JPH11223112A - Valve timing control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To surely prevent the generation of hammering by positioning the relative phase of a rotary member and a rotation transmitting member between the maximum lag and the maximum spark-advance phase corresponding to the relative phase in the valve timing when an engine can be started, by a relative phase regulating means in the start of an internal combustion engine, and holding the same by a phase holding mechanism. SOLUTION: When a starter switch is on for starting an internal combustion engine, a switch valve is switched, and a connection path communicating with a lag path to a control valve, is connected with an oil pan. On this occasion, the control valve is not energized, and both of a chamber for spark-advance R1 and a chamber for lag R2 are made to communicate with the oil pan, so that an internal roller 20 easily tramps to an external rotor 30. The tramping of the internal rotor and a vane 60 are prevented by inserting a head part of a small diameter part 101a of a lock pin 101 into a receiving hole 26. The head part of the small diameter part 101a of the lock pin 101 is inserted in the receiving hole 26 in a state that a refuge hole 32 and the receiving hole 26 are synchronized, and the relative phase of both rotors 20, 30 is held.

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 valve timing control apparatus of this type, a rotary member which rotates with a camshaft is provided so as to be relatively rotatable within a predetermined range, and rotational power is transmitted from a crank sprocket or a pulley of a crankshaft. A rotation transmission member, a plurality of vanes provided on the rotation member, and a vane formed between the projection provided on the rotation transmission member and the rotation member and divided into an advance chamber and a retard chamber by the vane. A plurality of fluid pressure chambers, 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, and a relative phase of the rotating member and the rotation transmitting member are predetermined. And a phase holding mechanism for holding the relative phase between the rotating member and the rotation transmitting member when the phase is the same as described above.
No. 4 and JP-A-9-250310.

In the valve timing control devices disclosed in the above publications, the working fluid is supplied to the advance chamber through the first fluid passage, and the working fluid is supplied from the retard chamber through the second fluid passage. By discharging the hydraulic oil, the rotary member rotates in the advance direction to an arbitrary position up to the maximum advance position where the vane abuts the circumferential end surface on the advance side of the protrusion with respect to the rotation transmitting member, and the valve rotates. The opening / closing timing is advanced, the working fluid is supplied to the retard chamber through the second fluid passage, and the working oil is discharged from the advance chamber through the first fluid passage, so that the rotation member transmits the rotation. The vane rotates in the retard direction to an arbitrary position up to the maximum retard position where the vane contacts the peripheral end surface on the retard side of the protrusion with respect to the member, and the valve opening / closing timing is retarded.

In the valve timing control devices disclosed in the above publications, during operation of the internal combustion engine, a force in the retard direction always acts on the rotating member due to the fluctuating torque acting on the camshaft. If the supply of 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. During the period (until the crankshaft completely stops), the rotating member and the rotation transmitting member stop at a relative phase corresponding to the relative phase between them immediately before the stop. 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 is at the maximum retarded position where it comes into contact. When the internal combustion engine is started in this state, the oil pressure in the fluid pressure chamber rises and becomes unstable until 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 face of the protrusion, and a tapping sound is generated. To avoid this, the phase holding mechanism sets the relative phase between the rotation member and the rotation transmission member to the maximum retard 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 opening / closing timing control device disclosed in each of the above publications is used to control the opening / closing timing of an intake valve, the valve opening / closing timing at the maximum retard position is
As described above, since it is necessary to set a timing at which intake is possible at the time of starting the internal combustion engine, it is not possible to delay the closing timing of the intake valve in a high-speed rotation range to improve volumetric efficiency due to inertia of intake. This is because if the valve opening / closing timing at the maximum retard 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 and top dead when the internal combustion engine starts at the maximum retard position. Even if it starts to go to the point, the intake valve is open and there is no inertia in the intake air, so the intake air once sucked flows backward and discharges, and the compression ratio does not increase,
This is because a state in which combustion is impossible occurs, and it becomes difficult to start the internal combustion engine. This problem can be solved by the valve opening / closing timing control device disclosed in each of the above publications without setting the valve opening / closing timing at the maximum retard position to a timing at which the volume efficiency can be improved by the inertia of the intake air. Even if the valve opening / closing timing at the maximum retard position is set to a timing at which intake is possible at the start, if the closing timing of the intake valve is set after the bottom dead center of the piston, the high It is easy to occur in places.

Also, when the valve opening / closing timing control device disclosed in each of the above publications is used to control the opening / closing timing of an exhaust valve, if the closing timing of the exhaust valve is similarly delayed, the intake valve and the exhaust valve are controlled. Of the internal EG
The R amount (exhaust gas recirculation amount) increases, causing a decrease in the startability of the internal combustion engine.

[0008] Therefore, the present invention provides a valve timing control apparatus capable of expanding the variable control range thereof while preventing occurrence of a tapping sound and poor starting due to the vane when the internal combustion engine is started. , The subject.

[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 transmitting member that is mounted so as to be relatively rotatable and rotates together with the other of the crankshaft or the camshaft, a vane provided on the rotating member, and the vane formed between the rotating member and the rotation transmitting 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. And a phase holding mechanism that performs
The rotation member and the rotation transmission member are relatively rotated by the fluid pressure applied to the advance chamber and the retard chamber, and the rotation phase of the camshaft with respect to the rotation phase of the crankshaft is changed. In the valve opening / closing timing control device for changing the opening / closing timing of a valve driven by the camshaft, the rotation member and the rotation transmission member in a maximum advance state in which the volume of the retard chamber is minimized by the vane. A relative phase and an intermediate relative phase between the relative phase of the rotation member and the rotation transmission member in the maximum retarded state in which the volume of the advance chamber is minimized by the vane, wherein the internal combustion engine is The phase holding mechanism holds the relative phase of the rotating member and the rotation transmitting member at a predetermined intermediate relative phase at the time of the valve opening / closing timing at which the valve can be started. With Unisuru is to the relative phase of the rotary member and the rotation transmitting member provided with a relative phase regulating means capable regulations to the predetermined relative phase at the start of the internal combustion engine.

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,
When the internal combustion engine is started, the relative phase regulating means regulates the relative phase between the rotating member and the rotation transmitting member to a predetermined intermediate relative phase, and the phase maintaining mechanism causes the relative phase between the rotating member and the rotation transmitting member to be an intermediate relative phase. Is held. Thus, it is possible to prevent the vane from colliding with the circumferential end face of the rotation transmitting member 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. In addition, 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 and the like. It becomes possible.

In the above means, the relative phase regulating means may be constituted by an urging member which constantly urges the rotating member toward the advance angle side with respect to the rotation transmitting member with a predetermined urging force.

[0013] In the above means, the phase holding mechanism may be configured such that when the fluid pressures of the first fluid passage and the second fluid passage decrease at the predetermined relative phase, the rotation member and the rotation transmitting member are rotated. The configuration may be such that the relative phase is maintained.

[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.

One embodiment of the valve timing control apparatus shown in FIGS. 1 to 4 is a front end portion (FIG. 1) of a camshaft 10 rotatably supported by a cylinder head 70 of the internal combustion engine.
A rotating member for opening and closing a valve comprising an internal rotor 20 integrally assembled with the camshaft 10 and the internal rotor 20; A rotation transmitting member including a rear plate 50 and a timing sprocket 51 provided integrally on the outer periphery of the rear plate 50;
And a phase holding mechanism including a lock pin 101 mounted on the external rotor 30 and the like. The timing sprocket 5
As is well known, a crank sprocket (not shown) and a timing chain 54
The rotational power is transmitted clockwise in FIG.

The camshaft 10 has a well-known cam 11 for opening and closing an intake valve.
An advancing passage 12 and a retarding passage 13 extending in the axial direction are provided. The advance angle passage 12 is connected to a connection port 91 a of a housing 91 of the control valve 90 through a radial passage provided in the camshaft 10, an annular groove and a connection passage 71 provided in the cylinder head 70. Also, the retard passage 13
Is connected to a connection port 91b of a housing 91 of the control valve 90 via a radial passage and an annular groove provided in the camshaft 10 and a connection passage 72 provided in the cylinder head 70. In FIG. 1, reference numeral 14 denotes a ball for closing one end opening of the retard passage 13.

In FIG. 1 and FIG. 2, a control valve 90 shows a spool 92 movably fitted in an axial direction in a housing 91 by energizing a solenoid 95 together with a movable core 94 against a spring 93. 1, and the supply port 91c of the housing 91 connected to the oil pump 110 driven by the internal combustion engine via the supply passage 100 when the power is not supplied, through the annular groove 92a of the spool 92. While communicating with the connection port 91b, the connection port 91a communicates with the discharge port 91d via the communication passage 92b of the spool 92,
When the power is supplied, the supply port 91c communicates with the connection port 91a via the annular groove 92a, and
b is configured to communicate with the discharge port 91d via the communication passage 92c of the spool 92. Therefore, when the solenoid 95 is not energized, hydraulic oil is supplied to the retard passage 13, and when energized, hydraulic oil is supplied to the advance passage 12, and the energization of the solenoid 95 is duty-controlled by a control device (not shown). The discharge port 91d is connected to the oil pan 1 through a discharge passage 73 provided in the cylinder head 70.
11 is connected.

As shown in FIG. 2, the connection passage 72 is connected to a bypass passage 74 that bypasses the control valve 90 and communicates with the oil pan 111. Bypass passage 74
A switching valve 120 is provided therein. Switching valve 120
The spool 121, which is movably inserted in the housing in the axial direction by energizing the solenoid 122, can move to the left in FIG. The switching valve 120 cuts off the communication with the oil pan 111 via the bypass passage 74 of the connection passage 71 when the solenoid 122 is not energized, and connects the connection passage 72 to the drain via the bypass passage 74 when the solenoid 122 is energized. It is configured as follows. The energization of the solenoid 122 is on / off controlled by a control device (not shown).

The internal rotor 20 has a single mounting bolt 81.
And is integrally fixed to the camshaft 10 by
Each of the five vanes 60 has a vane groove 21 for mounting the vanes 60 so as to be movable in the radial direction.
0 and a receiving hole 26 into which the head of the small diameter portion 101a of the lock pin 101 is inserted by a predetermined amount when the relative phases of the inner rotor 20 and the outer rotor 30 are synchronized at a predetermined phase (neutral position of the vane). A passage 27 for supplying and discharging hydraulic oil from the retard passage 12 to the receiving hole 26, and a passage for supplying and discharging hydraulic oil from the advance passage 12 to the advance chamber R1 partitioned by the vanes 60 (the passages 12). Communicating radial passage 22
And an annular groove communicating with the radial passage 22 and five communication holes extending radially outward from the annular groove.
And a passage 25 for supplying and discharging hydraulic oil from the retard passage 13 to the retard chamber R2 partitioned by the vanes 60. The receiving hole 26 is formed on the outer periphery of the internal rotor 20 in the radial direction. Each vane 60 is urged radially outward by a vane spring 61 (see FIG. 1) housed in the bottom of the vane groove 21.

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. A front plate 40 and a rear plate 50 are joined to both sides thereof, and are integrally formed by three connecting bolts 82. Are linked together. In addition, five protrusions 31 are formed on the inner periphery of the outer rotor 30 at predetermined intervals in the circumferential direction so as to protrude inward in the radial direction.
The outer rotor 30 is rotatably supported by the inner rotor 20 in a configuration in which the outer rotor 30 is in sliding contact with the outer peripheral surface of the inner rotor 20. A stepped evacuation hole 32 for accommodating the lock pin 101 and the spring 102 is provided in one protrusion 31. It is formed in the radial direction of the rotor 30.

Each of the vanes 60 has an arc-shaped cross section at the tip, and the inner rotor 20 is located between the plates 40 and 50.
The outer rotor 30 and the projections 31 of the outer rotor 30 are attached to the vane groove 21 so as to be movable in the radial direction.
The fluid pressure chamber R0 formed between the internal rotor 20, the front plate 40, and the rear plate 50 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 abutting the circumferential end surface of each projection 31 formed at zero.

The lock pin 101 has a small diameter portion 101a.
The large-diameter portion 101b is slidably mounted in the stepped evacuation hole 32 in the axial direction, and is urged toward the internal rotor 20 by the spring 102. The spring 102 is interposed between the lock pin 101 and the retainer 103, and the retainer 103 is fixed in the evacuation hole 32 by a snap ring 104 so as not to come off. An annular depression is formed in the step between the small diameter portion 101a and the large diameter portion 101b of the lock pin 101, and the relative phases of the camshaft 10 and the inner rotor 20 and the outer rotor 30 are determined by the receiving hole 26 and the evacuation hole 32. At a predetermined phase (neutral position of the vane) in which the heads of the small-diameter portions 101a of the lock pins 101 are fitted into the receiving holes 26, as shown in FIG.
An annular space 34 is formed between the two steps. The annular space 34 communicates with the adjacent advance chamber R1 via a communication hole 33 formed in the protrusion 31.

Incidentally, the torque required to drive the camshaft 10 is not constant but fluctuates based on the opening / closing drive of an intake valve (not shown). That is, as shown in FIG. 5, this torque is generated in the retard side torque (the cam shaft 10 is retarded (counterclockwise in FIGS. 3 and 4)) generated when the camshaft 10 opens the intake valve. The camshaft 10 rotates the camshaft 10 in the advanced direction (clockwise in FIGS. 3 and 4) generated when the camshaft 10 closes the intake valve and the maximum value of the torque acting to rotate the camshaft 10. The torque fluctuates periodically with the maximum value of the torque acting as described above. As shown in FIG. 5, the maximum value of the retarding torque of the variable torque is larger than the maximum value of the advanced torque, and therefore, the average value of the variable torque is reduced as shown by the one-dot chain line in FIG. Present on the torque side. Therefore, during the operation of the internal combustion engine, the fluctuating torque acts to rotate the camshaft 10 to the retard side on average.

In this embodiment, the camshaft 10
Of the external rotor 30, the front plate 40, the rear plate 50, the rear plate 50, and the like, together with the rotating member consisting of the internal rotor 20 and the vane 60, It is constantly urged in the advance direction by the urging force. The torsion coil spring 80 is housed in an annular hollow portion 52 formed in a portion of the rear plate 50 facing the rear end surface of the internal rotor 20 so as to open toward the internal rotor 20. One end of the torsion coil spring 80 is locked by a locking hole 50a formed at the bottom of the hollow portion 52, and the other end is formed by a locking hole 20a formed at the end face of the internal rotor 20 facing the opening of the hollow portion 52. It is locked to.

Further, in the present embodiment, 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 60 are in the neutral positions in the respective fluid pressure chambers R0 (the respective phases are different). The retreat hole 32 and the receiving hole 26 are synchronized when the vane is at an intermediate phase where the vanes are not in contact with the advance-side circumferential end face and the retard-side circumferential end face of each protrusion 31). In this relative phase, the opening / closing timing of an intake valve (not shown) is set to a timing at which the internal combustion engine can be started.

In the valve opening / closing timing control apparatus of the present embodiment configured as described above, the state shown in FIG. 4, that is, when the internal combustion engine is started and each advance chamber R1 and each retard chamber R2
(The sum of the pressing force by the advance hydraulic pressure in each advance chamber R1 and the urging force of the torsion coil spring 80 is equal to each retard chamber R2).
And the control valve 9 according to the operating state of the internal combustion engine in a state in which the sum of the pressing force due to the retard hydraulic pressure and the average torque of the fluctuation torque acting on the camshaft 10 is balanced.
By increasing the duty ratio of the current supplied to the solenoid 95 of 0, hydraulic fluid is supplied to each advance chamber R1 through the advance passages 12 and 24, and at the same time, each passage is transmitted from each retard chamber R2. When the hydraulic oil is discharged through the passage 25, the retard passage 13, the control valve 90, etc., the internal rotor 20 and each vane 60 are advanced (clockwise in FIG. 4) with respect to the external rotor 30, both plates 40, 50, etc. 4), and the relative rotation amount (maximum advance amount) is limited by the contact of each vane 60 with the circumferential end surface on the advance side of the protrusion 31 as shown by a dashed line in FIG. Further, by lowering the duty ratio of the current supplied to the solenoid 95 of the control valve 90, each of the retard chambers R2 through the retard passage 13 and the passage 25 is reduced.
When the hydraulic oil is supplied to each of the advance chambers R1 and the hydraulic oil is discharged from the advance chambers R1 through the passages 24, the advance passages 12, the control valve 90, and the like, the internal rotor 20 and the vanes 60 are connected to the external rotor 30, The rotation relative to the two plates 40, 50, etc., is retarded (counterclockwise in FIG. 4), and the relative rotation amount (maximum retardation amount) is such that each vane 60 contacts the other end surface of the projection 31. Is limited by During this phase conversion control, a predetermined oil pressure is supplied to at least one of the receiving hole 26 and the annular space 34 in the evacuation hole 32 through the passage 27 or the communication hole 33, and the lock pin 101 resists the spring 102. And move to the small diameter portion 1 of the lock pin 101.
01a retreats from the receiving hole 26 to the evacuation hole 32,
The lock by the lock pin 101 has been released. Further, during the above-described phase conversion control, the switching valve 120 is in a non-energized state, and the communication between the connection passage 72 and the oil pan 111 is cut off.

In this embodiment, as described above, the relative phase between the inner rotor 20 and the outer rotor 30 is such that each vane 60 is in the neutral position (the position shown in FIGS. 3 and 4) in each fluid pressure chamber R0. In addition, when the evacuation hole 32 and the receiving hole 26 are in a predetermined phase synchronized with each other, the opening / closing timing of the intake valve (not shown) is set to be a timing at which the internal combustion engine can be started. Therefore, from this neutral position, the vane 60 is shifted from the projection 3 on the retard side.
The valve opening / closing timing can be further delayed than the valve opening / closing timing at which the internal combustion engine can be started up to the most retarded position abutting on the circumferential end surface of the internal combustion engine 1. By controlling the phase shift from the neutral position to the retard side and delaying the closing timing of an intake valve (not shown) until the start of the internal combustion engine is difficult, the volumetric efficiency is improved by the inertia of the intake air, and the output of the internal combustion engine is improved. Improvement can be achieved.

When the internal combustion engine is stopped, the oil pump 11
0 is stopped, the supply of hydraulic oil to the fluid pressure chamber R0 is stopped, and the control valve 90 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 60, and the internal rotor 20 and the camshaft 10
, Only the average value of the above-mentioned fluctuation torque (until the crankshaft 53 of the internal combustion engine is completely stopped) and the urging force of the torsion coil spring 80 act.
The relative phase between the internal rotor 20 and the external rotor 30 at the time of stoppage is determined according to the relative phase between the internal rotor 20 and the external rotor 30 immediately before stoppage. At this time, if the relative phase of the inner rotor 20 and the outer rotor 30 at the time of stop is in a predetermined phase in which the retreat hole 32 and the receiving hole 26 are synchronized, as shown in FIG. 101a fits into the receiving hole 26, and the inner rotor 2
0 and the relative phase of the external rotor 30 are held (locked). Further, the inner rotor 20 and the outer rotor 30 just before the stop are stopped.
Is more advanced than the predetermined phase in which the retreat hole 32 and the receiving hole 26 are synchronized with each other, the internal rotor 2 is caused by the retarding torque of the fluctuating torque acting on the camshaft 10.
0 and the camshaft 10 rotate to the retard side with respect to the external rotor 30, and when the evacuation hole 32 and the receiving hole 26 reach a predetermined phase synchronized with each other, the spring 102 locks the lock pin 10.
The head of one small diameter portion 101a fits into the receiving hole 26, and the relative phase between the inner rotor 20 and the outer rotor 30 is held (locked). At this time, the fluctuation torque shown in FIG. 5 acts on the camshaft 10 until the crankshaft 53 of the internal combustion engine completely stops, but since the control valve 90 is not energized, The internal rotor 20 and the camshaft 1 are driven by the advanced torque acting on the shaft 10.
A value of 0 makes it difficult to rotate the external rotor 30 on the advance side, and makes it easy to rotate on the retard side by the retard torque. Further, since the internal rotor 20 is biased toward the advance side with respect to the external rotor 30 by the torsion coil spring 80 with the biasing force corresponding to the average value of the fluctuation torque, the maximum of the retard side torque acting on the camshaft 10 is maximized. Since the value is reduced, the head of the small-diameter portion 101a of the lock pin 101 easily fits into the receiving hole 26 when the inner rotor 20 rotates to the retard side with respect to the outer rotor 30.

In this embodiment, when a starter switch (not shown) is turned on when the internal combustion engine is started, the switching valve 120 is turned on for a predetermined time after the starter switch is turned on.
When the solenoid 122 is energized, the connection passage 72 communicating with the retard passage 13 is connected to the oil pan 111.
As a result, when the internal combustion engine is started, the control valve 90 is in a non-energized state, so that the advance chamber R1 and the retard chamber R2
Are both connected to the oil pan 111. For this reason, when the internal combustion engine is started, the internal rotor 20 easily flaps greatly toward the retard side and the advance side with respect to the external rotor 30 due to the urging force of the torsion coil spring 80 and the fluctuating torque acting on the camshaft 10 (vibration occurs). Easier). At this time, as described above, the internal rotor 2 when the internal combustion engine is stopped
0 and the relative phase between the outer rotor 30 and the evacuation hole 32 and the receiving hole 2
6 is synchronized, or 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 advance side of the predetermined phase, the head of the small diameter portion 101a of the lock pin 101 is received. Since the inner rotor 20 and the vane 60 are fitted in the holes 26, fluttering is prevented.

If the relative phase between the internal rotor 20 and the external rotor 30 immediately before the stop of the internal combustion engine is more retarded than the predetermined phase at which the retreat hole 32 and the receiving hole 26 are synchronized, the lock pin 101 The internal combustion engine may be stopped with the head not fitted in the receiving hole 26. When the internal combustion engine is started in this state, the internal rotor 20 and the camshaft 1
0 may rotate to the retard side with respect to the external rotor 30 and may be in the maximum retard state, which may make it difficult to start the internal combustion engine.
In the present embodiment, as described above, when the internal combustion engine is started, both the advance chamber R1 and the retard chamber R2 are connected to the oil pan 1.
11 and the internal rotor 20 is urged toward the advancing side by the torsion coil spring 80 toward the external rotor 30 with an urging force corresponding to the average value of the fluctuation torque. When the camshaft 10 flaps (vibrates) greatly on the advance side and on the retard side, and flaps on the advance side, the evacuation hole 32 and the receiving hole 2
6, the head of the small diameter portion 101a of the lock pin 101 is fitted into the receiving hole 26, and the relative phase between the inner rotor 20 and the outer rotor 30 is held (locked).

Therefore, when the internal combustion engine is started, the rotating members including the internal rotor 20 and the respective vanes 60, the external rotor 30, the front plate 40 and the rear plate 5
Unnecessary relative rotation of the rotation transmission member composed of zero or the like is restricted, and the generation of a tapping sound by the vane 60 due to the unnecessary relative rotation of the rotation member and the rotation transmission member caused by the fluctuation torque acting on the camshaft 10 is suppressed. Can be prevented.

As described above, according to the present embodiment, at the time of starting the internal combustion engine, it is possible to prevent the occurrence of a tapping sound due to the collision between the vane 60 and the circumferential end face of the projection 31 while maintaining the high speed range of the internal combustion engine. In this case, the volume efficiency can be improved.

In the above embodiment, each vane 6
The present invention is applied to a valve opening / closing timing control device in which the relative rotation amount of a rotation member such as the internal rotor 20 and a rotation transmission member such as the external rotor 30 is limited by abutting the peripheral end surface of each protrusion 31 on the circumferential direction. However, the present invention is similarly applied to a valve opening / closing timing control device in which the relative rotation amount of the rotation member and the rotation transmission member is limited by only one vane abutting on the circumferential end surface of the corresponding protrusion. What you get. In the present embodiment, the vane is provided separately from the internal rotor, the receiving hole and the retreat hole are formed in the radial direction, and the present invention is applied to a valve timing control device in which the lock pin moves in the radial direction. However, according to the present invention, the vane is formed so as to be thick in the circumferential direction, is integrally provided on the internal rotor, and the evacuation hole is formed in the vane or the rear plate (or the front plate) in the axial direction, and the rear plate (or the front plate) is formed. ) Or a valve opening / closing timing control device in which a receiving hole is formed in the vane in the axial direction and the lock pin moves in the axial direction.

Further, in the above embodiment, the present invention is applied to the valve opening / closing timing control device mounted on the intake camshaft 10, but the present invention is applied to the valve opening / closing device mounted on the exhaust camshaft. The timing control device can be similarly implemented.

[0035]

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 Rotates in the retard direction with respect to the rotation transmitting member, but when the internal combustion engine starts, the relative phase of the rotating member and the rotation transmitting member is intermediate between the maximum retard position and the maximum advance position by the relative phase regulating means. The relative phase is set at a predetermined relative phase between the rotating member and the rotation transmitting member when the internal combustion engine is at a valve opening / closing timing that can be started, and the predetermined relative phase is held by the phase holding mechanism. Thus, when starting the internal combustion engine, it is possible to accurately prevent the vane from colliding with the circumferential end face of the rotation transmitting member due to the fluctuating torque acting on the camshaft and generating a tapping sound.

Further, since the valve opening / closing timing at the time of starting 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. 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. It is possible to prevent poor starting of the internal combustion engine due to a decrease or the like.

[Brief description of the drawings]

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

FIG. 2 is a schematic configuration diagram of a control valve and a switching valve in the embodiment shown in FIG.

FIG. 3 is a cross-sectional view taken along line AA of FIG. 1, showing a state in which a phase is held by a phase holding mechanism.

FIG. 4 shows a state in which the phase holding mechanism is released.
It is AA sectional drawing of.

FIG. 5 is a graph showing a change in torque acting on a camshaft.

[Explanation of symbols]

Reference Signs List 10 camshaft 12 advance passage 13 retard passage 20 internal rotor (rotary member) 24 passage 25 passage 26 receiving hole 30 external rotor (rotation transmission member) 31 protrusion 32 evacuation hole 33 communication hole 40 front plate (rotation transmission member) Reference Signs List 50 rear plate (rotation transmitting member) 51 timing sprocket (rotation transmitting member) 53 crankshaft 60 vane 70 cylinder head 80 torsion coil spring (relative phase regulating means, urging member) 90 control valve 120 switching valve R0 fluid pressure chamber R1 advance Room for corner R2 Room for retard angle

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 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, wherein the advance chamber and the retard chamber Opening and closing timing of a valve driven by the camshaft by changing the rotation phase of the camshaft with respect to the rotation phase of the crankshaft by rotating the rotation member and the rotation transmission member relative to each other by the fluid pressure applied to the camshaft In the valve opening / closing timing control device, the relative phase of the rotation member and the rotation transmitting member in the maximum advance state in which the volume of the retard chamber is minimized by the vane, and the advance chamber by the vane A relative phase intermediate between the relative phases of the rotating member and the rotation transmitting member in the maximum retarded state in which the volume of the internal combustion engine is minimized. The phase holding mechanism holds the relative phase between the rotating member and the rotation transmitting member at a predetermined intermediate relative phase when the valve is in a valve opening / closing timing that can be started, and the rotating member and the rotating member A valve opening / closing timing control device comprising a relative phase regulating means capable of regulating a relative phase of a transmission member to the predetermined relative phase when the internal combustion engine is started. 2. The apparatus according to claim 1, wherein said relative phase regulating means comprises an urging member which constantly urges said rotating member toward said advancing side with respect to said rotation transmitting member with a predetermined urging force. 2. The valve timing control apparatus according to claim 1. 3. The phase holding mechanism holds the relative phase of the rotation member and the rotation transmission member when the fluid pressure in the advance chamber and the retard chamber decreases during the predetermined relative phase. The valve opening / closing timing control device according to claim 2, characterized in that: