JP2003113702A - Valve timing control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve timing control device that has small build, improved responsiveness and high sealing performance. SOLUTION: A spring 21 generating torque for turning a vane rotor 50 to an advance side relative to a shoe housing 10 is housed in a housing portion 22 of a pulley housing 20. One end 21a of the spring 21 is inserted and locked in a recess 61 formed in a spacer 60. The other end of the spring 21 is locked onto a pin member 23 pressed in the shoe housing 10 and projected into the housing portion 22 through a seal plate 40. A hole 42 formed in the seal plate 40 to allow the passage of the pin member 23 is shaped in correspondence with a sectional shape of the pin member 23. An increase in size of the hole and intercommunication between oil pressure chambers can be prevented. The vane rotor 50 can be reduced in size. An O-ring 43 is protected from dislocation at the assembly of the spring 21 to improve sealing performance.

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to an internal combustion engine (hereinafter,
The "internal combustion engine" is called an engine. ) Opening and closing timing of at least one of the intake valve and the exhaust valve (hereinafter,
"Opening / closing timing" is called valve timing. ) 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 valve or an exhaust valve is generated by a phase difference caused by relative rotation between the timing pulley or the chain sprocket and the camshaft. A vane type valve timing adjusting device is known that hydraulically controls the valve timing of at least one of the valves.

The valve timing adjusting device as described above is provided with, for example, a spring as an advancing means for applying an advancing torque to the driven shaft in the direction of advancing the drive shaft.
In the conventional valve timing adjusting device, one end of the spring is locked to the housing member in which the spring is housed. The other end of the spring is inserted into and fixed to a spring stopper press-fitted into the vane member.

Further, in the conventional valve timing adjusting device, the housing member for accommodating the vane member is composed of, for example, two members divided in the axial direction, and the plate member is sandwiched between these two members. The plate member seals between the two members.

[0005]

However, when fixing the end of the spring as the advancing means to the spring stopper press-fitted into the vane member, the plate member needs a hole through which the end of the spring passes. . Therefore, an elongated hole must be formed in the plate member for the angle by which the valve timing is converted, that is, for the relative rotation between the housing member and the vane member. As a result, it is necessary to increase the size of the vane member to which the ends of the spring are fixed so that the plurality of advance chambers formed inside the housing member do not communicate with each other through the elongated holes.

Further, by forming the elongated holes in the plate member, the distance between the hydraulic chambers becomes small, and it is difficult to secure the sealing performance between the hydraulic chambers. As a result, the amount of working fluid leaking from the hydraulic chamber increases, and the responsiveness of the valve timing adjusting device decreases. Further, when fixing the end portion of the spring to the vane member, it is necessary to move the two housing members and the plate member relative to each other, so that the spring member is installed in the groove formed on the plate member side of the housing member. For example O
A seal member such as a ring may stick out of the groove, making it difficult to secure the sealing property.

On the other hand, in the case of the conventional valve timing adjusting device, a seal member such as an O-ring is installed between the plate member and the two housing members which are installed on both sides of the plate member. ing. The seal member is housed in the groove formed on both sides of the plate member.

However, when the seal member is housed in the grooves formed on both sides of the plate member, for example, the seal member is housed on one surface side of the plate member, and two housing members are arranged from above the housed seal member. One of the members is assembled. Then, after one of the plate member and the housing member is assembled, they are axially inverted and the groove formed on the other surface side of the plate member is directed upward, so that the seal member and the other housing member are It can be assembled. That is, when the plate member, the two housing members, and the seal member are assembled, a step of reversing in the axial direction is required during the assembly. As a result, there is a problem that the assembling property of the valve timing adjusting device deteriorates.

Therefore, an object of the present invention is to have a small physique,
An object of the present invention is to provide a valve timing adjusting device with improved responsiveness and high sealing performance. Another object of the present invention is to provide a valve timing adjusting device having a high sealing property and easy to assemble.

[0010]

According to the valve timing adjusting device of the first aspect of the present invention, the advancing means accommodated in the accommodating portion of the second housing member has one end engaged with the shaft portion. It has been stopped. By locking one end of the advance means to the shaft, it is not necessary to form an elongated hole in the plate member. Therefore, the hydraulic chambers do not communicate with each other through the long holes, and it is possible to prevent the responsiveness from being deteriorated due to the leakage of the hydraulic oil. As a result, it is not necessary to increase the size of the vane member in order to secure the distance between the hydraulic chambers. Also,
By locking one end of the advance means to the shaft, the force applied to the end of the advance means is received by the shaft. Therefore, it is not necessary to increase the wall thickness to increase the strength of the vane member. Therefore, the vane member and the first housing member and the second housing member can be downsized. Further, by locking the advance means on the shaft portion, the advance means can be assembled before the plate member is assembled. Therefore, there is no relative movement between the first housing member and the second housing member and the plate member,
Displacement of the seal member can be prevented and the sealing performance can be improved.

According to the valve timing adjusting device of the second aspect of the present invention, one end of the advance means is locked to the drive shaft or the driven shaft. That is, the shaft portion extends integrally with the drive shaft or the driven shaft. Therefore, the structure is simple. According to the valve timing adjusting device of the third aspect of the present invention, the spacer is installed between the drive shaft or the driven shaft and the vane member, and one end of the advance means is locked to the spacer. That is, the shaft portion is connected separately from the drive shaft or the driven shaft. Therefore, the valve adjusting device can be configured separately from the drive shaft or the driven shaft.

According to the valve timing adjusting device of the fourth aspect of the present invention, the vane member has a neck portion projecting toward the drive shaft or the driven shaft, and one end portion of the advance means is locked to the neck portion. There is. That is, the shaft portion is connected separately from the drive shaft or the driven shaft. Therefore, the valve adjusting device can be configured separately from the drive shaft or the driven shaft.
Further, by forming the shaft portion integrally with the vane member,
The structure is simplified and the number of parts can be reduced.

According to the valve timing adjusting device of the fifth aspect of the present invention, the other end of the advance means is locked to the pin member projecting from the first housing to the accommodating portion.
The pin member projects from the first housing to the accommodation portion through the plate member. Since the first housing and the second housing and the plate member rotate integrally, the hole formed in the plate member for the pin member to pass through can be a hole having a shape corresponding to the cross-sectional shape of the pin member. , Do not need slots. Therefore, it is possible to prevent the hydraulic oil from leaking between the hydraulic chambers without increasing the size of the plate member.

According to the valve timing adjusting device of the sixth, seventh or eighth aspect of the present invention, the first housing member or the plate member is formed with the first groove portion or the second groove portion for accommodating the seal member. . The first groove portion is formed on the plate member side of the first housing, and the second groove portion is formed on the side opposite to the first housing of the plate member. That is, the first groove portion and the second groove portion are formed on the same surface side in the axial direction. Therefore, the seal member can be installed in the first groove portion of the first housing and the second groove portion of the plate member from the same direction, and it is not necessary to reverse the axial direction during the assembling of the valve timing adjusting device. . Further, since it is not necessary to reverse the sealing member during the assembling, it is possible to prevent the deterioration of the sealing property due to the displacement of the sealing member or the dropping of the sealing member. Therefore, the sealing property can be improved and the assembly can be easily performed.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A plurality of embodiments showing the embodiments of the present invention will be described below with reference to the drawings. (First Embodiment) FIG. 1 shows an engine valve timing adjusting device according to a first embodiment of the present invention. The valve timing adjusting device 1 according to the first embodiment is a hydraulic control type,
The valve timing of the intake valve is adjusted.

As shown in FIG. 1, the valve timing adjusting apparatus 1 according to this embodiment includes a shoe housing 10 as a first housing member and a pulley housing 20 as a second housing. A pulley 30 having a gear train (not shown) is installed on the outer peripheral side of the pulley housing 20. The pulley 30 is coupled with a crankshaft serving as a drive shaft of an engine (not shown) by a gear train (not shown), transmits a driving force, and rotates in synchronization with the crankshaft. The driving force is transmitted from the pulley 30 to the camshaft 2 as a driven shaft to open / close an intake valve (not shown). The camshaft 2 is rotatable with a predetermined phase difference with respect to the pulley 30. The pulley 30 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.

A seal plate 40 as a plate member is installed between the shoe housing 10 and the pulley housing 20. The seal plate 40 includes the shoe housing 10, the vane rotor 50, and the pulley housing 2.
It prevents oil leaks between 0 and 0. Shoe housing 1
0, the pulley housing 20, the pulley 30, and the seal plate 40 constitute a driving side rotating body, and are coaxially fixed by the bolt 3.

The shoe housing 10 comprises a peripheral wall 11, a front plate 12 and a flange 13 and is integrally formed in a bowl shape. As shown in FIG. 2, the shoe housing 10 has shoes 10a, 10b, 10c, and 10d formed in a trapezoidal shape at substantially equal intervals in the circumferential direction.
The vanes 50a, 50 as vane members are provided in the gaps at four circumferential positions of the shoes 10a, 10b, 10c, 10d.
A fan-shaped accommodating chamber 14 for accommodating b, 50c, 50d is formed, and the inner peripheral surfaces of the shoes 10a, 10b, 10c, 10d are formed in an arc-shaped cross section. The shoe housing 10 has an annular first groove 15 formed on the seal plate side of the flange 13.

As shown in FIG. 2, the vane rotor 50 has vanes 50a, 50b, 50c, and 5 at substantially equal intervals in the circumferential direction.
0d, and the vanes 50a, 50b, 50c, 50d are rotatably housed in the respective housing chambers 14. Each vane divides each accommodation chamber 14 into a retard hydraulic chamber and an advance hydraulic chamber. The arrows indicating the retard direction and the advance direction shown in FIG. 2 indicate the retard direction and the advance direction of the vane rotor 50 with respect to the shoe housing 10.

As shown in FIG. 1, a spacer 60 as a shaft portion is installed between the vane rotor 50 and the cam shaft 2. The vane rotor 50, the spacer 60, and the bush 51 are integrally fixed to the camshaft 2 by the bolt 4, and form a driven side rotating body. The positioning of the vane rotor 50 in the rotational direction with respect to the spacer 60 is performed by the pin 52.

The camshaft 2 and the spacer 60 are fitted to the inner peripheral wall 20a of the pulley housing 20 so as to be rotatable relative to each other. Therefore, the cam shaft 2 and the vane rotor 50 are coaxially rotatable relative to the shoe housing 10, the pulley housing 20, the pulley 30, and the seal plate 40. Inner peripheral wall 20a of pulley housing 20 and inner peripheral wall 40a of seal plate 40
Constitutes a bearing of the driven side rotating body.

As shown in FIG. 2, the shoe seal 53 is fitted on the outer peripheral wall of the vane rotor 50. A minute clearance is provided between the outer peripheral wall of the vane rotor 50 and the inner peripheral wall of the peripheral wall 11, and the shoe seal 53 prevents the hydraulic oil from leaking between the hydraulic chambers via this clearance. The shoe seals 53 are biased toward the peripheral wall 11 by the biasing force of a leaf spring (not shown).

As shown in FIG. 1, the guide ring 70 is press-fitted and held in the vane 50d, and an annular stopper piston 71 is housed in the guide ring 70 so as to be slidable in the rotational axis direction of the camshaft 2. ing. The fitting ring 72 is a recess 12a formed in the front plate 12.
Press-fitted and held. The stopper piston 71 abuts on the fitting ring 72 and can be fitted therein. The spring 73 biases the stopper piston 71 toward the fitting ring 72 side.

The tip portion of the stopper piston 71 can be fitted into the fitting ring 72 when the vane rotor 50 is located at the most retarded position with respect to the shoe housing 10. With the stopper piston 71 fitted in the fitting ring 72, the relative rotation of the vane rotor 50 with respect to the shoe housing 10 is restricted. When the vane rotor 50 rotates from the most retarded side to the advanced side with respect to the shoe housing 10,
The positions of the stopper piston 71 and the fitting ring 72 in the circumferential direction are displaced. As a result, the stopper piston 71 is no longer fitted to the fitting ring 72.

As shown in FIG. 1, a communication passage 41 formed in the seal plate 40, a communication passage 54 formed in the vane 50d, and a hole formed on the side opposite to the fitting ring of the stopper piston 71. 74 communicates with the shoe housing 10 when the vane rotor 50 is at the most retarded position. Since the communication passage 41 is open to the atmosphere,
When the communication passage 41 and the hole 74 communicate with each other, the hole 74 is opened to the atmosphere. Therefore, the fitting ring 72 is at the most retarded position.
The movement of the stopper piston 71 coming out of the stopper piston 71 is not hindered. When the vane rotor 50 rotates toward the advance side from the most retarded position, the positions of the communication passage 41 and the communication passage 54 are displaced, so that the communication between the communication passage 41 and the hole 74 is blocked.

As shown in FIG. 2, a retard angle hydraulic chamber 16a is formed between the shoe 10a and the vane 50a, and the shoe 1
0b and the vane 50b form a retard hydraulic chamber 16b, and between the shoe 10c and the vane 50c, the retard hydraulic chamber 1b.
6c is formed, and a retarded hydraulic chamber 16d is formed between the shoe 10d and the vane 50d. Also, shoe 10
The advancing hydraulic chamber 17a is formed between b and the vane 50a, and the advancing hydraulic chamber 1 is formed between the shoe 10c and the vane 50b.
7b is formed, an advance hydraulic chamber 17c is formed between the shoe 10d and the vane 50c, and the shoe 10a and the vane 5 are formed.
An advancing hydraulic chamber 17d is formed between it and 0d.

The retard hydraulic chambers 16a and 16b communicate with the oil passage 81, and the retard hydraulic chambers 16c and 16d communicate with the oil passage 82. The advance hydraulic chambers 17a and 17d communicate with the oil passage 83, and the advance hydraulic chambers 17b and 17c communicate with the oil passage 84. Oil passages 81, 82, 83, 84 are formed in the vane rotor 50, the spacer 60 and the camshaft 2 in the axial direction. Further, the oil passage 82 communicates with the hydraulic chamber 121 formed on the outer peripheral side of the stopper piston 71.

The oil passages 81 and 82 communicate with the oil passage 91 formed in the camshaft 2, and the oil passages 83 and 84 communicate with the oil passage 92 formed in the camshaft 2. Figure 1
As shown in FIG.
4 is connected to the switching valve 100. An oil supply path 101 for supplying a working fluid is connected to an oil pump 102,
The oil discharge path 103 for discharging the working fluid is open toward the drain 104. The oil pump 102 is a drain 104
The hydraulic oil pumped up from is supplied to each hydraulic chamber via the switching valve 100. The switching valve 100 is a well-known 4-port guide valve.

The valve member 105 of the switching valve 100 is biased in one direction by the spring 106, and the solenoid 1
It reciprocates by controlling the energization to 07. The energization of the solenoid 107 is controlled by an ECU (not shown). When the valve member 105 reciprocates, the oil passage 9
The combination of the communication between the oil passages 3, 94 and the oil supply passage 101 and the oil discharge passage 103 and the cutoff are switched. With the above oil passage configuration, the oil pump 102 is connected to the retard angle hydraulic chambers 16a, 16a.
b, 16c, 16d, advance hydraulic chambers 17a, 17b, 17
The hydraulic oil can be supplied to the hydraulic chambers c, 17d or the hydraulic chamber 121, and the hydraulic oil can be discharged from each hydraulic chamber to the drain 104.

As shown in FIG. 1, the spring 21 as the advancing means is housed in an annular housing portion 22 formed in the pulley housing 20. One end 21 a of the spring 21 is inserted and locked in a cylindrical recess 61 formed in the spacer 60. The other end 21b of the spring 21 extends from the shoe housing 10 to the housing 2
It is locked to the pin member 23 protruding to 2. The pin member 23 is press-fitted into the hole portion 18 of the shoe housing 10 and extends to the accommodation portion 22 through the hole portion 42 formed in the seal plate 40.

The load torque received when the camshaft 2 drives the intake valve fluctuates positively or negatively as shown in FIG. Here, the positive side of the load torque biases the vane rotor 50 to the retard side with respect to the shoe housing 10, and the negative side of the load torque biases the vane rotor 50 to the advance side with respect to the shoe housing 10. The average value of the load torque works on the positive side, that is, the retard side. The biasing force of the spring 21 acts as a torque that rotates the vane rotor 50 toward the advance side with respect to the shoe housing 10. The torque in the advance direction applied to the vane rotor 50 by the spring 21 is the maximum when the vane rotor 50 is at the most retarded position with respect to the shoe housing 10, and becomes smaller as the vane rotor 50 advances in the advance direction. The advance torque applied to the vane rotor 50 by the spring 21 is larger than the average load torque received by the camshaft 2 regardless of the relative rotational position of the vane rotor 50 with respect to the shoe housing 10, and the maximum positive load torque that acts in the retard direction is obtained. It is set to be smaller than the value.

As shown in FIG. 1, the shoe housing 10
The seal plate 40 has an O
A groove is formed in which the rings 19 and 43 are accommodated.
The shoe housing 10 is provided with a first groove portion 15 on the surface side that contacts the seal plate 40. First groove 1
As shown in FIG. 2, 5 is formed in an annular shape on the seal plate side of the shoe housing 10. The second groove portion 4 is provided on the seal plate 40 on the surface side that contacts the pulley housing 20, that is, on the surface side opposite to the shoe housing 10.
4 are formed. The second groove portion 44 is formed in an annular shape on the seal plate 40 like the first groove portion 15.
Both the first groove portion 15 and the second groove portion 44 are formed on the pulley housing side of the shoe housing 10 or the seal plate 40. Therefore, when the valve timing adjusting device 1 according to the present embodiment is assembled, the shoe housing 10, the O-ring 19, the seal plate 40, and the O-ring 19.
The ring 43 and the pulley housing 20 can be assembled in this order, and it is not necessary to reverse them in the axial direction during the assembly.

Next, the operation of the valve timing adjusting device 1 will be described. Stopper piston 7 during normal engine operation
Since the stopper piston 71 is pulled out from the fitting ring 72 by the hydraulic pressure of the hydraulic oil supplied to the hydraulic chamber 121 on the outer peripheral side of the vane rotor 1, the vane rotor 50 with respect to the shoe housing 10, the pulley housing 20, and the seal plate 40.
Is relatively rotatable. Then, the phase difference of the camshaft 2 with respect to the crankshaft is adjusted by controlling the hydraulic pressure applied to each hydraulic chamber.

When the engine is stopped, the solenoid 107 is energized for a certain period of time so that the valve member 1 shown in FIG.
05 to the right to connect the oil passages 83 and 84 communicating with the advance hydraulic chambers 17a, 17b, 17c and 17d via the oil passages 92 and 94 to the oil supply passage 101, and to connect the shoe housing. With respect to 10, the vane rotor 50 is rotated to the most advanced position. Since the average of the fluctuating torque received by the camshaft 2 acts on the retard side, the vane rotor 50 is retarded from the most advanced position by the fluctuating torque received by the camshaft 2 before the engine stops when the solenoid 107 is de-energized. When the stopper piston 71 rotates to the side and reaches the most retarded position, the stopper piston 71 is pressed by the spring 73 and the fitting ring 7 is pressed.
Fit to 2. The stopper piston 71 is fitted with the fitting ring 72.
When fitted to, the relative rotation of the vane rotor 50 with respect to the shoe housing 10 is restricted.

Even if the engine is restarted, the retarded hydraulic chamber 16
a, 16b, 16c, 16d, advance hydraulic chambers 17a, 17
Since the hydraulic oil is not supplied to the hydraulic chamber 121 on the outer peripheral side of the stopper piston 71 until the hydraulic oil is supplied to b, 17c, and 17d, the stopper piston 71 is connected to the fitting ring 7.
The camshaft 2 is held in the most retarded position with respect to the crankshaft.

Each retarded hydraulic chamber 16a, 16b, 16c, 1
6d or each advance hydraulic chamber 17a, 17b, 17c, 17
When the hydraulic oil is supplied to d and the hydraulic oil is also supplied to the hydraulic chamber 121 on the outer peripheral side of the stopper piston 71, the stopper piston 71 receives a force on the right side in FIG. 1 and therefore resists the biasing force of the spring 73. The stopper piston 71 comes out of the fitting ring 72. As a result, the shoe housing 1
0 and the restraint between the vane rotor 50 are released, the retard angle hydraulic chambers 16a, 16b, 16c, 16d, the advance hydraulic chamber 1
The vane rotor 50 relatively rotates with respect to the shoe housing 10 by the hydraulic pressure applied to 7a, 17b, 17c, 17d, and the relative phase difference of the camshaft 2 with respect to the crankshaft is adjusted.

Next, a method for manufacturing the valve timing adjusting device 1 according to the first embodiment of the present invention will be briefly described. The vane rotor 50 provided with the guide ring 70, the stopper piston 71 and the like is joined to the spacer 60 by the pin 52. As shown in FIG. 4, the shoe housing 10
The shoe housing 10 is placed with the flange 13 thereof positioned above, and the vane rotor 50 to which the spacer 60 is joined is inserted into the accommodation chamber 14 of the shoe housing 10. After inserting the vane rotor 50 into the shoe housing 10, the O-ring 19 is attached to the first groove portion 15 of the shoe housing 10. Then, the seal plate 40 is placed above the shoe housing 10 and the vane rotor 50. When the seal plate 40 is placed, one end 21a of the spring 21 is inserted into the recess 61 formed in the spacer 60 and locked. End 2 of spring 21
With the spring 1a locked in the recess 61, the spring 21
Is rotated in the retard direction along the circumferential direction of the spacer 60. The spring 21 is rotated against the biasing force, and the other end 21b of the spring 21 is turned to a position corresponding to the hole 42 of the seal plate 40. When the end 21b of the spring 21 reaches a position corresponding to the hole 42 of the seal plate 40, the bent end 21b of the spring 21 is locked to the pin member 23, and the pin 21b is locked. The member 23 is pressed into the hole 18 of the shoe housing 10. As a result, both ends 21 a and 21 b of the spring 21 are respectively formed in the recesses 6 of the spacer 60.
1 or the pin member 23. At this time, the assembled members are in the state shown in FIG.

When both ends of the spring 21 are locked,
The pulley housing 20 and the pulley 30 are fixed to the shoe housing 10 with the bolt 3 shown in FIG. At this time,
An O-ring 43 is installed in the second groove portion 44 formed on the upper surface side of the seal plate 40. Therefore, by tightening the bolt 3, the O-ring 19 and the O-ring 43 are sandwiched between the shoe housing 10 and the seal plate 40 and between the seal plate 40 and the pulley housing 20, respectively. The assembly of the valve timing adjusting apparatus 1 according to the first embodiment is completed by the above procedure. The assembled valve timing adjusting device 1 is attached to the camshaft 2 together with the bush 51 by the bolt 4.

As described above, in the first embodiment of the present invention, the spring 21 has one end 21a locked to the spacer 60 which is the shaft. As a result, only the hole 42 through which the pin member 23 passes is formed in the seal plate 40, and it is not necessary to form the eyebrow-shaped long hole in the seal plate 40. Therefore, it is possible to prevent the hydraulic oil from leaking from the long hole and the communication between the hydraulic chambers. Therefore, a decrease in responsiveness due to leakage of hydraulic oil is prevented, and the distance between the hydraulic chambers can be reduced, so that the vane rotor 50, the shoe housing 10, and the like can be downsized.

Further, by locking the spring 21 to the spacer 60, the vanes 50a, 5a, 5a are formed in order to increase the strength of the vane rotor 50 which receives the urging force of the spring 21.
There is no need to increase the thickness of 0b, 50c, and 50d.
Therefore, the vane rotor 50 can be downsized.

In the first embodiment, the spring 21 can be assembled before the pulley housing 20 is installed in the shoe housing 10. Therefore, when the spring 21 is assembled, the pulley housing 20 does not rotate due to the rotation of the spring 21.
The O-rings 19 and 43 are rotated by the first groove 15
Alternatively, it does not protrude from the second groove portion 44. Therefore, the sealing performance of the O-rings 19 and 43 can be improved.

Further, in the first embodiment, the first groove portion 15 and the second groove portion 44 are formed on the pulley housing side of the shoe housing 10 or the seal plate 40. Accordingly, the two O-rings 19 and 44 can be attached to the first groove portion 15 or the second groove portion 44 from the same direction. Therefore, it is not necessary to reverse the valve timing adjusting device 1 during the assembling. Therefore, the assembling property is improved, and it is possible to prevent the deterioration of the sealing property due to the displacement or the dropping of the O-rings 19, 44.

(Second Embodiment) FIG. 5 shows a second embodiment of the present invention.
Shown in. The same components as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. The second embodiment differs from the first embodiment in that the camshaft 110 extends in the direction of the vane rotor 50. That is, in the second embodiment,
No spacer is interposed between the vane rotor 50 and the cam shaft 110, and the shaft portion is formed integrally with the cam shaft 110.

The pulley housing 20 is the camshaft 1
The pulley housing 20 is provided on the outer peripheral side of the pulley 10, and the inner peripheral side of the pulley housing 20 serves as a bearing for rotatably supporting the camshaft 110. A recess 111 is formed in the camshaft 110, and one end 21a of the spring 21 is inserted into and locked in the recess 111. In the second embodiment,
As compared with the first embodiment, since the spacer is not required, the structure is simple and the number of parts can be reduced.

(Third Embodiment) FIG. 6 shows a third embodiment of the present invention.
Shown in. The same components as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. The third embodiment differs from the first embodiment in that the vane rotor 150 extends in the direction of the camshaft 2.

In the third embodiment, the vane rotor 150 is provided with a neck 151 extending in the direction of the camshaft 2. The neck portion 151 is formed so as to project from the main body of the vane rotor 150 toward the camshaft 2 and constitutes a shaft portion. The pulley housing 20 is installed on the outer peripheral side of the neck portion 151, and the inner peripheral side of the pulley housing 20 serves as a bearing that rotatably supports the neck portion 151. A recess 152 is formed in the neck 151, and one end of the spring 21 is inserted into and locked in the recess 152.

Since the third embodiment does not require a spacer as compared with the first embodiment, the structure is simple and the number of parts can be reduced. Further, the valve timing adjusting device can be configured separately from the camshaft 2.

Although the valve timing adjusting device for driving the intake valve has been described in the above-described embodiments of the present invention, the valve timing adjusting device drives only the exhaust valve or both the intake valve and the exhaust valve. It is also possible. In addition, in the above-described embodiments, the stopper piston moves in the axial direction and fits into the fitting ring, but the stopper piston may move in the radial direction and fit into the fitting ring. is there.

Further, in a plurality of embodiments of the present invention, the structure in which the rotational driving force of the crankshaft is transmitted to the camshaft by the timing gear is adopted, but a structure using a timing pulley or a chain sprocket can also be adopted. is there. It is also possible that the vane member receives the driving force of the crankshaft serving as the driving shaft, and the camshaft serving as the driven shaft and the first housing and the second housing are integrally rotated.

[Brief description of drawings]

FIG. 1 is a schematic cross-sectional view showing a valve timing adjusting device according to a first embodiment of the present invention, which is I-O- of FIG.
It is the figure cut at the position corresponding to the I line.

FIG. 2 is a schematic view showing the valve timing device according to the first embodiment of the present invention, and is a view of a vane rotor housed in a shoe housing and a spacer connected to the vane rotor as seen from the crankshaft side.

3 is a cross-sectional view taken along line I-O-I of FIG. 2, showing a state in which a seal plate, a spring and a pin member are attached to the state shown in FIG.

FIG. 4A is a schematic diagram showing a rotation direction of a camshaft and a pulley, and FIG. 4B is a characteristic diagram showing a load torque received by the camshaft.

FIG. 5 is a schematic cross-sectional view showing the same cross section as FIG. 1 of the valve timing adjusting device according to the second embodiment of the present invention.

FIG. 6 is a schematic cross-sectional view showing the same cross section as FIG. 1 of a valve timing adjusting device according to a third embodiment of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Valve timing adjusting device 2 Camshaft (driven shaft) 10a, 10b, 10c, 10d Shoe 10 Shoe housing (first housing member) 14 Storage chamber 15 First groove portions 16a, 16b, 16c, 16d Delay angle hydraulic chambers 17a, 17b , 17c, 17d Advance angle hydraulic chamber 19 O-ring (seal member) 20 Pulley housing (second housing member) 21 Spring (advance means) 22 Housing portion 23 Pin member 40 Seal plate (plate member) 43 O-ring 44 Second Groove portion 50 Vane rotor (vane member) 50a, 50b, 50c, 50d Vane (vane member) 60 Spacer (shaft portion) 61 Recessed portion 110 Camshaft (shaft portion) 111 Recessed portion 150 Vane rotor 151 Neck portion (shaft portion) 152 Recessed portion 1 Valve timing adjustment apparatus

Claims (8)

[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, and at least the intake valve and the exhaust valve. A valve timing adjustment device that adjusts the opening / closing timing of either one of the drive shaft or the driven shaft, and a shaft portion connected to an end of the drive shaft or the driven shaft, and an opposite side of the drive shaft or the driven shaft of the shaft portion. A first housing member that is installed at an end portion of the shaft and that rotates together with one of the drive shaft and the driven shaft, and is rotatable with the first housing member, and the first housing member is radially outside the shaft portion. A second housing member installed to face the housing, and a housing formed on the first housing member that rotates together with the other of the drive shaft and the driven shaft. A vane member that is housed in the housing chamber, divides the housing chamber into an advance chamber and a retard chamber, and is driven to rotate relative to the housing member by working fluid pressure only within a predetermined angle range; A plate member that is installed between the second housing member and seals between the first housing member and the vane member and the second housing, and is housed in a housing portion formed in the second housing. A valve timing adjusting device, comprising: one end portion that is locked to the shaft portion, and advance means that applies advance torque to the driven shaft in a direction that advances the drive shaft. 2. The valve timing adjusting device according to claim 1, wherein one end of the advance means is locked to the drive shaft or the driven shaft. 3. The shaft portion has a spacer installed between the vane member and the drive shaft or the driven shaft, and one end portion of the advance means is locked to the spacer. The valve timing adjusting device according to claim 1, wherein 4. The vane member has a neck portion protruding toward the drive shaft or the driven shaft, and one end portion of the advance means is locked to the neck portion. 1. The valve timing adjusting device according to 1. 5. The other end portion of the advance means is locked to a pin member protruding from the first housing to the housing portion through the plate member.
5. The valve timing adjusting device according to any one of items 4 to 4. 6. A drive force transmission system that transmits 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, and at least the intake valve and the exhaust valve. A valve timing adjusting device for adjusting the opening / closing timing of any one of the first and second housing members, which is installed at an end of the drive shaft or the driven shaft and rotates together with one of the drive shaft or the driven shaft, The drive shaft or the driven shaft has a housing portion capable of housing an advance means for applying advance torque to the driven shaft in a direction of advancing the drive shaft, and is rotatable with the first housing. The second housing member, which is installed on the outside in the radial direction so as to face the first housing member, rotates together with the other of the drive shaft and the driven shaft, A vane that is housed in a housing chamber formed in a housing member, divides the housing chamber into an advance chamber and a retard chamber, and is rotationally driven relative to the housing member by working fluid pressure within a predetermined angle range. A member, a plate member installed between the first housing member and the second housing member, and sealing between the first housing member and the vane member, and the second housing member; Of the first housing and the plate member, which are installed in a first groove portion circumferentially formed on the plate member side and a second groove portion circumferentially formed on the opposite first housing side of the plate member. And a seal member that seals between the plate member and the second housing, and a valve timing adjusting device. 7. The valve timing adjusting device according to claim 6, wherein the first groove portion and the second groove portion are formed in an annular shape. 8. The valve timing adjusting device according to claim 6, wherein the seal member is an O-ring.