JP2000045724A - Valve operation timing controller - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve operation timing controller which can enlarge the variable control domain of valve operation timing by certainly preventing the occurrence of hammering sound of a vane and defective start at the time of starting an internal combustion engine. SOLUTION: This valve operation timing controller is provided with a relative rotation holding mechanism (a lock pin, etc.), by which, in a middle relative phase between a relative phase of a rotation member (an inner rotor 20) and rotation transmitting member (an outer rotor 30) in the maximum spark advance state where the volume of a lag angle chamber is minimized by a vane 80 and a relative phase of the rotation member and the rotation transmitting member in the maximum lag angle state where the volume of a spark advance chamber is minimized by the vane 80, the relative phase between the rotation member and the rotation transmitting member is held in a specified middle relative phase during the valve operation timing when an internal combustion engine can start, and a relative rotation restricting mechanism (a restriction member 40, a torsion coil spring 90 etc.) which restricts spring-loadedly the relative rotation of the rotation member toward a lag angle side to the rotation transmitting member when a hydraulic pressure in the lag angle chamber is lower than a prescribed value in a prescribed relative phase.

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 apparatus used for controlling the timing of opening and closing an intake / exhaust valve in a valve train of an internal combustion engine.

[0002]

2. Description of the Related Art As one type of this type of valve train, a rotary member which rotates with a camshaft is provided so as to be relatively rotatable within a predetermined range, and rotational transmission from a crank sprocket or a pulley of a crankshaft is transmitted. A member, a plurality of vanes provided on the rotating member, and an advancing chamber and a retarding chamber respectively formed by the vanes formed between the protrusion provided on the rotation transmitting member and the rotating member. A plurality of fluid pressure chambers divided into two, a first fluid passage for supplying and discharging fluid to the advance chamber, a second fluid passage for supplying and discharging fluid to the retard chamber, the rotating member and the rotation transmission Some include a phase holding mechanism that holds the relative phase of the rotation member and the rotation transmission member when the relative phase of the member is a predetermined phase,
For example, JP-A-1-92504 and JP-A-9-25
No. 0310.

In the valve gears of internal combustion engines disclosed in the above publications, a working fluid is supplied to an advance chamber through a first fluid passage, and a retard chamber is supplied through a second fluid passage. By discharging the hydraulic oil from the rotating member, the rotating member rotates in the advancing direction to an arbitrary position up to the most advanced position where the vane abuts the circumferential end surface on the advancing side of the protrusion with respect to the rotation transmitting member. The valve opening / closing timing is advanced, and the working fluid is supplied to the retarding chamber through the second fluid passage and the working oil is discharged from the advance chamber through the first fluid passage, whereby the rotating shaft rotates. The vane rotates in the retard direction to an arbitrary position up to the most retarded position where the vane abuts on the circumferential end surface on the retard side of the projection with respect to the transmission member, and the valve opening / closing timing is retarded.

In the valve gears disclosed in the above publications, 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 fluctuation torque is applied to the camshaft. Therefore, during operation of the internal combustion engine, a force in the retard direction always acts on the rotating member, and when the supply of the hydraulic oil to the fluid pressure chamber is stopped when the internal combustion engine is stopped, The vane cannot be held by the hydraulic pressure of the fluid pressure chamber, and the rotating member rotates in the retard direction with respect to the rotation transmitting member (until the crankshaft is completely stopped). It stops at the relative phase according to the relative phase of both. When the internal combustion engine is started in this state, the rotating member rotates in the retard direction with respect to the rotation transmitting member due to the above-described force in the retard direction, and the vane is moved to the circumferential end surface on the retard side of the protrusion. The phase at the most retarded position where it comes into contact is in an unstable state until the oil pressure in the fluid pressure chamber rises and the vane can be held by the oil pressure, and the vane is caused by the fluctuating torque acting on the camshaft. Vibrates, and repeatedly hits the circumferential end surface of the projection to produce a tapping sound. To avoid this, the phase holding mechanism sets the relative phase between the rotating member and the rotation transmitting member to the most retarded position. Is to be held.

[0005]

By the way, in the high-speed rotation range of the internal combustion engine, even if the piston starts to move toward the top dead center,
It is known that, since the intake air tends to enter the cylinder further by inertia, the volume efficiency is improved by delaying the closing timing of the intake valve, so that the output of the internal combustion engine can be improved.

However, when the valve train disclosed in each of the above publications is used to control the opening / closing timing of the intake valve, the valve opening / closing timing at the most retarded position is determined as described above. Since it is necessary to set the intake timing at the start, the closing timing of the intake valve cannot be delayed in the high-speed rotation range to improve the volumetric efficiency due to the inertia of the intake. This is because if the valve opening / closing timing at the most retarded position is set to a time at which the volume efficiency can be improved by the inertia of the intake air, the piston passes through the bottom dead center when the internal combustion engine is started at the most retarded position, and the upper dead point. Even if it starts to move to the point, the intake valve is open and there is no inertia in the intake air, so the intake air once sucked flows back and is exhausted, and the compression ratio does not increase, and a state where combustion is not possible occurs. Is difficult to start.
Incidentally, this problem can be solved even if the valve opening / closing timing at the most retarded position is not set to a timing at which the volumetric efficiency can be improved by the inertia of the intake air, as in the valve operating devices disclosed in the above publications. Even if the valve opening / closing timing at the most retarded position is set to a timing at which intake is possible at the time of startup, if the intake valve closing timing is set after the bottom dead center of the piston, high altitudes where the air pressure is low, etc. Then it is easy to occur.

In the case where the valve trains disclosed in the above publications are used to control the opening / closing timing of the exhaust valve, if the closing timing of the exhaust valve is similarly delayed, the over-opening of the intake valve and the exhaust valve may occur. The lap period becomes longer, the internal EGR amount (exhaust gas recirculation amount) increases, and the startability of the internal combustion engine is reduced.

In order to solve these problems, the relative phase between the rotating member and the rotation transmitting member is advanced by a predetermined angle from the most retarded position corresponding to the valve opening / closing timing capable of improving the volume efficiency due to the inertia of the intake air. Japanese Patent Application Laid-Open No. Hei 9-324613 proposes a valve train that is held at an intermediate position by a phase holding mechanism. However, in this device, when the rotation member rotates in the retard direction with respect to the rotation transmission member as described above when the internal combustion engine is stopped, the relative phase between the rotation member and the rotation transmission member becomes a predetermined intermediate position. Is momentary, the phase holding mechanism may not be able to hold the relative phase between the rotating member and the rotation transmitting member at a predetermined intermediate position. It is not possible to reliably prevent the generation of a tapping sound due to a collision with the projection of the member.

Therefore, the present invention is to provide a valve train capable of enlarging a variable control range thereof while reliably preventing generation of a tapping sound and poor starting by a vane at the time of starting the internal combustion engine. , The subject.

[0010]

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 which is provided so as to be relatively rotatable and rotates together with the other of the crankshaft or the camshaft, a vane provided on the rotation member, and the vane formed between the rotation member and the rotation transmission member. A fluid pressure chamber divided into an advance chamber and a retard chamber, and the relative phase between the rotation member and the rotation transmission member is maintained when the relative phase between the rotation member and the rotation transmission member is a predetermined phase. A phase control mechanism having a phase holding mechanism that performs rotation of the rotation member and the rotation transmission member by fluid pressure applied to the advance chamber and the retard chamber. In a valve opening / closing timing control device that changes an opening / closing timing of a valve driven by the camshaft by changing a rotation phase of the camshaft with respect to a rotation phase of the crankshaft, the vane adjusts the volume of the retard chamber. The rotation member and the rotation transmission member in the maximum retarded state where the volume of the advance chamber is minimized by the relative phase of the rotation member and the rotation transmission member in the maximum advance state in which is minimized and the vane. And the rotation transmitting member and the rotation transmitting member by the phase holding mechanism at a predetermined intermediate relative phase when the internal combustion engine is at a valve opening / closing timing at which the internal combustion engine can be started. And when the fluid pressure in the retard chamber is lower than a predetermined value at the predetermined relative phase, Relative rotation to the retarded angle side relative to the rotation transmitting member of the member is the provision of the relative rotation limiting mechanism for Tamabachi limiting.

According to the above means, when the supply of the working fluid to the fluid pressure chamber is stopped when the internal combustion engine is stopped, the vane cannot be held by the fluid pressure in the fluid pressure chamber, and the rotating member is connected to the rotation transmitting member. Although it rotates in the retard direction,
A relative phase intermediate between the relative phase of the rotation shaft and the rotation transmitting member in the maximum advance state and the relative phase in the maximum retardation state, and a predetermined relative phase corresponding to the valve opening / closing timing at the start of the internal combustion engine. When an intermediate relative phase is reached, the relative rotation of the rotating member to the retard side with respect to the rotation transmitting member is resiliently limited by the relative rotation limiting mechanism, and the relative phase between the rotating member and the rotation transmitting member is intermediate by the phase holding mechanism. Relative phase. Accordingly, it is possible to prevent the vane from colliding with the circumferential end face of the fluid pressure chamber at the start of the internal combustion engine, thereby preventing the occurrence of a tapping sound.

Further, since the valve opening / closing timing at the start of the internal combustion engine is obtained at the intermediate relative phase, the valve opening / closing timing at the most retarded position can be further delayed than at the intermediate relative phase. It is possible to improve the volumetric efficiency by utilizing the inertia of the intake air, to advance the valve opening / closing timing at the time of starting, and to prevent the starting failure of the internal combustion engine due to a decrease in the compression ratio. Becomes

In the above means, the relative rotation restricting mechanism is provided with a restricting member provided on the rotation transmitting member so as to be relatively rotatable by a predetermined angle, and the restricting member is urged toward the advance side with respect to the rotation transmitting member. The restricting member resiliently contacts the vane in the fluid pressure chamber when the rotating member and the rotation transmitting member relatively rotate from the predetermined relative phase to the retard side. You may comprise so that it may have a regulation part. Alternatively, the relative rotation restricting mechanism includes a first restricting member provided so as to be integrally rotatable with the rotation transmitting member, a second restricting member provided to the first restricting member so as to be relatively rotatable by a predetermined angle, An urging means for resiliently connecting the second restricting member and the rotating member so as to be relatively rotatable and urging the second restricting member toward the retard side with respect to the rotating member; And a regulating means for regulating the movement of the second restricting member to the retard side when the rotation transmitting member is in the predetermined relative phase.

[0014]

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.

FIG. 1 to FIG. 5 show a first embodiment of the present invention. 1 to 5, a valve timing control device is provided with a camshaft 10 rotatably supported by a cylinder head 110 of an internal combustion engine. And a rotation transmitting member including an outer rotor 30, a front plate 50, a rear plate 60, and a timing sprocket 70, which are externally rotatable relative to the camshaft 10 and the inner rotor 20 within a predetermined range. The attached four vanes 80 and the lock pins 9 assembled to the external rotor 30
1 and the internal rotor 2 between the internal rotor 20 and the external rotor 30 and the front plate 50.
It is constituted by a relative rotation restricting mechanism or the like including a restricting member 40 and the like interposed rotatably within a predetermined range with respect to the front plate 50 and the front plate 50, respectively. As is well known, the timing sprocket 70 is configured to transmit rotational power clockwise in FIGS. 2 and 3 from a crankshaft (not shown) via a crank sprocket and a timing chain.

The camshaft 10 has a well-known cam (not shown) for opening and closing the intake valve, and includes therein an advance passage 11 and a retard passage 12 extending in the axial direction of the camshaft 10.
Is provided. The advance passage 11 is connected to the camshaft 10.
And formed in a mounting hole for a mounting bolt 82 provided in the camshaft 10 and through a radial passage provided in the camshaft 10 and a connection passage 72 provided in the annular groove 14 and the cylinder head 70 to the connection port 101 of the control valve 100. It is connected.
The retard passage 12 is connected to a connection port 102 of the control valve 100 via a radial passage provided in the camshaft 10, an annular groove 13 and a connection passage 71 provided in the cylinder head 70.

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 connection port 102 and the connection port 101 communicates with the discharge port 107. Supply port 106 is connected to connection port 1
01, and the connection port 102 is configured to communicate with the discharge port 107. For this reason, when the solenoid 103 of the control valve 100 is not energized, the hydraulic oil is supplied to the retard passage 12, and when the solenoid 103 is energized, the hydraulic oil is supplied to the advance passage 11.
The power supply to the motor is duty-controlled by a control device (not shown).

The switching valve 120 is interposed in a branch passage 73 branched from the connection passage 71 and connected to the drain.
When the solenoid 122 is energized, the spool 121 movably fitted in the housing in the axial direction can be moved downward in FIG. 1 against the spring 123. The connection with the drain through the drain 73 is cut off, and the connection passage 71 is connected to the drain through the branch passage 73 when electricity is supplied. The energization of the solenoid 122 is on / off controlled by a control device (not shown).

The inner rotor 20 has a single mounting bolt 82
And is integrally fixed to the camshaft 10 by
Each of the four vanes 80 has a vane groove 20a for movably attaching the vane 80 in a radial direction, and a relative phase between the camshaft 10 and the inner rotor 20 and the outer rotor 30 is a predetermined phase (neutral position of the vane) to be described later. When the phase is synchronized, the head of the lock pin 91 of the phase holding mechanism is advanced into the receiving hole 29 into which a predetermined amount is fitted and the advance chamber R1 (except for the upper left one in FIG. 2) defined by each vane 80. A passage 24 communicating the advance passage 11 and each advance chamber R1 so as to supply and discharge the hydraulic oil from the passage 11, and a retard passage 12 formed on one end surface of the cam shaft 10 on the side facing the tip end surface of the camshaft 10. An annular groove 21 communicating therewith, four passages 22 extending axially from the annular groove 21 to the other end face side, and hydraulic oil from the retard passage 12 into the retard chamber R2 defined by each vane 80 from the retard passage 12. And passage Each passage 2 to feed and discharge through 2
2, a passage 25 communicating with the retard chamber R2, a passage 25 having one end communicating with the advance passage 11 and having the other end opening on the outer peripheral surface of the internal rotor 20, and an opening at the other end of the passage 25 extending in the axial direction. The axial groove 26 formed in the outer peripheral surface of the internal rotor 20 in the axial direction so as to penetrate the inner rotor 20, and the axial groove 26 and the upper left advance chamber R1 are formed by a passage formed in the external rotor 30 described later. The circumferential phase of the circumferential groove 27 formed on the outer peripheral edge of the end face of the inner rotor 20 on the rear plate 60 side, and the relative phases of the camshaft 10 and the inner rotor 20 and the outer rotor 30 will be described later. When synchronized with a predetermined phase (neutral position of the vane), the axial groove 26 has a communication hole 28 that communicates with the receiving hole 29 via an axial groove 33 formed in the external rotor 30 described later. I have. The receiving hole 29 is formed on the outer periphery of the inner rotor 20 in the radial direction. Further, each vane 80 is urged radially outward by a vane spring 81 housed in the bottom of the vane groove 20a.

The outer rotor 30 is mounted on the outer periphery of the inner rotor 20 so as to be relatively rotatable within a predetermined range, and a rear plate 60 is integrally connected to the rear side by five connecting bolts 84. . A cylindrical timing sprocket 70 having a shaft length longer than the shaft length of the external rotor 30 is fitted on the outer periphery of the external rotor 30. On both sides of the timing sprocket 70, the front plate 5
The outer rotor 30, the front plate 50, the rear plate 60, and the timing sprocket 70 are integrally and firmly connected by five connecting bolts 83 in this state. External rotor 3
Between the zero and the front plate 50, a limiting member 40 described later is interposed so as to be rotatable relative to the external rotor 30 by a predetermined angle. In addition, four protrusions 31 are formed on the inner periphery of the outer rotor 30 at predetermined intervals in the circumferential direction so as to protrude radially inward, and the inner peripheral surfaces of these protrusions 31 The outer rotor 30 is rotatably supported by the inner rotor 20 so as to be in sliding contact with the outer peripheral surface. In one protruding portion 31, a retreat hole 34 for accommodating a lock pin 91 and a spring 92 is formed in the radial direction of the external rotor 30, and the above-described passage 32 and the axial groove 33 are formed in the inner peripheral surface. ing.

Each of the vanes 80 has an arc-shaped cross section at the tip, and is mounted between the rear plate 60 and the restricting member 40 in the vane groove 20a of the internal rotor 20 so as to be movable in the radial direction. Rotor 30 and external rotor 3
0, each of the protrusions 31, the inner rotor 20,
And a fluid pressure chamber R0 formed between the
Is divided into an advancing chamber R1 and a retarding chamber R2, and the vane 80 abuts one circumferential end face of the protrusion 31 formed on the external rotor 30. The phase (relative rotation amount) to be adjusted is limited.

The lock pin 91 is slidably mounted in the evacuation hole 34 in the axial direction, and is urged by the spring 92 toward the internal rotor 20. The spring 92 is interposed between the lock pin 91 and the retainer 93, and the retainer 93 is fixed in the evacuation hole 34 so as not to come off.

The restricting member 40 is interposed between the external rotor 30 and the front plate 50 so as to be rotatable relative to the external rotor 30 by a predetermined angle, and slidably contacts the front plate 50 on one side surface on the front side. At the same time, the other side surface on the rear side is in sliding contact with the front end surface of the internal rotor 20 and the front end surface of the external rotor 30. As shown in FIG. 3, on the other side surface on the rear side of the limiting member 40, protrusions 41 having the same shape as the protrusions 31 are formed at the same predetermined circumferential intervals as the protrusions 31 of the external rotor 30. Is formed with a concave groove 40a. The inner peripheral surface of each projection 41 is in sliding contact with the outer peripheral surface of the internal rotor 20, and each concave groove 40a does not penetrate in the axial direction and opens only to the rear side. It constitutes a part of the chamber R0. At the portion of the restriction member 40 where the protrusion 41 is formed, five long holes 42 through which the connecting bolt 83 penetrates are formed, and as shown in FIG. 5, one protrusion 41 is formed. One end of a stopper pin 94 is press-fitted and fixed in the shaft hole 43 provided in the portion.

The restricting member 40 includes a front plate 50
The other end 90b of the torsion coil spring 90, which is disposed in an annular hole formed in the cylindrical portion and has one end 90a locked at the bottom of the annular hole, is locked. The coil spring 90 constantly urges the external rotor 30 to the advanced angle side (clockwise in FIG. 3). Further, the other end of the stopper pin 94 is fitted into a circumferential groove 35 formed in the protrusion 31 of the external rotor 30 as shown in FIG. The rotation angle relative to the external rotor 30 is limited to a predetermined angle α.

In the first embodiment, FIGS. 2 and 3
As described above, as described above, the relative phases of the camshaft 10 and the inner rotor 20 and the outer rotor 30 are determined when the respective vanes 80 are at the neutral positions in the respective fluid pressure chambers R0 (each of the vanes is At an intermediate phase in a position where it does not come into contact with the advance-side circumferential end surface and the retard-side circumferential end surface), and is urged in the advance direction by a predetermined angle α with respect to the external rotor 30. Of the limiting member 40 in the twisted position
When one of the vanes 80 (the upper vane in FIGS. 2 and 3) is in a predetermined relative phase in contact with the circumferential end face on the advanced side of the retracting hole 34 and the receiving hole 29, the lock pin is locked. The head of 91 can be fitted into the receiving hole 29. When the predetermined relative phase is attained, the opening / closing timing of an intake valve (not shown) is adjusted to a timing at which the internal combustion engine can be started (opening / closing timing of the intake valve is slightly advanced (intermediate advance) (from the maximum retarded position). The timing is set so as to be advanced by a predetermined angle α)).

In the valve timing control apparatus of the first embodiment configured as described above, the internal combustion engine is started and a predetermined hydraulic pressure is supplied to each advance chamber R1 and each retard chamber R2. Hydraulic oil at an intermediate pressure (in FIG. 2, higher than a set oil pressure (oil pressure lower than the predetermined oil pressure) described above) is supplied to the receiving hole 29, and the head of the lock pin 91 is retracted to the evacuation hole 34, and the external rotor 30 (A state where relative rotation of the internal rotor 20 is allowed) and each advance chamber R1
The pressing force due to the advance hydraulic pressure in the inner rotor 2 is different from the pressing force due to the retard hydraulic pressure in each of the retard chambers R2.
Since the fluid pressure chamber R0 and the vane 80 are interposed in the rotation transmission path to the inner rotor 20 and the camshaft 1
0), the duty ratio of the current supplied to the solenoid 103 of the control valve 100 is increased according to the operating state of the internal combustion engine. As a result, hydraulic oil is supplied to the advance chamber R1 through the advance passage 11 and the passages 24, 25, etc., and the passages 23, 22 from the retard chamber R2.
When the hydraulic oil is discharged through the retard passage 12 and the control valve 100, the internal rotor 20 and each vane 80 are advanced with respect to the external rotor 30, the plates 50 and 60, the restricting member 40, and the like (FIG. 2). ), And the relative rotation amount (maximum advance amount) is limited by the contact of one vane (the lower left vane in FIG. 3) 80 with the retard side end surface of the projection 31. . Also, by lowering the duty ratio of the current supplied to the solenoid 103 of the control valve 100,
Each of the retard chambers R through the retard passage 12 and the passages 22 and 23
When the hydraulic oil is supplied to each of the advance chambers R1 and the hydraulic oil is discharged from each advance chamber R1 through each of the passages 24 and 25, the advance passage 11, the control valve 100, and the like, the internal rotor 20 and each of the vanes 8
0 rotates relative to the external rotor 30, both plates 50 and 60, the limiting member 40, and the like on the retard side (counterclockwise in FIG. 2), and the external rotor 3 is integrated with the limiting member 40.
0, relative to the two plates 50, 60, etc., by a predetermined angle α toward the retard side against the urging force of the torsion coil spring 90. As shown in FIG. 3, the relative rotation amount (maximum retard amount) is limited by one vane 80 (upper left vane in the drawing) abutting on the advance side end surface of the projection 31. During this phase conversion control, the lock pin 91 moves against the spring 92, and the head of the lock pin 91 retreats from the receiving hole 29 to the retreat hole 34, and the lock pin 9 moves.
1 has been unlocked. Further, during the above-described phase conversion control, the switching valve 120 is in a non-energized state, and cuts off communication between the connection passage 71 and the drain.

In the first embodiment, as described above, the relative phase of the inner rotor 20 and the outer rotor 30 is such that each vane 80 is in the neutral position between the protrusions 31 in each fluid pressure chamber R0 (see FIG. 2). 1), and the vane 80 is attached to the circumferential end surface on the advance side of the protrusion 41 of the restricting member 40 which is urged in the advance direction by a predetermined angle α with respect to the external rotor 30 and twisted. 2 (the upper vanes in FIGS. 2 and 3) are in contact with each other.
When 9 is in the synchronous predetermined phase, the opening / closing timing of the intake valve (not shown) is set to a timing at which the internal combustion engine can be started. Therefore, the valve opening / closing timing can be further delayed than the valve opening / closing timing at which the internal combustion engine can be started from the neutral position to the most retarded position where the vane 80 abuts on the advanced side circumferential end face of the projection 31. When the internal combustion engine is rotating at high speed, the control valve 100 is controlled as described above to change the phase from the neutral position to the retard side, and the closing timing of the intake valve (not shown) is delayed until the start of the internal combustion engine is difficult. The volume efficiency is improved by the inertia of the intake air, and the output of the internal combustion engine can be improved.

When the internal combustion engine is stopped, the operation of the oil pump P is stopped, the supply of the hydraulic oil to the fluid pressure chamber R0 is stopped, and the control valve 100 is turned off. As a result, the pressing force of the advance hydraulic pressure in the advance chamber R1 and the pressing force of the retard hydraulic pressure in the retard chamber R2 do not act on the vane 80, and the internal rotor 20 and the cam shaft 10 Only the force in the retard direction (until the crankshaft of the internal combustion engine completely stops) acts, and the internal rotor 20 at the time of stoppage is stopped according to the relative phase between the internal rotor 20 and the external rotor 30 immediately before the stop. And the relative phase of the external rotor 30 is determined. At this time, the internal rotor 2 immediately before the stop
When the relative phase between 0 and the external rotor 30 is more advanced than a predetermined phase in which the retreat hole 33 and the receiving hole 29 are synchronized,
The internal rotor 20 and the camshaft 10 are moved to the retard side with respect to the external rotor 30 by the above-mentioned retarding force acting on the internal rotor 20 and the camshaft 10.
One vane 80 (the upper left vane in FIGS. 2 and 3) is urged in the advance direction by a predetermined angle α with respect to the external rotor 30, and the protrusion 41 of the restricting member 40 at the twisted position is advanced. Abuts on the circumferential end face of the first member, the movement toward the retard side from the predetermined intermediate phase is resiliently restricted. As a result, 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
Are held (locked).

In the first embodiment, when a starter switch (not shown) is turned on when the internal combustion engine is started, the switching valve 1 is turned on for a predetermined time after the starter switch is turned on.
When the solenoid 122 is energized, the connection passage 71 communicating with the retard passage 12 is connected to the drain. As a result, when the internal combustion engine is started, the control valve 100 is in the non-energized state, so that the advance chamber R1 and the retard chamber R2 are both connected to the drain. For this reason, at the time of starting the internal combustion engine, the camshaft 10, the internal rotor 20, and the vane 80 are likely to largely flutter toward the retard side and the advance side with respect to the external rotor 30 due to the cam fluctuating torque acting on the camshaft 10 (vibrating. However, as described above, the relative phase between the internal rotor 20 and the external rotor 30 immediately before the stop of the internal combustion engine is the predetermined phase in which the evacuation hole 34 and the receiving hole 29 are synchronized, or the evacuation hole 34 and the receiving hole 29 are synchronized. When the phase is on the advance side of the predetermined phase, the head of the lock pin 91 is fitted into the receiving hole 29, so that the camshaft 10, the internal rotor 20, and the vane 80 are prevented from fluttering.

When the relative phase between the internal rotor 20 and the external rotor 30 immediately before the stop of the internal combustion engine is on the retard side with respect to the predetermined phase at which the retreat hole 34 and the receiving hole 29 are synchronized, or the relative phase in the maximum retard state When the phase is in the phase, the internal combustion engine may be stopped in a state where the head of the lock pin 91 is not fitted into the receiving hole 29. When the internal combustion engine is started in this state, the internal rotor 20 and the camshaft 10 are moved to the retard side with respect to the external rotor 30 by the above-mentioned force in the retard direction, and the internal combustion engine is in the maximum retard state. Starting is difficult. At this time, since the urging force of the torsion coil spring 90 for urging the restriction member 40 is small, the camshaft 10 and the internal rotor 20 are
Cannot be advanced by α from the maximum retard position. In the first embodiment, as described above, when the internal combustion engine is started, the advance chamber R1 and the retard chamber R2
Are both connected to the drain, so that the camshaft 10
When the camshaft 10, the internal rotor 20, and the vane 60 largely flutter (vibrate) toward the retard side and the advance side with respect to the external rotor 30 due to the cam fluctuating torque acting on the torsion coil, The restricting member 40 is rotated by a predetermined angle α toward the advance side with respect to the external rotor 30 by the spring 90. Thereby, when the inner rotor 20 and the camshaft 10 move to the retard side with respect to the outer rotor 30, one vane 80 (upper left vane in FIGS. 2 and 3) advances the protrusion 41 of the restriction member 40. By contacting the circumferential end face on the corner side, the movement to the retard side from the predetermined intermediate phase is resiliently restricted, and the spring is moved at the predetermined phase in which the retreat hole 34 and the receiving hole 29 are synchronized. The head of the lock pin 91 fits into the receiving hole 29 by 92, and the relative phase between the inner rotor 20 and the outer rotor 30 is maintained (locked).
Is done.

Therefore, when the internal combustion engine is started, a rotating member including the camshaft 10, the internal rotor 20, the respective vanes 80, etc., accompanied by a large rotational fluctuation, and a rotational transmission including the external rotor 30, the front plate 50, the rear plate 60, etc. Unnecessary relative rotation of the member is surely regulated by the phase holding mechanism, and it is possible to reliably prevent the vane 80 from hitting due to unnecessary relative rotation of the rotating member and the rotation transmitting member.

As described above, according to the first embodiment,
It is possible to improve the volumetric efficiency in a high-speed rotation range of the internal combustion engine while preventing the generation of a tapping sound due to the collision between the vane 80 and the circumferential end surface of the projection 31 at the time of starting the internal combustion engine and the start failure of the internal combustion engine. it can. Further, in the first embodiment, since the relative rotation limiting mechanism including the limiting member 40 and the like is provided in the fluid pressure chamber R0, the size of the valve timing control device can be reduced.

FIGS. 6 to 9 show a second embodiment of the present invention. 6 to 9, the valve timing control device includes a camshaft 10 rotatably supported by a cylinder head 110 of an internal combustion engine. Rotating member, an outer rotor 230 and an intermediate plate 27 which are externally rotatable relative to the camshaft 10 and the inner rotor 220 within a predetermined range.
0, a rotation transmitting member composed of a timing sprocket 230a integrally provided on the outer periphery of the rear plate 260 and the external rotor 230, four vanes 280 mounted on the internal rotor 220, and a lock pin mounted on the external rotor 230 292 etc., and a first limiting member 240 provided to rotate integrally with the rotation transmitting member.
And a relative rotation limiting mechanism including a second limiting member 250 and the like that is rotatably assembled within a predetermined range with respect to the first limiting member 240. As is well known, the timing sprocket 230a is configured to transmit rotational power clockwise in FIGS. 7 to 9 from a crankshaft (not shown) via a crank sprocket and a timing chain.

The camshaft 10 has a well-known cam (not shown) for opening and closing the intake valve, and includes therein an advance passage 11 and a retard passage 12 extending in the axial direction of the camshaft 10.
Is provided. The advance passage 11 is provided with the camshaft 10.
Is formed in a mounting hole for a mounting bolt 282 provided in the control valve 100 through a radial passage provided in the camshaft 10 and a connection passage 72 provided in the annular groove 14 and the cylinder head 70. It is connected.
The retard passage 12 is connected to a connection port 102 of the control valve 100 via a radial passage provided in the camshaft 10, an annular groove 13 and a connection passage 71 provided in the cylinder head 70.

As shown in FIG. 6, the control valve 100 and the switching valve 120 have the same configuration and the same operation as those of the above-described first embodiment. The description is omitted by assigning the same reference numerals.

The inner rotor 220 has a single mounting bolt 2
82, is integrally fixed to the camshaft 10 via the sensor plate 290, and the four vanes 2
Each of the camshafts 80 has a vane groove for movably mounting in the radial direction, and as shown in FIG.
A receiving hole 229 into which the head of the lock pin 292 of the phase holding mechanism is inserted by a predetermined amount when the relative phases of the internal rotor 220 and the external rotor 230 are synchronized with a predetermined phase (neutral position of the vane) described later; The advancing passage 11 is supplied to the advancing chamber R1 (excluding the upper chamber in FIG. 7) partitioned by the vane 280 so that hydraulic oil is supplied and discharged from the advancing passage 11.
A passage 224 that communicates with the advance chamber R1; an annular groove 221 that is formed on one end surface of the cam shaft 10 on the side facing the distal end surface and communicates with the retard passage 12; Four passages 222 extending to the other end face side, and a retard passage 1 in a retard chamber R2 defined by each vane 280.
2, a passage 223 communicating the passages 222 and the retard chambers R <b> 2 so as to supply and discharge the hydraulic oil through the annular groove 221 and the passages 222, and one end is communicated with the advance passage 11 and the other end of the internal rotor 220. A passage 225 opening in the outer peripheral surface, and an axial groove 226 formed in the outer peripheral surface of the internal rotor 20 in the axial direction so as to penetrate the other end opening of the passage 225 in the axial direction.
And the outside of the end face of the internal rotor 220 on the rear plate 260 side so that the axial groove 226 and the advance chamber R1 shown in the figure are always communicated (via a passage 232 formed in the external rotor 230 described later). Circumferential groove 2 formed in peripheral edge
When the relative phases of the camshaft 10 and the internal rotor 220 and the external rotor 230 synchronize with each other at a predetermined phase (neutral position of the vane) described later, the axial groove 226 is formed in the axial direction formed on the external rotor 230 described later. A circumferential groove 227b formed on the outer peripheral edge of the end face on the rear plate 260 side of the inner rotor 220 so as to communicate with the groove 233 communicates with the axial groove 233 of the outer rotor 230 and the receiving hole 229 at a predetermined phase. And a communication hole 228. still,
The receiving hole 229 is formed in the outer periphery of the internal rotor 220 in the radial direction. Further, each vane 280 is urged radially outward by a vane spring 281 housed in the bottom of the vane groove.

The outer rotor 230 is mounted on the outer periphery of the inner rotor 220 so as to be relatively rotatable within a predetermined range, and an intermediate plate 270 and a rear plate 260 are joined to both sides thereof. First limiting member 240 and front plate 245 to be joined
And are firmly connected integrally by five connecting bolts 283. As shown in FIG.
Are formed on the inner periphery of each of them at predetermined intervals in the circumferential direction so as to protrude radially inward.
The outer rotor 230 is rotatably supported by the inner rotor 220 so that the inner peripheral surface of the inner rotor 31 slides on the outer circumferential surface of the inner rotor 220. One protrusion 231 has a lock pin 2
A retreat hole 234 for accommodating the spring 92 and the spring 293 is formed in the radial direction of the outer rotor 230, and the above-described passage 232 and the axial groove 233 are formed on the inner peripheral surface.

Each vane 280 has an arc-shaped cross section at the tip, and has a rear plate 260 and an intermediate plate 270.
The outer rotor 230, each protrusion 231 of the outer rotor 230, the inner rotor 220,
The fluid pressure chamber R0 formed between the intermediate plate 270 and the rear plate 260 is divided into an advance chamber R1 and a retard chamber R2.
The phase (relative rotation amount) adjusted by the valve opening / closing timing control device is limited by the abutment of the vanes 280 on each of the one circumferential end surfaces (see FIG. 7).

The lock pin 292 is slidably mounted in the evacuation hole 234 in the axial direction.
3 urged toward the inner rotor 220.
The spring 293 includes a lock pin 291 and a retainer 294.
The retainer 294 is interposed therebetween and is fitted into an axial hole formed in the external rotor 230 so as to penetrate the evacuation hole 234 at right angles, and is fixed in the evacuation hole 234 so as not to come off. .

On the inner periphery of the first restricting member 240 integrally connected to the outer rotor 230, the intermediate plate 270 and the like,
As shown in FIG. 8, five protrusions 241 are formed at regular intervals so as to protrude radially inward. Internal rotor 22
A second restricting member 250 is rotatably supported on the outer periphery of the cylindrical portion of the sensor plate 290 integrally connected to the first restricting member 240, and the inner peripheral surface of the protrusion 241 of the first restricting member 240 conforms to the second restricting member. The first limiting member 240 is rotatably supported by the second limiting member 250 in a configuration in which the first limiting member 240 is in sliding contact with the outer peripheral surface of the member 250. In addition, one concave portion 2 that extends radially outward on the outer periphery of the second restriction member 250 and that is formed between adjacent protrusions 241.
A restricting portion 251 protruding into the groove 54 is formed, and the relative rotation between the first restricting member 240 and the second restricting member 250 is restricted by the restricting portion 251 abutting on the adjacent protruding portion 241. ing.

The inner rotor 2 of the second restricting member 250
As shown in FIGS. 6 and 8, an annular hole 252 is formed in the surface facing the inner rotor 20. As shown in FIGS. Similarly, an annular hole 220a is formed. A torsion coil spring 291 is provided in each of the annular holes 252 and 220a.
1b are locked to the bottoms of the annular holes 252 and 220a, respectively.
(The second restricting member 250 is on the retard side with respect to the internal rotor 220, and the internal rotor 220 is on the advance side with respect to the second restricting member 250). And is resiliently connected via a torsion coil spring 291.

As shown in FIGS. 6 and 8, the annular hole 2 in the surface of the second restricting member 250 facing the internal rotor 220 is formed.
A shaft hole 253 is formed radially inward of 52, and one end of a stopper pin 300 is press-fitted and fixed in the shaft hole 253. The other end of the stopper pin 300 is fitted into a circumferential groove 301 formed on the facing surface of the internal rotor 220 as shown in FIGS.
The relative rotation between the limiting member 250 and the internal rotor 220 is limited to a predetermined angle.

In the second embodiment, FIGS.
As described above, the relative phases of the camshaft 10 and the inner rotor 220 and the outer rotor 230 are determined when the vanes 280 are in the neutral positions in the fluid pressure chambers R0 (each vane is at each protrusion 231). At the intermediate phase in a position where it does not come into contact with the circumferential end face on the advance side and the circumferential end face on the retard side), and the restricting portion 251 of the second restricting member 250 8 and the other end of the stopper pin 300 abuts on the retarded end surface of the circumferential groove 301 of the internal rotor 220 (FIG. 9). 230 and first
The retracting hole 234 and the receiving hole 229 synchronize with each other when the restricting member 240 is urged in the advance direction by a predetermined angle and is in a twisted position at a predetermined relative phase, and the head of the lock pin 292 is moved to the receiving hole 229. It is adapted to be fittable into the device. When the predetermined relative phase is attained, the opening / closing timing of an intake valve (not shown) is adjusted to a timing at which the internal combustion engine can be started (opening / closing timing of the intake valve is slightly advanced (intermediate advance) (from the maximum retarded position). The timing is advanced by a predetermined angle)).

In the valve timing control apparatus of the second embodiment configured as described above, the internal combustion engine is started and a predetermined hydraulic pressure is supplied to each advance chamber R1 and each retard chamber R2. In the intermediate phase (in FIG. 7, the receiving oil 229 is supplied with hydraulic oil of a set oil pressure (oil pressure lower than the above-mentioned predetermined oil pressure) or more, the head of the lock pin 292 is retreated to the retreat hole 234, and the external rotor 230 And the internal rotor 220 is allowed to rotate relative to each other, the pressing force of the advance hydraulic pressure in each advance chamber R1 is applied to each of the retard chambers R1.
2 and the rotation pressure transmission path from the outer rotor 230 to the inner rotor 220, the fluid pressure chamber R0 and the vane 280 intervene.
And the balance with the sum of the force in the retard direction acting on the camshaft 10) and the solenoid 103 of the control valve 100 according to the operating state of the internal combustion engine.
The hydraulic oil is supplied to each advance chamber R1 through the advance passage 11 and the passages 224, 225, and the like, and the retard chamber R
2 to each passage 223, 222, the retard passage 12, and the control valve 1.
00 and the like, the internal rotor 22
0 and each vane 280 are integrated with the second limiting member 250 to form the external rotor 230, the first limiting member 240, the front plate 245, the rear plate 260, and the intermediate plate 2.
70, etc., on the advance side (clockwise direction in FIG. 7), and this relative rotation amount (maximum advance amount) is such that one vane (lower left vane in FIG. It is limited by contact with the corner side end surface. The control valve 10
By reducing the duty ratio of the current supplied to the solenoid 103 of 0, the retard passage 12 and each passage 222,
When hydraulic oil is supplied to each of the retard chambers R2 through 223, and when hydraulic oil is discharged from each of the advance chambers R1 through the passages 224, 225, the advance passage 11, the control valve 100, and the like, the internal rotor The outer rotor 230, the first limiting member 240, the front plate 245, the second limiting member 250, and the rear plate 26 while the torsion coil spring 291 is twisted against the biasing force of the torsion coil spring 291.
It rotates relatively to the retard angle side (counterclockwise direction in FIG. 7) with respect to the 0 and intermediate plates 270 and the like. As shown in FIG. 7, the relative rotation amount (maximum retard angle amount) is limited by one vane 280 (the upper left vane in the drawing) abutting on the advance side end surface of the projection 231. Note that the inner rotor 220 and the vane 280 are moved only when the relative phase between the inner rotor 220 and the outer rotor 230 is between the above-described relative phase at the most retarded position and the predetermined intermediate phase shown in FIG. The second limiting member 250 is rotated relatively to the advance angle side and the retard angle side with respect to the second limiting member 250, and is located between the above-described relative phase at the most advanced position and a predetermined intermediate phase. The motor 250 is rotated to the advance side and the retard side integrally. Also, during this phase conversion control, the lock pin 292 moves against the spring 293, the head of the lock pin 292 retreats from the receiving hole 229 to the retreat hole 234, and the lock by the lock pin 292 is released. I have. Further, during the above-described phase conversion control, the switching valve 120 is in a non-energized state, and cuts off communication between the connection passage 71 and the drain.

In the second embodiment, as described above, the relative phases of the inner rotor 220 and the outer rotor 230 are
Each vane 280 is in a neutral position (position shown in FIG. 7) between the protrusions 231 in each fluid pressure chamber R0, and the internal rotor 220 advances by a predetermined angle with respect to the external rotor 230 and the first limiting member 240. When the retraction hole 234 and the receiving hole 229 are in a predetermined phase in which the retraction hole 234 and the receiving hole 229 are synchronized with each other in the angularly biased and twisted position, the opening / closing timing of an intake valve (not shown) is set to a timing at which the internal combustion engine can be started. Is set to Therefore, the valve opening / closing timing can be further delayed than the valve opening / closing timing at which the internal combustion engine can be started from the neutral position to the most retarded position where the vane 280 abuts on the advancing side circumferential end face of the projection 231. When the internal combustion engine is rotating at high speed, the control valve 100 is controlled as described above to change the phase from the neutral position to the retard side, and the closing timing of the intake valve (not shown) is delayed until the start of the internal combustion engine is difficult. The volume efficiency is improved by the inertia of the intake air, and the output of the internal combustion engine can be improved.

When the internal combustion engine is stopped, the operation of the oil pump P is stopped, the supply of the hydraulic oil to the fluid 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 280, and the inner rotor 220 and the outer rotor 230
Stop at a relative phase corresponding to the relative phase immediately before both stop. At this time, when the relative phase between the inner rotor 220 and the outer rotor 230 immediately before the stop is on the advance side with respect to the predetermined phase at which the retreat hole 234 and the receiving hole 229 are synchronized with each other, the inner rotor 220 and the camshaft 10 are acted on. Due to the above-described force in the retard direction, the internal rotor 220 and the camshaft 10 move to the retard side with respect to the external rotor 230 together with the second restricting member 250, but the restricting portion 251 of the second restricting member 250 By contacting the protrusion 241 of the restriction member 240, the movement to the retard side from the predetermined intermediate phase is resiliently restricted. Thereby, the head of the lock pin 292 is fitted into the receiving hole 229 by the spring 293,
The relative phase between the inner rotor 220 and the outer rotor 230 is held (locked).

In the second embodiment, the first
Similarly to the embodiment, when a starter switch (not shown) is turned on when the internal combustion engine is started, the solenoid 12 of the switching valve 120 is turned on for a predetermined time after the starter switch is turned on.
2 is connected to the retard passage 12 and is electrically connected to the retard passage 12.
1 is connected to the drain. As a result, when the internal combustion engine is started, the control valve 100 is in the non-energized state, so that the advance chamber R1 and the retard chamber R2 are both connected to the drain. For this reason, when starting the internal combustion engine, the camshaft 10
The cam fluctuation torque acting on the camshaft 10, the internal rotor 220, and the vane 280 easily flap (vibrate) greatly with respect to the external rotor 230 and the like toward the retard side and the advance side. When the relative phase between the inner rotor 220 and the outer rotor 230 immediately before the stop of the engine is more advanced than a predetermined phase in which the evacuation hole 234 and the receiving hole 229 are synchronized or a predetermined phase in which the evacuation hole 234 and the receiving hole 229 are synchronized. Since the head of the lock pin 292 is fitted into the receiving hole 229,
0, fluttering of the internal rotor 220 and the vanes 280 is prevented. Further, the internal rotor 22 immediately before the stop of the internal combustion engine
If the relative phase between 0 and the external rotor 230 is on the retard side relative to the predetermined phase in which the retreat hole 234 and the receiving hole 229 are synchronized or in the relative phase in the maximum retard state,
When the internal combustion engine is stopped in a state where the head of the lock pin 292 is not fitted into the receiving hole 229 and the internal combustion engine is started in this state, the internal rotor 220 and the camshaft 10 are actuated by the above-described retarding force. It moves to the retard side with respect to the external rotor 230 and the like, becomes the maximum retard state, and it becomes difficult to start the internal combustion engine. At this time, since the biasing force of the torsion coil spring 291 for biasing the internal rotor 220 is small, the torsion coil spring 29
Due to 1, the camshaft 10 and the internal rotor 220 cannot be rotated from the maximum retarded position to the advanced side with respect to the external rotor 230 and the like.

In the second embodiment, since the advance chamber R1 and the retard chamber R2 are both connected to the drain when the internal combustion engine is started as described above, the cam fluctuation torque acting on the camshaft 10 is controlled. As a result, the camshaft 10, the internal rotor 220, and the vane 280 flutter (vibrate) largely toward the retard side and the advance side with respect to the external rotor 230 and the like.
Torsion coil spring 2 when fluttering to the advance side
Due to 91, the second limiting member 250 is rotated by a predetermined angle toward the advance side. Thereby, when the internal rotor 220 and the camshaft 10 move to the retard side with respect to the external rotor 230 and the like, the restricting portion 251 of the second restricting member 250 comes into contact with the protrusion 241 of the first restricting member 240. The movement of the locking pin 292 to the retard side from the predetermined intermediate phase is resiliently restricted, and the spring 293 causes the head of the lock pin 292 to be moved by the spring 293 at the predetermined phase in which the evacuation hole 234 and the receiving hole 229 are synchronized. 229, and the relative phases of the inner rotor 220 and the outer rotor 230 are held (locked).

Therefore, when the internal combustion engine is started, the rotating member including the camshaft 10, the internal rotor 220, each vane 280, and the like accompanied by large rotation fluctuation, and the external rotor 23
0, unnecessary relative rotation of the rotation transmitting member including the intermediate plate 270, the rear plate 260, and the like is reliably regulated by the phase holding mechanism, and the sound of the vane 280 caused by the unnecessary relative rotation of the rotating member and the rotation transmitting member. Can be reliably prevented.

As described above, according to the second embodiment,
It is possible to improve the volumetric efficiency in the high-speed rotation range of the internal combustion engine while preventing occurrence of a tapping sound due to collision between the vane 280 and the circumferential end surface of the projection 231 at the time of starting the internal combustion engine and poor starting of the internal combustion engine. it can. Further, in the second embodiment, since the relative rotation restricting mechanism including the first and second restricting members 240 and 250 is provided outside the fluid pressure chamber R0, it is easy to secure the liquid tightness of the fluid pressure chamber R0. At the same time, the precision of the components of the relative rotation limiting mechanism can be reduced, and the manufacturing cost of the valve timing control apparatus can be reduced.

In the above 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 lock pin moves in the radial direction. Although the present invention has been practiced, the present invention is characterized in that the vane is thickened in the circumferential direction and is integrally provided on the internal rotor, and a retreat hole is formed in the vane or the rear plate (or front plate) in the axial direction, and the rear plate ( Alternatively, the present invention can be similarly applied to a valve opening / closing timing control device in which a receiving hole and a receiving hole are formed in an axial direction in a vane or a vane and a lock pin moves in an axial direction. In the above-described embodiment, the present invention is applied to the valve opening / closing timing control device in which the lock by the lock pin is released by the hydraulic pressure supplied to the advance chamber R1. And a step having a small-diameter portion to apply one of the hydraulic pressures supplied to the advance chamber R1 and the retard chamber R2 to the small-diameter portion of the lock pin, The other of the hydraulic pressures supplied to the advance chamber R1 and the retard chamber R2 is applied to the annular space formed in the hole, and the valve opening / closing timing control device in which the lock by the lock pin is released by any of the hydraulic pressures is also provided. It can be implemented similarly. Further, in the above-described embodiment, the present invention is applied to the valve opening / closing timing control device which is limited by one or each vane abutting on the peripheral end surface on the retard side of one or each protrusion. The present invention also applies to a valve opening / closing timing control device in which the maximum amount of advance is controlled before the vane comes into contact with the projection by controlling the hydraulic pressure of the advance chamber R1 and the retard chamber R2. It can be implemented. Further, in the above embodiment, the present invention is applied to the valve opening / closing timing control device mounted on the intake camshaft. However, the present invention is also applied to the valve opening / closing timing control device mounted on the exhaust camshaft. It can be implemented similarly.

[0052]

As described above, according to the present invention, when the supply of the working fluid to the fluid pressure chamber is stopped when the internal combustion engine is stopped, the vane cannot be held by the fluid pressure in the fluid pressure chamber, and the rotating member Is a relative phase intermediate between the relative phase of the rotation axis and the rotation transmitting member in the maximum advance state and the relative phase in the maximum retardation state, although the rotation in the retard direction with respect to the rotation transmission member is performed. When a predetermined intermediate relative phase corresponding to the valve opening / closing timing at the start of the internal combustion engine is reached, the relative rotation of the rotating member to the retard side with respect to the rotation transmitting member is resiliently limited by the relative rotation limiting mechanism, The relative phase between the rotating member and the rotation transmitting member is held at an intermediate relative phase by the phase holding mechanism. Thus, it is possible to appropriately prevent the vane from colliding with the circumferential end face of the fluid pressure chamber and generating a tapping sound when the internal combustion engine is started.

Further, since the valve opening / closing timing at the start of the internal combustion engine is obtained at the intermediate relative phase described above, the valve opening / closing timing at the most retarded position can be further delayed than at the intermediate relative phase. By improving the volumetric efficiency by utilizing the inertia of the intake air at the time of high-speed rotation of the internal combustion engine, the output of the internal combustion engine can be improved, the valve opening / closing timing at the start can be advanced, and the compression ratio can be increased. The starting failure of the internal combustion engine due to the decrease can be prevented.

[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 AA of FIG.

FIG. 3 is a sectional view taken along line BB of FIG. 1;

FIG. 4 is a sectional view taken along the line CC of FIG. 2;

FIG. 5 is a sectional view taken along line DD of FIG. 3;

FIG. 6 is a vertical sectional side view showing a second embodiment of the valve timing control apparatus according to the present invention.

FIG. 7 is a sectional view taken along the line EE of FIG. 6;

FIG. 8 is a sectional view taken along line FF of FIG. 6;

FIG. 9 is a sectional view taken along line GG of FIG. 6;

[Explanation of symbols]

Reference Signs List 10 camshaft 11 advance passage 12 retard passage 20, 220 internal rotor (rotating member) 29, 229 receiving hole 30, 230 external rotor (rotation transmitting member) 34, 234 evacuation hole 40 restricting member (relative rotation restricting mechanism) 41 Protrusion (regulation part) 50 Front plate (rotation transmission member) 60, 260 Rear plate (rotation transmission member) 80, 280 Vane 90, 291 Torsion coil spring (biasing member, relative rotation restricting mechanism) 91, 292 Lock pin ( Phase holding mechanism) 100 Control valve 110 Cylinder head 120 Switching valve 240 First restricting member (Relative rotation restricting mechanism) 241 Projection (Regulating means) 250 Second restricting member (Relative rotation restricting mechanism) 251 Restricting part (Regulating means) R0 Fluid pressure chamber R1 advance chamber R2 retard chamber

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3G016 AA06 AA19 BA23 CA05 CA13 CA21 CA24 CA27 CA33 CA36 CA52 CA57 CA59 DA06 DA22 GA00 GA01 GA04 GA07 3G092 AA11 DA09 DG05 EA03 EA04 FA14 FA31 FA50

Claims (3)

[Claims] 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 mounted on 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 the rotating member, a fluid pressure chamber formed between the rotating member and the rotation transmitting member and divided into an advancing chamber and a retarding chamber by the vane,
A phase control mechanism having a phase holding mechanism that holds a relative phase between the rotation member and the rotation transmission member when a relative phase between the rotation member and the rotation transmission member is a predetermined phase, the advance chamber and The rotation member and the rotation transmission member rotate relative to each other by the fluid pressure applied to the retard chamber, and the rotation phase of the camshaft with respect to the rotation phase of the crankshaft is changed to be driven by the camshaft. In the valve opening / closing timing control device for changing the opening / closing timing of the valve, the relative phase of the rotating member and the rotation transmitting member in the maximum advance state in which the volume of the retarding chamber is minimized by the vane, and the vane An intermediate relative phase between the relative phase of the rotation member and the rotation transmission member in the maximum retarded state where the volume of the advance chamber is minimized. And, the relative phase between the rotating member and the rotation transmitting member is held by the phase holding mechanism at a predetermined intermediate relative phase when the internal combustion engine is at a valve opening / closing timing that can be started, A relative rotation limiting mechanism that resiliently limits relative rotation of the rotating member to the rotation transmitting member toward the retard side when the fluid pressure in the retarding chamber is lower than a predetermined value at the predetermined relative phase. A valve opening / closing timing control device characterized by being provided. 2. A limiting member, wherein said relative rotation limiting mechanism is provided on said rotation transmitting member so as to be relatively rotatable by a predetermined angle;
An urging member for urging the rotation member toward the advance side with respect to the rotation transmission member, wherein the restriction member moves the rotation member and the rotation transmission member relative to the retard side from the predetermined relative phase. The valve opening / closing timing control device according to claim 1, further comprising a regulating portion that resiliently contacts the vane in the fluid pressure chamber when rotating. 3. A first limiting member provided so as to be able to rotate integrally with the rotation transmitting member, a second limiting member provided so as to be able to rotate relative to the first limiting member by a predetermined angle, and Urging means for resiliently connecting the second restricting member and the rotating member so as to be relatively rotatable and urging the second restricting member toward the retard side with respect to the rotating member; 2. The valve opening / closing timing according to claim 1, wherein the rotation transmitting member comprises a restricting means for restricting a movement of the second restricting member to the retard side when the rotation transmitting member is in the predetermined relative phase. Control device.