive-side rotor. The protrusion of the planetary rotor engages with the engagement recess. The engaging projections and the engaging recesses are formed by extending the entire circumference of the Oldham intermediate by 4 or so so that the straight line connecting the two engaging projections and the straight line connecting the two engaging recesses are perpendicular to each other at the axis center of the Oldham intermediate. It is formed in a divided position.

JP 2018-87564 A

By the way, the Oldham intermediate body interposed between the driving-side rotating body and the driven-side rotating body has a predetermined clearance in the thrust direction. In addition, since the Oldham intermediate is supplied with high-temperature lubricating oil from the shaft center side, when the temperature of the Oldham intermediate rises due to an operating state or the like, the temperature in the center is particularly likely to rise. In this case, the vicinity of the inner peripheral edge of the Oldham intermediate body becomes hot and expands, whereas the vicinity of the outer peripheral edge does not expand, so the inner strain acts in the axial direction.

At that time, if the Oldham intermediate is in the form of an ideal flat plate, it will only be deformed by expansion, but since it always has a slight warp in manufacturing, it will be deformed so as to increase the warp. In addition, warping of the inner peripheral edge of the Oldham intermediate body increases, and warping beyond the clearance causes a problem that it collides with surrounding members, causing noise, abnormal wear, and seizure.

The present invention has been created in view of such a point, and its object is to suppress warping of the Oldham intermediate when the temperature rises, thereby suppressing wear and seizure with peripheral members. To provide an adjusting device.

The valve timing adjusting device of the present invention adjusts the opening/closing timing of valves (103, 104) that are opened/closed via a camshaft (102) by a crankshaft (101) of an engine (100). The valve timing adjusting device includes a driving side rotating body (10), a driven side rotating body (20), a planetary rotating body (30), an eccentric shaft (40), an Oldham coupling (50), and a fluid supply section ( 60) and

The drive-side rotating body is rotated by the crankshaft about the same axis as the rotation axis (91) of the camshaft. The driven-side rotating body rotates together with the camshaft around the same axis as the driving-side rotating body. The planetary rotor has a planetary gear portion (31) that meshes with an internal gear portion (21) formed on either the drive side rotor or the driven side rotor. The eccentric shaft supports the planetary rotor rotatably about an eccentric axis (92) displaced parallel to the rotation axis of the camshaft.

The Oldham's coupling includes a first Oldham's coupling (51) provided on either the driven-side rotating body or the driving-side rotating body, a second Oldham's coupling (52) provided on the planetary rotating body, and an annular plate shape. An Oldham intermediate body (53) for eccentrically rotating and synchronizing the first Oldham coupling portion and the second Oldham coupling portion. The fluid supply section supplies the lubricating fluid (O) from the camshaft to the Oldham intermediate body side.

The Oldham intermediate includes an engaging protrusion (54), an engaging recess (55), and a notch groove (56). The engagement protrusion is formed on the outer peripheral edge so as to protrude radially outward, and slidably engages with either the first Oldham's coupling or the second Oldham's coupling. The engaging recess is recessed in the inner peripheral edge and slidably engages with the other of the first Oldham's coupling portion and the second Oldham's coupling portion. The notch groove is formed by notching the inner peripheral edge so as to suppress warping of the Oldham intermediate in the axial direction when the temperature rises.

Since the Oldham intermediate is supplied with a high-temperature lubricating fluid from the shaft center side, when the temperature of the Oldham intermediate rises due to an operating state or the like, the temperature of the center is particularly likely to rise. In the configuration of the present invention, the notched groove is formed by notching the inner peripheral edge of the Oldham intermediate body, so that thermal strain near the inner peripheral edge is relieved in the notched groove when the temperature rises. For this reason, the deformation of the central portion of the Oldham intermediate body that warps in the axial direction is suppressed, and in turn, the wear and seizure between the Oldham intermediate body and the peripheral members can be suppressed.

1 is a sectional view showing a schematic configuration of a valve timing adjusting device according to a first embodiment; FIG. FIG. 2 is a cross-sectional view taken along line II-II of FIG. 1 showing an Oldham coupling portion; It is a perspective view of a planetary rotor showing a second Oldham's coupling portion of the Oldham's coupling. 4(a) is a front cross-sectional view and FIG. 4(b) is a cross-sectional view taken along line bb of FIG. 4(a). FIG. It is front sectional drawing which shows the Oldham intermediate by 2nd Embodiment. It is front sectional drawing which shows the Oldham intermediate by 3rd Embodiment. It is front sectional drawing which shows the Oldham intermediate by 4th Embodiment. It is front sectional drawing which shows the Oldham intermediate by 5th Embodiment. It is front sectional drawing which shows the Oldham intermediate by 6th Embodiment. 10(a) is a front cross-sectional view, and FIG. 10(b) is a cross-sectional view along the line bb of FIG. 10(a). FIG. is.

A plurality of embodiments according to the present invention will be described below with reference to the drawings. In addition, the same code|symbol is attached|subjected to the substantially same component in each embodiment, and description is abbreviate|omitted.
<First embodiment>
[Constitution]
First, a first embodiment of the present invention will be described with reference to FIGS. 1 to 4. FIG. As shown in FIG. 1, the valve timing adjusting device 1 of the first embodiment is provided in a torque transmission path from a crankshaft 101 to a camshaft 102 in a vehicle engine 100, for example. Camshaft 102 opens and closes intake valve 103 or exhaust valve 104 of engine 100 . In some embodiments of the present invention, the valve timing adjustment device 1 adjusts the opening/closing timing of the intake valve 103 .

A valve timing adjusting device 1 includes a phase changing mechanism 2 driven by a motor (not shown). The phase change mechanism 2 is provided with a driving side rotating body 10, a driven side rotating body 20, a planetary rotating body 30, an eccentric shaft 40, an Oldham coupling 50, a fluid supply section 60, and the like.

The drive-side rotor 10 has a housing 11 and a sprocket member 12 . The housing 11 is formed in an annular plate shape, and the sprocket member 12 is formed in a cup shape. The housing 11 and the sprocket member 12 are integrally assembled with a plurality of bolts 13 and rotate around the same rotation axis 91 as the camshaft 102 . The sprocket member 12 has sprocket teeth 14 on its outer periphery and is connected to the crankshaft 101 via a chain 105 wound around the sprocket teeth 14 . As a result, the drive-side rotor 10 is rotated around the rotation axis 91 by the torque of the crankshaft 101 in conjunction with the crankshaft 101 .

The driven-side rotor 20 is coupled to the camshaft 102 by a bolt 15 and rotates integrally with the camshaft 102 about the same rotation axis 91 as the drive-side rotor 10 . A planetary rotor 30 is accommodated inside the driven side rotor 20 , and a planetary gear portion 31 that meshes with the internal gear portion 21 of the driven side rotor 20 is formed on the outer peripheral surface of the planetary rotor 30 . The internal gear portion 21 can be formed on either the driving side rotating body 10 or the driven side rotating body 20, but in this embodiment, it is formed on the inner peripheral surface of the driven side rotating body 20. .

The planetary rotor 30 is supported by a camshaft-side end portion 41 of an eccentric shaft 40 via a first bearing 33 . The camshaft-side end portion 41 of the eccentric shaft 40 rotates around an eccentric axis 92 displaced parallel to the rotation axis 91 of the camshaft 102 on its outer peripheral surface. The end 42 of the eccentric shaft 40 opposite to the cam shaft rotates around the same axis as the rotation axis 91 of the cam shaft 102 . The non-camshaft side end portion 42 is supported by the housing 11 via the second bearing 34 and is connected to the output shaft of the motor via a joint member (not shown).

When the eccentric shaft 40 is rotated by the motor, part of the planetary gear portion 31 meshes with the internal gear portion 21 due to the eccentric rotation of the camshaft side end portion 41, and a meshing portion 32 (see FIG. 2) is formed between the two. is formed. Two recesses 43 are formed in the outer peripheral surface of the camshaft-side end 41 so as to approach each other in the circumferential direction of the eccentric shaft 40 , and leaf springs 44 are mounted in the recesses 43 . The leaf spring 44 urges the planetary rotor 30 radially outward through the first bearing 33 to press the planetary gear portion 31 against the internal gear portion 21 . As a result, the clearance of the meshing portion 32 can be eliminated, and noise such as impact and backlash generated during rotation can be suppressed.

The Oldham coupling 50 includes a first Oldham coupling portion 51 , a second Oldham coupling portion 52 (see FIGS. 2 and 3 ), and an Oldham intermediate body 53 . In this embodiment, as shown in FIGS. 1 and 2, the first Oldham coupling portion 51 is attached to one end face of the sprocket member 12 (the end face on the Oldham intermediate body 53 side) of the drive-side rotor 10 at an angle of 180 degrees. Two recesses are provided at an angle. As shown in FIG. 3 , two second Oldham joints 52 are projected from one end face of the planetary rotor 30 (the end face on the Oldham intermediate body 53 side) at an angle of 180 degrees.

As shown in FIGS. 2 and 4(a), the Oldham intermediate 53 is formed in an annular plate shape. The outer shape is a perfect circle, and the inner shape has curved surfaces with arcuate cross-sections at both end portions in the second direction, and flat planes with linear cross-sections at both end portions in the first direction. In FIG. 4 , the horizontal direction on the page is the first direction, and the vertical direction on the page is the second direction. The Oldham intermediate 53 has a cross-sectional shape as a whole that is point-symmetrical with respect to the axial center C (see FIG. 4A) and line-symmetrical with the straight lines L and M as axes of symmetry. The Oldham intermediate 53 has two engaging projections 54 and two engaging recesses. The engagement protrusion is provided to protrude radially outward from the outer peripheral edge of the Oldham intermediate body 53 and is slidably fitted to the first Oldham joint 51 . The engagement recess 55 is recessed in the inner peripheral edge of the Oldham intermediate body 53, and the second Oldham joint 52 is slidably fitted therein.

As shown in FIG. 4A, a straight line connecting two engaging protrusions 54 is defined as a convex straight line L, and a straight line connecting two engaging recesses 55 is defined as a concave straight line M. As shown in FIG. The convex straight line L extends in the second direction. The concave straight line M extends in the first direction. The engaging convex portion 54 and the engaging concave portion 55 are located at positions where the entire circumference of the Oldham intermediate 53 is divided into four equal parts so that the convex straight line L and the concave straight line M are perpendicular to each other at the axial center C of the Oldham intermediate 53. formed. A predetermined clearance is set between the engaging convex portion 54 and the engaging concave portion 55 in order to allow inclination (deviation angle) of the Oldham intermediate 53 and prevent twisting thereof.

Notch grooves 56 are formed in the inner peripheral edges of the pair of engaging protrusions 54 of the Oldham intermediate body 53 by cutting the inner peripheral edges up to the outline line. The notched groove portion 56 has a substantially rectangular shape in a cross-sectional view, and its width is about one-third that of the engagement convex portion 54 . The notch groove portion 56 is formed to have a size that fits within the engagement convex portion 54 in the circumferential direction and the radial direction. A straight line connecting the two notch grooves 56 is defined as a groove straight line N. As shown in FIG. The groove straight line N coincides with the convex straight line L. FIG.

The Oldham intermediate body 53 rotates synchronously with the sprocket member 12 through the fitting of the engaging convex portion 54 and the first Oldham coupling portion 51, and also engages the engaging concave portion 55 and the second Oldham coupling portion 52. It rotates synchronously with the planetary rotating body 30 via. Further, when the Oldham intermediate body 53 moves in the first direction in FIG. When the Oldham intermediate body 53 moves in the second direction perpendicular to the first direction with respect to the first Oldham joint 51, the engaging protrusion 54 slides in the second direction with respect to the first Oldham joint 51. do. Therefore, the Oldham intermediate body 53 can eccentrically synchronize the rotation of the first Oldham coupling portion 51 and the second Oldham coupling portion 52 .

In the phase changing mechanism 2 configured as described above, when the eccentric shaft 40 is rotated in one direction by the motor, the driven side rotating body 20 shifts to the driving side rotating body 10 through the engagement between the planetary gear portion 31 and the internal gear portion 21 . rotates in one direction relative to As a result, a difference occurs in the rotational phases of both rotors 10 and 20, the camshaft 102 advances in one direction at an angle corresponding to the phase difference, and the opening/closing timing of the intake valve 103 advances. Further, when the eccentric shaft 40 is rotated in the opposite direction by the motor, the driven side rotating body 20 rotates in the opposite direction relative to the driving side rotating body 10, resulting in an angle corresponding to the phase difference between both rotating bodies 10, 20. , the camshaft 102 is retarded in the opposite direction, and the opening/closing timing of the intake valve 103 is retarded.

Next, the fluid supply section 60 will be described. In the fluid supply unit 60 shown in FIG. 1 , lubricating oil O as a lubricating fluid is supplied from the pump unit 61 to the inside of the phase change mechanism 2 via the camshaft 102 . That is, the fluid supply portion 60 has an inflow passage 63 at the joint portion between the cam shaft 102 and the driven side rotating body 20, and the lubricating oil O is introduced from an internal oil passage (hereinafter referred to as a cam shaft oil passage) 62 of the cam shaft 102. It is made to flow into the inside of the sprocket member 12 of the drive-side rotating body 10 through the passage 63 .

The lubricating oil O flows from the internal oil passage 62 to the annular groove 64 formed in the driven rotating body 20 . The lubricating oil O in the annular groove 64 moves radially outward due to centrifugal force while passing through gaps and spaces 67 in the axial direction and the radial direction between the rotating bodies. , and while lubricating friction-generating locations such as the bearings 33 and 34 .

[Effect]
Since the Oldham intermediate 53 is supplied with the high-temperature lubricating oil O from the shaft center side, when the temperature of the Oldham intermediate 53 rises in the operating state in which the high-temperature lubricating oil O flows after the engine is started, the center part The vicinity of the inner peripheral edge of is likely to become hot.

10 and 4, the directions in which the Oldham intermediate 53 is deformed by thermal strain are indicated by solid arrows A and B, and the shape after deformation is indicated by broken lines. In addition, in order to explain the deformation in an easy-to-understand manner, the degree of deformation is illustrated larger than it actually is. For example, as in the Oldham intermediate body 110 of the comparative form shown in FIG. Since the vicinity of the periphery does not expand, the inner strain acts in the axial direction. The portion where the engaging recess 55 is formed can release strain in the circumferential direction as indicated by arrow A.

However, since the portion where the engaging projection 54 is formed has a larger radial width than other portions, the radially inner inner peripheral edge S of the engaging projection 54 (in FIG. 10, the two-dot chain line Thermal strain accumulates in the area enclosed by ). Then, as indicated by an arrow B in FIG. 10(b), the Oldham intermediate 110 warps in the axial direction. The amount of warp in the axial direction of the inner peripheral edge S in this comparative embodiment is illustrated as the amount of warp W2.

On the other hand, according to the first embodiment, as shown in FIG. 4A, not only the portion where the engaging recess 55 is formed but also the notch groove 56 are allowed to deform in the circumferential direction. Therefore, as shown in FIG. 4(b), the warp amount W1 in the axial direction is minimized (W1<W2). In addition, in FIG.4(b), it abbreviate|omits about the line seen on the other side of a cross section. As described above, by intentionally releasing the thermal strain at the notch groove portion 56, the warpage of the inner peripheral edge of the Oldham intermediate 53 can be minimized. For this reason, the Oldham intermediate 53 does not warp beyond the clearance in the axial direction, and problems such as noise, abnormal wear, seizure, etc. due to collision with peripheral members due to warping can be suppressed. can be done.

In the first embodiment, the notched groove portion 56 is formed so as to be point symmetrical with respect to the axial center C. As shown in FIG. Therefore, deformation can be uniformly suppressed in the circumferential direction when the temperature rises, so oblique warping can be suppressed.

In addition, the notch groove 56 is formed in a size that fits in the engagement convex portion 54 in the circumferential direction and the radial direction, and since a part with extremely low rigidity is not formed around the notch groove 56, the shape is stable during high temperature deformation. can ensure the integrity of the

<Second embodiment>
Next, a modification of the Oldham intermediate will be described with reference to FIG. As shown in FIG. 5, the Oldham intermediate 71 of the valve timing device of the second embodiment is partially different in shape from the Oldham intermediate 53 of the first embodiment. The point that the engaging recess 55 is formed is the same.

A pair of outer peripheral protrusions 72 different from the engaging protrusions 54 are formed on the outer peripheral edge of the Oldham intermediate 71 of the second embodiment. The outer peripheral protrusion 72 is provided at a position corresponding to the engagement recess 55 and formed outside the engagement recess 55 . Furthermore, all portions of the inner circumference of the Oldham intermediate 71 where the engaging recess 55 and the notch groove 56 are not formed are formed to have a regular arc shape in cross section.

According to the second embodiment, the same effects as those of the first embodiment can be obtained.

<Third Embodiment>
Next, a modification of the Oldham intermediate will be described with reference to FIG. As shown in FIG. 6, the Oldham intermediate body 74 of the valve timing device of the third embodiment differs from the Oldham intermediate body 71 of the second embodiment in the formation position and the number of notch grooves. In the third embodiment, four notch grooves 75 are provided radially between the engaging projections 54 and the engaging recesses 55 on the inner peripheral edge of the Oldham intermediate body 74 . The angle θ1 formed by the groove straight line N connecting the two point-symmetric cutout grooves 75 and the convex straight line L is approximately 45 degrees. The Oldham intermediate 74 has a cross-sectional shape that is point-symmetrical with respect to the axial center C as a whole and line-symmetrical with the straight lines L and M as axes of symmetry.

According to the third embodiment, the notch groove 75 is not formed at a position corresponding to the engaging protrusion 54, but is formed between the engaging protrusion 54 and the engaging recess 55 in the circumferential direction. . Therefore, deformation in the circumferential direction is allowed in the four notch grooves 75 . As a result, as in the first embodiment, noise caused by warping of the Oldham intermediate body 74, abnormal wear and seizure, etc. can be suppressed.

<Fourth Embodiment>
Next, a modification of the Oldham intermediate will be described with reference to FIG. As shown in FIG. 7, the Oldham intermediate body 76 of the valve timing device of the fourth embodiment differs from the Oldham intermediate body 71 of the second embodiment in that the outer peripheral protrusion 72 is not formed. Along with this, the depth of cut of the engaging recess 55 is slightly small and does not reach the contour line forming a perfect circle. Other configurations are the same as those of the second embodiment.

According to the fourth embodiment, the same effects as those of the first embodiment can be obtained.

<Fifth embodiment>
Next, a modification of the Oldham intermediate will be described with reference to FIG. The Oldham's intermediate body 78 of the fifth embodiment differs from the Oldham's intermediate body 76 of the fourth embodiment in the configurations of the engaging recesses and the notched grooves. The configuration of the engaging convex portion 54 is the same. As shown in FIG. 8, in the Oldham intermediate body 78 of the valve timing device of the fifth embodiment, two engaging recesses 79 are provided in the inner peripheral edge of the Oldham intermediate body 78 in point symmetry with respect to the axis C. ing. Each engaging recess 79 has two sliding surfaces 81 extending in the first direction and facing each other in the second direction, and a curved surface 82 having an arcuate cross-section that is continuous with the opposing sliding surfaces 81 . ing. The second Oldham joint 52 of the planetary rotor 30 is slidably fitted into the engaging recess 79, and the same effects as in the above-described embodiments are achieved.

In the fifth embodiment, the convex straight line L connecting the two engaging convex portions 54 and the concave straight line M connecting the two engaging concave portions 79 intersect at the axial center C of the Oldham intermediate 78 at an angle θ2. ing. The angle θ2 is approximately 70 degrees, not 90 degrees. In the first, second, and fourth embodiments, the arrangement of the engagement projections 54 and the engagement recesses 55 is different from the arrangement in which the entire circumference of the Oldham intermediates 53, 71, 76 is divided into four equal parts.

Furthermore, in the present embodiment, by forming the engaging recesses 79 in the above arrangement, the engaging recesses 79 also function as notch grooves. As described above, one engaging concave portion 79 is formed at a position closer to one engaging convex portion 54 in the circumferential direction compared to the four-part arrangement. Therefore, when the temperature rises, it is possible to suppress the accumulation of thermal strain in the engaging convex portion 54 due to the circumferential deformation of the engaging concave portion 79 . As a result, noise, abnormal wear, seizure, etc. caused by warping of the Oldham intermediate body 78 can be suppressed as in the above-described embodiments.

<Sixth Embodiment>
Next, a modification of the Oldham intermediate will be described with reference to FIG. The Oldham intermediate body 83 of the sixth embodiment differs from the Oldham intermediate body 78 of the fifth embodiment in the position of the engagement concave portion that also serves as the notch groove.

The engaging recesses 84 of the sixth embodiment are spaced further apart in the second direction than in the fifth embodiment. That is, one engaging concave portion 84 is formed at a position closer to one engaging convex portion 54 in the circumferential direction. The angle θ3 formed by the convex straight line L and the concave straight line M is smaller than the angle θ2 in the fifth embodiment (θ3<θ2) and is approximately 60 degrees. Further, a pair of outer peripheral protrusions 85 different from the engaging protrusions 54 are formed on the outer peripheral edge of the Oldham intermediate body 83 . The outer peripheral protrusion 85 is formed on the outer periphery of the engaging recess 84 .

According to the sixth embodiment, the engagement concave portion 84 also functions as the notched groove portion, and the same effects as those of the fifth embodiment can be obtained.

<Other embodiments>
In each of the above embodiments, the internal gear portion 21 is formed on the driven side rotating body 20 and the first Oldham coupling portion 51 is formed on the driving side rotating body 10, but the internal gear portion is formed on the driving side rotating body. , the first Oldham's coupling portion can be formed on the driven side rotating body.

Further, in each of the above embodiments, the valve timing adjusting device 1 is configured to adjust the opening/closing timing of the intake valve 103 of the vehicle engine 100, but it may be configured to adjust the opening/closing timing of the exhaust valve 104. can also

The cut depth from the inner peripheral edge of the notch grooves 56 and 75 and the length in the circumferential direction in each of the above-described embodiments can be changed as appropriate. For example, in the Oldham intermediate body 53 of the first embodiment, it may exceed the circumferential length of the engaging convex portion 54 as long as it does not impair the rigidity of other parts during operation and deformation, It may be formed so that the cut depth to the radially outer side is even deeper.

In the fifth and sixth embodiments, the magnitudes of the angles θ2 and θ3 formed by the convex straight line L and the concave straight line M are not limited to those in the above embodiments. Since the positions of the engaging recesses 79 and 84 should be close to the engaging protrusions 54 in the circumferential direction, the angle should be less than approximately 80 degrees. If the angle is less than approximately 80 degrees, the engagement concave portion can also be used as the notch groove portion.

The present invention is not limited to the above-described embodiments, and can be implemented by appropriately changing the shape and configuration of each part including the Oldham intermediate within the scope of the invention.

Reference Signs List 1 Valve timing adjusting device 10 Drive-side rotor 20 Driven-side rotor 30 Planetary rotor 40 Eccentric shaft 50 Oldham joint 51 First Oldham Coupling portion 52 Second Oldham coupling portion 53 Oldham intermediate body 54 Engaging convex portion 55 Engaging concave portion 56 Notch groove portion 60 Fluid supply portion

Claims (7)

A valve timing adjusting device (1) for adjusting the opening/closing timing of valves (103, 104) opened and closed by a crankshaft (101) of an engine (100) via a camshaft (102),
a drive-side rotating body (10) rotated by the crankshaft about the same axis as the rotation axis (91) of the camshaft;
a driven-side rotating body (20) that rotates integrally with the camshaft around the same axis as the driving-side rotating body;
a planetary rotator (30) having a planetary gear portion (31) meshing with an internal gear portion (21) formed on either the driving side rotator or the driven side rotator;
an eccentric shaft (40) rotatably supporting the planetary rotor around an eccentric axis (92) displaced parallel to the rotation axis of the camshaft;
A first Oldham's coupling (51) provided on the other of the driven-side rotating body and the driving-side rotating body, a second Oldham's coupling (52) provided on the planetary rotating body, and an annular plate-like shape. an Oldham coupling (50) having an Oldham intermediate body (53, 71, 74, 76, 78, 83) that eccentrically synchronizes the rotation of the first Oldham coupling portion and the second Oldham coupling portion;
a fluid supply portion (60) for supplying a lubricating fluid (O) from the camshaft to the Oldham intermediate body;
with
The Oldham intermediate is
an engaging protrusion (54) formed on the outer peripheral edge so as to protrude radially outward and slidably engage with either the first Oldham's coupling portion or the second Oldham's coupling portion;
Engagement recesses (55, 79, 84) recessed in the inner peripheral edge and slidably engaged with the other of the first Oldham's coupling portion and the second Oldham's coupling portion;
notch grooves (56, 75) formed by notching the inner peripheral edge so as to suppress warping in the axial direction of the Oldham intermediate when the temperature rises;
valve timing adjustment device including; 2. The valve timing adjusting device according to claim 1, wherein the notched groove portion is provided point-symmetrically with respect to the axial center of the Oldham intermediate. 3. The valve timing adjusting device according to claim 1, wherein the notch groove is formed in the inner peripheral edge corresponding to the engaging projection. 4. The valve timing adjusting device according to claim 3, wherein the notched groove portion is formed to have a size that can be accommodated in the engaging convex portion in the circumferential direction and the radial direction. A pair of the engaging convex portion and the engaging concave portion are provided point-symmetrically with respect to the axis center of the Oldham intermediate,
According to any one of claims 2 to 4, wherein a convex straight line connecting the two engaging convex portions and a groove straight line connecting the two notch grooves are perpendicular to each other at the axis center of the Oldham intermediate. valve timing adjustment device. A pair of the engaging convex portion and the engaging concave portion are provided point-symmetrically with respect to the axis center of the Oldham intermediate,
A convex straight line connecting the two engaging convex portions and a concave straight line connecting the two engaging concave portions intersect at an angle other than 90 degrees at the axis center of the Oldham intermediate,
2. The valve timing adjusting device according to claim 1, wherein the engaging recess also serves as the notch groove. 7. The valve timing adjusting device according to claim 6, wherein an angle formed by said convex straight line and said concave straight line is less than 80 degrees.

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