JP2000097006A - Valve opening/closing timing control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enhance the responsiveness of the relative rotation to the advance side without bringing about increase in the manufacturing cost and an obstruction for the supply and exhaust of fluid to/from a fluid pressure chamber. SOLUTION: A cylindrical part 41 is formed in a rotation transmitting member (outer rotor 30, front plate 40, rear plate 50) in such a way as extending in the axial direction, and in this cylindrical part 41, a torsion coil spring 80 is installed whose one end is locked to a rotary member (inner rotor 20) and other end is engaged with the end of the cylindrical part for energizing the rotary member to the rotation transmitting member at all times in the advance direction, wherein one of the first fluid passage and second fluid passage is composed of a shaft hole 12 formed in the rotary member and opening to inside the cylindrical part, a communication line 25 formed between the rotation transmitting member and the rotary member and opening at one of the advancing chamber and lay chamber, and a passage means 26 to put the communication line leading to the shaft hole.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve timing control device for controlling the timing of opening or closing an intake valve or an exhaust valve in a valve train of an internal combustion engine.

[0002]

2. Description of the Related Art As one type of a valve opening / closing timing control device of this kind, a rotating member integrally provided on a valve opening / closing camshaft rotatably mounted on a cylinder head of an internal combustion engine has a relative rotation within a predetermined range. A rotation transmission member which is externally provided and to which rotational power from a crankshaft is transmitted, a vane provided on the rotation member, and an advance chamber formed between the rotation member and the rotation transmission member by the vane. A fluid pressure chamber divided into two chambers, a first fluid passage for supplying and discharging the fluid to the advance chamber, and a second fluid passage for supplying and discharging the fluid to the retard chamber. For example, JP-A-1-9
No. 2504. In this conventional apparatus, a control valve is used to selectively supply and discharge fluid from an oil pump to an advance chamber and a retard chamber via a first fluid passage and a second fluid passage, respectively. The rotating member and the rotation transmitting member are relatively rotated by a fluid pressure difference generated between the chamber and the retarding chamber, and the opening / closing timing of the intake valve or the exhaust valve is adjusted (advance angle) by adjusting the relative rotation amount (fluid pressure difference). Or retarded)
Is done.

[0003]

In the valve timing control apparatus disclosed in the above publication, the fluid pressure chamber and the vane are interposed in the rotation transmission path from the rotation transmission member to the rotation member, and the camshaft is provided. Since a torque to the retard side acts on the rotary member due to frictional force, a force in the retard direction always acts on the rotating member during operation of the internal combustion engine.
Therefore, as described above, when the rotation shaft and the rotation transmitting member are relatively rotated to the advance side or the retard side due to the fluid pressure difference between the advance chamber and the retard chamber, the relative rotation to the retard side is performed. In comparison with the above, the response in the case of relative rotation to the advance side is reduced.

Further, when the above-described valve opening / closing timing control device is mounted on the exhaust side camshaft to adjust the opening / closing timing of the exhaust valve, the relative position between the rotation transmitting member and the rotating member is reduced by stopping the internal combustion engine. When the internal combustion engine is started in a state where the fluid pressure in the advance chamber and the retard chamber is reduced at an arbitrary position, the rotation transmission member and the rotation member are maximally driven by the force in the retard direction described above. The relative rotation to the retarded position results in the overlap between the exhaust valve and the intake valve becoming unnecessarily large, leading to poor starting of the internal combustion engine.

In order to solve these problems, the present applicant has
The rotation transmitting member extends in the axial direction to form a cylindrical portion. In the cylindrical portion, one end is locked by the rotating member and the other end is locked by the end of the cylindrical portion to rotate the rotating member. If a torsion coil spring that constantly urges the transmission member in the advance direction is provided, and the valve timing control device is attached to the camshaft on the exhaust side, the relative position between the rotation member and the rotation transmission member is reduced. Japanese Patent Application No. 9-063247 proposes a novel valve opening / closing timing adjusting device which is provided with a relative rotation restricting means for restricting the relative rotation between the exhaust camshaft and the rotation transmitting member when it is at the most advanced position. According to this device, the force in the retarding direction is offset by the biasing force of the torsion coil spring, and the responsiveness of the relative rotation to the advance side is improved. Further, in the case where the rotation transmission member and the rotation member are attached to the exhaust-side camshaft, the fluid pressure in the advance chamber and the retard chamber decreases when the relative position between the rotation transmission member and the rotation member is arbitrary at the stop of the internal combustion engine. When the internal combustion engine is started while the engine is running, the rotation transmitting member and the exhaust side camshaft are relatively rotated in the advance direction by the fluctuating torque acting on the camshaft and the torsion coil spring, and the relative rotation is restricted at the most advanced position. The relative rotation is restricted by the means, and the overlap between the exhaust valve and the intake valve is prevented from increasing as described above.

However, in this device, the first fluid passage and the second fluid passage communicate with each shaft hole provided in the rotating member, and each of the shaft holes communicates with the advance chamber and the retard chamber. Therefore, a large amount of drilling is required to form each radial passage, and the manufacturing cost of the valve timing control apparatus increases. there were. The problem is that one of the first fluid passage and the second fluid passage is provided with a shaft hole provided in the rotating member so as to open into the cylindrical portion, and the shaft hole is connected to the advance chamber or the retard chamber through the space in the cylindrical portion. A communication passage provided between the rotation member and the rotation transmission member so as to communicate with the corner chamber, and the communication passage is formed in a groove shape on the end surface of the rotation member so as to be formed simultaneously with the molding of the rotation member. This can be solved by reducing the number of drilling processes.

However, according to this configuration, the communication between the shaft hole and the communication passage through the internal space of the cylindrical portion is cut off by the torsion coil spring, and the supply and discharge of the fluid to the advance chamber or the retard chamber is hindered. This causes a problem that the responsiveness of the valve timing control device is reduced.

Therefore, the present invention provides a valve opening / closing timing control device which improves the responsiveness of the relative rotation to the advance angle side without increasing the manufacturing cost and obstructing the supply and discharge of the fluid to and from the fluid pressure chamber. Is the task.

[0009]

Means for Solving the Problems The technical means of the present invention taken to solve the above-mentioned problems is to provide a rotating member which rotates together with one of a crankshaft and a camshaft of an internal combustion engine; A rotation transmission member that is attached so as to be relatively rotatable and rotates together with the other of the crankshaft or the camshaft; a vane provided on one of the rotation member or the rotation transmission member; A fluid pressure chamber formed between the advancing chamber and the retarding chamber by the vane, a first fluid passage for supplying and discharging a fluid to the advancing chamber, and a fluid to the retarding chamber. A second fluid passage which supplies and discharges the rotation of the crankshaft. The rotation member and the rotation transmission member rotate relative to each other by the fluid pressure applied to the advance chamber and the retard chamber. A valve opening / closing timing control device that changes and controls the opening / closing timing of a valve driven by the camshaft by changing the rotation phase of the camshaft with respect to the rotation shaft. In the cylindrical portion, one end is locked to the rotating member and the other end is locked to the end of the cylindrical portion to constantly bias the rotating member in the advance direction with respect to the rotation transmitting member. A coil spring is provided, and one of the first fluid passage and the second fluid passage is provided between a shaft hole formed in the rotating member and opened in the cylindrical portion, and the rotation transmitting member and the rotating member. A communication passage is formed and opened to one of the advance chamber and the retard chamber, and a passage means for communicating the communication passage with the shaft hole.

According to the above-mentioned means, the communication between the shaft hole and the communication passage through the internal space of the cylindrical portion is compensated for by the passage means, so that the torsion coil spring is used to move to one of the advance chamber or the retard chamber. The responsiveness of the relative rotation to the advance side can be improved by the torsion coil spring without obstructing the supply and discharge of the fluid.

In the above means, the passage means is
It may be configured by a gap provided between adjacent winding portions of the torsion coil spring, and an annular gap provided between the inner periphery of the cylindrical portion and the torsion coil spring. Alternatively, the passage means may be constituted by a communication groove provided so as to communicate with the rotating member radially inward and outward of the end turn portion on one end side of the torsion coil spring.

In the above means, a lid member is fixed to the distal end of the cylindrical portion in a liquid-tight manner, and the torsion coil spring extends in the cylindrical portion in the axial direction and extends radially in the cylindrical portion. A bearing portion for bearing may be provided.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a valve timing control apparatus according to the present invention will be described below with reference to the drawings.

The valve timing control apparatus according to the first embodiment shown in FIGS. 1 to 5 has a camshaft 10 rotatably supported by a cylinder head 110 of an internal combustion engine, and is integrated with a tip end of the camshaft 10. Assembled internal rotor 20
(Rotating member), camshaft 10 and internal rotor 20
External rotor 3 externally rotatable relative to a predetermined range
0, a front plate 40, a rear plate 50, a timing pulley 60, etc., a rotation transmitting member, four vanes 70 attached to the internal rotor 20, and an internal rotor 20.
And a torsion coil spring 80 attached between the front rotor 40 and the front plate 40, a lock pin 90 attached to the external rotor 30, and the like. As is well known, the timing pulley 60 is configured to transmit rotational power clockwise in FIG. 2 from a crankshaft 61 via a crank pulley (not shown) and a timing belt 62. The power transmission from the crankshaft 61 to the rotation transmitting member can be performed via a timing chain or a timing gear instead of the timing belt.

The camshaft 10 has a well-known cam for opening and closing an intake valve and an exhaust valve (both not shown).
An advance passage 1 extending in the axial direction of the camshaft 10 therein.
1 and a retard passage 12 are provided. The retard passage 12
The control valve 100 is formed in a mounting hole for a mounting bolt 19 provided in the camshaft 10, and passes through a radial passage 13 and an annular groove 14 provided in the camshaft 10 and a connection passage P1 provided in the cylinder head 110. It is connected to the first connection port 101. Further, the advance passage 11 is provided between the annular groove 15 provided in the camshaft 10 and the cylinder head 10.
The control valve 100 is connected to the second connection port 102 of the control valve 100 through a connection passage P2 provided in the control valve 100.

When the solenoid 103 is energized, the control valve 100 pushes the spool 104 inserted in the housing movably in the axial direction against the spring 105 as shown in FIG.
When the power is not supplied, the supply port 106 connected to the oil pump P driven by the internal combustion engine communicates with the first connection port 101, and the second connection port 102 connects to the discharge port 107. The supply port 106 communicates with the second connection port 102 so that the first connection port 101
Are configured to communicate with the discharge port 107.
For this reason, when the solenoid 103 of the control valve 100 is not energized, hydraulic oil is supplied to the retard passage 11 and the solenoid 10
At the time of energization of 3, hydraulic oil is supplied to the advance passage 12, and energization of the solenoid 103 is duty-controlled by a control device (not shown).

The inner rotor 20 has a single mounting bolt 19
And is integrally fixed to the camshaft 10 by
Each of the four vanes 70 has a vane groove 21 for movably attaching the vane 70 in a radial direction, and the state shown in FIG. 2, that is, the relative phase between the camshaft 10 and the internal rotor 20 and the external rotor 30 is a predetermined phase. The receiving hole 22 into which the head of the cylindrical lock pin 80 is fitted by a predetermined amount when synchronized at the (most advanced position), and the advanced angle passage 12
From one of the advance chambers R1 partitioned by the vanes 70 from
A passage 23 through which hydraulic oil can be supplied and discharged, and
A passage 25 for supplying and discharging hydraulic oil from the advance passage 12 to the advance chamber R1 defined by 0, and a hydraulic oil from the retard passage 11 to the retard chamber R2 defined by each vane 70. It has a passage 24. As shown in FIGS. 3 and 4, the receiving hole 22 is a bottomed hole having a diameter larger than the outer diameter of the head of the lock pin 90 by a predetermined amount, and is an annular gap formed by the head of the lock pin 90. The working oil is supplied to and discharged from the bottom of the receiving hole 22 through the through hole. In addition, each vane 70
Is urged radially outward by a spring 71 (see FIG. 1) housed in the bottom of the vane groove 21.

The outer rotor 30 is relatively rotatably mounted on its inner periphery to the outer peripheral surface of the inner rotor 20 with a predetermined clearance (a minimal clearance through which hydraulic oil is interposed), and a front plate 40 is provided on both sides thereof. And the rear plate 50 are joined via seal members S1 and S2, and are integrally connected with the timing pulley 60 by bolts B1. In the outer rotor 30, a pressure chamber R0 accommodating each vane 70 and divided into an advance chamber R1 and a retard chamber R2 by each vane 70 is formed by the internal rotor 20, the front plate 40 and the rear plate 50. A concave portion 32 is formed, and a retracting hole 33 for accommodating a lock pin 90 and a spring 91 for urging the lock pin 90 toward the internal rotor 20 is formed in a radial direction of the external rotor 30.

Each vane 70 connects the pressure chamber R0 to the advance chamber R.
1 and a retarding chamber R2, and are located in the fluid pressure chamber R0 at stopper portions 34 and 35 formed on circumferential end surfaces of a recess 32 defining the pressure chamber R0 shown in the lower part of FIG. When one of the vanes 70 abuts, the phase (the relative rotation amount) adjusted by the valve opening / closing timing control device is limited. In the present embodiment, the stopper portions 34 and 35 are formed so as to protrude in the circumferential direction at the inner end of the circumferential end surface of the concave portion 32. Groove passages 34a and 34b are formed to compensate for communication with the chamber R2, and the stopper portion 3
The groove passages 35a and 35b for compensating the communication between the passage 24 and the advance chamber R1 are formed on the side surface of the rear plate 50 on the rear plate 50 side.

The evacuation hole 33 has an outer end liquid-tightly closed by a plug 92 and a sealing member 93, and a back pressure chamber R 3 is formed at the back of the lock pin 90. As shown in FIGS. 3 and 4, the back pressure chamber R3 has a communication hole 36 formed in the external rotor 30 and communicating with the back pressure chamber R3, and a radially outer end formed in the rear plate 50. A communication groove 51 communicating with the communication hole 36 and a boss 52 of the rear plate 50
(The outer periphery is engaged with the oil seal 111 attached to the cylinder head 110, and the inner periphery is rotatably attached to the outer periphery of the camshaft 10 with a predetermined gap.
Of the cylinder head 110 through a communication hole (not shown) formed in the camshaft support portion 112 of the cylinder head 110. The evacuation hole side opening of the communication hole 36 is formed by the skirt portion of the lock pin 90 even when the lock pin 90 moves against the urging force of the spring 91 by the hydraulic oil supplied to the receiving hole 22 through the passage 23. It is arranged so that it is not blocked. Further, the plug 92 is prevented from coming off by the timing pulley 60.

The lock pin 90 has a head portion and a skirt portion, and can be moved in the evacuation hole 33 in the skirt portion in a radial direction of the external rotor 30 through a predetermined gap (a very small gap where hydraulic oil is interposed). And is always urged toward the internal rotor 20 by the spring 91. Thus, when the relative phase between the camshaft 10 and the internal rotor 20 and the external rotor 30 is synchronized at a predetermined phase (the most advanced position), the lock pin 90 moves its head to the internal rotor 20 as shown in FIG. Of the inner rotor 20 and the outer rotor 30 is regulated.

The front plate 40 is provided with a cylindrical portion 41 projecting in the axial direction of the camshaft 10.
The cylindrical portion 41 has a stepped inner hole having a large diameter portion 42 and a small diameter portion 43, and a torsion coil spring 80 is housed in the large diameter portion 42. Torsion coil spring 8
Reference numeral 0 indicates that one end 80a is engaged with the notch 45 provided in the large diameter portion 42 of the cylindrical portion 41, and the other end 80b is engaged with the engaging portion 28 (see FIG. 2) provided on the side surface of the internal rotor 20. Stop,
The inner rotor 20 is attached to the outer rotor 3 so as to extend in the axial direction along the large-diameter portion 42.
0, the front plate 40 and the rear plate 50 are constantly biased clockwise in FIG. In the torsion spring 60, the fluid pressure chamber R0 and the vane 71 are interposed in the rotation transmission path from the outer rotor 30 to the inner rotor, and a torque is applied to the camshaft to the retard side by frictional force. For this reason, the internal rotor 20 and the external rotor 30 are provided in consideration of the force in the retard direction (force that hinders the rotation to the advance side) always acting between the internal rotor 20 and the external rotor 30 during operation of the internal combustion engine. The inner rotor 20 is urged toward the advancing side with respect to the outer rotor 30, the front plate 40, and the rear plate 50, thereby improving the operation responsiveness of the inner rotor 20 toward the advancing side. The biasing force of the torsion coil spring 80 is set to an average torque (torque to the retard side described above) acting on the camshaft 10.

On the side surface of the internal rotor 20, a recess 2 for accommodating the end turn on the other end of the torsion coil spring 80 is provided.
7 is formed, and the inner diameter of the recess 27 is
Is set to be the same as the inner diameter of the large-diameter portion 42. In the present embodiment, the outer diameter of the winding portion of the torsion coil spring 80 is set slightly smaller than the inner diameter of the concave portion 27 and the large diameter portion 42, whereby the torsion coil spring 80 is guided in the radial direction. ing. The bottom surface of the recess 27 communicates with the inside and outside of the end turn on the other end side of the torsion coil spring 80, and the outside end thereof is connected to the passage 25.
Is formed with a communication groove 26 that is connected to the first groove. In the present embodiment, the passage 25 is formed in a continuous groove with the communication groove 26.

The open end of the cylindrical portion 41 is closed in a liquid-tight manner by a cap 82 screwed and fixed by the small-diameter portion 43, whereby the communication between the retard passage 12 of the camshaft 10 and the internal rotor 20 is established. Passage 2 connecting passage 26 and passage 25
8 are formed. In the present embodiment, a cylindrical guide that extends into the winding portion of the torsion coil spring 80 on the cap 82, guides the inner periphery of the winding portion, and prevents radial movement due to twisting of both ends of the torsion coil spring 80. The part 83 is formed integrally. As shown in FIGS. 5 and 6, a plurality of slits 84 extending in the axial direction are formed in the guide portion 83, and the retard passage 12 of the camshaft 10 and the communication groove 26 of the internal rotor 20 are formed. The communication with the passage 25 via the passage 28 is not hindered. The outer peripheral surface of the guide portion 83 is covered with a low friction material 85 such as a Teflon resin material.
The relative rotation between the internal rotor 20 and the like and the external rotor 30 and the like is not hindered by friction caused by the interference.

In the valve timing control apparatus of the first embodiment configured as described above, the state shown in FIG. 2, that is, the internal combustion engine is stopped and the oil pump P is stopped, and the solenoid 103 of the control valve 100 is turned off. In the non-energized state, the inner rotor 20 and the outer rotor 30 synchronize at the most advanced position, the head of the lock pin 90 fits into the receiving hole 22 by a predetermined amount, and the inner rotor 20 at the most advanced position. And external rotor 3
When the internal combustion engine is started in the locked state that restricts the relative rotation of 0, the oil pump P is driven to control the control valve 1
00 solenoid 103 is energized. As a result, hydraulic oil is supplied from the oil pump P to the receiving hole 22 through the control valve 100, the connection passage P2, the advance passage 11, the passage 24, the advance chamber R1, and the passage 23 of the camshaft 10. It takes a predetermined time until the pressure of the hydraulic oil in the receiving hole 22 rises to a pressure sufficient to move the lock pin 90 from the receiving hole 22 into the evacuation hole 33 against the spring 91. The locked state shown in FIGS. 2 and 3 is maintained. As a result, the internal rotor 20 and the external rotor 30 rotate relative to each other due to large torque fluctuations acting on the camshaft 10 when the internal combustion engine is started, and the vanes 70 collide with the stopper portions 34 and 35 of the external rotor 30 to generate a tapping sound. Is prevented.

After a lapse of a predetermined time from the start of the internal combustion engine and the driving of the oil pump P, the oil is supplied from the energized control valve 100 to the receiving hole 22 through the advance passage 11 of the camshaft 10 and the like. The pressure of the hydraulic oil rises, and as shown in FIG. 4, the lock pin 90 moves against the spring 91, comes out of the receiving hole 22 to the evacuation hole 33, and the lock is released. Accordingly, the duty ratio of the current supplied to the solenoid 103 of the control valve 100 is reduced according to the operating state of the internal combustion engine, so that the retard passage 12 and the passage 25
When the hydraulic oil is supplied to each of the retard chambers R2 through the like, and the hydraulic oil is discharged from each of the advance chambers R1 through the passages 24, the advance passages 11, the control valve 100, and the like, the camshaft 10, The internal rotor 20 and each vane 70 rotate relative to the external rotor 30 and the like on the retard side (counterclockwise in FIG. 2), and the relative rotation amount (maximum retard amount) is one vane (FIG. 2). The lower vane 70 is restricted by contact with the stopper portion 35. In addition, by increasing the duty ratio of the current supplied to the solenoid 103 of the control valve 100, hydraulic oil is supplied to each advance chamber R1 through the advance passages 11 and each passage 24, and at the same time, When the hydraulic oil is discharged from the chamber R2 through the passages 25, the retard passages 12, the control valve 100, and the like, the camshaft 10, the internal rotor 20, and the vanes 70 are advanced with respect to the external rotor 30 and the like (FIG. 2). ), And the relative rotation amount (the maximum advance amount) is one vane (the lower vane in FIG. 2).
70 is limited by contact with the stopper 34 (the state of FIG. 2). Thus, by controlling the duty ratio of the current supplied to the solenoid 103 of the control valve 100 according to the operating state of the internal combustion engine, the opening / closing timing of the intake valve and the exhaust valve (not shown) driven to open and close by the camshaft 10 is controlled. Is precisely controlled in accordance with the operating state of the internal combustion engine.

The pressure chamber R0 and the vane 70 are interposed in the rotation transmission path from the rotation transmitting member such as the external rotor 30 to the internal rotor 20 and the camshaft 10, and the camshaft 10 is retarded by frictional force. While the internal torque is acting on the internal rotor 20 and the camshaft 10 during operation of the internal combustion engine, a force in the retard direction always acts on the internal rotor 20 and the camshaft 10 according to the present embodiment. 80 can offset the force in the retard direction. Accordingly, it is possible to prevent the responsiveness when the internal rotor 20 and the camshaft 10 are relatively rotated to the advance side with respect to the rotation transmitting member such as the external rotor 30 by the above-described force in the retard direction from being reduced. it can. In the present embodiment, the passage 25 is connected to the internal rotor 20.
Since the inner rotor 20 is formed in a groove shape on the side surface, it is not necessary to perform post-processing such as drilling.
5 can be formed, and the manufacturing cost of the valve timing control device can be reduced. In addition, this passage 25
Although the torsion coil spring 80 is located between the passage 25 and the retard passage 12 according to the configuration described above, the communication between the passage 25, the retard passage 12 and the passage 28 can be better secured by the communication groove 26, so that the Oil retarding chamber R2
This prevents the torsion coil spring 80 from obstructing the supply to the exhaust port and the discharge from the retard chamber R2, thereby ensuring the responsiveness of the inner rotor 20 and the outer rotor 30. Since the communication groove 26 is provided continuously with the passage 25 and can be formed at the same time when the passage 25 is formed, the above-described passage 25 and the retard passage 12 and the passage 28 can be formed without post-processing. Good communication can be ensured.

When the internal combustion engine is stopped, the operation of the oil pump P is stopped, the supply of the hydraulic oil to the pressure chamber R0 is stopped, and the control valve 100 is turned off. As a result, the pressing force by the advance hydraulic pressure in the advance chamber R1 and the pressing force by the retard hydraulic pressure in the retard chamber R2 do not act on the vane 80, and the internal rotor 20 and the external rotor 3 immediately before the stop are stopped.
The relative phase of the internal rotor 20 and the external rotor 30 at the time of stoppage is determined according to the relative phase of zero. At this time, the relative phase between the internal rotor 20 and the external rotor 30 immediately before the stop is
When the evacuation hole 33 and the receiving hole 22 are in a predetermined phase (the most advanced position) synchronized with each other, the head of the lock pin 91 is fitted into the receiving hole 29 by the spring 92, and the inner rotor 20 and the outer rotor 30 The relative phase is held (locked). On the other hand, when the relative phase between the internal rotor 20 and the external rotor 30 immediately before the stop is on the more retarded side than the predetermined phase in which the retreat hole 33 and the receiving hole 22 are synchronized, the lock pin 90 causes the internal rotor 20 and the external rotor Stop at an arbitrary relative phase without maintaining the relative phase of 30. When the internal combustion engine is started and the oil pump P is driven in this state, the pressure of the hydraulic oil in the pressure chamber R0 is low for a predetermined time after the start, and
Can not hold. Therefore, the inner rotor 20
Tries to rotate relative to the external rotor 30 in the retarded direction due to the above-described force in the retard direction, but the relative phase between the internal rotor 20 and the external rotor 30 is held by the lock pin 90 at the time of stopping as described above. , This relative rotation is prevented. If the relative phase is not held by the lock pin 90 at the time of stopping, the internal rotor 2
0 attempts to rotate relative to the external rotor 30 in the retard direction due to the above-described force in the retard direction. However, since the force in the retard direction is offset by the torsion coil spring 80, the camshaft 10 Of the fluctuating torque that acts,
The internal rotor 20 can be relatively rotated with respect to the external rotor 30 to the advance side by the urging force of the torsion coil spring 80 by multiplying the torque to the advance side. And
During the relative rotation to the advance side, the relative phase of the inner rotor 20 and the outer rotor 30 becomes a predetermined phase (the most advanced position) in which the retreat hole 33 and the receiving hole 22 are synchronized, and the head of the lock pin 90 is moved to the receiving hole 29. And the relative phase between the inner rotor 20 and the outer rotor 30 is held (locked). As described above, in the present embodiment, when the internal combustion engine is started, the relative phase between the internal rotor 20 and the external rotor 30 is held at the most advanced position by the lock pin 90. The outer rotor 30 and the inner rotor 20 rotate relatively to the most retarded position. As a result, the opening / closing timing of the intake valve and the exhaust valve is delayed, so that the internal EGR amount increases, leading to poor starting of the internal combustion engine. Is prevented.

FIG. 7 shows a second embodiment of the present invention. In the second embodiment, the outer diameter a of the torsion coil spring 80 (the inner diameter of the recess 27 of the inner rotor 20) is set smaller than the inner diameter A of the large diameter portion 42 of the cylindrical portion 41 by a predetermined amount. An annular gap C1 communicating with the passage 25 is formed between the outer periphery of the coil spring 80 and the inner periphery of the large diameter portion 42. Further, the torsion coil spring 80 is set such that a predetermined gap C2 is always formed between adjacent windings of the torsion coil spring 80.

According to the second embodiment, the communication between the passage 25, the retard passage 12, and the passage 28 can be better ensured by the annular gap C1 and the gap C2. Is prevented from being hindered by the torsion coil spring 80, and the responsiveness of the inner rotor 20 and the outer rotor 30 can be guaranteed. In the second embodiment, the other configurations and operations are the same as those of the above-described first embodiment. Therefore, in FIG. 7, the same configurations are denoted by the same reference numerals used in FIGS. Description is omitted.

In each of the above embodiments, the slit 84 is provided in the guide portion 83 of the cap 82, but as shown in FIGS. 8 and 9, the guide portion 183 of the cap 182 is provided.
May be provided with a plurality of through holes 184 in the radial direction. In FIG. 9, reference numeral 185 denotes a low friction material.

In each of the above-described embodiments, the present invention is applied to a valve opening / closing timing control device which is mounted on the camshaft 10 for simultaneously driving the intake valve and the exhaust valve.
The present invention can be similarly applied to a valve opening / closing timing control device mounted on an intake camshaft or an exhaust camshaft.

In each of the above-described embodiments, the vane is provided separately from the internal rotor, the receiving hole and the retreat hole are formed in the radial direction, and the valve timing control device in which the lock pin moves in the radial direction. According to the present invention, the vane is made thicker in the circumferential direction, is integrally provided in the inner rotor, and has an evacuation hole formed in the vane or the rear plate (or front plate) in the axial direction. The present invention can be similarly applied to a valve timing control device in which a receiving hole is formed in a plate (or a front plate) or a vane in an axial direction, and a lock pin moves in an axial direction.

In each of the above embodiments, the present invention is applied to a valve timing control apparatus configured to supply hydraulic oil to the receiving hole 22 from the advance chamber R1 through the passage 23. According to the present invention, hydraulic oil is supplied to the receiving hole 22 from the retard passage and the lock pin 9 is actuated by the hydraulic oil in the retard passage.
The same applies to a valve opening / closing timing control device configured so that 0 is retracted to the retreat hole 33.

Further, in each of the above-described embodiments, the state in which the retard chamber R2 has the minimum volume (the most advanced state).
Although the head of the lock pin 90 assembled to the outer rotor 30 is configured to be fitted into the receiving hole 22 of the inner rotor 20, the state in which the advance chamber R1 has the minimum volume (most retarded state) It is also possible to configure and implement such that the head of the lock pin assembled to the outer rotor is fitted into the receiving hole of the inner rotor.

[0036]

As described above, according to the present invention, the communication between the shaft hole and the communication passage through the internal space of the cylindrical portion is compensated by the passage means, so that the manufacturing cost is increased and the advance angle is increased by the torsion coil spring. The response of the relative rotation to the advance side can be improved by the torsion coil spring without inhibiting the supply / discharge operation of the fluid to one of the chamber for use or the chamber for retard angle.

[Brief description of the drawings]

FIG. 1 is a vertical sectional side view showing a first embodiment of a valve timing control apparatus according to the present invention.

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

FIG. 3 is a sectional view taken along line 3-3 in FIG. 2;

FIG. 4 is a view showing a state in which a lock pin is retracted into an evacuation hole.
FIG. 3 is a sectional view taken along line 3-3 of FIG.

FIG. 5 is a perspective view of the cap of FIG. 1;

FIG. 6 is a side view of the cap of FIG. 1;

FIG. 7 is a vertical sectional side view showing a second embodiment of the valve timing control apparatus according to the present invention.

FIG. 8 is a perspective view showing a modification of the cap.

FIG. 9 is a side view of the cap of FIG. 8;

[Explanation of symbols]

 Reference Signs List 10 camshaft 11 advance passage (first fluid passage) 12 retard passage (second fluid passage, shaft hole) 20 internal rotor (rotating member) 22 receiving hole 23 passage 24 passage (first fluid passage) 25 passage (first) 2 fluid passage) 26 communication groove (passage means) 30 external rotor (rotation transmission member) 32 recess 33 evacuation hole 40 front plate (rotation transmission member) 41 cylindrical portion 50 rear plate (rotation transmission member) 60 timing pulley (rotation transmission) 61) Crankshaft 70 Vane 80 Torsion coil spring 90 Lock pin 100 Control valve 110 Cylinder head C1 Annular gap (passage means) C2 Gap (passage means) R0 Fluid pressure chamber R1 Delay chamber R2 Advance chamber

Claims (4)

[Claims] 1. A rotating member that rotates with one of a crankshaft and a camshaft of an internal combustion engine, and a rotation transmitting member that is attached to the rotating member so as to be relatively rotatable within a predetermined range and rotates with the other of the crankshaft and the camshaft. And a vane provided on one of the rotating member or the rotation transmitting member, and a vane formed between the rotating member and the rotation transmitting member and divided into an advance chamber and a retard chamber by the vane. A fluid pressure chamber, a first fluid passage for supplying and discharging fluid to the advance chamber, and a second fluid passage for supplying and discharging fluid to the retard chamber, wherein the advance chamber and the retard The rotating member and the rotation transmitting member are relatively rotated by the fluid pressure applied to the working chamber, and the rotational phase of the camshaft with respect to the rotational phase of the crankshaft is changed, whereby the rotational phase is changed. In a valve opening / closing timing control device that changes and controls the opening / closing timing of a valve driven by a camshaft,
In the cylindrical portion formed to extend in the axial direction of the rotation transmitting member, one end of the rotary member is locked to the rotating member and the other end is locked to the end of the cylindrical portion to lock the rotating member. A shaft provided with a torsion coil spring that constantly urges the rotation transmitting member in the advance angle direction, wherein one of the first fluid passage and the second fluid passage is formed in the rotating member and opens into the cylindrical portion; A hole, a communication passage formed between the rotation transmitting member and the rotation member, the communication passage opening to one of the advance chamber or the retard chamber, and passage means for communicating the communication passage with the shaft hole. And a valve timing control device. 2. The communication device according to claim 1, wherein the passage means includes a communication groove provided to communicate with the rotating member radially inward and outward of the end turn portion on one end side of the torsion coil spring. 2. The valve timing control apparatus according to claim 1. 3. The passage means comprises a gap provided between adjacent winding portions of the torsion coil spring, and an annular gap provided between the inner periphery of the cylindrical portion and the torsion coil spring. The valve timing control device according to claim 1, wherein 4. A lid member is fixed to the tip of the cylindrical portion in a liquid-tight manner, and a support portion extending in the axial direction inside the cylindrical portion and radially supporting the torsion coil spring is provided on the lid member. The valve opening / closing timing control device according to claim 1, wherein the valve opening / closing timing control device is provided.