WO2021084634A1

WO2021084634A1 - Valve timing adjustment device

Info

Publication number: WO2021084634A1
Application number: PCT/JP2019/042485
Authority: WO
Inventors: 琢也國重
Original assignee: 三菱電機株式会社
Priority date: 2019-10-30
Filing date: 2019-10-30
Publication date: 2021-05-06

Abstract

A spool (12) of an OCV function-equipped center bolt (10) comprises: a first land portion (12a) which, in a state in which the spool (12) is not pushed into the cam shaft (6) side, isolates a retard port (11c) and a drain port (11b) from each other, and which, in a state in which the spool (12) is pushed into the cam shaft (6) side, provides communication between the retard port (11c) and the drain port (11b); an opening portion (12d) which opens at a position closer to the drain port (11b) than the first land portion (12a) and communicates with the drain port (11b); and a wall portion (12e) which, in a state in which the spool (12) is pushed into the cam shaft (6) side, faces the retard port (11c) and extends to the drain port (11b) side beyond the retard port (11c).

Description

Valve timing adjuster

The present invention relates to a valve timing adjusting device.

The variable valve timing adjusting device (hereinafter referred to as "valve timing adjusting device" or "VVT") is a device that adjusts the opening / closing timing of the intake valve or the exhaust valve of the vehicle engine. This VVT is a case that rotates synchronously with the crankshaft, a rotor whose rotation phase is adjusted with respect to the case by the inflow and outflow of oil to the hydraulic chamber partitioned in the case, and an oil control valve that fastens the camshaft and the rotor (hereinafter referred to as an oil control valve). It is equipped with a center bolt with a function (referred to as "OCV"). When the VFS (Variable Force Solenoid) pushes the spool installed inside the center bolt and moves it in the axial direction, the path for supplying oil to the hydraulic chamber and the path for discharging oil from the hydraulic chamber are switched.

A center bolt with an OCV function as described in Patent Document 1 has a discharge port for discharging oil in a hydraulic chamber and a drain for discharging oil to the outside by opening an axial end on the side opposite to the camshaft. Has a port. The spool has a cylindrical drain hole extending in the axial direction and an opening in the drain hole that opens at the axial end on the side opposite to the camshaft and communicates with the drain port. When the VFS does not push the spool, the oil discharged from the hydraulic chamber enters the drain hole of the spool from the discharge port, flows from the opening to the drain port, and is discharged to the outside of the center bolt (for example, the figure of the same document). 3). When the VFS pushes the spool, the oil discharged from the hydraulic chamber flows from the discharge port to the drain port and is discharged to the outside of the center bolt (for example, FIG. 4 of the same document).

Japanese Patent No. 5637106

In the conventional center bolt with OCV function as described in Patent Document 1, when the VFS does not push the spool, the discharged oil that has entered the drain hole from the discharge port reaches the axial end inside the drain hole. There was a concern that the spool would collide and dynamic pressure would be generated, resulting in a shift in the moving position of the spool and deterioration of the control accuracy of oil inflow and outflow to the hydraulic chamber. Therefore, a large opening is provided in the spool to reduce the influence of the dynamic pressure of the discharged oil on the axial end portion inside the drain hole. However, if the spool opening is large, the drain port and the opening will be close to each other when the VFS pushes the spool, so that the drain oil will not flow directly from the drain port to the drain port, but from the drain port to the opening. It flows into the drain hole through the drain hole, and the discharged oil collides with the axial end portion inside the drain hole, causing dynamic pressure in the spool. In that case, when the spool is pushed in, the moving position of the spool shifts, and the accuracy of controlling oil inflow and outflow to and from the hydraulic chamber deteriorates.

The present invention has been made to solve the above problems, and an object of the present invention is to suppress the flow of discharged oil from the opening of the discharged oil into the spool when the spool is pushed.

The valve timing adjusting device according to the present invention includes a case that rotates synchronously with the crankshaft, a rotor that adjusts the rotation phase with respect to the case by injecting and discharging oil into and out of the hydraulic chamber partitioned in the case, a sleeve provided with a housing hole, and It has a bottomed tubular shape with the camshaft side open, has a spool that is coaxially accommodated in the accommodating hole, has a center bolt that fastens the camshaft and rotor, and the sleeve is on the opposite side of the camshaft. It has a drain port where the axial end of the is opened to discharge oil to the outside, and a first port which opens to the inner peripheral surface of the accommodating hole and discharges oil from the hydraulic chamber. The shape protrudes from the outer peripheral surface, and when the spool is not pushed toward the camshaft side, the first port and the drain port are blocked, and when the spool is pushed toward the camshaft side, the first port and the drain port are separated. The first land part that communicates, the opening that opens closer to the drain port than the first land part and communicates with the drain port, and when the spool is pushed toward the camshaft side, it faces the first port. It has a wall portion which is an outer peripheral surface from the first land portion to the opening of the outer peripheral surface of the spool extending beyond the first port toward the drain port side.

According to the present invention, in a state where the spool is pushed toward the camshaft side, there is a wall portion facing the first port and extending beyond the first port toward the drain port side, so that the spool is discharged from the first port. The oil can flow to the drain port along the wall portion, and the flow from the opening to the inside of the spool can be suppressed.

It is sectional drawing which shows the structural example of the VVT which concerns on Embodiment 1. FIG. It is an enlarged view of the center bolt with an OCV function of FIG. 1, FIG. 2A is before the spool is pushed in, and FIG. 2B is after the spool is pushed in. FIG. 3A is a cross-sectional view showing a configuration example of a conventional center bolt with an OCV function, FIG. 3A is before the spool is pushed in, and FIG. 3B is after the spool is pushed in. FIG. 4A is a cross-sectional view showing a configuration example of a center bolt with an OCV function according to a second embodiment, FIG. 4A is before the spool is pushed in, and FIG. 4B is after the spool is pushed in. It is an external perspective view which shows the spool. It is an external perspective view which shows the modification of the spool. It is an external perspective view which shows another modification of a spool.

Hereinafter, in order to explain the present invention in more detail, a mode for carrying out the present invention will be described with reference to the accompanying drawings.
Embodiment 1.
FIG. 1 is a cross-sectional view showing a configuration example of VVT1 according to the first embodiment. A plurality of hydraulic chambers (not shown) are formed inside the tubular case 2. Each of the plurality of hydraulic chambers is divided into an advance angle hydraulic chamber and a retard oil pressure chamber by a rotor 3 housed in the case 2. With the rotor 3 housed inside the case 2, the cover 4 is fixed to one opening of the case 2, and the plate 5 is fixed to the other opening of the case 2. A through hole 3a through which the center bolt 10 with an OCV function penetrates is provided in the central portion of the rotor 3, and a screw hole 6a for fastening the center bolt 10 with an OCV function is provided at the end of the camshaft 6. Has been done. Further, the rotor 3 has a supply oil passage 3e in which oil is supplied from an oil pump (not shown), a retard oil passage 3c communicating with the retard hydraulic chamber, and an advance oil passage communicating with the advance hydraulic chamber. 3d is provided.

A sprocket is formed on the outer peripheral surface of the case 2, and the driving force of the crankshaft of the engine is transmitted to the case 2 by a timing belt (not shown) attached to the sprocket, and the case 2 rotates synchronously with the crankshaft. To do. On the other hand, the rotor 3 is fixed to the camshaft 6 by the center bolt 10 with an OCV function and rotates synchronously with the camshaft 6. The rotation phase of the rotor 3 with respect to the case 2 is adjusted by the inflow and outflow of oil into the advance hydraulic chamber and the retard hydraulic chamber.

FIG. 2 is an enlarged view of the center bolt 10 with the OCV function of FIG. 1, FIG. 2A is before the spool 12 is pushed in, and FIG. 2B is after the spool 12 is pushed in. The center bolt 10 with an OCV function includes a sleeve 11, a spool 12, a bush 13, and a spring 14.

A male screw corresponding to the screw hole 6a of the camshaft 6 is provided on the outer peripheral surface of the sleeve 11. An accommodating hole 11a is provided inside the sleeve 11. The axial end of the accommodating hole 11a on the camshaft 6 side is closed, and the axial end of the accommodating hole 11a opposite to the camshaft 6 side is opened to drain oil to the outside. It is a port 11b. Further, the sleeve 11 is provided with a supply port 11e, a retard port 11c, and an advance port 11d opened on the inner peripheral surface of the accommodating hole 11a. The supply port 11e communicates with the supply oil passage 3e of the rotor 3. The retard angle port 11c communicates with the retard angle hydraulic chamber via the retard angle oil passage 3c of the rotor 3. The advance port 11d communicates with the advance hydraulic chamber via the advance oil passage 3d of the rotor 3.
In FIG. 2, the retarded port 11c closest to the drain port 11b corresponds to the “first port”.

The spool 12 has a bottomed tubular shape with the camshaft 6 side open, and is coaxially accommodated in the accommodating hole 11a of the sleeve 11. The spool 12 is pushed to the side opposite to the camshaft 6 side by a spring 14 installed at the axial end of the accommodating hole 11a on the camshaft 6 side, and is provided on the inner peripheral surface of the accommodating hole 11a. The position is regulated by the contact of the first land portion 12a with the bush 13. The spool 12 is pushed toward the camshaft 6 side against the load of the spring by a VFS (not shown) arranged at the axial end portion on the side opposite to the camshaft 6 side.

The outer peripheral surface of the spool 12 is provided with a first land portion 12a and a second land portion 12b having a shape protruding from the outer peripheral surface. As shown in FIG. 2A, the first land portion 12a shuts off the retard angle port 11c and the drain port 11b when the spool 12 is not pushed toward the camshaft 6, and the retard angle port 11c and the supply port 11e. Communicate with. Further, in the state where the spool 12 is pushed toward the camshaft 6 side as shown in FIG. 2B, the first land portion 12a communicates the retard angle port 11c and the drain port 11b, and communicates the retard angle port 11c and the supply port. It shuts off 11e. As shown in FIG. 2A, the second land portion 12b communicates the retard angle port 11c and the supply port 11e with the advance angle port 11d and the drain hole 12c in a state where the spool 12 is not pushed toward the camshaft 6 side. And shut off the advance port 11d and the supply port 11e. Further, in the state where the spool 12 is pushed toward the camshaft 6 side as shown in FIG. 2B, the second land portion 12b communicates the advance angle port 11d and the supply port 11e with the advance angle port 11d and the drain hole. It shuts off 12c.

Further, the spool 12 is provided with an opening 12d that opens at a position closer to the drain port 11b than the first land portion 12a and communicates with the drain port 11b. The opening 12d has, for example, a circular shape. Further, with the spool 12 pushed toward the camshaft 6, the first land on the outer peripheral surface of the spool 12 faces the retard port 11c and extends beyond the retard port 11c to the drain port 11b side. It has a wall portion 12e which is an outer peripheral surface from the portion 12a to the opening 12d.

When adjusting the rotation phase of VVT1 in the retard direction, the VFS does not push the spool 12. At this time, as shown in FIG. 2A, the oil supplied by the oil pump enters the supply port 11e from the supply oil passage 3e, flows through the retard angle oil passage 3c from the retard angle port 11c, and is introduced into the retard angle hydraulic chamber. To. At the same time, the oil in the advance hydraulic chamber exits from the advance oil passage 3d to the advance port 11d, flows through the accommodating hole 11a to the drain hole 12c, and flows to the opening 12d as shown by the arrow in FIG. 2A. It is discharged to the outside from the drain port 11b through the drain port 11b. Since the opening 12d is sufficiently large, the oil that has entered the drain hole 12c exits the opening 12d without colliding with the axial end inside the drain hole 12c. Therefore, the dynamic pressure received by the axial end inside the drain hole 12c at the time of oil discharge is suppressed, the moving position of the spool 12 does not shift, and the control accuracy of oil inflow and outflow to the advance hydraulic chamber and the retard hydraulic chamber is improved. To do.

When adjusting the rotation phase of VVT1 in the advance angle direction, the VFS pushes in the spool 12. At this time, as shown in FIG. 2B, the oil supplied by the oil pump enters the supply port 11e from the supply oil passage 3e, flows from the advance angle port 11d through the advance angle oil passage 3d, and is introduced into the advance angle hydraulic chamber. To. At the same time, the oil in the retard angle hydraulic chamber exits from the retard angle oil passage 3c to the retard angle port 11c and is led out to the drain port 11b along the wall portion 12e as shown by an arrow in FIG. 2B to the outside. It is discharged. Since the wall portion 12e changes the direction in which the oil flows toward the drain port 11b, the oil in the retard angle port 11c is suppressed from flowing into the drain hole 12c from the opening 12d. Therefore, the dynamic pressure received by the axial end inside the drain hole 12c at the time of oil discharge is suppressed, the moving position of the spool 12 does not shift, and the control accuracy of oil inflow and outflow to the advance hydraulic chamber and the retard hydraulic chamber is improved. To do.

Here, the effect produced by VVT1 according to the first embodiment will be described with reference to FIG.
FIG. 3 is a cross-sectional view showing a configuration example of a conventional center bolt 10A with an OCV function. FIG. 3A is before the spool 12 is pushed in, and FIG. 3B is after the spool 12 is pushed in. The difference between the conventional center bolt 10A with an OCV function and the center bolt 10 with an OCV function according to the first embodiment is the length of the wall portion 12e. The wall portion 12f of the conventional center bolt 10A with an OCV function has a length facing the retard angle port 11c when the spool 12 is pushed in, and is the retard angle port 11c as in the wall portion 12e of the first embodiment. Does not extend beyond the drain port 11b side.

When the spool 12 is not pushed as shown in FIG. 3A, the oil in the advance hydraulic chamber exits the advance oil passage 3d to the advance port 11d and is accommodated as shown by the arrow in FIG. 3A. It flows through the hole 11a to the drain hole 12c, passes through the opening 12d, and is discharged to the outside from the drain port 11b. Since the opening 12d is sufficiently large, the oil that has entered the drain hole 12c exits the opening 12d without colliding with the axial end inside the drain hole 12c. Therefore, the dynamic pressure received by the axial end inside the drain hole 12c at the time of oil discharge is suppressed, the moving position of the spool 12 does not shift, and the control accuracy of oil inflow and outflow to the advance hydraulic chamber and the retard hydraulic chamber is improved. To do.

When the spool 12 is pushed in as shown in FIG. 3B, the oil in the retard angle hydraulic chamber exits from the retard angle oil passage 3c to the retard angle port 11c, and as shown by the arrow in FIG. 3B, the retard angle It flows into the drain hole 12c through the opening 12d near the port 11c. The oil that has flowed into the drain hole 12c collides with the axial end portion inside the drain hole 12c, then exits from the opening 12d and is discharged to the outside from the drain port 11b. Since the wall portion 12f is shorter than the wall portion 12e, the direction in which the oil flowing out of the retard angle port 11c cannot be changed, and the oil flows from the retard angle port 11c to the opening 12d. Therefore, when the oil is discharged, the axial end portion inside the drain hole 12c receives dynamic pressure, the moving position of the spool 12 shifts, and the control accuracy of oil inflow and outflow to the advance angle hydraulic chamber and the retard angle hydraulic chamber deteriorates.

As described above, the VVT 1 according to the first embodiment includes a case 2 that rotates synchronously with the crankshaft, a rotor 3 whose rotation phase with respect to the case 2 is adjusted by the inflow and outflow of oil to the hydraulic chamber partitioned in the case 2. The camshaft 6 and the rotor 3 are fastened together with a sleeve 11 provided with the accommodating hole 11a and a spool 12 having a bottomed tubular shape with the camshaft 6 side open and accommodated coaxially in the accommodating hole 11a. It is provided with a center bolt 10 with an OCV function. The sleeve 11 has a drain port 11b whose axial end on the side opposite to the camshaft 6 side is opened to discharge oil to the outside, and an opening on the inner peripheral surface of the accommodating hole 11a to allow oil to flow from the retarded hydraulic chamber. It has a retarded port 11c to be discharged. The spool 12 has a shape protruding from the outer peripheral surface of the spool 12, and when the spool 12 is not pushed toward the camshaft 6, the retard port 11c and the drain port 11b are blocked and pushed toward the camshaft 6. In this state, the first land portion 12a communicating the retarded port 11c and the drain port 11b, and the opening 12d opening at a position closer to the drain port 11b than the first land portion 12a and communicating with the drain port 11b. The spool 12 faces the retard port 11c in a state of being pushed toward the camshaft 6, and has a wall portion 12e extending beyond the retard port 11c to the drain port 11b side. With this configuration, when the spool 12 is pushed toward the camshaft 6, the oil discharged from the retarded port 11c flows to the drain port 11b along the wall portion 12e, so that the spool 12 is flown from the opening 12d. It is possible to suppress the inflow to the inside.

In FIG. 2, the retarded port 11c closest to the drain port 11b corresponds to the “first port”.
The positions of the retard oil passage 3c and the advance oil passage 3d of the rotor 3 may be opposite to each other. In that case, the positions of the retard port 11c and the advance port 11d of the sleeve 11 are also reversed. That is, in FIG. 2, the retard port 11c is arranged at the position farthest from the drain port 11b, and the advance port 11d is arranged at the position closest to the drain port 11b. Then, the advance port 11d closest to the drain port 11b becomes the "first port".

Embodiment 2.
In the first embodiment, the first land portion 12a that switches the oil flow path also functions as a stopper portion that regulates the position of the spool 12 in the axial direction. On the other hand, in the second embodiment, the first land portion 12a and the stopper portion are separate bodies.

FIG. 4 is a cross-sectional view showing a configuration example of the center bolt 10 with an OCV function according to the second embodiment, FIG. 4A is before the spool 12 is pushed in, and FIG. 4B is after the spool 12 is pushed in. FIG. 5 is an external perspective view showing the spool 12 of FIG. In FIGS. 4 and 5, the same or corresponding parts as those in FIGS. 1 to 3 are designated by the same reference numerals, and the description thereof will be omitted.

The spool 12 has a plurality of column portions 12g extending in the axial direction provided at the axial end portion on the side opposite to the camshaft 6 side. In the illustrated example, the spool 12 is provided with three pillars 12g, but the number of pillars 12g may be arbitrary. The gap between the adjacent pillar portions 12g is an opening 12d1 that communicates the drain hole 12c and the drain port 11b.

Each of the pillar portions 12g is provided with a stopper portion 12h having a shape protruding from the outer peripheral surface. The stopper portion 12h regulates the position of the spool 12 pushed by the spring 14 by abutting the bush 13 in a state where the spool 12 is not pushed toward the camshaft 6. Further, when the spool 12 moves in the axial direction, the stopper portion 12h functions as a sliding portion that moves while being in contact with the inner peripheral surface of the accommodating hole 11a. The first land portion 12a and the second land portion 12b also function as sliding portions.

Further, the surface of the stopper portion 12h on the camshaft 6 side is an inclined surface 12i in which the amount of protrusion in the radial direction increases from the camshaft 6 side toward the side opposite to the camshaft 6.

As described above, the sleeve 11 of the second embodiment has a bush 13 protruding from the inner peripheral surface of the accommodating hole 11a. The spool 12 has a plurality of pillars 12g extending in the axial direction provided at the axial end on the side opposite to the camshaft 6 side, and the spool 12 has a shape protruding from the pillars 12g. It has a stopper portion 12h that comes into contact with the bush 13 in a state where it is not pushed to the side, and a gap between adjacent pillar portions 12g constitutes the opening portion 12d1. Since the first land portion 12a, the second land portion 12b, and the stopper portion 12h come into contact with the inner peripheral surface of the accommodating hole 11a, the first land portion 12a and the second land portion 12a and the second land portion as in the first embodiment. The inclination of the spool 12 with respect to the axial direction is suppressed as compared with the case where the two points of 12b are in contact with each other. Therefore, the accuracy of controlling the oil inflow and outflow to and from the advance hydraulic chamber and the retard hydraulic chamber is improved.

Further, according to the second embodiment, the surface of the stopper portion 12h on the camshaft 6 side is an inclined surface 12i in which the amount of protrusion in the radial direction increases from the camshaft 6 side toward the side opposite to the camshaft 6. is there. When the surface of the stopper portion 12h on the camshaft 6 side is a surface perpendicular to the outer peripheral surface of the spool 12, the spool 12 comes out of the retard port 11c and the wall portion is in a state of being pushed toward the camshaft 6 side. Since the oil flowing along 12e hits this vertical surface, the oil flow is likely to be disturbed. On the other hand, when the surface of the stopper portion 12h on the camshaft 6 side is an inclined surface 12i, the oil that comes out of the retard angle port 11c and flows along the wall portion 12e can smoothly flow in the direction of the drain port 11b. .. Further, since the dynamic pressure received by the inclined surface 12i is smaller than the dynamic pressure received by the vertical surface, the deviation of the moving position of the spool 12 is suppressed.

The inclined surface 12i is not limited to the shapes shown in FIGS. 4 and 5, and the oil that comes out of the retarded port 11c and flows along the wall portion 12e can smoothly flow in the direction of the drain port 11b. It may be in shape. A modified example of the inclined surface 12i is shown below.

FIG. 6 is an external perspective view showing a modified example of the spool 12. In the modified example of FIG. 6, the surface of the stopper portion 12h on the camshaft 6 side is an inclined surface 12i in which the amount of protrusion in the circumferential direction increases from the camshaft 6 side toward the side opposite to the camshaft 6. The inclined surface 12i having this shape also allows the oil flowing out of the retarded port 11c and flowing along the wall portion 12e to smoothly flow in the direction of the drain port 11b when the spool 12 is pushed toward the camshaft 6. ..

FIG. 7 is an external perspective view showing another modified example of the spool 12. In the modified example of FIG. 7, the surface of the stopper portion 12h on the camshaft 6 side is a V-shaped inclined surface 12i whose width increases from the camshaft 6 side toward the side opposite to the camshaft 6. The inclined surface 12i having this shape also allows the oil flowing out of the retarded port 11c and flowing along the wall portion 12e to smoothly flow in the direction of the drain port 11b when the spool 12 is pushed toward the camshaft 6. ..

In the first embodiment, the pillar portion 12g and the opening portion 12d1 of the second embodiment are provided at a position closer to the drain port 11b than the first land portion 12a of the spool 12 instead of the opening 12d. You may.

The present invention allows any combination of embodiments, modifications of any component of each embodiment, or omission of any component of each embodiment within the scope of the invention.

The VVT according to the present invention is suitable for use in a VVT that adjusts the opening / closing timing of the intake valve or the exhaust valve of an engine.

1 VVT, 2 case, 3 rotor, 3a through hole, 3c retard angle oil passage, 3d advance angle oil passage, 3e supply oil passage, 4 cover, 5 plate, 6 camshaft, 6a screw hole, 10, 10A with OCV function Center bolt, 11 sleeve, 11a accommodating hole, 11b drain port, 11c retard angle port (1st port), 11d advance angle port, 11e supply port, 12 spool, 12a 1st land part, 12b 2nd land part, 12c drain Holes, 12d, 12d1 openings, 12e, 12f walls, 12g pillars, 12h stoppers, 12i inclined surfaces, 13 bushes, 14 springs.

Claims

A case that rotates synchronously with the crankshaft,
A rotor whose rotational phase with respect to the case is adjusted by the inflow and outflow of oil into and out of the hydraulic chamber partitioned in the case.
A sleeve provided with an accommodating hole and a bottomed tubular shape having an open camshaft side, having a spool coaxially accommodating in the accommodating hole, and a center bolt for fastening the camshaft and the rotor. Prepare,
The sleeve
A drain port that opens the axial end on the opposite side of the camshaft to drain oil to the outside.
It has a first port that opens to the inner peripheral surface of the accommodating hole and discharges oil from the hydraulic chamber.
The spool
When the spool has a shape protruding from the outer peripheral surface and the spool is not pushed toward the camshaft side, the first port and the drain port are blocked, and when the spool is pushed toward the camshaft side. A first land portion that communicates the first port and the drain port,
An opening that opens closer to the drain port than the first land portion and communicates with the drain port.
From the first land portion of the outer peripheral surface of the spool, which faces the first port in a state where the spool is pushed toward the camshaft side and extends beyond the first port to the drain port side. A valve timing adjusting device having a wall portion that is an outer peripheral surface up to the opening.
The sleeve has a bush protruding from the inner peripheral surface of the accommodating hole.
The spool has a plurality of pillars extending in the axial direction provided at the axial end on the opposite side of the camshaft, and the spool has a shape protruding from the pillars so that the spool moves toward the camshaft. The valve timing adjusting device according to claim 1, further comprising a stopper portion that comes into contact with the bush in a non-pushed state, and a gap between adjacent pillar portions constitutes the opening.
The second aspect of claim 2, wherein the surface of the stopper portion on the camshaft side is an inclined surface in which the amount of protrusion in the radial direction increases from the camshaft side toward the side opposite to the camshaft. Valve timing adjuster.
The second aspect of claim 2, wherein the surface of the stopper portion on the camshaft side is an inclined surface in which the amount of protrusion in the circumferential direction increases from the camshaft side toward the side opposite to the camshaft. Valve timing adjuster.
The valve according to claim 2, wherein the surface of the stopper portion on the camshaft side is a V-shaped inclined surface whose width increases from the camshaft side toward the side opposite to the camshaft. Timing adjuster.