JP3384559B2 - Valve timing adjustment device for internal combustion engine - Google Patents

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to an internal combustion engine (hereinafter,
The present invention relates to a valve timing adjusting device for changing the opening / closing timing of intake / exhaust valves 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 an intake / exhaust valve is opened / closed by a phase difference due to relative rotation between the timing pulley and the camshaft. A vane type valve timing adjusting device is known. As such a vane type valve timing adjusting device, JP-A-1-92504 and Japanese Utility Model Laid-Open No. 2-5
Those disclosed in Japanese Patent Application Laid-Open No. 0105, Japanese Patent Application Laid-Open No. H05-106412, and Japanese Patent Application Laid-Open No. H5-214907 are known. In such a vane type valve timing adjusting device, for example, a pressure chamber is provided on the inner peripheral wall of a timing pulley, and a vane that rotates integrally with a camshaft is sucked by rotating it to an advance side or a retard side by hydraulic pressure, for example. The opening / closing timing of the exhaust valve is controlled.

[0003]

However, in such a conventional vane type valve timing adjusting device,
When, for example, a sliding portion between the cam journal and the bearing portion of the cam journal is present in the oil passage that connects the hydraulic pressure supply source and the pressure chamber, oil leakage may occur from the sliding clearance between the cam journal and the bearing portion. Therefore, the pressure in the pressure chamber may not be set to a predetermined pressure. Then, there is a problem that the responsiveness of the opening / closing control of the intake / exhaust valve deteriorates and it becomes difficult to perform the highly accurate opening / closing control of the intake / exhaust valve.

Further, the rotation of the camshaft is accompanied by torque fluctuations that generate large and small torques. When such large torques are generated in the camshaft, the driving oil pressure of the vanes loses the torque reaction force and the vanes are pushed back, so that the cams are pushed back. Shaking vibration of the shaft may occur. As described above, when the camshaft swings to oscillate and swings to a desired advance position or retard position during hydraulic drive, there is a problem that the responsiveness of the opening / closing control of the intake / exhaust valve decreases. In order to solve this problem, a check valve for preventing backflow of oil from the hydraulic chamber is installed in the oil passage that hydraulically controls the vane, so that when a large torque is generated in the camshaft, the oil from the pressure chamber due to the torque reaction force is generated. A vane-type valve timing adjusting device that prevents the reverse flow of However, even if a check valve for preventing backflow is provided in the oil passage, it is not possible to reduce the oil leakage from the sliding portion interposed in the oil passage, so the effect of preventing the oscillation vibration of the camshaft is reduced. Also, when oil is supplied to the advance side of the pressure chamber and discharged from the retard side to rotate the camshaft to the advance side, the oil discharged from the retard side is blocked by the check valve. Is difficult to discharge. For this reason, there is a problem that the camshaft cannot rotate due to the pressure difference between the advance side and the retard side of the pressure chamber or the camshaft cannot rotate due to a slow rotation speed, resulting in uncontrollability or deterioration in responsiveness.

The present invention has been made to solve such a problem, and provides a highly accurate valve timing adjusting device for an engine which reduces oil leakage in an oil passage and is excellent in response of intake / exhaust valve opening / closing control. The purpose is to provide.

Another object of the present invention is to provide a highly accurate valve timing adjusting device for an engine, which is excellent in responsiveness of intake / exhaust valve opening / closing control with respect to camshaft torque fluctuations.

[0007]

According to a first aspect of the present invention, there is provided a valve timing adjusting device for an engine, comprising: a rotation transmitting member rotating in synchronization with a crankshaft of an engine; and the rotation transmitting member. A cam shaft that is rotatable relative to the member, a vane that rotates integrally with the cam shaft, and a vane that is disposed coaxially with the cam shaft on the opposite side of the cam shaft with the vane sandwiched between the vane and the vane. A rotating support member that rotates,

A retard oil pressure chamber for rotating the vane by hydraulic pressure to relatively rotate the camshaft relative to the rotation transmitting member toward the retard angle side, and a first oil passage communicating with the retard angle hydraulic chamber. And an advance hydraulic chamber for rotating the vane by hydraulic pressure to relatively rotate the camshaft with respect to the rotation transmitting member toward the advance side,

Oil can be supplied from the second oil passage communicating with the advance hydraulic chamber to the retard hydraulic chamber from the first oil passage, and the advance hydraulic pressure can be supplied from the second oil passage. A valve timing adjusting device for an engine, comprising: a hydraulic pressure supply means capable of supplying oil to a chamber, wherein the first oil passage and the second oil passage are provided inside the vane through the inside of the rotation support member. The first oil passage and the second oil passage are provided with an axial end surface of the rotary support member and an end surface of the central cylindrical portion that supports the vane blade portion and that faces the rotary support member. Of the first oil passage inside the vane, one opening is connected to the end surface of the rotation support member, the other opening is connected to the retard hydraulic chamber, To the second oil passage inside the vane Information, and connected to the end face of one of the opening faces the rotary support member and the other opening, characterized in that characterized in that connected to the advancing hydraulic chamber.

According to a second aspect of the present invention, there is provided a valve timing adjusting device for an engine according to the first aspect, wherein a seal member is provided between the rotation supporting member and a bearing portion of the rotation supporting member. It is characterized by interposing. According to the engine valve timing adjusting device of the first aspect of the present invention, the rotation support member is provided on the opposite side of the camshaft with the vane interposed. This rotation support member is disposed coaxially with the cam shaft,
And it rotates with the vane. Then, the first oil passage and the second oil passage are contact portions between an axial end surface of the rotation support member and an end surface of the central cylindrical portion that supports the vane blade portion and that faces the rotation support member. Connected by. Since the sealability at the abutting portion due to the connection of the end faces having the opening is high, it is possible to easily seal without using a seal member and the number of parts can be reduced. Since the first oil passage and the second oil passage are provided inside the vane through the inside of the rotation support member, the first oil passage and the second oil passage provided inside the vane through the inside of the rotation support member are It is possible to communicate with each other without interposing the sliding portion as much as possible. Therefore, the amount of oil leaking from the first oil passage and the second oil passage can be reduced. According to the engine valve timing adjusting device of the second aspect of the present invention, by interposing the seal member between the rotation supporting member and the bearing portion of the rotation supporting member, the rotation supporting member and the bearing portion of the rotation supporting member are provided. It is possible to reduce oil leakage at the sliding portion of the.

[0011]

Embodiments of the present invention will be described with reference to the drawings.
First, a comparative example is shown, and then an example of the present invention is shown. (Comparative Example) FIGS. 1 to 4 show an engine valve timing adjusting device according to a comparative example.

A driving force is transmitted to the timing pulley 1 by a timing belt (not shown), and the timing pulley 1 rotates in synchronization with a crankshaft of an engine (not shown). The camshaft 2 receives the driving force from the timing pulley 1 which is a rotation transmitting member, and can rotate with a predetermined phase difference with respect to the timing pulley 1. The timing pulley 1 and the cam shaft 2 rotate clockwise when viewed from the arrow X direction shown in FIG. Hereinafter, this rotation direction will be referred to as the advance direction.

As shown in FIGS. 2 and 3, the shoe housing 3 is integrally formed coaxially with the timing pulley 1.
The front plate 4 is coaxially fixed by a bolt 14. Timing pulley 1 and rear plate 5 are 4
It is fixed coaxially with a bolt 6 of a book. The inner peripheral wall of the boss portion 5a of the rear plate 5 is fitted to the tip end portion 2a of the cam shaft 2 so as to be relatively rotatable, and the outer peripheral wall of the boss portion 5a is in contact with the oil seal 8 of the cylinder head 7.

As shown in FIG. 2, 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 a fan-shaped space is formed in the circumferential gap between the shoes 3a and 3b.

As shown in FIGS. 2 and 3, the vane rotor 9 has fan-shaped vanes 9a and 9b at both ends in the radial direction, and the vanes 9a and 9b are shoes 3a and 3b.
It is rotatably accommodated in a fan-shaped space formed in the circumferential gap b. The spigot portion 9c is coaxially fitted to the tip portion 2a of the camshaft 2, and the vane rotor 9 is integrally fixed to the camshaft 2 by two bolts 15. Cylindrical protrusion 9 formed integrally with the vane rotor 9
d is fitted to the inner peripheral wall of the boss portion 4a of the front plate 4 so as to be relatively rotatable. As shown in FIG. 2, 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 9a, shoe 3b and vane 9
b, shoe 3a and vane 9b, shoe 3b and vane 9a
Between the retard angle hydraulic chambers 10 and 11 and the advance angle hydraulic chamber 1 respectively.
2 and 13 are formed. The axial length of the vanes 9a and 9b is set to be slightly smaller than the axial length of the shoe housing 3 sandwiched between the front plate 4 and the rear plate 5.

With the above structure, the camshaft 2 and the vane rotor 9 are coaxially rotatable relative to the timing pulley 1, the shoe housing 3, the front plate 4 and the rear plate 5. As shown in FIG. 1, the check valves 20 and 30 are housed inside the vanes 9 a and 9 b of the vane rotor 9, respectively. Check valve 20
Is composed of a valve body 21, a valve seat 22, a guide portion 23, and a compression coil spring 24, and the check valve 30 is
It is composed of a valve body 31, a valve seat 32, a guide portion 33, and a compression coil spring 34. The valve bodies 21 and 31 are formed in a cylindrical shape with a bottom, and a plurality of oil passage holes 21a and 31a are formed in the side wall on the same circumference. The valve bodies 21 and 31 are compression coil springs 24, respectively.
The seat portions provided at the bottom are pressed against the valve seats provided at the valve seats 22 and 32 by the urging forces of
In the state shown in (1), the valve is closed. The guide portions 23 and 33 are formed in a bottomed cylindrical shape having an opening in a direction opposite to the openings of the valve bodies 21 and 31. Valve body 2
1 and 31 are slidably supported by the inner walls of the guide portions 23 and 33 in the rotation axis direction of the camshaft 2. Oil passage holes 50 a and 50 b are formed in the valve seats 22 and 32.

The pilot valves 25 and 35 are provided so as to face the check valves 20 and 30, respectively. The pilot valve 25 includes a valve body 26 and a compression coil spring 2
7, the pilot valve 35 includes a valve body 36 and a compression coil spring 37. Valve bodies 26 and 36
Is a vane 9 that can reciprocate in the rotation axis direction of the camshaft 2.
It is housed in a and 9b. Valve bodies 26 and 36
Is pressed against the inner surface of the front plate 4 by the urging force of the compression coil springs 27 and 37. The valve body 26 is integrally formed by the rod 26a and the sliding member 26b, and the valve body 36 is integrally formed by the rod 36a and the sliding member 36b. The rods 26a and 36a pass through the insides of the valve seats 22 and 32, respectively, and protrude to the vicinity of the valve bodies 21 and 31. Each of the sliding members 26b and 36b includes a disk-shaped locking portion that locks the compression coil springs 27 and 37, and an annular sliding portion that extends in the axial direction from the outer circumference of the locking portion. Here, the check valve 20 and the pilot valve 25 are the first
4 is a pilot type check valve of FIG. 4, and the check valve 30 and the pilot valve 35 are second pilot type check valves shown in FIG. It constitutes 100b.

Hydraulic chambers 40 and 4 are provided in front of and behind the valve body 26.
1, and hydraulic chambers 45 and 46 are formed in front of and behind the valve body 36. A hydraulic chamber 4 is provided in front of and behind the valve body 21.
2, 43 and 44 are formed, and hydraulic chambers 47, 48 and 49 are formed in front of and behind the valve body 31. The hydraulic chambers 41 and 42 communicate with each other inside the valve seat 22, and the hydraulic chambers 46 and 47 communicate with each other inside the valve seat 32. Further, the oil pressure chambers 43 and 44 communicate with each other through an oil passage hole 21a provided in the valve body 21, and the oil pressure chambers 48 and 49 communicate with each other through an oil passage hole 31a provided in the valve body 31. The hydraulic chambers 42 and 44 are shut off by the valve body 21 coming into contact with the valve seat 22, and communicated via the oil passage 43 and the oil passage hole 21 a when the valve body 21 is separated from the valve seat 22. The hydraulic chambers 47 and 49 include the valve body 31.
Is blocked by contacting the valve seat 32, and the valve body 31 is separated from the valve seat 32 to communicate with each other via the oil passage 48 and the oil passage hole 31a. Hydraulic chamber 42
Through the oil passage hole 50a and the oil passage 62a.
The hydraulic chamber 47 communicates with the oil passage 61b through the oil passage hole 50b and the oil passage 62b. Further, the hydraulic chamber 40 communicates with the oil passage 61b through the oil passage 63b,
The hydraulic chamber 45 communicates with the oil passage 61a via the oil passage 63a. The hydraulic chamber 43 communicates with the retard hydraulic chamber 10 through the oil passage 51a shown in FIG. 2, and the hydraulic chamber 48 communicates with the advance hydraulic chamber 12 through the oil passage 51b shown in FIG. As shown in FIG. 1, the valve bodies 26 and 36 are compressed by the compression coil spring 27 by the differential pressure between the hydraulic chambers 40 and 41 or the differential pressure between the hydraulic chambers 45 and 46, that is, the differential pressure between the oil passages 61a and 61b. And 37 against the urging force of the valve main bodies 21 and 31 toward the check valves 20 and 30.
Can abut. The rods 26a and 36a come into contact with the valve bodies 21 and 31, respectively, and then further resist the urging forces of the compression coil springs 24 and 34, respectively.
And 31 are pressed to separate the valve bodies 21 and 31 from the valve seats 22 and 32, respectively.
And 30 are opened. As shown in FIG. 2, a virtual straight line 201 connecting the pilot check valves 100a and 100b.
And a virtual straight line 20 connecting the oil passage 61a and the oil passage 61b.
Pilot type check valve 1 so that 2 and 2 intersect almost vertically
00a, 100b and oil passages 61a, 61b are arranged on the outer peripheral side inside the vane rotor 9.

In this comparative example, the oil passages 61a, 62a,
65a is a first oil passage, and oil passages 61b, 62b,
65b is a second oil passage. As shown in FIG. 1, the journal portion 52 of the camshaft 2 is rotatably supported by a bearing portion 53 provided on the cylinder head 7, and is restricted from moving in the rotation axis direction. Outer peripheral grooves 54a and 54b are provided in the peripheral direction of the outer peripheral wall of the journal portion 52. The supply oil passage 57 for pumping the oil in the oil tank 55 by the pump 56 and the discharge oil passage 58 for discharging the oil into the oil tank 55 are selectively communicated with the outer peripheral grooves 54a and 54b by the switching operation of the switching valve 59. Or it can be shut off. In this comparative example, the switching valve 59 is a well-known 4-port guide valve.

The oil passage 60a, which is the first oil passage inside the camshaft 2, communicates with the outer peripheral groove 54a, and the contact portion 7 between the camshaft 2 and the vane rotor 9 in the axial direction.
0 communicates with the oil passage 61a inside the vane rotor 9, and the oil passage 61a is connected through the oil passage 62a to the hydraulic chamber 4 of the vane 9a.
2 and the vane 9b through the oil passage 63a.
Of the hydraulic chamber 45. The oil passage 60b, which is the second oil passage inside the camshaft 2, communicates with the outer peripheral groove 54b, and at the contact portion 70, the oil passage 6 inside the vane rotor 9 is formed.
1b, the oil passage 61b communicates with the hydraulic chamber 47 of the vane 9b through the oil passage 62b, and the oil passage 63b.
Through the hydraulic chamber 40 of the vane 9a. Since the camshaft 2 and the vane rotor 9 rotate integrally,
Axial contact portion 7 between camshaft 2 and vane rotor 9
At 0, the sealing property can be made extremely high. As shown in FIG. 2, the oil passages 62a, 62b are connected to the valve seats 22, 3
The communication with the clearance 16 is blocked by 2.
Inside the vane rotor 9, an oil passage 65a that communicates the retarded angle hydraulic chambers 10 and 11 and an oil passage 65b that communicates the advanced angle hydraulic chambers 12 and 13 are provided. With the above configuration, the pressure oil from the pump 56 is selectively supplied to the outer peripheral grooves 54a and 54b by the switching valve 59, and the check valve 20 is provided.
By opening the valves 30 and 30, pressure oil from the pump 56 can be supplied to the retarded angle hydraulic chambers 10 and 11 or the advanced angle hydraulic chambers 12 and 13.

Here, the pilot type check valves 100a and 1
00b and the virtual straight line 202 connecting the oil passage 61a and the oil passage 61b intersect substantially perpendicularly, so that the pilot check valves 100a and 100b and the oil passages 61a and 61b are located inside the vane rotor 9. Since it is arranged on the outer peripheral side, the bolt 15, the oil passages 62a, 62b,
63a, 63b, 65a, 65b are arranged inside the vane rotor 9 so as not to interfere with each other.

By making the clearance 16 at the outermost diameter portion of the vanes 9a and 9b minute, the retarded hydraulic chamber 10 and the advanced hydraulic chamber 13 and the retarded hydraulic chamber 11 and the advanced hydraulic chamber 12 form the clearance 16. It is prevented as much as possible from communicating with each other. Further, since the vane seal 73 is provided on the innermost diameter portions of the shoes 3 a and 3 b, the retard hydraulic chamber 10 and the advance hydraulic chamber 12, and the retard hydraulic chamber 11 and the advance hydraulic chamber 13 communicate with each other through the clearance 17. To prevent that. As shown in FIG. 3, the retard angle hydraulic chambers 10 and 11 and the advance angle hydraulic chambers 12 and 13 are provided between the shoe housing 3 and the front plate 4 and between the shoe housing 3 and the rear plate 5, respectively. Rubber packings 74 and 75 are pressure-bonded so that pressure oil does not leak to the outside. The front cover 80 is crimped to the front plate 4 with the rubber packing 76 sandwiched between the bolts 14.

Next, the operation of the valve timing adjusting device will be described with reference to FIGS. 1, 2 and 4. (1) When the first valve 59a of the switching valve 59 is selected,
The pressure oil discharged from the pump 56 is used for the outer peripheral groove 54 a and the oil passage 6.
0a, 61a, 62a is sent to the hydraulic chamber 42 by pressure,
The valve body 21 is separated from the valve seat 22 against the biasing force of the compression coil spring 24. The pressure oil is pressure-fed to the retard hydraulic chamber 10 through the hydraulic chamber 43 and the oil passage 51a, and further passes through the oil passage 65a.
Pumped to. The pressure oil in the retard angle hydraulic chambers 10 and 11 acts on the shoes 3a and 3b to push the vanes 9a and 9b to rotate the vane rotor 9 in the counterclockwise retard angle direction. Further, the pressure oil in the oil passage 61a is pressure-fed to the hydraulic chamber 45 through the oil passage 63a. On the other hand, the outer peripheral groove 54b communicates with the discharge oil passage 58 and is normally at atmospheric pressure. The hydraulic pressure chambers 47 and 46 communicating with the outer peripheral groove 54b via the oil passages 60b, 61b, 62b also correspond to atmospheric pressure. Since the oil pressure in the oil pressure chamber 45 is higher than the oil pressure in the oil pressure chamber 46, the valve body 36 moves in the direction of the check valve 30 against the biasing force of the compression coil spring 37, and the rod 36a presses the valve body 31. , Further compression coil spring 34
The valve body 31 is separated from the valve seat 32 against the urging force of the valve seat 32. As a result, the advance hydraulic chambers 12 and 13 communicate with the discharge oil passage 58 via the pressure chamber 47 and the oil passages 62b, 61b, and 60b, and the advance hydraulic chambers 12 and 13 are communicated with the rotation of the vane rotor 9 toward the retard side. The oil in 13 is the discharge oil passage 58.
Is discharged to.

(2) When the second valve 59b of the switching valve 59 is selected, the pressure oil discharged by the pump 56 is
b through the oil passages 60b, 61b and 62b.
The valve body 31 is separated from the valve seat 32 against the biasing force of the compression coil spring 34. Then, the pressure oil is pumped to the advance hydraulic chamber 12 through the hydraulic chamber 48 and the oil passage 51b, and further pumped to the advance hydraulic chamber 13 through the oil passage 65b. Advance hydraulic chambers 12 and 13
The pressure oil inside acts on the shoes 3a and 3b to push the vanes 9a and 9b to rotate the vane rotor 9 in the clockwise advance direction. Further, the pressure oil in the oil passage 61b is pressure-fed to the hydraulic chamber 40 through the oil passage 63b.
On the other hand, the outer peripheral groove 54a communicates with the discharge oil passage 58 and is normally at atmospheric pressure. The hydraulic chambers 42 and 41 communicating with the outer peripheral groove 54a via the oil passages 60a, 61a, 62a also correspond to atmospheric pressure. Since the hydraulic pressure in the hydraulic chamber 40 is higher than the hydraulic pressure in the hydraulic chamber 41, the valve body 26 moves in the direction of the check valve 20 against the biasing force of the compression coil spring 27, and the rod 26a presses the valve body 21. Further, the valve body 21 is separated from the valve seat 22 against the biasing force of the compression coil spring 24. As a result, the retard hydraulic chambers 10 and 1
1 communicates with the discharge oil passage 58 via the pressure chamber 42 and the oil passages 62a, 61a, 60a, and the oil in the retard angle hydraulic chambers 10 and 11 is discharged as the vane rotor 9 rotates toward the advance side. It is discharged to 58.

(3) When the third valve 59c of the switching valve 59 is selected, the retarding hydraulic chambers 10, 11, the advancing hydraulic chambers 12,
The oil in 13 cannot flow, and the phase difference between the vane rotor 9 and the camshaft 2 with respect to the timing pulley 1 is maintained. Next, the operation of the valve timing adjusting device with respect to the torque fluctuation of the camshaft 2 will be described. The camshaft 2 is rotating clockwise as shown in FIG. 5A while generating torque on the timing pulley 1 in accordance with the driving of an intake / exhaust valve (not shown).

(1) The second valve 59b of the switching valve 59 is selected so that the pressure oil in the advance hydraulic chambers 12 and 13 becomes the shoe 3.
When the vanes 9a and 9b are pressed against a and 3b to rotate the vane rotor 9 in the clockwise direction, the positive torque shown in FIG. 5B repels, and the advance hydraulic chambers 12 and 13 have positive torque. Generates hydraulic pressure according to the reaction force. When the hydraulic pressure pumped by the pump 56 is higher than the hydraulic pressure in the advance hydraulic chambers 12 and 13, that is, when the positive torque is small or the negative torque is negative, the hydraulic pressure of the hydraulic oil pumped by the pump 56 causes the vane rotor 9 to move to the shoe housing 3. And acts to rotate it clockwise. Further, since the retarded hydraulic chambers 10 and 11 communicate with the discharge oil passage 58,
Since the oil in and 11 can be discharged to the oil tank 55, the vane rotor 9 rotates clockwise with respect to the shoe housing 3. That is, the camshaft 2 rotates in the advance side with respect to the timing pulley 1. Advance hydraulic chambers 12 and 1
When the hydraulic pressure of 3 is larger than the hydraulic pressure pumped by the pump 56, that is, when the positive torque is large, the hydraulic pressure of the hydraulic chamber 49 becomes higher than the hydraulic pressure of the hydraulic chamber 47. This hydraulic chamber 47 and 49
Since the valve body 31 is seated on the valve seat 32 and the check valve 30 is closed due to the pressure difference between and, the oil in the advance hydraulic chambers 12 and 13 is prevented from flowing back to the pump 56 side. The hydraulic pressures of the advance hydraulic chambers 12 and 13 do not decrease. For this reason, the vane rotor 9 is prevented from rotating counterclockwise with respect to the shoe housing 3 and stands still.
Therefore, the camshaft 2 does not return counterclockwise with respect to the timing pulley 1 but rotates intermittently only in the clockwise direction, and as a result, the opening / closing timing of the intake / exhaust valve driven by the camshaft 2 is advanced.

(2) Select the first valve 59a of the switching valve 59 and press the vanes 9a and 9b to press the vane rotor 9
5 is rotated counterclockwise with respect to the shoe housing 3, the negative torque shown in FIG. 5B repels. When the negative torque is small or positive, the vane rotor 9 rotates counterclockwise with respect to the shoe housing 3, and when the negative torque is large, the vane rotor 9 stands still. Therefore, the camshaft 2 intermittently rotates with respect to the timing pulley 1 only in the counterclockwise retard direction, and as a result, the opening / closing timing of the intake / exhaust valve driven by the camshaft 2 is delayed.

(3) When the third valve 59c of the switching valve 59 is selected, the retard angle hydraulic chambers 10 and 11 and the advance angle hydraulic chamber 1
The communication between the oil supply passages 2 and 13 and the supply oil passage 57 and the discharge oil passage 58 is cut off, and the retard hydraulic chambers 10, 11 and the advance hydraulic chamber 12,
The oil in 13 is contained and the vane rotor 9 stands still at an arbitrary position. Pilot type check valve 100 of this comparative example
Assuming that a and 100b are not present, the camshaft 2
The intermittent positive or negative hydraulic pressure generated in the retarding hydraulic chambers 10, 11 and the advancing hydraulic chambers 12, 13 due to the torque fluctuation of the above causes leakage of pressure oil from the clearance between the cam journal portion 52 and the bearing portion 53 and Since air is sucked in, the swing vibration of the vane rotor 9 gradually increases while being generated.

In the comparative example, the communication between the oil passages 60a and 61a which are the first oil passages and the communication between the oil passages 60b and 61b which are the second oil passages are the axes of the camshaft 2 and the vane rotor 9. Is performed at the contact portion 70 in the direction. Since the camshaft 2 and the vane rotor 9 rotate integrally, the sealability at the contact portion 70 can be made very high, so that the vane rotor 9 and the camshaft 2 can be axially fluidized without using a special sealing member. Can be assembled closely. Therefore, the communication between the oil passages 60a and 61a and the communication between the oil passages 60b and 61b can be facilitated, and the number of parts can be reduced.

In the comparative example, the pilot type check valve 10
By accommodating 0a and 100b in the vanes 9a and 9b of the vane rotor 9, the retard angle hydraulic chambers 10, 11,
The reverse flow of the pressure oil in the advance hydraulic chambers 12 and 13 is applied to the vane rotor 9
Since it can be prevented by the internal pilot check valves 100a and 100b, the portion where the pressure oil leaks can be minimized. Further, since the valve bodies 21, 26, 31 and 36 are housed in the vanes 9a and 9b so that the reciprocating direction is the same as the rotation axis direction of the camshaft 2, centrifugal force due to the rotation of the vane rotor 9 is generated. Main body 21, 26, 3
Since they do not work in the reciprocating directions of 1 and 36, the accuracy of the opening / closing control of the intake / exhaust valve by the pilot check valves 100a and 100b can be improved. Further, the virtual straight line 201 connecting the pilot type check valves 100a and 100b is the oil passage 6
Since the pilot check valves 100a and 100b and the oil passages 61a and 61b are arranged on the outer peripheral side inside the vane rotor 9 so as to intersect substantially perpendicularly with the virtual straight line 202 connecting 1a and 61b, the oil passages 62a and 62b are arranged. , 63a, 63
The b, 65a, 65b and the bolt 15 can be arranged so as not to interfere with each other inside the vane rotor 9.

(Example)

An embodiment of the present invention is shown in FIG. 6, the same components as those of the comparative example are designated by the same reference numerals.
The outer peripheral grooves 154a and 154b are the outer peripheral groove 54a of the comparative example.
Oil passages 160a, 16
0b, 161a, 161b, 165a, 165b are oil passages 60a, 60b, 61a, 61b, 65a of the comparative example.
65b respectively.

The drive force is transmitted to the chain sprocket 91 by a timing chain (not shown), and the chain sprocket 91 rotates in synchronization with a crankshaft of an engine (not shown). The cam shaft 92 receives a driving force from a chain sprocket 91, which is a rotation transmitting member, and can rotate relative to the chain sprocket 91 with a predetermined phase difference. The chain sprocket 91 is fixed to the shoe housing 93 by the bolt 6 and rotates together with the shoe housing 93. The rotation support member 94 has the cam shaft 9 and the cam shaft 9 with the vane 99 interposed therebetween.
It is arranged on the opposite side to the No. 2 and is fixed to the vane 99 and the camshaft 92 by the bolt 15. Therefore, the rotation support member 94 can rotate relative to the shoe housing 93 together with the vane 99 and the cam shaft 92. The rotation support member 94 is rotatably supported by the bearing portion 101a of the cover 101 attached to the cylinder head 97. A seal member 102 is interposed at a sliding portion between the rotation support member 94 and the bearing portion 101a so as to sandwich the outer peripheral grooves 154a and 154b.

Oil passage 160a and oil passage 161a forming the first oil passage, and oil passage 1 forming the second oil passage.
The 60b and the oil passage 161b are formed inside the rotation support member 94 and the vane 99, respectively, and communicate with each other at the contact portion 81 in the axial direction between the rotation support member 94 and the vane 99. Therefore, as in the comparative example, the oil passage 160a and the oil passage 161a are assembled by assembling the rotation support member 94 and the vane 99 without using a special seal member.
The oil passage 160b and the oil passage 161b can be easily communicated with each other, and the number of parts can be reduced.

In this embodiment, even if it is difficult to form an oil passage in the cam shaft 92, the rotation support member 94 is disposed on the opposite side of the cam shaft 99 with the vane 99 interposed coaxially with the cam shaft 92. By forming oil passages 160a and 160b inside the camshaft 92,
Oil leakage can be reduced as in the case where the oil passage is formed in. Further, even if the rotation support member 94 and the bearing portion 101a are eccentric due to manufacturing errors or the like and the clearance between the rotation support member 94 and the bearing portion 101a is increased, the sliding portion between the rotation support member 94 and the bearing portion 101a is increased. Seal member 10
By interposing 2, the oil leakage due to eccentricity can be reduced.

In the above-described comparative example and the embodiment of the present invention, two retard hydraulic chambers and two advance hydraulic chambers are provided to adjust the valve timing, but in the present invention, the retard hydraulic chamber and the advance hydraulic chamber are used. The number of hydraulic chambers is not limited to two, but three or more hydraulic chambers can be provided.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing an engine valve timing adjusting device according to a comparative example.

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

FIG. 3 is a cross-sectional view showing a fixed state of each member of a comparative example.

FIG. 4 is a schematic diagram showing a hydraulic circuit of a comparative example.

FIG. 5A is a schematic view showing the rotation directions of a camshaft and a timing pulley of a comparative example. (B) is an explanatory view showing a torque fluctuation of the camshaft of the comparative example.

FIG. 6 is a sectional view showing a valve timing adjusting device for an engine according to an embodiment of the present invention.

[Description of Reference Signs] 3 shoe housing 3a, 3b shoe 9 vane rotor (vane) 9a, 9b vane 51a oil passage (first oil passage) 51b oil passage (second oil passage) 56 pump (hydraulic supply means) 60a oil Passage (first oil passage) 60b oil passage (second oil passage) 61a oil passage (first oil passage) 61b oil passage (second oil passage) 62a oil passage (first oil passage) 62b oil Passage (second oil passage) 81 Contact portion 91 Chain sprocket (rotation transmission member) 92 Camshaft 93 Shoe housing 94 Rotation support member 99 Vane rotor (vane) 100a Pilot type check valve (first pilot type check valve) ) 100b Pilot type check valve (second pilot type check valve) 101 Cover 101a Bearing portion 102 Seal member 160a Oil passage (first oil Passage) 160b oil passage (second oil passage) 161a oil passage (first oil passage) 161b oil passage (second oil passage)

─────────────────────────────────────────────────── ─── Continuation of the front page (58) Fields surveyed (Int.Cl. ⁷ , DB name) F01L 1/34

Claims (2)

(57) [Claims] 1. A rotation transmission member that rotates in synchronization with a crankshaft of an internal combustion engine, a cam shaft that can rotate relative to the rotation transmission member, a vane that rotates integrally with the cam shaft, and a vane. A rotation support member which is disposed on the opposite side of the cam shaft and coaxially with the cam shaft and which rotates together with the vane; and the vane is rotated by hydraulic pressure to rotate the vane with respect to the rotation transmission member. A retard oil pressure chamber that relatively rotates the shaft toward the retard angle side, a first oil passage that communicates with the retard angle hydraulic chamber, the vane is rotated by hydraulic pressure, and the camshaft with respect to the rotation transmission member. Is relatively rotatable to the advance side, a second oil passage communicating with the advance hydraulic chamber, and oil can be supplied from the first oil passage to the retard hydraulic chamber. , The above A valve timing adjusting device for an internal combustion engine, comprising: a hydraulic pressure supply device capable of supplying oil from the second oil passage to the advance hydraulic chamber, wherein the first oil passage and the second oil passage are the rotations. The first oil passage and the second oil passage are provided inside the vane through the inside of a support member, and the first oil passage and the second oil passage are central cylinders that support the axial end surface of the rotary support member and the vane blade portion. Of the first oil passage inside the vane, one opening is connected to the end surface of the rotation supporting member, and the other opening is connected to the contact surface of the rotating support member. Is connected to the retard hydraulic chamber, and with respect to the second oil passage inside the vane, one opening is connected to an end surface facing the rotation support member,
A valve timing adjusting device for an internal combustion engine, wherein the other opening is connected to the advance hydraulic chamber. 2. The valve timing adjusting device for an internal combustion engine according to claim 1, wherein a seal member is interposed between the rotary support member and a bearing portion of the rotary support member.