JPH0960507A - Valve timing adjusting device for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To attain miniaturization while ensuring member strength and sealability, by receiving three vanes relatively turnably only in a prescribed angular range in a housing member rotated with either one of a drive shaft or driven shaft. SOLUTION: When pressure oil from a pump is supplied to each oil path 36, 29, pressure oil is distributed to each delay timing pressure oil chamber 10, 11 and an oil pressure chamber through each oil path 31 to 33 form the oil path 29, and a vane rotor 9 is released from connection to a shoe housing 3. From an oil path 30 through each oil path 34, 45, pressure oil is distributed to a pressure oil chamber 24 through each advance timing pressure oil chamber 12, 13 and pressure oil path 25, and when each delay timing pressure oil chamber 10, 11 and pressure oil chamber are opened to an oil tank 45, an oil pressure of each advance timing oil pressure chamber 12, 13 acts in a side surface of each vane 9a, 9b, the vane rotor 9 is turned, for instance, in the clockwise direction, that is, in an advance timing direction relating to the shoe housing 3, and valve timing of a cam shaft 2 is advanced.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an internal combustion engine (hereinafter referred to as "internal combustion engine").
The present invention relates to a valve timing adjustment device for changing the opening / closing timing of at least one of an intake valve and an exhaust valve of an "internal combustion engine" as an engine according to operating conditions.

[0002]

2. Description of the Related Art Conventionally, a camshaft is driven via a timing pulley or a chain sprocket that rotates in synchronization with an engine crankshaft, and the intake valve and the exhaust valve are driven by the phase difference caused by the relative rotation of the timing pulley or the chain sprocket and the camshaft. As a vane type valve timing adjusting device that opens and closes at least one of the valves, many that have two vanes or four or more vanes are disclosed.

[0003]

However, in such a conventional vane type valve timing adjusting device,
It is necessary to axially tighten the housing made up of a plurality of members and liquid-tightly accommodate the vane in the housing. With two vanes, the housing is tightened in two places and the tightening force is weak, so there is a risk of hydraulic oil leaking when the operating pressure becomes high. Further, since the pressure receiving area of the vane is small, it is necessary to increase the working pressure, which causes a problem that the device becomes large.

When there are four or more vanes, the pressure receiving area increases, but the thickness of the vane in the circumferential direction decreases, so that the strength of the vane decreases. In addition, since the circumferential seal length at the axial end contact portions between the vane and the housing is shortened, there is a problem that the sealing performance is deteriorated. Further, in such a vane type valve timing adjusting device, since a plurality of hydraulic chambers are provided, the structure of the oil passage that distributes the operating pressure to each hydraulic chamber becomes complicated, which makes it difficult to downsize the device and reduce the oil size. There is a problem that the number of man-hours for processing the road increases.

The present invention has been made in order to solve such a problem, and provides a vane type valve timing adjusting device which is easy to process and has a shape capable of reliably exhibiting required performance. With the goal. Another object of the present invention is to provide a valve timing adjusting device that is optimally miniaturized and easy to process while ensuring member strength and sealing performance.

[0006]

According to the valve timing adjusting apparatus for an engine of the present invention, the number of vanes accommodated in the housing is three, and
Optimal downsizing of the device can be achieved while ensuring the strength of the vane and the sealing property in the vane circumferential direction. According to the valve timing adjusting apparatus for an engine of claim 2 of the present invention, a groove passage is provided in at least one of both axial end faces of a supporting member of a vane that rotates together with a drive shaft or a driven shaft, and the vane is provided via this groove passage. By applying the working pressure to the working pressure chambers defined by, the structure of the oil passage from the hydraulic drive source to the support member and the oil passage from the groove passage to each working pressure chamber is simplified regardless of the number of vanes. It also facilitates the distribution of operating pressure to each vane. Therefore, it is easy to downsize the device.

According to the engine valve timing adjusting apparatus of the third aspect of the present invention, the vane strength and the vane strength are improved by providing three vanes and providing groove passages on at least one of both axial end faces of the support member. Since the structure of the oil passage can be simplified while ensuring the sealing performance in the circumferential direction of the vane, the size of the device can be optimized. According to the engine valve timing adjusting device of the fourth aspect of the present invention, by forming the groove passages for applying the working pressure to the advance hydraulic chamber and the retard hydraulic chamber respectively on both axial end faces of the support member, the advance angle is increased. Since the oil passages that apply operating pressure to the hydraulic chamber and the retard hydraulic chamber do not interfere with each other in the support member,
Distribution of operating pressure to each hydraulic chamber becomes easy. Therefore, it is easy to downsize the device.

[0008]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a block diagram showing a first embodiment of the present invention; (First Embodiment) FIGS. 1 to 8 show an engine valve timing adjusting device according to a first embodiment of the present invention. FIG.
It shows a hydraulic circuit of the first embodiment.

A chain sprocket 1 shown in FIG. 2 receives a driving force from a crankshaft as a drive shaft of an engine (not shown) by a chain (not shown) and rotates in synchronization with the crankshaft. The camshaft 2 as a driven shaft receives the driving force from the chain sprocket 1 and drives at least one of an intake valve and an exhaust valve (not shown) to open and close. The camshaft 2 is rotatable with a predetermined phase difference with respect to the chain sprocket 1. The chain sprocket 1 and the camshaft 2 rotate clockwise as viewed in the direction of arrow X shown in FIG. Hereinafter, this rotation direction is referred to as an advance direction.

As shown in FIGS. 1 and 2, the chain sprocket 1, the shoe housing 3, and the front plate 4, which are housing members, are coaxially fixed by bolts 14. Boss 1a of chain sprocket 1
The inner peripheral wall of is fitted to the tip portion 2a of the camshaft 2 so as to be relatively rotatable. The front plate 4 and the shoe housing 3 are positioned by a knock pin 26, and the shoe housing 3 and the chain sprocket 1 are positioned by a knock pin 27 in the rotational angle direction.

As shown in FIG. 1, the shoe housing 3 has trapezoidal shoes 3a and 3b facing each other. The respective facing surfaces of the shoes 3a and 3b are formed in an arcuate cross section, and the vanes 9a and 9b are respectively provided in the two circumferential gaps of the shoes 3a and 3b.
A fan-shaped space portion is formed as a storage chamber for the. As shown in FIGS. 1 and 2, the vane rotor 9 has a support member 9f.
And a vane 9a which is integrally formed with the support member 9f at both ends in the radial direction of the support member 9f and which rotates together with the support member 9f.
And 9b. The support member 9f is integrally fixed to the camshaft 2 with a bolt 15. Vane 9a
And 9b are fan-shaped, and the vanes 9a and 9b are rotatably accommodated in a fan-shaped space formed in a circumferential gap between the shoes 3a and 3b. The spigot portion 9c is coaxially fitted to the tip portion 2a of the cam shaft 2, and the vane rotor 9 and the cam shaft 2 are fitted with a knock pin 2a.
Positioning in the rotational angle direction is performed by 8. The cylindrical protrusion 5 fixed integrally with the vane rotor 9 is fitted to the inner peripheral wall of the front plate 4 so as to be relatively rotatable.
As shown in FIG. 1, minute clearances 16 and 17 are provided between the outer peripheral wall of the vane rotor 9 and the inner peripheral wall of the shoe housing 3, and the vane rotor 9 is rotatable relative to the shoe housing 3. Shoe 3a and vane 9
A retarded hydraulic chamber 10 is formed between the shoe 3b and the vane 9b, and a retarded hydraulic chamber 12 is formed between the shoe 3a and the vane 9b. The advancing hydraulic chamber 13 is formed between the shoe 3b and the vane 9a.
Are formed.

As shown in FIGS. 1, 2 and 3, on both axial end surfaces of the supporting member 9f of the vane rotor 9, the oil passage 29 as a groove passage and the camshaft 2 at the contact portion with the cylindrical protrusion portion 5 are provided. Oil passage 30 as a groove passage at the contact portion with
Are provided so as to be shifted in the circumferential direction in a C shape.
The oil passage 29 is connected to the retard angle hydraulic chambers 10 and 1 by the oil passages 31 and 32.
1, and communicates with the hydraulic chamber 23 through the oil passage 33. The oil passage 30 is advanced by the oil passages 34 and 35,
It communicates with 13. The oil passage 36 communicates with an oil passage 39 formed in the cam shaft 2 at an axial contact portion between the support member 9f and the cam shaft 2, and the oil passage 29 is connected to the support member 9f and the cylindrical protruding portion 5. Is in communication with the oil passage 36 at an axial contact portion thereof. The oil passage 30 communicates with an oil passage 38 formed in the camshaft 2 at an axial contact portion between the support member 9f and the camshaft 2. By thus forming the oil passages 29 and 30 on both axial end surfaces of the support member 9f, it becomes easy to distribute the hydraulic pressure to each hydraulic chamber.
Further, by simplifying the structure of the oil passage in the support member 9f, it is possible to prevent the oil passages from interfering with each other in the support member 9f and to reduce the diameter of the support member 9f. Furthermore, the oil passage in the support member 9f can be easily processed.

The axial length of the vanes 9a and 9b is
It is set to be slightly smaller than the axial length of the shoe housing 3 sandwiched between the front plate 4 and the chain sprocket 1. With the above structure, the camshaft 2 and the vane rotor 9 are connected to the chain sprocket 1,
It is rotatable relative to the shoe housing 3 and the front plate 4 coaxially.

As shown in FIG. 2, the journal portion 42 of the camshaft 2 is rotatably supported by a bearing portion 41 provided on the cylinder head 40 and is restricted from moving in the rotation axis direction. Outer peripheral groove passages 43 and 44 are provided in the outer peripheral wall of the journal portion 42 in the circumferential direction. The supply oil passage 47 for pumping the oil in the oil tank 45 by the pump 46 and the discharge oil passage 48 for discharging the oil into the oil tank 45 are selectively connected to the outer peripheral groove passages 43 and 44 by the switching operation of the switching valve 49. Can be connected or disconnected. The pump 46 and the switching valve 49 constitute hydraulic drive means. In this embodiment, the switching valve 49 is a well-known 4-port guide valve.

As shown in FIG. 3, the outer peripheral groove passage 43 communicates with the oil passage 30 at the axial contact portion between the support member 9f and the cam shaft 2 by the oil passages 37 and 38 in the cam shaft 2. . As shown in FIG. 2, the outer peripheral groove passage 44 is connected to the oil passage 36 of the support member 9f at the axial contact portion between the support member 9f and the camshaft 2 by the oil passage 39 in the camshaft 2. With the above configuration, the outer peripheral groove passage 4
A switching valve 49 for supplying pressure oil from the pump 46 to 3 and 44.
To selectively supply the retarded hydraulic chambers 10 and 11 and the hydraulic chambers 23, the advanced hydraulic chambers 12 and 13 and the hydraulic chambers 24 from the pump 46, and to the oil tank 45. Can be discharged.

As shown in FIG. 2, the stopper piston 7 as a connecting member is housed inside the vane 9a of the vane rotor 9. The stopper piston 7 is composed of a small-diameter portion 7a and a large-diameter portion 7b, and the tip portion 7c of the small-diameter portion 7a is located on the side opposite to the large-diameter portion 7b, that is, in the direction in which the stopper piston 7 fits into the stopper hole 20. Therefore, it is formed in a slightly tapered shape. The large diameter portion 7b of the stopper piston 7 is housed in the housing hole 8 of the vane 9a,
The camshaft 2 is provided on the inner wall of the vane 9a forming the accommodation hole 8.
Is slidably supported in the axial direction. A spring 18 is incorporated in the accommodation hole 8 on the right side in the axial direction of the stopper piston 7 shown in FIG. The guide ring 19 is loosely fitted or press-fitted to the inner wall of the vane 9a forming the accommodation hole 8, and is loosely fitted to the outer wall of the small diameter portion 7a of the stopper piston 7. Therefore, the stopper piston 7 is the camshaft 2
Is housed in the vane 9a so as to be slidable in the axial direction and is biased to the front plate 4 side by the spring 18.

As shown in FIG. 4, the tapered surface of the tip portion 7c of the stopper piston 7 abuts the tapered surface of the stopper hole 20, and the tip surface 7d of the stopper piston 7 has a stopper hole 2
It is not in contact with the bottom of 0. Therefore, the stopper piston 7
Even if the positional relationship between the axis of the stopper and the center of the stopper hole 20 varies due to an error in manufacturing accuracy, etc., the axial position correction of the stopper piston 7 automatically performed by the spring 18
It is possible to prevent fitting error or backlash.

1 and 2 show the vane rotor 9 in the most retarded state with respect to the shoe housing 3,
The stopper portion 9e of the vane 9b is in contact with the side surface of the shoe 3a. As shown in FIG. 4, in this state, the tip portion 7c of the stopper piston 7 is fitted into the tapered stopper hole 20 of the front plate 4, and the tapered side surface of the tip portion 7c is tapered by the spring 18. Is urged by. Tip part 7 of stopper piston 7
The taper angle of c and the taper angle of the stopper hole 20 are set to be the same.

As shown in FIG. 2, a drain hole 21 is provided on the side wall of the vane 9a forming the accommodation hole 8 on the side of the chain sprocket 1 so that the vane rotor 9 has the most retarded angle. Since the atmosphere hole 22 and the drain hole 21 are substantially aligned with each other, the accommodation hole 8
The space portion on the spring 18 side of the stopper piston 7, which is a part of the above, corresponds to atmospheric pressure. As shown in FIG. 2, a hydraulic chamber 23 is formed between the guide ring 19 and the large diameter portion 7b of the stopper piston 7. A hydraulic chamber 24 is formed between the stopper hole 20 of the front plate 4 and the small diameter portion 7a of the stopper piston 7, and the hydraulic chamber 24 and the advance hydraulic chamber 1 are formed.
An oil passage 25 of the front plate 4 communicates with the oil tank 3.

By making the clearance 16 at the outermost diameter portion of the vanes 9a and 9b minute, the circumferential lengths of the vanes 9a and 9b are relatively long, so that the retarded hydraulic chamber 10 and the advanced hydraulic chamber are provided. 13, the retard hydraulic chamber 11 and the advance hydraulic chamber 12 are prevented from communicating with each other through the clearance 16 as much as possible. Further, the seal component 6 is mounted in the groove 9d formed on the outer peripheral wall of the support member 9f in the minute clearance 17 formed in the minimum diameter portion of the shoes 3a and 3b, and the retard angle hydraulic chamber 10 and the advance angle hydraulic pressure are provided. Chamber 12, retard hydraulic chamber 1
1 and the advance hydraulic chamber 13 are prevented from communicating with each other through the clearance 17 as much as possible. Also, shoe housing 3
Since the vane rotor 9 rotates relative to the vane rotor 9, a sliding clearance is formed between the axially opposite end faces of the vane rotor 9 and the inner side faces of the chain sprocket 1 and the front plate 4. Oil may leak from the sliding clearance between the hydraulic chambers. However, by making the axial length of the vane rotor 9 slightly smaller than the axial length of the shoe housing 3, both ends of the vane rotor 9 in the axial direction can be reduced. The sliding clearance formed on the surface can be made minute. Further, the circumferential length of the vanes 9a and 9b is relatively long, that is, the cross-sectional area of the vanes 9a and 9b is large, so that the oil leak between the hydraulic chambers can be prevented as much as possible. Therefore, the hydraulic pressure in each hydraulic chamber can be maintained at a predetermined value, so that the vane rotor 9 with respect to the shoe housing 3 can be held.
Relative rotation can be controlled with high accuracy. Further, since the cross-sectional area of the vanes 9a and 9b is large, the stopper piston 7 can be easily housed.

Next, the operation of the valve timing adjusting device will be described. As shown in FIGS. 1 and 2, when the pressure oil from the pump 46 at the time of engine start is not yet introduced into the hydraulic chambers 23 and 24, the vane rotor 9 is the slowest with respect to the shoe housing 3 as the crankshaft rotates. At the angular position, the tip end portion 7c of the stopper piston 7 is fitted into the stopper hole 20 of the front plate 4 by the urging force of the spring 18, and the vane rotor 9 is connected to the shoe housing 3 by the stopper piston 7. At this time, the vane stopper 9e is in contact with the side surface of the shoe 3a. Therefore, the rotational driving force is transmitted from the chain sprocket 1 to the camshaft 2 and the camshaft 2 is positively moved.
Even if a negative reversing torque is generated, the vane rotor 9 and the shoe housing 3 do not generate relative rotational vibration,
Generation of tapping sound is prevented.

As shown in FIG. 5, 49 of the switching valve 49
When a is selected and the pressure oil is pumped from the pump 46, the pressure oil is supplied to the outer peripheral groove passage 44 and the oil passages 39, 36 and 29, and is delayed from the oil passage 29 via the oil passages 31, 32 and 33. Pressure oil is distributed to the angular hydraulic chambers 10 and 11 and the hydraulic chamber 23.
The force received by the stopper piston 7 due to the oil pressure in the hydraulic chamber 23 is the chain of the housing hole 8 against the urging force of the spring 18 due to the difference in pressure receiving area due to the diameter difference between the small diameter portion 7a and the large diameter portion 7b of the stopper piston 7. It works to push the stopper piston 7 toward the sprocket 1 side. Then, the tip end portion 7c of the stopper piston 7 completely comes out of the stopper hole 20 of the front plate 4, so that the vane rotor 9 is disconnected from the shoe housing 3. However, the oil pressure in the retard hydraulic chambers 10 and 11 is reduced by the vanes 9a and 9b.
, The vane rotor 9 is still held in the most retarded position shown in FIG. 1 with respect to the shoe housing 3. For this reason, generation of hammering sound between the vane rotor 9 and the shoe housing 3 is prevented. Note that the retard hydraulic chamber 1
The oil that slightly leaks from 0, 11 to the advance hydraulic chambers 12, 13 is the oil passages 34, 35, 30, 38, 37, and the outer peripheral groove passage 4
The oil is discharged from the switching valve 49a to the oil tank 45 via the valve 3.

FIG. 5 shows that 49a of the switching valve 49 is selected.
From the state shown in FIG.
When 9c is selected, the pressure oil from the pump 46 is supplied to the outer peripheral groove passage 43 and the oil passages 37, 38, 30 and is advanced from the oil passage 30 via the oil passages 34, 35 to the advance hydraulic chambers 12, 13 and. Pressure oil is distributed to the hydraulic chamber 24 via the oil passage 25, and the retard hydraulic chambers 10, 11 and the hydraulic chamber 23 are connected to the oil tank 45.
Is released to. At this time, since the hydraulic pressure in the hydraulic chamber 23 is reduced to almost atmospheric pressure, the stopper piston 7 tries to return to the stopper hole 20 by the spring 18, but the hydraulic pressure in the hydraulic chamber 24 acts on the tip surface 7d of the stopper piston 7, and the stopper piston 7 is stopped. The piston 7 remains pushed into the chain sprocket 1 side of the accommodation hole 8 against the biasing force of the spring 18. Therefore, the hydraulic pressure in the advance hydraulic chambers 12 and 13 causes the vane 9 to move.
The vane rotor 9 acts on the side surfaces of a and 9b and rotates in the clockwise direction, that is, the advance direction with respect to the shoe housing 3, and the valve timing of the camshaft 2 is advanced. When the vane rotor 9 rotates with respect to the shoe housing 3, the distal end portion 7c of the stopper piston 7 and the stopper hole 20 of the front plate 4 are displaced from each other in the circumferential direction, so that the stopper piston 7 does not fit into the stopper hole 20. FIG. 7 shows a state in which the vane rotor 9 is most advanced with respect to the shoe housing 3. When 49a of the switching valve 49 is selected from the state of FIG. 7, the vane rotor 9 rotates counterclockwise, that is, in the retard direction with respect to the shoe housing 3 when viewed from the X direction of FIG. 2, and the valve timing of the camshaft 2 is delayed. To be done. If the switching valve 49b is selected while the vane rotor 9 is rotating in the advance direction or the retard direction with respect to the shoe housing 3, the retard angle hydraulic chambers 10 and 11 are selected.
Inflow and outflow of oil in the advance hydraulic chambers 12 and 13 are blocked, and the vane rotor 9 is held at an intermediate position, so that a desired valve timing can be obtained. As described above, the stopper piston 7 is fitted into the stopper hole 20 of the front plate 4 when the vane rotor 9 is at the most retarded position with respect to the shoe housing 3 and pressure oil is not introduced, and the pressure oil is When it is introduced, it will not fit into the stopper hole 20.

(Second Embodiment) A second embodiment of the present invention is shown in FIG.
And FIG. The second embodiment uses a stopper piston 50 instead of the stopper piston 7 of the first embodiment,
Replace the guide ring 19 with the guide ring 51 and the vane 9
It is housed inside a. In addition, the same components as those in the first embodiment are designated by the same reference numerals. 9 shows a state in which the stopper piston 50 is fitted in the stopper hole 20 of the front plate 4, and FIG. 10 shows a state in which the pressure oil is introduced into the hydraulic chamber 23 and the stopper piston 50 comes out of the stopper hole 20.

The stopper piston 50 has a small diameter portion 50a, a medium diameter portion 50b and a large diameter portion 50c, and the guide ring 51 has a small inner diameter portion 51a and a large inner diameter portion 51b. The guide ring 51 is fixed to the vane rotor 9 by press fitting or the like, and the stopper piston 50 is slidable with respect to the guide ring 51. Stopper piston 50
The outer peripheral walls of the small diameter portion 50a and the medium diameter portion 50b and the inner peripheral wall of the guide ring 51 form a substantially sealed annular damper chamber 52 which is a hydraulic damper.

As shown in FIG. 9, the vane rotor 9 is at the most retarded position with respect to the shoe housing 3 and the stopper is in a state where the pressure oil is not yet supplied from the pump 46 to the hydraulic chambers 23 or 24 immediately after the engine is started. The piston 50 is fitted into the stopper hole 20 by the urging force of the spring 18, and connects the front plate 4 and the vane rotor 9.

From the state shown in FIG. 9, 49 of the switching valve 49
When a is selected, pressure oil is supplied to the hydraulic chamber 23, and
The stopper piston 50 comes out of the stopper hole 20 as shown in FIG. 9 and 10 both show the vane rotor 9 in the most retarded position with respect to the shoe housing 3. When pressure oil is supplied to the hydraulic chamber 23, the damper chamber 52 is filled with oil through a fitting clearance between the stopper piston 50 and the guide ring 51.

From the state shown in FIG. 10, when 49c of the switching valve 49 is selected to rotate the vane rotor 9 in the advancing direction with respect to the shoe housing 3, even if the switching valve 49 is switched, the hydraulic chamber 24 of the hydraulic chamber 24 is switched. There is a slight time delay until the hydraulic pressure reaches a predetermined value. Then spring 1
The stopper piston 50 is moved to the stopper hole 2 by the urging force of
It may move in the direction of fitting to zero. Even if the stopper piston 50 tries to move in the fitting direction with the stopper hole 20, the oil in the damper chamber 52 is discharged little by little from the fitting clearance, so that the moving speed of the stopper piston 50 in the fitting direction is moderated. Damper room 52
Works. Therefore, the hydraulic pressure in the hydraulic chamber 24 reaches a predetermined value before the stopper piston 50 is fitted in the stopper hole 20, so that the stopper piston 50 does not fit in the stopper hole 20 and the vane rotor 9 for the shoe housing 3 is hydraulically applied. The relative rotation control of can be continued.

In the second embodiment, it is ensured that the stopper piston 50 is momentarily pushed into the stopper hole 20 during the transitional period in which the vane rotor 9 moves in the advance direction from the state where the vane rotor 9 is at the most retarded position with respect to the shoe housing 3. Can be prevented. As another embodiment of the present invention, in the first or second embodiment, the hydraulic chamber 23 is communicated with the advance hydraulic chambers 12 and 13, and the hydraulic chamber 24 is connected to the retard hydraulic chamber 10,
Even when communicating with 11, the same effect as that of the first or second embodiment can be obtained.

(Third Embodiment) A third embodiment of the present invention is shown in FIG.
1 to 14 show. In the third embodiment, a gear 61 is used instead of the chain sprocket 1 of the first embodiment, and the cam shaft 62 is gear driven. As shown in FIGS. 11 and 12, the shoe housing 63 has trapezoidal shoes 63a, 6 formed at substantially equal angular intervals in the circumferential direction.
It has 3b and 63c. Shoes 63c and 63
A fan-shaped space portion, which is a storage chamber for the three vanes 64a, 64b, 64c, is formed in each of the gaps formed by the a, the shoes 63a and 63b, and the shoes 6b and 63a at three locations in the circumferential direction.

The vane rotor 64 comprises a support member 65 and vanes 64a, 64b, 64c which are formed integrally with the support member 65 and extend radially outward. Vanes 64a, 6
4b and 64c are formed at substantially equal angular intervals in the circumferential direction, and are rotatably housed in a fan-shaped space formed by the shoes 63a, 63b, and 63c in the circumferential direction.

A retard hydraulic chamber 90 is formed between the shoe 63a and the vane 64a, and the shoe 63b and the vane 64b are formed.
A retarded angle hydraulic chamber 91 is formed between and, and a retarded angle hydraulic chamber 92 is formed between the shoe 63c and the vane 64c. An advance hydraulic chamber 93 is formed between the shoe 63c and the vane 64a, and an advance hydraulic chamber 94 is formed between the shoe 63a and the vane 64b.
An advancing hydraulic chamber 95 is formed between 4c and 4c. A stopper piston 80 as a connecting member is housed in the vane 64a.

As shown in FIGS. 11, 12 and 13, on both axial end surfaces of the support member 65, the oil passage 76 and the cylindrical protruding portion 5 are provided as groove passages at the contact portion with the cam shaft 62.
The oil passages 77 are provided in the abutting portions with and shifted in the circumferential direction in a C shape. As shown in FIG. 14, the oil passage 7
6 is a retard angle hydraulic chamber 9 due to the oil passages 76a, 76b and 76c.
It is in communication with 0, 91 and 92. Oil passage 77, oil passage 77
Advance hydraulic chambers 93, 94, 95 by a, 77b, 77c
Is in communication with Also, as shown in FIG.
Is in communication with an oil passage 73 formed in the cam shaft 62 at an axial contact portion between the support member 65 and the cam shaft 62. The oil passage 75 communicates with an oil passage 74 formed in the cam shaft 62 at an axial contact portion between the support member 65 and the cam shaft 62, and the oil passage 77 connects the support member 65 and the cylindrical protrusion 5 to each other. Oil path 75 at the axial contact portion of
Is in communication with

In the third embodiment, the vanes 64a, 64b,
If the pressure receiving areas of both side surfaces of 64c in the circumferential direction are the same as those of the vanes of the first embodiment, the sum of the pressure receiving areas where the vane rotor 64 receives the force in the circumferential direction as compared with the two vanes by providing three vanes. Since it increases, the force received by the operating pressure increases. If the force that the vane rotor 64 receives in the circumferential direction may be the same as in the first embodiment, the vanes 64a, 64a
It is possible to reduce the area of both circumferential side surfaces of b and 64c. That is, the device can be further miniaturized by reducing the size of the vane rotor.

Although the vane and the supporting member are integrally formed in the above-described embodiment of the present invention, the vane and the supporting member may be separately formed in the present invention. Further, in the above embodiment, the vane rotor is provided with two or three vanes, but an oil passage is formed on the end surface of the supporting member of the vane rotor having one or four vanes to distribute the hydraulic pressure as the working pressure. May be.

In the above embodiment, the taper angle of the stopper piston and the taper angle of the stopper hole are the same. The angle need not be the same. Further, in the above-described embodiment, the chain sprocket 1 or the gear 61 is rotated together with the crankshaft serving as the drive shaft, the shoe housing as a housing member fixed to the chain sprocket 1 or the gear 61 is rotated together with the crankshaft, and the vane rotor 9 is rotated. Although it is rotated together with the camshaft 2 which is a driven shaft, it is also possible to rotate the chain sprocket with the camshaft and the vane rotor with the crankshaft. In this case, the vane rotor is connected to the shoe housing by the connecting member at the most advanced position with respect to the shoe housing.

Further, in the above embodiment, in the engine in which the two camshafts for opening and closing the intake valve and the camshaft for opening and closing the exhaust valve are provided in parallel, the valve timing adjusting device is provided between the two camshafts. You may intervene. For example, in the case where one camshaft that is rotated from a crankshaft in synchronization by a chain or the like is a drive shaft and the other camshaft is a driven shaft by a transmission device such as a gear, one vane rotor is one of the drive shafts. The housing member may be rotated together with the shaft, and the housing member may be rotated together with the other cam shaft, which is the driven shaft, or vice versa.

[Brief description of drawings]

FIG. 1 is a cross-sectional view illustrating a valve timing adjusting device according to a first embodiment of the present invention.

FIG. 2 is a sectional view taken along line II-II of FIG.

3 is a sectional view taken along line III-III in FIG.

FIG. 4 is an enlarged cross-sectional view showing a fitted state of a stopper piston and a stopper hole of the first embodiment.

FIG. 5 is a vertical cross-sectional view showing a state where the stopper piston of the first embodiment is pulled out from the stopper hole.

FIG. 6 is a vertical cross-sectional view showing a state in which the vane rotor has rotated in the advance direction with respect to the shoe housing of the first embodiment.

7 is a cross-sectional view showing the first embodiment in the state of FIG.

FIG. 8 is a schematic diagram showing a hydraulic circuit of the first embodiment.

FIG. 9 is a vertical sectional view showing a valve timing adjusting device according to a second embodiment of the present invention.

FIG. 10 is a vertical cross-sectional view showing a state where the stopper piston of the second embodiment is pulled out from the stopper hole.

11 is a sectional view taken along line XI-XI of FIG. 13 showing a valve timing adjusting device according to a third embodiment of the present invention.

12 is a sectional view taken along line XII-XII in FIG.

FIG. 13 is a vertical sectional view showing a valve timing adjusting device according to a third embodiment.

FIG. 14 is a schematic diagram showing a hydraulic circuit of a third embodiment.

[Explanation of symbols]

 1 chain sprocket (housing member) 2 camshaft (driven shaft) 3 shoe housing (housing member) 3a, 3b shoe 4 front plate (housing member) 7c tip part 9 vane rotor 9a, 9b vane 9f support member 29, 30 oil passage ( Groove passage) 46 Pump (hydraulic driving means) 49 Switching valve (hydraulic driving means) 63 Shoe housing (housing member) 63a, 63b, 63c Shoe 64 Vane rotor 64a, 64b, 64c vane 65 Support member 76, 77 Oil passage (groove passage) )

Claims (4)

[Claims] 1. A drive force transmission system for transmitting a drive force from a drive shaft of an internal combustion engine to a driven shaft that opens and closes at least one of an intake valve and an exhaust valve of the internal combustion engine, the drive shaft or the driven shaft. A housing member that rotates together with one of the drive shaft and the driven shaft, and the housing member is rotatably housed in the housing member together with the other of the drive shaft and the driven shaft, and is rotatable relative to the housing member within a predetermined angle range. A valve timing adjusting device for an internal combustion engine, further comprising three vanes each forming an operating pressure chamber with the housing member. 2. A driving force transmission system for transmitting a driving force from a drive shaft of an internal combustion engine to a driven shaft that opens and closes at least one of an intake valve and an exhaust valve of the internal combustion engine, the drive shaft or the driven shaft. A housing member that rotates with any one of the above, and a supporting member and a vane that rotates with the supporting member, the supporting member rotates with the other of the drive shaft and the driven shaft, and the vane is accommodated in the housing member. And a vane rotor that is rotatable relative to the housing member only within a predetermined angle range and that forms a working pressure chamber between the housing member and at least one of both end surfaces in the axial direction of the support member. A valve timing adjusting device for an internal combustion engine, wherein a groove passage is provided in the groove, and an operating pressure is applied to the vane via the groove passage. 3. The valve timing adjusting device for an internal combustion engine according to claim 2, wherein three vanes are provided. 4. An advance hydraulic chamber and a retard hydraulic chamber are formed on both sides of the vane in the circumferential direction, respectively, and the groove passages are formed on both axial end surfaces of the support member, respectively. Applying working pressure to the advance hydraulic chamber via
The valve timing adjusting device for an internal combustion engine according to claim 2 or 3, wherein an operating pressure is applied to the retarded hydraulic chamber via the other groove passage.