Valve timing control device

Abstract

To provide a valve opening / closing timing control device capable of reducing noise or vibration during operation of an internal combustion engine.SOLUTION: A valve opening / closing timing control device 100 comprises: a driving-side rotor A which is rotated synchronously with a crankshaft 1 of an internal combustion engine E; a driven-side rotor B which is rotated integrally with a camshaft 2 of the internal combustion engine E; and a phase adjustment mechanism C which sets relative rotation phases of the driving-side rotor A and the driven-side rotor B. The driven-side rotor B has a support wall part 21 which is connected to an end of the camshaft 2. The support wall part 21 has a supply oil path 21a in which a lubricant can be supplied from the outside into the driven-side rotor B. The valve opening / closing timing control device has an oil sump structure Z in which, when the driving-side rotor A is being rotated, a discharge amount of the lubricant to be discharged from the inside of the driving-side rotor A is reduced in relative to a supply amount of the lubricant supplied from the supply oil path 21a to the inside of the driven-side rotor B.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a valve timing control device. [Background technology]

[0002] Conventionally, internal combustion engines have utilized valve timing control devices that control the valve opening and closing timing using a cam portion of a camshaft in response to torque transmission from a crankshaft. One example of such a valve timing control device is described in Patent Document 1, the source of which is shown below.

[0003] Patent Document 1 describes a valve timing control device. This valve timing control device includes a drive rotor, a driven rotor, and a phase adjustment mechanism that sets the relative rotational phase between the drive rotor and the driven rotor. The phase adjustment mechanism includes an output gear that is provided on the driven rotor and is coaxial with the rotation axis, an input gear that rotates about an eccentric axis that is parallel to the rotation axis and is connected to the drive rotor, a first bearing, a second bearing, and a cylindrical eccentric member that supports the input gear from its inner periphery via the second bearing and rotates the input gear. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Publication No. 2018-087564 Summary of the Invention [Problem to be solved by the invention]

[0005] In a valve timing control device, lubricating oil is generally supplied to the inside of the driven-side rotor while the internal combustion engine is operating. In the valve timing control device described in Patent Document 1, the drive-side rotor has a front plate on the opposite side of the camshaft from the eccentric member in the direction along the rotation axis. This front plate is circular when viewed in the direction along the rotation axis and has a circular opening in its center. This opening is provided to discharge lubricating oil from the internal space of the eccentric member to the outside. However, if too much lubricating oil is discharged to the outside during operation of the internal combustion engine, components constituting the valve timing control device may come into contact (crash) with each other, causing contact noise (impact noise), and potentially increasing noise and vibration generated by the valve timing control device.

[0006] Therefore, there is a demand for a valve timing control device that can reduce noise and vibration during operation of an internal combustion engine. [Means for solving the problem]

[0007] A characteristic configuration of a valve opening / closing timing control device according to the present invention includes a drive-side rotor that rotates synchronously with a crankshaft of an internal combustion engine about a rotational axis, a driven-side rotor that is coaxial with the rotational axis and is arranged inside the drive-side rotor and rotates integrally with a camshaft for opening and closing valves of the internal combustion engine, and a phase adjustment mechanism that sets a relative rotational phase between the drive-side rotor and the driven-side rotor, wherein the phase adjustment mechanism includes an output gear that is coaxial with the rotational axis and is provided on the driven-side rotor, an input gear that rotates about an eccentric axis that is parallel to the rotational axis and is connected to the drive-side rotor, and a cylindrical eccentric member that supports the input gear from the inner peripheral side via a support bearing and rotates the input gear, The eccentric member is configured to revolve around the eccentric axis by rotation to change the position of the meshing portion between the output gear and the input gear, the driven-side rotor has a support wall portion connected to an end of the camshaft in an orientation perpendicular to the rotation axis, and the support wall portion has an oil supply passage that can supply lubricating oil from the outside to the inside of the driven-side rotor, the drive-side rotor has a front plate on the opposite side to the camshaft with respect to the eccentric member in a direction along the rotation axis, and has an oil reservoir structure that reduces the amount of lubricating oil discharged from the inside of the drive-side rotor relative to the amount of lubricating oil supplied from the oil supply passage to the inside of the driven-side rotor when the drive-side rotor is rotating. The lubricating oil passes between the front plate and the driving-side rotor and is discharged to the outside of the driving-side rotor, and the amount of the lubricating oil that passes between the front plate and the driving-side rotor and is discharged to the outside of the driving-side rotor is less than the amount of lubricating oil that flows through the meshing portion between the input gear and the driven-side rotor and the amount of lubricating oil that flows through the support bearing. It's at the point.

[0008] With this characteristic configuration, when the drive-side rotor is rotating, the lubricating oil supplied from the oil supply passage to the inside of the driven-side rotor is less likely to be discharged from inside the drive-side rotor, making it possible to store the oil (lubricating oil) inside the drive-side rotor. By storing the lubricating oil inside the drive-side rotor in this way, the damping effect of the oil can reduce the volume of noise caused by contact or collision between various parts. Therefore, it is possible to suppress noise and vibration generated by the valve timing control device.

[0009] Also, Another characteristic configuration of the valve opening / closing timing control device according to the present invention includes a drive-side rotor that rotates synchronously with a crankshaft of an internal combustion engine about a rotational axis, a driven-side rotor that is coaxial with the rotational axis and is arranged inside the drive-side rotor and rotates integrally with a camshaft for opening and closing valves of the internal combustion engine, and a phase adjustment mechanism that sets the relative rotational phase of the drive-side rotor and the driven-side rotor, wherein the phase adjustment mechanism includes an output gear that is coaxial with the rotational axis and is provided on the driven-side rotor, an input gear that rotates about an eccentric axis that is parallel to the rotational axis and is connected to the drive-side rotor, and a cylindrical eccentric member that supports the input gear from the inner peripheral side via a support bearing and rotates the input gear, the rotation of the eccentric member causes the eccentric axis to revolve, changing the position of the meshing portion between the output gear and the input gear; the driven-side rotating body has a support wall portion connected to an end of the camshaft in an orientation perpendicular to the rotation axis, and the support wall portion has an oil supply passage that can supply lubricating oil from the outside to the inside of the driven-side rotating body; the drive-side rotating body has a front plate on the opposite side of the camshaft with respect to the eccentric member in a direction along the rotation axis, and has an oil reservoir structure that reduces the amount of lubricating oil discharged from the inside of the drive-side rotating body relative to the amount of lubricating oil supplied from the oil supply passage to the inside of the driven-side rotating body when the drive-side rotating body is rotating;The support bearing is configured as a ball bearing having an inner ring in contact with the outer peripheral surface of the eccentric member and an outer ring in contact with the inner peripheral surface of the input gear, one axial side of the eccentric member is inserted into an opening in the radial center of the front plate, and when the driving-side rotating body is rotating, the lubricating oil supplied to the inside of the driven-side rotating body flows between the inner peripheral surface of the driven-side rotating body and the outer peripheral surface of the eccentric member, and into the inside of the eccentric member, and when the support bearing is viewed from a direction along the rotation axis, the front plate covers the area where the lubricating oil flows between the inner peripheral surface of the driven-side rotating body and the outer peripheral surface of the eccentric member. To the point be.

[0010] With this configuration, when the drive-side rotor is rotating, the amount of lubricating oil supplied to the inside of the driven-side rotor can be reduced compared to the amount of lubricating oil discharged from the inside of the drive-side rotor. Therefore, when the drive-side rotor is rotating, the lubricating oil supplied to the inside of the driven-side rotor can be accumulated from the inner circumferential surface of the driven-side rotor until it reaches the opening in the front plate.

[0011] Also, Another characteristic configuration of the valve opening / closing timing control device according to the present invention includes a drive-side rotor that rotates synchronously with a crankshaft of an internal combustion engine about a rotational axis, a driven-side rotor that is coaxial with the rotational axis and is arranged inside the drive-side rotor and rotates integrally with a camshaft for opening and closing valves of the internal combustion engine, and a phase adjustment mechanism that sets the relative rotational phase of the drive-side rotor and the driven-side rotor, wherein the phase adjustment mechanism includes an output gear that is coaxial with the rotational axis and is provided on the driven-side rotor, an input gear that rotates about an eccentric axis that is parallel to the rotational axis and is connected to the drive-side rotor, and a cylindrical eccentric member that supports the input gear from the inner peripheral side via a support bearing and rotates the input gear, the rotation of the eccentric member causes the eccentric axis to revolve, changing the position of the meshing portion between the output gear and the input gear; the driven-side rotating body has a support wall portion connected to an end of the camshaft in an orientation perpendicular to the rotation axis, and the support wall portion has an oil supply passage that can supply lubricating oil from the outside to the inside of the driven-side rotating body; the drive-side rotating body has a front plate on the opposite side of the camshaft with respect to the eccentric member in a direction along the rotation axis, and has an oil reservoir structure that reduces the amount of lubricating oil discharged from the inside of the drive-side rotating body relative to the amount of lubricating oil supplied from the oil supply passage to the inside of the driven-side rotating body when the drive-side rotating body is rotating; The phase adjustment mechanism further includes an Oldham coupling having an annular portion and a pair of external engagement arms protruding radially outward from the annular portion in directions opposing each other, and the drive-side rotor has a pair of guide grooves formed as through-grooves at an opening edge with which the front plate abuts, the guide grooves extending radially outward in directions opposing each other from the inside to the outside of the drive-side rotor, and each of the pair of external engagement arms engages with the pair of guide grooves, and each of the pair of guide grooves has a discharge flow path formed by cutting out from the inside to the outside of the drive-side rotor, and the oil reservoir structure is configured such that the amount of lubricating oil discharged from the discharge flow path is less than the amount of lubricating oil flowing through the supply oil path when the drive-side rotor is rotating. To the point be.

[0012] In order to set the relative rotational phase between the drive-side rotor and the driven-side rotor, the phase adjustment mechanism has an external engagement arm of an Oldham coupling engaged with a guide groove of the drive-side rotor, and lubricating oil is supplied to lubricate the space between the external engagement arm and the guide groove. However, because this guide groove is a through groove extending from the inside to the outside of the drive-side rotor, the lubricating oil supplied to the inside of the drive-side rotor is subjected to centrifugal force due to the rotation of the drive-side rotor and is discharged to the outside of the drive-side rotor. Therefore, by making the flow rate of lubricating oil flowing through the discharge flow passage formed in the guide groove less than the flow rate of lubricating oil flowing through the supply oil passage as described above, it becomes possible to make it easier for lubricating oil to accumulate inside the drive-side rotor.

[0013] It is also preferable that the amount of lubricating oil discharged from the discharge flow path is less than the amount of lubricating oil circulating through the supply oil path minus the amount of lubricating oil circulating inside the eccentric member.

[0014] In this way, by making the amount of lubricating oil discharged from the discharge flow path less than the amount of lubricating oil circulating through the supply oil path minus the amount of lubricating oil circulating inside the eccentric member, it becomes easier to accumulate lubricating oil inside the drive side rotating body.

[0015] It is also preferable that one axial side of the eccentric member is inserted into an opening in the radial center of the front plate, and that the front plate is open up to the position of the inserted radial outer end portion when the difference between the eccentric axis of the eccentric member and the rotation axis is greatest, centered on the rotation axis.

[0016] With this configuration, when the internal combustion engine is operating (when the valve timing control device is operating and centrifugal force is acting on the lubricating oil), the movable range of the eccentric member is ensured while suppressing the discharge of lubricating oil from between the eccentric member and the opening, and the lubricating oil can be stored from the outer peripheral surface of the drive-side rotor to the opening in the radial center of the front plate.On the other hand, when the internal combustion engine is stopped (when the valve timing control device is not operating), the lubricating oil can be discharged from the opening in the radial center of the front plate, preventing deterioration of startability due to the lubricating oil the next time the internal combustion engine is started. [Brief explanation of the drawings]

[0017] [Figure 1] FIG. 2 is a cross-sectional view of the valve timing control device. [Figure 2] FIG. 2 is a cross-sectional view taken along line II-II in FIG. [Figure 3] FIG. 2 is an exploded perspective view of the valve timing control device. [Figure 4] FIG. 10 is a diagram showing a protrusion of the front plate. [Figure 5] FIG. [Figure 6] FIG. 2 is a diagram showing the flow of lubricating oil. [Figure 7] FIG. 10 is a diagram showing a discharge flow path according to another embodiment. [Figure 8] FIG. 10 is a diagram showing a discharge flow path according to another embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0018] Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

[0019] [Basic configuration] As shown in FIG. 1, the valve timing control device 100 according to this embodiment includes a drive-side rotor A, a driven-side rotor B, and a phase adjustment mechanism C. The drive-side rotor A rotates synchronously with a crankshaft 1 of an engine E, which serves as an internal combustion engine, about a rotational axis X. The driven-side rotor B is disposed coaxially with the rotational axis X and inside the drive-side rotor A. The driven-side rotor B rotates integrally with an intake camshaft 2 (an example of a camshaft) that opens and closes an intake valve 2B (an example of a valve) of the engine E. The phase adjustment mechanism C sets the relative rotational phase between the drive-side rotor A and the driven-side rotor B using the driving force of a phase control motor M.

[0020] The engine E is a four-stroke engine in which pistons 4 are housed in multiple cylinders 3 formed in a cylinder block, and the pistons 4 are connected to a crankshaft 1 by connecting rods 5. A timing chain 6 (which may be a timing belt or the like) is wound around an output sprocket 1S of the crankshaft 1 of the engine E and a drive sprocket 11S of the drive-side rotor A.

[0021] As a result, when the engine E is operating, the entire valve timing control device 100 rotates around the rotational axis X. In addition, the driving force of the phase control motor M operates the phase adjustment mechanism C, making it possible to displace the driven-side rotor B in the same direction as the rotational direction or in the opposite direction relative to the driving-side rotor A. This displacement by the phase adjustment mechanism C sets the relative rotational phase between the driving-side rotor A and the driven-side rotor B, thereby realizing control of the opening and closing timing of the intake valve 2B by the cam portion 2A of the intake camshaft 2.

[0022] The operation in which the driven-side rotor B is displaced relatively in the same direction as the rotational direction of the driving-side rotor A is called advance operation, and this advance operation increases the intake compression ratio. On the other hand, the operation in which the driven-side rotor B is displaced relatively in the opposite direction to the driving-side rotor A (operation in the opposite direction to advance operation) is called retard operation, and this retard operation reduces the intake compression ratio.

[0023] [Valve timing control device] As shown in Figure 1, the drive-side rotor A is configured by fastening an outer case 11, which has a drive sprocket 11S formed on its outer periphery, to a front plate 12 with a plurality of fastening bolts 13. The outer case 11 is a cylindrical type with a bottom and an opening at the bottom. The front plate 12 is provided on the opposite side of the eccentric member 26 from the intake camshaft 2 in the direction along the rotation axis X.

[0024] 1 and 2, an intermediate member 20 serving as a driven rotor B and a phase adjustment mechanism C having a hypotrochoid gear reduction mechanism are housed in the internal space of the outer case 11. The phase adjustment mechanism C also includes an Oldham coupling Cx that reflects a phase change in the driving rotor A and the driven rotor B.

[0025] The intermediate member 20 constituting the driven-side rotor B is integrally formed with a support wall portion 21 that is connected to the intake camshaft 2 in an orientation perpendicular to the rotation axis X, and a cylindrical wall portion 22 that is cylindrical and centered on the rotation axis X and protrudes from the outer peripheral edge of the support wall portion 21 in a direction away from the intake camshaft 2.

[0026] The intermediate member 20 is fitted so as to be relatively rotatable with the outer surface of the cylindrical wall portion 22 in contact with the inner surface of the outer case 11, and is fixed to the end of the intake camshaft 2 by a connecting bolt 23 inserted into a through-hole in the center of the support wall portion 21. In this fixed state, the outer end of the cylindrical wall portion 22 (the side farther from the intake camshaft 2) is configured to be located inside the front plate 12.

[0027] 1 and 2, a groove 22a is formed around the entire outer periphery of the cylindrical wall portion 22. The groove 22a improves the retention of lubricating oil between the outer surface of the cylindrical wall portion 22 and the inner surface of the outer case 11. This reduces the friction between the cylindrical wall portion 22 and the outer case 11, allowing the intermediate member 20 to rotate smoothly relative to the outer case 11.

[0028] As shown in Fig. 1, the phase control motor M is supported on the engine E by a support frame 7 so that its output shaft Ma is arranged coaxially with the rotation axis X. A pair of engagement pins 8 are formed on the output shaft Ma of the phase control motor M, and are oriented perpendicular to the rotation axis X.

[0029] [Phase adjustment mechanism] As shown in FIGS. 1 to 3 , the phase adjustment mechanism C includes an intermediate member 20, an output gear 25 formed on the inner circumferential surface of the cylindrical wall portion 22 of the intermediate member 20, an eccentric member 26, an elastic member S, a first bearing 28, a second bearing 29 (corresponding to a "support bearing"), an input gear 30, a fixed ring 31, a ring-shaped spacer 32, and an Oldham coupling Cx. While rolling bearings are used for the first bearing 28 and the second bearing 29, plain bearings may also be used. In this embodiment, the first bearing 28 is a ball bearing having an inner ring 28a that contacts the outer circumferential surface of the eccentric member 26 and an outer ring 28b that contacts the inner circumferential surface of the intermediate member 20. The second bearing 29 is a ball bearing having an inner ring 29a that contacts the outer circumferential surface of the eccentric member 26 and an outer ring 29b that contacts the inner circumferential surface of the input gear 30.

[0030] As shown in FIG. 1, a support surface 22S centered on the rotation axis X is formed on the inner periphery of the cylindrical wall portion 22 of the intermediate member 20 on the inside (at a position adjacent to the support wall portion 21) in a direction along the rotation axis X (hereinafter referred to as the axial direction), and an output gear 25 centered on the rotation axis X is integrally formed outside the support surface 22S (on the side farther from the intake camshaft 2).

[0031] As shown in FIGS. 1 to 3, the eccentric member 26 is cylindrical. The eccentric member 26 has a circumferential support surface 26S on its axially inner side (the side closer to the intake camshaft 2) that is centered on the rotational axis X. A flange 26Q is formed on an axially inner side (the side closer to the intake camshaft 2) of the circumferential support surface 26S, protruding radially outward from the circumferential support surface 26S. The eccentric member 26 also has an eccentric support surface 26E on its outer side (the side farther from the intake camshaft 2) that is centered on an eccentric axis Y that is eccentric and parallel to the rotational axis X. Therefore, the eccentric member 26 is formed with the flange 26Q, the circumferential support surface 26S, and the eccentric support surface 26E arranged in this order along the axial direction from the side closer to the intake camshaft 2. Because the direction along the eccentric axis Y is the same as the axial direction, hereinafter, the direction along the eccentric axis Y will also be referred to simply as the axial direction.

[0032] 1 and 3, a first recess 70 recessed inward along the radial direction of the eccentric member 26 is formed in the eccentric support surface 26E. A pair of second recesses 79, 79 recessed toward the radial axis of the eccentric member 26 are formed in the bottom surface of the first recess 70 at both ends in the circumferential direction of the eccentric member 26. In this embodiment, the first recess 70 is symmetrical in the circumferential direction.

[0033] The second recesses 79, 79 are respectively formed at the ends of the first recess 70 in the circumferential direction of the eccentric member 26. The maximum depth of the bottom surface of the second recesses 79, 79 in the radial direction of the eccentric member 26 is deeper than the depth of the bottom surface of the first recess 70 near the center in the circumferential direction of the eccentric member 26. The surfaces from the bottom surface to the ends of each of the second recesses 79, 79 in the circumferential direction of the eccentric member 26 are formed in a shape that follows the curved shape of a spring member 71, which will be described later.

[0034] An elastic member S is fitted into the first recess 70. The elastic member S includes a pair of spring members 71, 71. In this embodiment, the pair of spring members 71, 71 have the same shape and size. The elastic member S applies a biasing force to the input gear 30 via the second bearing 29 so that a portion of the external teeth portion 30A of the input gear 30 meshes with a portion of the internal teeth portion 25A of the output gear 25. This prevents the backlash between the input gear 30 and the output gear 25 from increasing, thereby preventing abnormal noise. This also improves the durability of the input gear 30 and the output gear 25.

[0035] As shown in Figures 1 and 3, a pair of engagement grooves 26T, which can engage with a pair of engagement pins 8 of a phase control motor M (see Figure 1), are formed on the inner periphery of the eccentric member 26 in a position parallel to the rotation axis X.

[0036] 3, tapered portions 26c (inclined portions) whose diameter decreases toward the inside (the side closer to the intake camshaft 2) are formed on both sides of the engagement groove 26T on the inner circumferential side of the open end on the outside (the side farther from the intake camshaft 2) of the eccentric member 26. When the pair of engagement pins 8 of the phase control motor M are engaged with the engagement grooves 26T of the eccentric member 26, the engagement pins 8 are guided into the engagement grooves 26T by the tapered portions 26c, which makes it easier to engage the phase control motor M with the eccentric member 26.

[0037] 1, a first bearing 28 is fitted onto the circumferential support surface 26S of the eccentric member 26, and the first bearing 28 is fitted into the support surface 22S of the cylindrical wall portion 22, so that the eccentric member 26 is rotatably supported about the rotation axis X with respect to the intermediate member 20. Also, as shown in FIG. 1, the input gear 30 is supported by the eccentric support surface 26E of the eccentric member 26 via a second bearing 29 so as to be rotatable about the eccentric axis Y.

[0038] In this phase adjustment mechanism C, the number of teeth of the external teeth portion 30A of the input gear 30 is set to be one tooth less than the number of teeth of the internal teeth portion 25A of the output gear 25. A portion of the external teeth portion 30A of the input gear 30 meshes with a portion of the internal teeth portion 25A of the output gear 25.

[0039] As shown in FIG. 1, the fixing ring 31 is supported in a fitted state on the outer periphery of the eccentric member 26, and prevents the second bearing 29 from coming off via the spacer 32.

[0040] As shown in FIG. 1, a gap is formed between the eccentric member 26 and the support wall portion 21 of the intermediate member 20.

[0041] [Phase adjustment mechanism: Oldham coupling] 1 to 3, the Oldham coupling Cx is composed of a plate-shaped coupling member 40 that is integrally formed with a central annular portion 41, a pair of external engagement arms 42 that protrude radially outward from the annular portion 41 in a first direction (the left-right direction in FIG. 2), and an internal engagement arm 43 that protrudes radially outward from the annular portion 41 in a second direction (the up-down direction in FIG. 2) that is perpendicular to the first direction. Each of the pair of internal engagement arms 43 is formed with an engagement recess 43a that communicates with the opening of the annular portion 41.

[0042] A pair of guide grooves 11a are formed in the outer case 11 at the opening edge against which the front plate 12 abuts, as through-grooves, extending from the interior space of the outer case 11 to the exterior space, radially from the rotation axis X. The groove width of the guide grooves 11a is set slightly wider than the width of the external engagement arms 42, and obliquely cut portions 42a are formed at both circumferential ends of the external engagement arms 42. A pair of discharge flow paths 11b are cut out in each of the guide grooves 11a and the cut portions 42a at both circumferential ends of the external engagement arms 42.

[0043] At the opening edge of the outer case 11, in a region other than the guide groove 11a, one or more pockets 11c are formed by cutting out the inner periphery along the circumferential direction. The pockets 11c collect foreign matter that moves toward the outer periphery due to centrifugal force caused by the rotation of the drive-side rotor A. Figures 2 and 3 show an example in which four pockets 11c are formed.

[0044] Furthermore, a pair of engagement protrusions 30T are integrally formed on the end surface of the input gear 30 that faces the front plate 12. The engagement width of these engagement protrusions 30T is set slightly narrower than the engagement width of the engagement recess 43a of the internal engagement arm 43.

[0045] With this configuration, the Oldham coupling Cx can be made to function by engaging the pair of outer engaging arms 42 of the coupling part 40 with the pair of guide grooves 11a of the outer case 11 and by engaging the pair of engaging projections 30T of the input gear 30 with the engaging recesses 43a of the pair of inner engaging arms 43 of the coupling part 40.

[0046] The coupling member 40 is displaceable relative to the outer case 11 in a first direction (left-right direction in FIG. 2) in which the external engagement arm 42 extends, and the input gear 30 is displaceable relative to this coupling member 40 in a second direction (up-down direction in FIG. 2) along the formation direction of the engagement recess 43a of the internal engagement arm 43.

[0047] As shown in FIGS. 1 and 3, the spacer 32 limits the distance of the gap through which the second bearing 29 can move in the axial direction to a predetermined set value or less. By providing the spacer 32 between the Oldham coupling Cx (coupling member 40) and the second bearing 29, the axial movement of the second bearing 29 is limited to a distance equal to or less than the predetermined set value. In addition, a recess 12d recessed outward (toward the side farther from the intake camshaft 2) is formed on the surface of the front plate 12 facing the input gear 30. The recess 12d is provided opposite the opening of the coupling member 40 in the front plate 12, and is formed slightly wider than the opening of the coupling member 40. This prevents contact between the engaging protrusion 30T of the input gear 30 and the front plate 12.

[0048] [Layout of each part of the valve timing control device] In the assembled valve timing control device 100, as shown in Fig. 1, the support wall portion 21 of the intermediate member 20 is connected to the end of the intake camshaft 2 by a connecting bolt 23, and they rotate together. The eccentric member 26 is supported by a first bearing 28 so as to be rotatable relative to the intermediate member 20 about the rotation axis X. As shown in Fig. 1, the input gear 30 is supported by an eccentric support surface 26E of the eccentric member 26 via a second bearing 29, and a portion of the external teeth portion 30A of the input gear 30 meshes with a portion of the internal teeth portion 25A of the output gear 25.

[0049] 2, the outer engagement arms 42 of the Oldham coupling Cx engage with a pair of guide groove portions 11a of the outer case 11, and the engagement projections 30T of the input gear 30 engage with the engagement recesses 43a of the inner engagement arms 43 of the Oldham coupling Cx. As shown in FIG. 1, the front plate 12 is disposed on the outer side of the coupling member 40 of the Oldham coupling Cx, so that the coupling member 40 can move in a direction perpendicular to the rotation axis X while contacting the inner surface of the front plate 12. With this arrangement, the Oldham coupling Cx is disposed outward from both the first bearing 28 and the second bearing 29 (on the side farther from the intake camshaft 2) and inward from the front plate 12 (on the side closer to the intake camshaft 2).

[0050] As shown in FIG. 1, a pair of engagement pins 8 formed on the output shaft Ma of the phase control motor M engage with the engagement grooves 26T of the eccentric member 26.

[0051] [Operational form of phase adjustment mechanism] Although not shown in the drawings, the phase control motor M is controlled by a control device configured as an ECU. The engine E is equipped with sensors that can detect the rotational speeds (number of rotations per unit time) of the crankshaft 1 and the intake camshaft 2 and their respective rotational phases, and the detection signals of these sensors are input to the control device.

[0052] When the engine E is running, the control device maintains the relative rotational phase by driving the phase control motor M at a speed equal to the rotational speed of the intake camshaft 2. On the other hand, an advance operation is performed by reducing the rotational speed of the phase control motor M below the rotational speed of the intake camshaft 2, and conversely, a retard operation is performed by increasing the rotational speed. As described above, an advance operation increases the intake compression ratio, and a retard operation decreases the intake compression ratio.

[0053] When the phase control motor M rotates at the same speed as the outer case 11 (same speed as the intake camshaft 2), the position of the meshing portion of the external tooth portion 30A of the input gear 30 with the internal tooth portion 25A of the output gear 25 does not change, so the relative rotational phase of the driven side rotating body B with respect to the driving side rotating body A is maintained.

[0054] On the other hand, by driving and rotating the output shaft Ma of the phase control motor M at a speed higher or lower than the rotational speed of the outer case 11, the eccentric shaft Y in the phase adjustment mechanism C revolves around the rotational shaft X. Due to this revolution, the position of the meshing portion between the internal teeth portion 25A of the output gear 25 and the external teeth portion 30A of the input gear 30 is displaced along the inner circumference of the output gear 25, and a rotational force acts between the input gear 30 and the output gear 25. In other words, a rotational force about the rotational shaft X acts on the output gear 25, and a rotational force that rotates the input gear 30 about the eccentric shaft Y acts on the input gear 30.

[0055] As described above, the input gear 30 does not rotate relative to the outer case 11 because its engagement projection 30T engages with the engagement recess 43a of the internal engagement arm 43 of the coupling member 40, and a rotational force acts on the output gear 25. The action of this rotational force causes the intermediate member 20, together with the output gear 25, to rotate about the rotation axis X relative to the outer case 11. As a result, the relative rotational phase between the drive-side rotor A and the driven-side rotor B is set, and the opening and closing timing of the intake camshaft 2 is set.

[0056] Furthermore, when the eccentric axis Y of the input gear 30 revolves around the rotation axis X, the input gear 30 is displaced, and therefore the coupling member 40 of the Oldham coupling Cx is displaced in the direction in which the external engagement arm 42 extends relative to the outer case 11 (first direction), and the input gear 30 is displaced in the direction in which the internal engagement arm 43 extends (second direction).

[0057] As described above, the number of teeth on the external toothed portion 30A of the input gear 30 is set to be one tooth less than the number of teeth on the internal toothed portion 25A of the output gear 25. Therefore, when the eccentric axis Y of the input gear 30 revolves around the rotation axis X by one revolution, the output gear 25 rotates by one tooth, thereby achieving a large reduction in speed.

[0058] [Lubrication of Phase Adjustment Mechanism] 1, the intake camshaft 2 is formed with a lubricating oil passage 15 to which lubricating oil is supplied from an external oil pump P via an oil passage forming member 9. A supply oil passage 21a is formed in a portion of the surface of the support wall portion 21 of the intermediate member 20 that abuts against the intake camshaft 2, and that guides the lubricating oil circulating through the lubricating oil passage 15 inside the eccentric member 26. In other words, the support wall portion 21 has the supply oil passage 21a that can supply lubricating oil from the outside to the inside of the driven-side rotor B.

[0059] As described above, a gap is formed between the eccentric member 26 and the support wall portion 21 of the intermediate member 20. The oil supply passage 21a communicates with this gap.

[0060] With this configuration, the lubricating oil supplied from the oil pump P is supplied from the lubricating oil passage 15 of the intake camshaft 2 through the supply oil passage 21a of the support wall portion 21 of the intermediate member 20 to the internal space of the intermediate member 20. Some of the lubricating oil supplied to the internal space of the intermediate member 20 flows into the internal space of the eccentric member 26, but some is supplied by centrifugal force through the gap between the eccentric member 26 and the support wall portion 21 of the intermediate member 20 to the first bearing 28, causing the first bearing 28 to operate (slide) smoothly. The lubricating oil supplied to the first bearing 28 is then supplied to the adjacent second bearing 29, and is also supplied between the internal teeth portion 25A of the output gear 25, which is arranged on the outer periphery of the second bearing 29 and is biased by the elastic member S, and the external teeth portion 30A of the input gear 30, causing these portions (particularly the meshing portions) to operate (slide) smoothly.

[0061] The lubricating oil supplied between the second bearing 29 and the internal teeth portion 25A of the output gear 25 and the external teeth portion 30A of the input gear 30 is further supplied to the coupling member 40. The lubricating oil supplied to the coupling member 40 is supplied between the front plate 12 and the coupling member 40, and is also supplied to the gap between the external engagement arm 42 of the coupling member 40 and the guide groove portion 11a of the outer case 11. This allows the coupling member 40 to operate smoothly.

[0062] As described above, a pair of discharge passages 11b are formed in the guide groove portion 11a (see FIGS. 2 and 3). Therefore, the lubricating oil supplied to the coupling member 40 is discharged to the outside through the gap between the external engagement arm 42 of the coupling member 40 and the guide groove portion 11a of the outer case 11. Furthermore, because the discharge passages 11b are formed in the guide groove portion 11a, the lubricating oil inside can be discharged from the discharge passages 11b by centrifugal force when the engine E is started.

[0063] 1 and 3, the front plate 12 has a circular opening 12a in its center, the opening being centered on the rotation axis X. By making the opening diameter of the opening 12a larger than the inner diameter of the eccentric member 26, a step G is formed between the edge of the opening 12a in the front plate 12 and the inner periphery of the eccentric member 26. This step G is set to a minimum extent so that the eccentric member 26 does not come into contact with the front plate 12 when it rotates.

[0064] When the engine E is stopped, the step G allows the lubricating oil in the internal space of the eccentric member 26 to be discharged through the opening 12a of the front plate 12, thereby reducing the amount of lubricating oil remaining inside.

[0065] In this way, in the valve timing control device 100, the lubricating oil supplied to the inside of the driven rotor B can be discharged from the guide groove portion 11a of the outer case 11 and the opening 12a of the front plate 12.

[0066] In this embodiment, as shown in Fig. 3, four protrusions 12e protruding inward (toward the intake camshaft 2) are formed along the circumferential direction of the front plate 12 on the surface of the front plate 12 facing the intermediate member 20. As shown in Fig. 4, the protrusions 12e are provided so as to face the boundary between the inner peripheral surface of the outer case 11 and the outer peripheral surface of the intermediate member 20 in the axial direction. This makes it possible to make the flow of lubricating oil discharged from between the outer case 11 and the intermediate member 20 different from the flow of lubricating oil discharged from between the outer case 11 and the intermediate member 20 in a portion where the protrusions 12e are not provided, thereby allowing the lubricating oil to flow inside the outer case 11.

[0067] As described above, when the outer case 11 is rotating, lubricating oil is supplied from the oil supply passage 21a to the inside of the intermediate member 20. The valve timing control device 100 is configured to have an oil reservoir structure Z that reduces the amount of lubricating oil discharged from the inside of the outer case 11 relative to the amount of lubricating oil supplied from the oil supply passage 21a to the inside of the intermediate member 20 during the synchronous rotation. The oil reservoir structure Z will be described below.

[0068] As described above, the external engagement arm 42 of the coupling member 40 engages with the guide groove portion 11a of the outer case 11. This guide groove portion 11a is configured to be supplied with lubricating oil in order to improve lubrication with the external engagement arm 42. However, because the lubricating oil that enters the guide groove portion 11a is structurally discharged to the outside of the outer case 11, in this embodiment, the amount of lubricating oil discharged from the guide groove portion 11a is configured to be limited to a predetermined amount or less.

[0069] Specifically, the lubricating oil in the guide groove 11a flows through a pair of discharge flow paths 11b that are formed by notches extending from the inside to the outside of the outer case 11 in each of the pair of guide grooves 11a, as shown in Fig. 5. In this embodiment, the oil reservoir structure Z is configured so that the amount of lubricating oil discharged from the pair of discharge flow paths 11b is less than the amount of lubricating oil that flows through the oil supply path 21a when the outer case 11 is rotating. This makes it possible for the lubricating oil supplied to the inside of the outer case 11 to be less likely to be discharged while maintaining its lubricating function in the guide groove 11a.

[0070] 1 and 2, one axial side of the eccentric member 26 is inserted into an opening 12a that is an opening in the radial center of the front plate 12. In this embodiment, the front plate 12 is open about the rotational axis X up to the position of the radially outer end of the eccentric member 26 inserted therethrough when the difference between the eccentric axis Y and the rotational axis X is the largest. In other words, the front plate 12 closes the opening in the outer case 11 about the rotational axis X up to the position of the radially outer end of the eccentric member 26 inserted therethrough when the difference between the eccentric axis Y and the rotational axis X is the largest. That is, as described above, the eccentric axis Y is eccentric with respect to the rotational axis X, and the eccentric axis Y revolves around the rotational axis X. Therefore, the portion of the eccentric member 26 that is inserted through the front plate 12 rotates about the rotation axis X with a rotation radius that is half the outer diameter of the portion of the eccentric member 26 that is inserted through the front plate 12 plus the eccentricity of the eccentric axis Y relative to the rotation axis X. To prevent the eccentric member 26 from coming into contact with the front plate 12 when the eccentric member 26 rotates, the opening 12a is configured so that the portion of the eccentric member 26 that is inserted through the front plate 12 has an inner radius that is the sum of half the outer diameter of the portion of the eccentric member 26 that is inserted through the front plate 12 and the eccentricity of the eccentric axis Y relative to the rotation axis X. Furthermore, the inner radius of the opening 12a is smaller than the inner radius of the coupling member 40, and the coupling member 40 is covered by the front plate 12, making it impossible to see the coupling member 40 from the outside. This makes it possible to configure the engine E so that lubricating oil can accumulate from the inner circumferential surface of the outer case 11 to the opening 12a when the engine E is operating. Such a configuration of the opening 12a also corresponds to the oil reservoir structure Z described above.

[0071] 6 shows the flow pattern of lubricating oil in the valve timing control device 100. In the valve timing control device 100, lubricating oil is supplied from the oil pump P to the oil supply passage 21a via the lubricating oil passage 15 (a). When the outer case 11 is rotating, the lubricating oil supplied from the oil supply passage 21a to the inside of the intermediate member 20 flows between the inner circumferential surface of the intermediate member 20 and the outer circumferential surface of the eccentric member 26, and into the inside of the eccentric member 26. That is, most of the lubricating oil supplied to the oil supply passage 21a flows between the eccentric member 26 and the support wall portion 21 of the intermediate member 20 due to centrifugal force, and then flows toward the first bearing 28 due to centrifugal force (b). In addition, some of the lubricating oil flows (drips) to the center (radial center) of the eccentric member 26 (h).

[0072] The lubricating oil that has flowed to the first bearing 28 flows between the inner ring 28a and the outer ring 28b (c), and is supplied to the gap between the intermediate member 20 and the input gear 30 (d), and to the second bearing 29 (e). The lubricating oil that has flowed between the intermediate member 20 and the input gear 30, and the lubricating oil that has been supplied to the second bearing 29 and has flowed between the inner ring 29a and the outer ring 29b, passes through the gap between the front plate 12 and the outer case 11 and is discharged to the outside of the outer case 11 (f), but most of it is stored inside the outer case 11.

[0073] When the second bearing 29 is viewed from a direction along the rotation axis X, the front plate 12 covers the region where the lubricating oil flows between the inner circumferential surface of the intermediate member 20 and the outer circumferential surface of the eccentric member 26. That is, the inner circumferential surface of the opening 12a is provided at a position closer to the rotation axis X than the above-mentioned area (d) between the intermediate member 20 and the input gear 30 and the path (e) through which the lubricating oil is supplied to the second bearing 29. As a result, the lubricating oil accumulates inside the outer case 11 from the inner circumferential surface side of the outer case 11 due to centrifugal force, and when the lubricating oil reaches the opening 12a, it is discharged from the opening 12a (g).

[0074] The pair of discharge flow paths 11b are configured so that the amount of lubricating oil discharged from the pair of discharge flow paths 11b is less than the amount of lubricating oil discharged between the inner circumferential surface of the intermediate member 20 and the outer circumferential surface of the eccentric member 26. As a result, the flow rate in (a) of FIG. 6 is the sum of the flow rate in (c) and the flow rate in (h), and the flow rate in (f) is less than the flow rate in (c), allowing the lubricating oil to accumulate inside the outer case 11 until the lubricating oil flows out along (g). That is, the lubricating oil flowing in (b) flows along (c), (d), and (e), accumulates inside the outer case 11 due to centrifugal force, and is discharged along (g) when the liquid level reaches the opening 12a. At this time, the flow rate in (b) is the sum of the flow rate in (f) and the flow rate in (g). That is, the amount of lubricating oil discharged from the discharge passage 11b is set to be less than the amount of lubricating oil flowing through the supply oil passage 21a minus the amount of lubricating oil flowing inside the eccentric member 26.

[0075] As a result, while the valve timing control device 100 is in operation, the lubricating oil can be stored inside, and the damping effect of the oil (lubricating oil) can reduce the volume of noise caused by contact or collision between various parts. This makes it possible to reduce noise and vibration emitted from the valve timing control device 100 (specifically, the above configuration can achieve a noise and vibration reduction effect of several dB). Furthermore, when the valve timing control device 100 is not in operation, the lubricating oil can be discharged from the opening 12a and the gap between the front plate 12 and the outer case 11. This makes it possible to suppress a decrease in the starting speed of the engine E (deterioration of the starting ability of the engine E) due to the viscosity of the lubricating oil at low temperatures, for example.

[0076] Other Embodiments In the above embodiment, the oil reservoir structure Z has been described as being formed by forming a discharge flow path 11b in each of the pair of guide groove portions 11a, cutting out the discharge flow path 11b from the inside to the outside of the outer case 11. For example, as shown in Fig. 7, the oil reservoir structure Z can be formed by rounding the corners on both circumferential sides of each of the pair of guide groove portions 11a into an arc shape, and forming a pair of discharge flow paths 11b between the cut portions 42a at both circumferential ends of the external engagement arm 42 and the corners on both circumferential sides of the guide groove portion 11a. Even with this configuration, it is possible to make it difficult for the lubricating oil supplied to the inside of the outer case 11 to be discharged while maintaining the lubricating function of the guide groove portion 11a.

[0077] 8, the pair of discharge flow paths 11b may be provided at the bottom of each of the pair of guide groove portions 11a, without providing cut portions 42a at both circumferential ends of the external engagement arm 42. Even in this case, it is possible to make it difficult for the lubricating oil supplied to the inside of the outer case 11 to be discharged while maintaining the lubricating function in the guide groove portions 11a.

[0078] In the above embodiment, the front plate 12 is described as opening up to the position of the radially outer end portion of the eccentric member 26 when the difference between the rotation axis X and the eccentric axis Y is greatest, with the rotation axis X as the center. However, the front plate 12 may be configured to open wider than the position of the radially outer end portion of the eccentric member 26 when the difference between the rotation axis X and the eccentric axis Y is greatest, with the rotation axis X as the center.

[0079] The present invention can be used in a valve timing control device. [Explanation of symbols]

[0080] 1: Crankshaft 2: Intake camshaft (camshaft) 11a: Guide groove portion 11b: Discharge flow path 12: Front plate 12a:Aperture 21: Support wall part 21a: Oil supply line 25: Output gear 26: Eccentric member 29: Second bearing (support bearing) 30: Input gear 41: Circular section 42: External engagement arm 100: Valve timing control device A: Drive side rotor B: Driven rotating body C: Phase adjustment mechanism Cx: Oldham coupling E: Engine (internal combustion engine) X: Rotation axis Y: Eccentric shaft center Z: Oil reservoir structure

Claims

1. a drive-side rotating body that rotates synchronously with the crankshaft of the internal combustion engine around a rotation axis; a driven-side rotor that is arranged coaxially with the rotation axis and inside the driving-side rotor, and that rotates integrally with a camshaft for opening and closing a valve of the internal combustion engine; and a phase adjustment mechanism that sets the relative rotational phase between the drive-side rotor and the driven-side rotor, The phase adjustment mechanism includes: an output gear provided on the driven rotor coaxially with the rotation axis; an input gear that rotates about an eccentric axis parallel to the rotation axis and is connected to the drive-side rotor; a cylindrical eccentric member that supports the input gear from an inner peripheral side via a support bearing and rotates the input gear, The rotation of the eccentric member causes the eccentric shaft to revolve, thereby changing the position of the meshing portion between the output gear and the input gear, the driven-side rotor has a support wall portion connected to an end of the camshaft in an orientation perpendicular to the rotation axis, the support wall portion has an oil supply passage that can supply lubricating oil from the outside to the inside of the driven-side rotating body, the drive-side rotor has a front plate on the opposite side of the eccentric member from the camshaft in the direction along the rotation axis, an oil reservoir structure that reduces the amount of lubricating oil discharged from the inside of the driving-side rotating body relative to the amount of lubricating oil supplied from the supply oil passage to the inside of the driven-side rotating body when the driving-side rotating body is rotating, the lubricating oil passes between the front plate and the drive-side rotor and is discharged to the outside of the drive-side rotor, A valve timing control device in which the amount of lubricating oil that passes between the front plate and the drive-side rotor and is discharged to the outside of the drive-side rotor is less than the amount of lubricating oil that flows through the meshing portion between the input gear and the driven-side rotor and the amount of lubricating oil that flows through the support bearing.

2. A drive-side rotating body that rotates synchronously with the crankshaft of an internal combustion engine around a rotation axis; a driven-side rotor that is arranged coaxially with the rotation axis and inside the driving-side rotor, and that rotates integrally with a camshaft for opening and closing a valve of the internal combustion engine; and a phase adjustment mechanism that sets the relative rotational phase between the drive-side rotor and the driven-side rotor, The phase adjustment mechanism includes: an output gear provided on the driven rotor coaxially with the rotation axis; an input gear that rotates about an eccentric axis parallel to the rotation axis and is connected to the drive-side rotor; a cylindrical eccentric member that supports the input gear from an inner peripheral side via a support bearing and rotates the input gear, The rotation of the eccentric member causes the eccentric shaft to revolve, thereby changing the position of the meshing portion between the output gear and the input gear, the driven-side rotor has a support wall portion connected to an end of the camshaft in an orientation perpendicular to the rotation axis, the support wall portion has an oil supply passage that can supply lubricating oil from the outside to the inside of the driven-side rotating body, the drive-side rotor has a front plate on the opposite side of the eccentric member from the camshaft in the direction along the rotation axis, an oil reservoir structure that reduces the amount of lubricating oil discharged from the inside of the driving-side rotating body relative to the amount of lubricating oil supplied from the supply oil passage to the inside of the driven-side rotating body when the driving-side rotating body is rotating, the support bearing is configured as a ball bearing having an inner ring that contacts an outer peripheral surface of the eccentric member and an outer ring that contacts an inner peripheral surface of the input gear, one axial side of the eccentric member is inserted into an opening in the radial center of the front plate, when the driving-side rotating body is rotating, the lubricating oil supplied to the inside of the driven-side rotating body flows between the inner circumferential surface of the driven-side rotating body and the outer circumferential surface of the eccentric member, and into the inside of the eccentric member; The valve timing control device has a front plate that covers the area through which the lubricating oil flows between the inner surface of the driven rotating body and the outer surface of the eccentric member when the support bearing is viewed from a direction along the rotation axis.

3. A drive-side rotating body that rotates synchronously with the crankshaft of an internal combustion engine around a rotation axis; a driven-side rotor that is arranged coaxially with the rotation axis and inside the driving-side rotor, and that rotates integrally with a camshaft for opening and closing a valve of the internal combustion engine; and a phase adjustment mechanism that sets the relative rotational phase between the drive-side rotor and the driven-side rotor, The phase adjustment mechanism includes: an output gear provided on the driven rotor coaxially with the rotation axis; an input gear that rotates about an eccentric axis parallel to the rotation axis and is connected to the drive-side rotor; a cylindrical eccentric member that supports the input gear from an inner peripheral side via a support bearing and rotates the input gear, The rotation of the eccentric member causes the eccentric shaft to revolve, thereby changing the position of the meshing portion between the output gear and the input gear, the driven-side rotor has a support wall portion connected to an end of the camshaft in an orientation perpendicular to the rotation axis, the support wall portion has an oil supply passage that can supply lubricating oil from the outside to the inside of the driven-side rotating body, the drive-side rotor has a front plate on the opposite side of the eccentric member from the camshaft in the direction along the rotation axis, an oil reservoir structure that reduces the amount of lubricating oil discharged from the inside of the driving-side rotating body relative to the amount of lubricating oil supplied from the supply oil passage to the inside of the driven-side rotating body when the driving-side rotating body is rotating, the phase adjustment mechanism further includes an Oldham coupling having an annular portion and a pair of external engagement arms projecting radially outward from the annular portion in directions opposite to each other, a pair of guide grooves extending radially outward in opposing directions from the inside to the outside of the drive-side rotor are formed in the opening edge portion with which the front plate abuts, in the shape of through grooves; the pair of external engagement arms are engaged with the pair of guide groove portions, respectively; Each of the pair of guide grooves has a discharge flow path formed by cutting from the inside to the outside of the driving-side rotor, A valve opening / closing timing control device in which the oil reservoir structure is configured so that the amount of lubricating oil discharged from the discharge flow path is less than the amount of lubricating oil circulating through the supply oil path when the drive side rotating body is rotating.

4. 4. The valve timing control device according to claim 3, wherein the amount of lubricating oil discharged from the discharge flow path is configured to be less than the amount of lubricating oil circulating through the supply oil path minus the amount of lubricating oil circulating inside the eccentric member.

5. one axial side of the eccentric member is inserted into an opening in the radial center of the front plate, 5. The valve timing control device according to claim 1, wherein the front plate is open to a position of the inserted radially outer end portion when the difference between the rotational axis and the eccentric axis of the eccentric member is greatest, with the rotational axis as the center.

6. A drive-side rotating body that rotates synchronously with the crankshaft of an internal combustion engine around a rotation axis; a driven-side rotor that is arranged coaxially with the rotation axis and inside the driving-side rotor, and that rotates integrally with a camshaft for opening and closing a valve of the internal combustion engine; and a phase adjustment mechanism that sets the relative rotational phase between the drive-side rotor and the driven-side rotor, The phase adjustment mechanism includes: an output gear provided on the driven rotor coaxially with the rotation axis; an input gear that rotates about an eccentric axis parallel to the rotation axis and is connected to the drive-side rotor; a cylindrical eccentric member that supports the input gear from an inner peripheral side via a support bearing and rotates the input gear, The rotation of the eccentric member causes the eccentric shaft to revolve, thereby changing the position of the meshing portion between the output gear and the input gear, the driven-side rotor has a support wall portion connected to an end of the camshaft in an orientation perpendicular to the rotation axis, the support wall portion has an oil supply passage that can supply lubricating oil from the outside to the inside of the driven-side rotating body, the drive-side rotor has a front plate on the opposite side of the eccentric member from the camshaft in the direction along the rotation axis, an oil reservoir structure that reduces the amount of lubricating oil discharged from the inside of the driving-side rotating body relative to the amount of lubricating oil supplied from the supply oil passage to the inside of the driven-side rotating body when the driving-side rotating body is rotating, one axial side of the eccentric member is inserted into an opening in the radial center of the front plate, the front plate is open to the position of the inserted radially outer end portion when the difference between the rotational axis and the eccentric axis of the eccentric member is greatest, with the rotational axis as the center.

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