JP2014114731A - Valve timing adjusting device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To perform a start appropriate to an engine temperature.SOLUTION: A main lock mechanism 16 for performing a rotational phase lock at a main lock phase for closing an air intake valve 9 at timing later than the arrival of a piston 8 to a bottom dead center comprises: a main lock member 160 supported to a vane rotor 14; and a movable member 164 supported to a housing rotor 11 and forming a main lock hole 162. A sub-lock mechanism 17 performs the rotation phase lock to a sub-lock phase which is advanced more than the main lock phase. The movable member 164 reciprocates between a lock position for achieving the lock at the main lock phase by the fit-in of the main lock member 160 to the main lock hole 162, and a permitting position for permitting the rotational phase lock at the sub-lock phase while keeping the fit-in. A lock control system 18 for controlling operations of the lock mechanisms 16, 17 holds the movable member 164 at the lock position at a warm start at a temperature not lower than a set temperature of the internal combustion engine, and permits the drive of the movable member 164 to the permitting position at a cold start at a temperature lower than the set temperature of the internal combustion engine.

Description

  The present invention relates to a valve timing adjusting device that adjusts the valve timing of an intake valve that opens and closes a cylinder of an internal combustion engine.

  2. Description of the Related Art Conventionally, a hydraulic valve timing adjusting device that adjusts the valve timing of an intake valve by the pressure of hydraulic fluid is widely known. In general, a hydraulic valve timing adjusting device includes a housing rotor and a vane rotor that rotate in conjunction with a crankshaft and a camshaft of an internal combustion engine, respectively. The rotation phase changes between. As a result of this rotational phase change, the valve timing is adjusted.

  As a kind of hydraulic valve timing adjusting device, Patent Document 1 discloses that a rotational phase advanced from the most retarded phase in an internal combustion engine is an intermediate phase, and the rotational phase reaching the intermediate phase is determined when the internal combustion engine is started. Locking is disclosed. According to such a lock function, the timing of closing the intake valve is made as early as possible, so that the actual compression ratio in the cylinder is increased, so that the temperature of the gas in the cylinder rises due to compression heating, and fuel vaporization is promoted. Will be. Therefore, for example, when the internal combustion engine is left in a stopped state in a low temperature environment such as an extremely low temperature, the startability can be ensured.

  However, in the hydraulic valve timing adjustment device of Patent Document 1 in which the closing timing of the intake valve is early, due to the high actual compression ratio in the cylinder, the warm start of the internal combustion engine in a relatively high temperature environment such as room temperature, for example Occasionally, the following problems may occur: One of the problems is the occurrence of knocking. Another one is that when the internal combustion engine applied to the idle stop system or the hybrid system is restarted, or when the engine is restarted immediately after the ignition is turned off, the temperature during compression of the in-cylinder gas becomes too high. The preignition that self-ignites before ignition is caused, and the fluctuation of cranking rotation is increased due to a large compression reaction force, thereby causing unpleasant vibration or noise.

  Therefore, in the hydraulic valve timing adjustment device disclosed in Patent Document 2, the retard phase for closing the intake valve at a timing later than the piston in the cylinder reaches the bottom dead center, and the retard phase One of the advanced intermediate phases is selected when the internal combustion engine is started. According to such selection of the rotational phase, it is possible to realize starting suitable for the temperature of the internal combustion engine (hereinafter referred to as “engine temperature”).

Japanese Patent No. 4161356 JP 2002-256910 A

  However, in the hydraulic valve timing adjusting device of Patent Document 2, the retarded phase is selected not by locking the rotational phase but by applying the pressure of the hydraulic fluid to the vane rotor in the housing rotor when the internal combustion engine is warmly started. doing. For this reason, at the time of start-up when the pressure of the hydraulic fluid is reduced, the vane rotor rotates relative to the advance side with respect to the housing rotor by the action of the variable torque from the cam shaft, and the rotation phase is easily shifted from the retard phase.

  Further, in the hydraulic valve timing adjusting device of Patent Document 2, since the rotational phase change to the intermediate phase is caused by the fluctuation torque when the internal combustion engine is cold started, the hydraulic fluid that applies pressure to the vane rotor in the housing rotor is drained. ing. As a result, since the hydraulic fluid that applies pressure to the lock body is also drained, the lock body moves to the lock release position, making it difficult to lock in the intermediate phase.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a hydraulic valve timing adjusting device that realizes starting suitable for engine temperature.

  The present invention relates to a housing rotor that rotates in conjunction with a crankshaft of an internal combustion engine in a valve timing adjustment device that adjusts the valve timing of an intake valve (9) that opens and closes a cylinder (7) of the internal combustion engine by the pressure of hydraulic fluid. (11) and a vane rotor (14) that rotates in conjunction with the camshaft (2) of the internal combustion engine and receives the pressure of hydraulic fluid in the housing rotor, and the rotational phase of the housing rotor changes, The rotation phase for closing the intake valve at a timing later than the piston (8) reaches the bottom dead center is defined as a main lock phase (Pm), and the rotation phase reaching the main lock phase when the internal combustion engine is started is defined as The main lock means (16) for locking and the rotation phase advanced from the main lock phase is defined as the sub lock phase (Ps), and the sub lock is applied when starting the internal combustion engine. A sub-lock means (17) for locking the rotational phase when the phase is changed, and a lock control means (18) for controlling the operation of the main lock means and the sub-lock means. The main lock means is a vane rotor. And a movable member (164) which is supported by a housing rotor and forms a main lock hole (162). The main lock member is inserted into the main lock hole by insertion of the main lock member. A movable member that reciprocates between a lock position (Ll) that achieves locking at the main lock phase and an allowable position (Lp) that allows locking at the sub lock phase by the sub lock means while maintaining the fitting; The lock control means holds the movable member in the locked position at the time of warm start at a temperature equal to or higher than the set temperature (Ts) of the internal combustion engine, while cooling the temperature below the set temperature of the internal combustion engine. Characterized in that it allows the driving of the tolerance position of the movable member at the time of starting.

  According to the present invention as described above, at the time of warm start above the set temperature of the internal combustion engine, the movable member supported by the housing rotor in the main lock means is held in the lock position by the lock control means. As a result, in the main lock phase reached when the internal combustion engine is started, the main lock member supported by the vane rotor in the main lock means is fitted into the main lock hole of the movable member at the lock position, so that the rotation in the main lock phase is performed. Phase lock is achieved. Here, in the main lock phase in which the intake valve is closed at a timing later than the in-cylinder piston reaches bottom dead center, the in-cylinder gas is pushed out to the intake system in accordance with the lift of the piston after reaching bottom dead center. As a result, the actual compression ratio decreases. Therefore, at the time of warm start, the rotation phase lock in the main lock phase can be maintained, and the occurrence of starting troubles (hereinafter simply referred to as “starting troubles”) such as knocking, pre-ignition, unpleasant vibration or noise can be suppressed.

  On the other hand, at the time of cold starting below the set temperature of the internal combustion engine, the movable member is allowed to drive to the allowable position by the lock control means. At this time, when the vane rotor rotates relative to the advance side with respect to the housing rotor by the fluctuating torque acting from the camshaft, the main lock member that is supported by the vane rotor and maintains the insertion into the main lock hole moves to the allowable position side together with the movable member. And move. As a result, when the rotation phase changes from the main lock phase to the sub lock phase advanced, the rotation lock at the sub lock phase allowed by the movable member at the allowable position is achieved by the sub lock means. The timing to close is made as early as possible. As a result, the amount of in-cylinder gas pushed out decreases and the temperature of the gas rises with the actual compression ratio. Therefore, even during cold start, the ignitability can be improved and startability can be ensured.

  According to the features of the present invention as described above, it is possible to realize starting suitable for the engine temperature.

  Here, as a further feature of the present invention, the lock control means includes a pressing member (182) that presses the movable member toward the lock position at the time of warm start, and relieves the pressure at the time of cold start.

  According to this feature, the movable member at the time of warm start is pressed against the fluctuation torque by the pressing member of the lock control means, and is held at the lock position on the pressing side. A rotational phase lock can be achieved. On the other hand, the movable member at the time of cold start is allowed to be driven to the allowable position by the fluctuation torque by relieving the pressing to the lock position side by the pressing member. Can be achieved. According to these, it is possible to accurately switch to a rotation phase suitable for each of the warm start and the cold start.

  Further, as a further feature of the present invention, the lock control means is a control chamber (183) for controlling the pressing of the movable member by the pressing member in accordance with the introduction amount of the working fluid introduced into the inside, and the introduction amount Is pressed to hold the movable member in the locked position when the predetermined amount of lock (Ql) is reached, while the movable member is moved to the allowable amount (Qp) smaller than the lock amount while the pressing amount is held. A control chamber that relieves the pressure to drive to the permissible position, and a control valve (60) that controls the introduction amount to a lock amount during a cold start, while controlling the introduction amount to a permissible amount during a cold start, Have.

  According to this feature, in the lock control means at the time of warm start, the control valve controls the amount of hydraulic fluid introduced into the control chamber to a predetermined lock amount. As a result, the movable member pressed by the pressing member is securely held at the lock position, and the rotation phase lock in the main lock phase can be achieved. On the other hand, the control valve at the time of cold start controls the amount of hydraulic fluid introduced into the control chamber to an allowable amount smaller than the lock amount. As a result, the movable member that is relieved by the pressing member can surely reach the allowable position by the varying torque, and the rotational phase lock in the secondary lock phase can be permitted. According to these, it is possible to increase the reliability with respect to switching to the rotation phase suitable for each of the warm start and the cold start.

It is a figure which shows the basic composition of the valve timing adjustment apparatus by one Embodiment of this invention, Comprising: It is the II sectional view taken on the line of FIG. It is the II-II sectional view taken on the line of FIG. It is sectional drawing which shows the operation state different from FIG. It is the IV-IV sectional view taken on the line of FIG. It is a schematic diagram which shows one operation state of the valve timing adjustment apparatus of FIG. It is a schematic diagram which shows the operation state different from FIG. 5 of the valve timing adjustment apparatus of FIG. It is a schematic diagram which shows the operation state different from FIG.5, 6 of the valve timing adjustment apparatus of FIG. It is a schematic diagram which shows the operation state different from FIGS. 5-7 of the valve timing adjustment apparatus of FIG. It is a schematic diagram which shows the operation state different from FIGS. 5-8 of the valve timing adjustment apparatus of FIG. It is a characteristic view for demonstrating the fluctuation | variation torque which acts on the valve timing adjustment apparatus of FIG. It is the XI-XI sectional view taken on the line of FIG. It is the XII-XII sectional view taken on the line of FIG. It is the XIII-XIII sectional view taken on the line of FIG. It is the XIV-XIV sectional view taken on the line of FIG. It is a schematic diagram for demonstrating the characteristic of the valve timing adjustment apparatus of FIG. It is a characteristic view for demonstrating the characteristic of the valve timing adjustment apparatus of FIG. It is a graph for demonstrating one operation example about the valve timing adjustment apparatus of FIG. FIG. 17 is a graph for explaining an operation example different from FIG. 16 for the valve timing adjusting device of FIG. 1. It is a schematic diagram which shows the modification of FIG. It is a schematic diagram which shows the modification of FIG.

  As shown in FIG. 1, a valve timing adjusting apparatus 1 according to an embodiment of the present invention is mounted on an internal combustion engine of a vehicle. In the present embodiment, the stop and start of the internal combustion engine are realized not only in response to the off command and on command of the engine switch SW but also in response to the idle stop command and restart command of the idle stop system ISS.

(Basic configuration)
First, the basic configuration of the valve timing adjusting device 1 will be described. The valve timing adjusting device 1 is a hydraulic type that uses the pressure of hydraulic oil as “pressure of hydraulic fluid”, and an intake valve 9 (described later in detail) as “valve” that opens and closes the camshaft 2 by transmission of engine torque. The valve timing shown in FIG. 16 is adjusted. As shown in FIGS. 1 to 4, the valve timing adjusting device 1 includes a rotary drive unit 10 installed in a transmission system that transmits engine torque output from a crankshaft (not shown) to the camshaft 2 in an internal combustion engine, A control unit 40 that controls the entry and exit of hydraulic oil to drive the drive unit 10 is provided.

(Rotation drive)
As shown in FIGS. 1, 2, and 4, the metal housing rotor 11 in the rotary drive unit 10 is formed by fastening a rear plate 13 and a front plate 15 to both ends in the axial direction of the shoe ring 12. The shoe ring 12 includes a cylindrical housing body 120, a plurality of shoes 121, 122, 123 and a sprocket 124. As shown in FIG. 2, each shoe 121, 122, 123 protrudes inward in the radial direction from a portion of the housing body 120 that is spaced by a predetermined interval in the rotation direction. A storage chamber 20 is formed between the shoes 121, 122, and 123 adjacent to each other in the rotation direction. The sprocket 124 is connected to the crankshaft via a timing chain (not shown). With this connection, while the internal combustion engine is rotating, engine torque is transmitted from the crankshaft to the sprocket 124, whereby the housing rotor 11 rotates in a fixed direction (clockwise in FIG. 2) in conjunction with the crankshaft.

  As shown in FIGS. 1, 2, and 4, the metal vane rotor 14 is coaxially accommodated in the housing rotor 11, and slides both ends in the axial direction to the rear plate 13 and the front plate 15, respectively. The vane rotor 14 includes a cylindrical rotating shaft 140 and a plurality of vanes 141, 142, and 143. As shown in FIG. 1, the rotary shaft 140 is fixed coaxially with the cam shaft 2. With this fixing, the vane rotor 14 can rotate relative to the housing rotor 11 while being able to rotate in the same direction as the housing rotor 11 (clockwise in FIG. 2) in conjunction with the camshaft 2.

  As shown in FIG. 2, the vanes 141, 142, and 143 protrude radially outward from the rotation shaft 140 at predetermined intervals in the rotation direction, and are stored in the corresponding storage chambers 20. The vanes 141, 142, and 143 divide the corresponding storage chambers 20 in the rotation direction, thereby converting the advance chambers 22, 23, 24 and the retard chambers 26, 27, 28 into which the hydraulic oil enters and exits the housing rotor 11. It is partitioned within. Specifically, an advance chamber 22 is formed between the shoe 121 and the vane 141, an advance chamber 23 is formed between the shoe 122 and the vane 142, and an advance angle is formed between the shoe 123 and the vane 143. A chamber 24 is formed. On the other hand, a retard chamber 26 is formed between the shoe 122 and the vane 141, a retard chamber 27 is formed between the shoe 123 and the vane 142, and a retard chamber 28 is formed between the shoe 121 and the vane 143. Is formed.

  The pressure of the hydraulic oil that enters and exits the advance chambers 22, 23, 24 and the retard chambers 26, 27, 28 acts on the vane rotor 14 in the housing rotor 11. Due to the pressure action, the vane rotor 14 rotates relative to the housing rotor 11, whereby the rotation phase of the vane rotor 14 with respect to the housing rotor 11 (hereinafter simply referred to as “rotation phase”) changes. Here, FIG. 2 shows a state in which the rotational phase has changed to the main lock phase Pm, and FIG. 3 shows a state in which the rotational phase has changed to the secondary lock phase Ps.

  As shown in FIG. 1, the main lock mechanism 16 as a “main lock means” has a main lock release chamber 161 that is formed in the vane 141 and into which hydraulic oil enters and exits. The main lock mechanism 16 locks the rotation phase to the main lock phase Pm as shown in FIG. 5 by discharging hydraulic oil from the main lock release chamber 161. On the other hand, the main lock mechanism 16 releases the rotational phase lock at the main lock phase Pm as shown in FIGS.

  As shown in FIG. 4, the sub-lock mechanism 17 as “sub-locking means” has a sub-lock release chamber 171 formed in the vane 142 and through which hydraulic oil enters and exits. The sub lock mechanism 17 locks the rotation phase to the sub lock phase Ps as shown in FIG. 7 by discharging hydraulic oil from the sub lock release chamber 171 or the like. On the other hand, by introducing hydraulic oil into the sub-lock release chamber 171, the sub-lock mechanism 17 releases the rotational phase lock at the sub-lock phase Ps as shown in FIGS.

  In the above rotary drive unit 10, hydraulic oil is introduced into the advance chambers 22, 23, 24 and discharged from the retard chambers 26, 27, 28 under the release of the rotational phase lock by the lock mechanisms 16, 17. As a result, the rotational phase changes toward the advance side (for example, change from FIG. 2 to FIG. 3). As a result, the valve timing is adjusted to advance. On the other hand, under the release of the rotational phase lock by the lock mechanisms 16 and 17, the operation oil is introduced into the retard chambers 26, 27 and 28 and the hydraulic oil is discharged from the advance chambers 22, 23 and 24. The phase changes to the retard side (for example, change from FIG. 3 to FIG. 2). As a result, the valve timing is adjusted to be retarded. Further, under the release of the rotation phase lock by the lock mechanisms 16 and 17, the working oil is confined in the advance chambers 22, 23 and 24 and the retard chambers 26, 27 and 28, so that the change in the rotation phase is suppressed. The valve timing is kept substantially constant.

(Control part)
In the control unit 40 shown in FIGS. 1 and 5, the main advance passage 41 is formed in the rotation shaft 140 and communicates with the advance chambers 22, 23, and 24. The main retardation passage 45 is formed in the rotating shaft 140 and communicates with the retardation chambers 26, 27, and 28. The unlocking passage 49 is formed in the rotating shaft 140 and communicates with both the unlocking chambers 161 and 171.

  The main supply passage 50 formed in the rotating shaft 140 communicates with the pump 4 as a “supply source” via the conveyance passage 3. Here, the pump 4 is a mechanical pump that is driven by receiving an engine torque during rotation of the internal combustion engine. During the rotation, the hydraulic oil sucked from the drain pan 5 is continuously discharged. At the same time, the conveyance path 3 penetrating the camshaft 2 and its bearing can always communicate with the discharge port of the pump 4 regardless of the rotation of the camshaft 2. For these reasons, the hydraulic oil supplied from the pump 4 to the main supply passage 50 is supplied to the respective chambers 22, 23, 24, 26, 27, 28, 161, 171 when the internal combustion engine is started by cranking to complete explosion. Is carried out at a high pressure required for the conveyance of the engine and stops together with the internal combustion engine.

  The sub supply passage 52 is formed in the rotating shaft 140 and branches from the main supply passage 50. The sub supply passage 52 receives the hydraulic oil supplied from the pump 4 through the main supply passage 50. The drain collection passage 54 is provided outside the rotation drive unit 10. The drain collecting passage 54 is opened to the atmosphere together with the drain pan 5 as a drain collecting portion, and the hydraulic oil can be discharged to the drain pan 5.

  The control valve 60 is a so-called spool valve that uses a driving force generated by the linear solenoid 62 and a restoring force generated by the urging member 64 in a direction opposite to the driving force. The control valve 60 connected to each of the passages 41, 45, 49, 50, 52, 54 reciprocally moves the spool 68 in the sleeve 66 shown in FIGS. Switch. As a result, when the spool 68 moves to the lock regions Rlh, Rlo, and Rli in FIGS. 5 to 7 and 9, hydraulic oil from the pump 4 is introduced into the retard chambers 26, 27, and 28 and the advance chamber 22. , 23, 24 and the unlocking chambers 161, 171 are discharged to the drain pan 5. Further, when the spool 68 moves to the retard angle region Rr in FIG. 8, the hydraulic oil in the advance chambers 22, 23, 24 is discharged to the drain pan 5, and the hydraulic oil from the pump 4 is retarded by the retard chambers 26, 27. , 28 and the lock release chambers 161 and 171. Further, when the spool 68 moves to the advance angle region Ra in FIG. 8, the hydraulic oil in the retard chambers 26, 27, 28 is discharged to the drain pan 5, and the hydraulic oil from the pump 4 is advanced to the advance chambers 22, 23. , 24 and the lock release chambers 161 and 171. Furthermore, when the spool 68 moves to the holding region Rh in FIG. 8, the hydraulic oil from the pump 4 is introduced into the lock release chambers 161, 171, while the advance chambers 22, 23, 24 and the retard chambers 26, 27. , 28 is trapped in hydraulic oil.

  The control circuit 80 is a microcomputer that is electrically connected to the linear solenoid 62, the engine switch SW, and various electrical components of the internal combustion engine shown in FIG. 1, and constitutes an idle stop system ISS. The control circuit 80 controls the operation of the internal combustion engine including energization to the linear solenoid 62 and idle stop according to a computer program.

(Variable torque action on the vane rotor)
Next, the variable torque that acts on the vane rotor 14 from the cam shaft 2 will be described.

  During the rotation of the internal combustion engine, fluctuating torque acts on the vane rotor 14 due to a spring reaction force from the intake valve 9 that the camshaft 2 is driven to open and close. As illustrated in FIG. 10, the fluctuating torque alternates between a negative torque acting on the advance side with respect to the housing rotor 11 and a positive torque acting on the retard side with respect to the housing rotor 11. Regarding the fluctuation torque of the present embodiment, the peak torque of the positive torque is larger than the peak torque of the negative torque due to the friction between the camshaft 2 and its bearing, and the average torque thereof is on the positive torque side. It is biased toward (retarded side).

(Van rotor energizing structure)
Next, a biasing structure for biasing the vane rotor 14 toward the sub lock phase Ps will be described.

  In the rotary drive unit 10 shown in FIG. 11, the rotors 11 and 14 are provided with locking pins 110 and 146, respectively. The first locking pin 110 is formed in a cylindrical shape that protrudes in the axial direction opposite to the shoe ring 12 in the front plate 15. The second locking pin 146 is formed in a columnar shape protruding from the arm plate 147 substantially parallel to the front plate 15 on the rotating shaft 140 toward the plate 15 in the axial direction. These locking pins 110 and 146 are arranged so as to be offset from each other in the axial direction at locations that are eccentric by substantially the same distance from the rotation center lines of the rotors 11 and 14.

  As shown in FIGS. 1 and 11, an advance elastic member 19 is disposed between the front plate 15 and the arm plate 147. The advance elastic member 19 is a spiral spring formed by winding a metal wire on substantially the same plane, and the center of the spiral is aligned with the rotation center line of the rotors 11 and 14. The inner peripheral side end of the advance angle elastic member 19 is wound around the outer peripheral portion of the rotating shaft 140. The outer peripheral side end of the advance angle elastic member 19 is bent into a U shape as shown in FIG. The locking part 190 can be locked by a pin corresponding to the rotation phase of the locking pins 110 and 146.

  With the above configuration, the locking portion 190 is locked to the first locking pin 110 when the rotational phase is changed from the sub-locking phase Ps to the retard side, that is, between the locking phases Ps and Pm. At this time, since the second locking pin 146 is detached from the locking portion 190, the restoring force generated by the torsional elastic deformation of the advance angle elastic member 19 is applied to the vane rotor 14 as a rotation torque on the advance angle side with respect to the housing rotor 11. Works. That is, the vane rotor 14 is urged toward the advance lock side sub-lock phase Ps. Here, the restoring force of the advance elastic member 19 between the lock phases Ps and Pm is larger than the average value of the fluctuation torque (see FIG. 10) biased to the retard side, and positive and negative torques. It is preset so as to be smaller than the peak torque. On the other hand, in a state where the rotation phase has changed to the advance side with respect to the sub lock phase Ps, the locking portion 190 is locked to the second locking pin 146. At this time, since the first locking pin 110 is detached from the locking portion 190, the biasing action of the vane rotor 14 by the advance elastic member 19 is limited.

(Main lock mechanism)
Next, details of the main lock mechanism 16 will be described. As shown in FIGS. 1, 2, and 12, the main lock mechanism 16 includes a main lock member 160, a main elastic member 163, a movable member 164, a support groove 165, and an allowable elastic member 166 in addition to the main lock release chamber 161. Yes.

  The cylindrical metal main lock member 160 is arranged eccentric from the rotation shaft 140 and is supported by the vane 141 so as to be reciprocally movable in the axial direction. A main lock release chamber 161 is formed around the main lock member 160 in the vane 141.

  As shown in FIGS. 1 and 12, the coil spring-like metal main elastic member 163 is accommodated in the vane 141. The main elastic member 163 is interposed between the spring receiving portion 141a of the vane 141 and the spring receiving portion 160a closer to the rear plate 13 than the receiving portion 141a in the main lock member 160. The interposed main elastic member 163 generates a restoring force so as to urge the main lock member 160 toward the rear plate 13. The driving force for driving the main lock member 160 by the pressure action from the main lock release chamber 161 acts on the main lock member 160 against the restoring force of the main elastic member 163.

  As shown in FIGS. 1 and 2, the arc-shaped flat plate-shaped metal movable member 164 is arranged so that the center of the arc shape is aligned with the rotation center line of the rotation shaft 140, and reciprocates in the rotation direction by the rear plate 13. Supported as possible. Here, as shown in FIGS. 12 to 14, a support groove 165 extending in the rotation direction is formed in an arcuate groove shape on the axial end surface sliding with the vane 141 in the rear plate 13 of the present embodiment. The movable member 164 is slidably supported in the groove 165. At the same time, the support groove 165 is closed on both sides in the rotational direction to form stoppers 165a and 165b. As shown in FIGS. 5 and 9, the retard stopper 165 a is engaged with the movable member 164 that has moved to the retard side with respect to the housing rotor 11 and has reached the lock position Ll. On the other hand, as shown in FIGS. 7 and 8, the advance stopper 165 b moves to the advance side with respect to the housing rotor 11 and locks the movable member 164 that has reached the allowable position Lp. With the above configuration, the movable member 164 can reciprocate between the lock position Ll and the allowable position Lp.

  In the movable member 164 shown in FIGS. 1, 2, and 12 to 14, a main lock hole 162 is formed in a cylindrical hole shape on an axial end surface that slides with the vane 141. The main lock member 160 that receives the restoring force of the main elastic member 163 can be fitted into the main lock hole 162 by discharging the hydraulic oil from the main lock release chamber 161 as shown in FIGS. Here, when the movable member 164 is held at the lock position L1 in FIG. 5 at the main lock phase Pm (the holding will be described in detail later), the main lock member 160 is fitted into the main lock hole 162. The rotation phase is locked to the phase Pm. On the other hand, the movable member 164 moves from the lock position Ll to the permissible position Lp side while maintaining the fitting of the main lock member 160 into the main lock hole 162 as shown in FIGS. The rotational phase lock at Pm is released. At this time, in particular, in the present embodiment, when the movable member 164 reaches the allowable position Lp in FIG. 7, the rotational phase lock at the sub lock phase Ps is allowed. Furthermore, in this embodiment, when the main lock member 160 is released from the main lock hole 162 as shown in FIGS. 8 and 9 by introducing hydraulic oil into the main lock release chamber 161, the rotational phase lock at the main lock phase Pm is also achieved. It is to be released.

  As shown in FIGS. 12 and 13, the metal allowable elastic member 166 in the form of a coil spring is accommodated in a bottomed cylindrical hole 13 a that opens to the retard stopper 165 a in the rear plate 13. The allowable elastic member 166 is interposed between the bottom surface of the cylindrical hole 13a and the retard side end surface of the movable member 164. The interposed allowable elastic member 166 generates a restoring force so as to urge the movable member 164 toward the allowable position Lp. That is, the restoring force of the allowable elastic member 166 acts toward the advance side with respect to the housing rotor 11. Therefore, when the main lock member 160 is fitted in the main lock hole 162 in the rotation phase from the main lock phase Pm to the sub lock phase Ps shown in FIGS. A resultant force with the restoring force of the elastic member 19 acts on the vane rotor 14 and the movable member 164. Therefore, in this embodiment, the resultant force of the restoring force of the allowable elastic member 166 and the restoring force of the advance elastic member 19 is also larger than the average value of the fluctuation torque (see FIG. 10) and from the peak torque of the positive and negative torques. Is also set to be smaller.

  The main lock phase Pm realized by the main lock mechanism 16 described above is preset to the most retarded phase as shown in FIGS. In particular, the main lock phase Pm of the present embodiment closes the intake valve 9 at a timing later than the timing at which the piston 8 in the cylinder 7 of the internal combustion engine reaches the bottom dead center BDC, as shown in FIG. The rotation phase is preset.

(Sub lock mechanism)
Next, details of the sub-lock mechanism 17 will be described. As shown in FIGS. 2, 4, and 14, the secondary lock mechanism 17 includes a secondary lock member 170, a secondary elastic member 173, restriction grooves 174 and 175, and a secondary lock hole 172 in addition to the secondary lock release chamber 171.

  The cylindrical metal sub-lock member 170 is arranged eccentric from the rotation shaft 140 and is supported by the vane 142 so as to be reciprocally movable in the axial direction. A secondary lock release chamber 171 is formed around the secondary lock member 170 in the vane 142.

  As shown in FIG. 4, the coil spring-like metal secondary elastic member 173 is accommodated in the vane 142. The secondary elastic member 173 is interposed between the spring receiving portion 142a of the vane 142 and the spring receiving portion 170a closer to the rear plate 13 than the receiving portion 142a in the secondary lock member 170. The interposed secondary elastic member 173 generates a restoring force so as to urge the secondary lock member 170 toward the rear plate 13. Further, the force for driving the sub-lock member 170 by the pressure action from the sub-lock release chamber 171 acts on the sub-lock member 170 against the restoring force of the sub-elastic member 173.

  As shown in FIGS. 4 and 14, a first limiting groove 174 is formed in an arcuate groove shape extending in the rotational direction on the axial end surface that slides with the vane 142 in the rear plate 13. Further, a second restriction groove 175 is formed in the shape of a circular arc groove extending in the rotation direction on the groove bottom surface of the first restriction groove 174. Further, a secondary lock hole 172 is formed in the groove bottom surface of the second restriction groove 175.

  Under such a configuration, the sub-lock member 170 can enter either of the restriction grooves 174 and 175 or be fitted into the sub-lock hole 172 by discharging hydraulic oil from the sub-lock release chamber 171. Here, as the sub-lock member 170 enters the first restriction groove 174 as shown in FIG. 6, the rotational phase is restricted to the first phase range Pr1 (see FIG. 15). Further, when the secondary lock member 170 enters the second restriction groove 175 through the first restriction groove 174, the rotational phase is restricted to the second phase range Pr2 (see FIG. 15). Further, as shown in FIG. 7, the secondary lock member 170 is fitted into the secondary lock hole 172 through the restriction grooves 174 and 175, whereby the rotational phase is locked to the secondary lock phase Ps.

  On the other hand, when the hydraulic oil is introduced into the secondary lock release chamber 171, the secondary lock member 170 escapes from the secondary lock hole 172 and the restriction grooves 174 and 175 as shown in FIG. Is released. Even if the hydraulic oil is discharged from the sub lock release chamber 171, the main lock can be obtained even when the sub lock member 170 contacts the rear plate 13 outside the sub lock hole 172 and the restriction grooves 174 and 175 as shown in FIG. The rotational phase lock at the phase Pm is released.

  The sub lock phase Ps realized by the sub lock mechanism 17 described above is preset to an intermediate phase advanced from the main lock phase Pm as shown in FIGS. In particular, the sub-lock phase Ps of the present embodiment is such that, as shown in FIG. 16, the intake valve 9 is moved at the timing when the piston 8 in the cylinder 7 of the internal combustion engine reaches the bottom dead center BDC or at a timing close thereto. The rotation phase for closing is preset. Further, as shown in FIG. 15, in the present embodiment, the second phase range Pr2 is compared to the first phase range Pr1 that is retarded from the secondary lock phase Ps and advanced from the main lock phase Pm. It is preset between the advance side end of the range Pr1 and the secondary lock phase Ps.

(Lock control system)
Next, details of the lock control system 18 provided across the sections 10 and 40 as shown in FIG. 1 as “lock control means” for controlling the operation of the lock mechanisms 16 and 17 will be described. The lock control system 18 is formed by combining a control valve 60 and a control circuit 80 with a control mechanism 180 and a control passage 181.

  As shown in FIGS. 12 and 13, the control mechanism 180 that forms a part of the rotation drive unit 10 includes a pressing member 182 that is driven by the pressure of the hydraulic oil, and a control chamber 183 into which the hydraulic oil enters and exits. ing.

  The cylindrical piston-shaped metal pressing member 182 is accommodated in a bottomed cylindrical hole 13 b that opens to the advance stopper 165 b in the rear plate 13. By pressing the pressing member 182 into the support groove 165, the curved convex end surface can be brought into contact with the end surface on the advance side of the movable member 164, which is a separate body, as shown in FIGS. Therefore, under such contact, as shown in FIGS. 5 to 9, the pressing member 182 presses the movable member 164 toward the lock position L <b> 1 by increasing the amount of entry into the supporting groove 165, while entering the supporting groove 165. The pressure is relieved by a decrease in the amount of entering.

  As shown in FIGS. 12 and 13, the control chamber 183 is formed in the rear plate 13 between the bottom surface of the cylindrical hole 13 b and the rear end surface of the pressing member 182. The control chamber 183 controls the pressing of the movable member 164 by the pressing member 182 according to the amount of hydraulic oil introduced into the control chamber 183. Specifically, when the amount of hydraulic oil introduced into the control chamber 183 increases, the amount of the pressing member 182 entering the support groove 165 also increases, so that the movable member 164 is pressed toward the lock position Ll. As a result, when the amount of hydraulic oil introduced into the control chamber 183 reaches the predetermined lock amount Ql as shown in FIGS. 5 and 9, the movable member 164 is sandwiched between the pressing member 182 and the retard stopper 165a, It is held at the lock position Ll. On the other hand, when the amount of hydraulic oil introduced into the control chamber 183 decreases, the amount of the pressing member 182 entering the support groove 165 also decreases, so that the movable member 164 receives a pressure relief action toward the lock position Ll. As a result, when the amount of hydraulic oil introduced into the control chamber 183 reaches the allowable amount Qp (in this embodiment, for example, an amount that is substantially zero) smaller than the lock amount Ql as shown in FIGS. 164 can be driven to the allowable position Lp.

  As shown in FIGS. 1 and 5, the control passage 181 forming a part of the control unit 40 is formed in the rear plate 13 and communicates with the control chamber 183. At the same time, the control passage 181 connected to the control valve 60 is switched between communication and blocking with the other passages 41, 45, 49, 50, 52, 54 by the reciprocating movement of the spool 68. As a result, when the spool 68 moves to the holding lock region Rlh in FIG. 5, the hydraulic oil is confined in the control chamber 183. Further, when the spool 68 moves to the introduction lock region Rli in FIG. 9, the hydraulic oil from the pump 4 is introduced into the control chamber 183. Further, when the spool 68 moves to the discharge lock region Rlo of FIGS. 6 and 7, the hydraulic oil in the control chamber 183 is discharged to the drain pan 5. Furthermore, when the spool 68 moves to any one of the regions Rr, Rh, Ra in FIG. 8, the hydraulic oil in the control chamber 183 is discharged to the drain pan 5.

  As will be described in detail later, the control circuit 80 controls the energization of the linear solenoid 62 according to the magnitude relationship between the engine temperature and the set temperature Ts (see FIGS. 17 and 18 described in detail later) when the internal combustion engine is started. On the other hand, control is performed during normal operation and startup of the internal combustion engine regardless of the engine temperature. The set temperature Ts is preset to, for example, a temperature within a range of 40 to 60 ° C. in order to appropriately discriminate between a warm start higher than that and a cold start lower than that.

(Operation)
Next, the operation of the device 1 will be described in detail.

(1) Normal operation During normal operation of the internal combustion engine after a complete explosion at the start, the spool 68 is moved to one of the regions Rr, Ra, Rh as shown in FIGS. At this time, the hydraulic oil supply from the pump 4 is continued at a high pressure corresponding to the rotational speed of the internal combustion engine. As a result, the lock oil 160 introduced into the lock release chambers 161 and 171 causes the lock members 160 and 170 to escape from the lock holes 162 and 172, respectively, so that the rotational phase lock at the lock phases Pm and Ps is achieved. The release state is maintained (FIG. 8). At the same time, in the control chamber 183 from which the hydraulic oil is discharged, the hydraulic oil introduction amount is controlled to the allowable amount Qp. Therefore, the movable member 164 receiving the restoring force of the allowable elastic member 166 is moved to the advance stopper 165b. It is pressed and localized at the allowable position Lp. Under such maintenance and orientation, the valve timing is appropriately adjusted by changing the moving position of the spool 68 to one of the regions Rr, Ra, Rh in a timely manner.

(2) Stop / Start When the internal combustion engine stops in response to a stop command such as an engine switch SW off command or an idle stop system ISS idle stop command, Prepare for the start-up.

  Specifically, in the preparation process, first, while the hydraulic oil supply from the pump 4 is continued at a high pressure due to idle rotation of the internal combustion engine, the spool 68 is moved to the introduction lock region Rli as shown in FIGS. As a result, the rotational phase reaches the main lock phase Pm as the most retarded angle phase due to the hydraulic oil pressure in the retarded angle chambers 26, 27, and 28. At the same time, when hydraulic oil from the pump 4 is introduced into the control chamber 183, when the introduction amount reaches the lock amount Ql, the movable member 164 pressed by the pressing member 182 is retarded at the lock position Ll. It receives the locking action of 165a (FIG. 9). In addition, since the restoring force of the main elastic member 163 is pre-adjusted, the main lock member 160 at this time maintains the state where it has escaped from the main lock hole 162 even when the pressure in the main lock release chamber 161 is reduced. To do. Similarly, since the restoring force of the secondary elastic member 173 is pre-adjusted, the secondary lock member 170 at this time has escaped from the secondary lock hole 172 even when the pressure in the secondary lock release chamber 171 drops. To maintain.

  Further, in the preparation process, the spool 68 is moved to the holding lock region Rlh as shown in FIGS. 17 and 18 while the hydraulic oil supply from the pump 4 is continued at a high pressure due to the idle rotation of the internal combustion engine. As a result, the rotation phase is held at the main lock phase Pm by the hydraulic oil pressure in the retard chambers 26, 27, and 28. At the same time, the amount of hydraulic oil introduced into the control chamber 183 is held at the lock amount Ql, whereby the movable member 164 is held at the lock position Ll. At this time, the main lock member 160 that receives the restoring force of the main elastic member 163 is fitted into the main lock hole 162 in accordance with the pressure drop in the main lock release chamber 161 (FIG. 5). At the same time, the secondary lock member 170 that receives the restoring force of the secondary elastic member 173 contacts the rear plate 13 outside the secondary lock hole 172 and the restriction grooves 174 and 175 in accordance with the pressure drop in the secondary lock release chamber 171 ( FIG. 5). As a result of such insertion and contact, the rotational phase is locked to the main lock phase Pm.

  When the above preparation process is completed, the internal combustion engine is brought into an inertial rotation state while the spool 68 is maintained in the holding lock region Rlh as shown in FIGS. As a result, the internal combustion engine is completely stopped with the rotational phase locked to the main lock phase Pm.

  Thereafter, in a warm start in which cranking of the internal combustion engine is started at the set temperature Ts or higher in response to a start command such as an on command for the engine switch SW or a restart command for the idle stop system ISS, the spool 68 is used as shown in FIG. Is maintained in the holding lock region Rlh. At this time, the hydraulic oil supply from the pump 4 substantially stops and the pressure of the supply does not reach the required pressure, but the hydraulic oil introduction amount into the control chamber 183 is controlled to the lock amount Ql. As a result, the movable member 164 is held at the pressing-side lock position Ll by being pressed by the pressing member 182 against the negative torque among the variable torques. Therefore, the main lock member 160 that receives the restoring force of the main elastic member 163 in the state where the pressure in the main lock release chamber 161 is lost maintains the fitting into the main lock hole 162 (FIG. 5). At the same time, the sub-lock member 170 that receives the restoring force of the sub-elastic member 173 when the pressure in the sub-lock release chamber 171 disappears contacts the rear plate 13 outside the sub-lock hole 172 and the restriction grooves 174 and 175 (see FIG. 5). As a result of such insertion maintenance and contact, the internal combustion engine is completely exploded in a state where the rotational phase lock at the main lock phase Pm is achieved.

  On the other hand, at the time of cold start in which cranking of the internal combustion engine is started below the set temperature Ts according to the start command, the spool 68 is moved to the discharge lock region Rlo as shown in FIG. Drain the oil. Here, particularly in the present embodiment, the hydraulic oil in the control chamber 183 is pushed into the control passage 181 by the pressing member 182 that receives a negative torque, so that the hydraulic oil discharge from the chamber 183 is promoted. As a result, when the amount of hydraulic oil introduced into the control chamber 183 is controlled to the allowable amount Qp, the movable member 164 is relieved from being pressed by the pressing member 182 toward the lock position Ll, so that the movable member 164 is driven to the allowable position Lp. Is acceptable. At this time, the main lock member 160 that receives the restoring force of the main elastic member 163 in a state where the pressure in the main lock release chamber 161 is lost maintains the fitting into the main lock hole 162 and the movable member 164 with respect to the housing rotor 11. And relative driving with the vane rotor 14 becomes possible. Further, the secondary lock member 170 that receives the restoring force of the secondary elastic member 173 in the state where the secondary lock release chamber 171 has lost pressure, together with the vane rotor 14 with respect to the housing rotor 11 from the same contact point with the rear plate 13 as when stopped. Relative driving is possible.

  At the time of cold start in which the rotational phase lock at the lock phases Pm and Ps is released in this way, the vane rotor 14 rotates relative to the advance side with respect to the housing rotor 11 by the negative torque. At this time, the main lock member 160 that is supported by the vane rotor 14 and maintains the insertion into the main lock hole 162 moves together with the movable member 164 to the allowable position Lp side (FIG. 6). As a result, when the rotational phase is advanced from the main lock phase Pm, the secondary lock member 170 that receives the restoring force of the secondary elastic member 173 in the pressure disappearance state of the secondary lock release chamber 171 receives the first restriction groove 174 and the second restriction groove 174. The grooves 175 are sequentially entered. Thereby, even if the vane rotor 14 at the time of the positive torque action is relatively rotated toward the retard side with respect to the housing rotor 11, the return of the rotational phase to the main lock phase Pm is the first phase range Pr1 or the second phase as shown in FIG. It is limited to the phase range Pr2.

  Thereafter, when the rotational phase is advanced by the negative torque and changes to the sub-lock phase Ps, the main lock member 160 that has been fitted into the main lock hole 162 reaches the allowable position Lp together with the movable member 164. It is locked by the advance stopper 165b (FIG. 7). At the same time, the sub-lock member 170 that receives the restoring force of the sub-elastic member 173 when the pressure in the sub-lock release chamber 171 disappears fits into the sub-lock hole 172 (FIG. 7). As a result of such engagement and insertion, the internal combustion engine is completely exploded in a state where the rotation phase is locked to the sub lock phase Ps as shown in FIG.

(Function and effect)
According to the apparatus 1 described above, at the time of warm start at the set temperature Ts or higher of the internal combustion engine, the movable member 164 supported by the housing rotor 11 in the main lock mechanism 16 is held at the lock position Ll by the lock control system 18. . As a result, in the main lock phase Pm reached when the internal combustion engine is started, the main lock member 160 supported by the vane rotor 14 in the main lock mechanism 16 is fitted into the main lock hole 162 of the movable member 164 at the lock position Ll. Rotational phase lock at the main lock phase Pm is achieved. Here, in the main lock phase Pm in which the intake valve 9 is closed at a timing later than the piston 8 in the cylinder 7 reaches the bottom dead center BDC, the piston 8 after the bottom dead center is reached at the next start of the internal combustion engine. When the cylinder 7 gas is pushed out to the intake system in accordance with the lift-up, the actual compression ratio is reduced (decompression effect). Therefore, at the time of warm start, for example, even when restart by the idle stop system ISS is frequently repeated, the rotation phase lock at the main lock phase Pm can be maintained, and the occurrence of a start failure can be suppressed.

  On the other hand, at the time of cold start below the set temperature Ts of the internal combustion engine, the lock control system 18 allows the movable member 164 to be driven to the allowable position Lp. At this time, when the vane rotor 14 is relatively rotated toward the advance side with respect to the housing rotor 11 by the fluctuating torque (negative torque) acting from the camshaft 2, the main lock member that is supported by the vane rotor 14 and maintains the insertion into the main lock hole 162. 160 moves to the allowable position Lp side together with the movable member 164. As a result, when the rotational phase changes from the main lock phase Pm to the secondary lock phase Ps advanced, the secondary lock mechanism 17 achieves the rotational phase lock at the phase Ps allowed by the movable member 164 at the allowable position Lp. Therefore, the timing for closing the intake valve 9 is advanced as much as possible. As a result, the amount of extrusion of the gas in the cylinder 7 decreases and the temperature of the gas rises with the actual compression ratio. Therefore, at the time of cold start, for example, after starting the vehicle for a long time in a cryogenic environment, Even at the time of restart when the operation is ended with the system ISS being temporarily stopped, the ignitability can be improved and the startability can be ensured.

  According to the apparatus 1 as described above, it is possible to realize a start suitable for the engine temperature.

  Here, in particular, the movable member 164 at the time of warm start is held by the pressing member 182 of the lock control system 18 against the fluctuating torque (negative torque), thereby being held at the locking position Ll on the pressing side. Thus, rotational phase lock at the main lock phase Pm can be achieved. On the other hand, the movable member 164 at the time of cold start is allowed to be driven to the allowable position Lp by the fluctuation torque because the pressing to the lock position Ll side by the pressing member 182 is relaxed, so that the sub-lock phase Ps. Rotational phase lock at can be achieved. According to these, it is possible to accurately switch to a rotation phase suitable for each of the warm start and the cold start.

  Further, in the lock control system 18 at the time of warm start, the control valve 60 controls the amount of hydraulic oil introduced into the control chamber 183 to a predetermined lock amount Ql. As a result, the movable member 164 pressed by the pressing member 182 is reliably held at the lock position Ll, and the rotation phase lock at the main lock phase Pm can be achieved. On the other hand, the control valve 60 at the time of cold start controls the amount of hydraulic oil introduced into the control chamber 183 to an allowable amount Qp smaller than the lock amount Ql. As a result, the movable member 164 that is relieved by the pressing member 182 can reliably reach the allowable position Lp due to the varying torque, and the rotational phase lock at the secondary lock phase Ps can be permitted. According to these, it is possible to increase the reliability with respect to switching to the rotation phase suitable for each of the warm start and the cold start.

  Furthermore, the supply pressure of the hydraulic oil from the pump 4 driven by the internal combustion engine is deficient compared to the pressure required to convey the hydraulic oil to the control chamber 183 when the internal combustion engine is started. However, since the amount of hydraulic oil introduced into the control chamber 183 is held at the lock amount Ql by the control valve 60 when the internal combustion engine is stopped, it is related to the supply pressure from the pump 4 during the warm start after the stop. Instead, the movable member 164 can be held at the lock position Ll to achieve the rotational phase lock at the main lock phase Pm. Therefore, it is possible to improve the reliability of warm startability.

  Further, when the rotational phase changes to the sub-lock phase Ps while driving the movable member 164 to the allowable position Lp due to the variable torque acting at the cold start, the sub-lock member 170 in the sub-lock mechanism 17 Fits into the sub-lock hole 172. Here, since one of the rotors 11 and 14 supports the sub-lock member 170 and the other of the rotors 11 and 14 forms the sub-lock hole 172, the sub-lock member 170 is fitted into the sub-lock hole 172. The rotational phase lock at the secondary lock phase Ps can be reliably achieved. Therefore, it is possible to improve the reliability of cold startability.

  In addition, the movable member 164 urged by the restoring force of the allowable elastic member 166 in the main lock mechanism 16 is engaged by the advance stopper 165b at the urging-side allowable position Lp during normal operation after the internal combustion engine is started. Stopped. At this time, the lock members 160 and 170 are escaped from the lock holes 162 and 172, so that the movable elastic member 166 receives the restoring force of the allowable elastic member 166 in a state where the rotational phase lock at both lock phases Pm and Ps is released. The member 164 can be pressed against the advance stopper 165b. According to this, when realizing a free valve timing adjustment by a change in rotational phase after starting suitable for the engine temperature, the movement of the movable member 164 is restricted, and the noise (impact noise / sliding) caused by the movement is restricted. Noise) and wear (collision wear, sliding wear, etc.) can be suppressed.

  In addition, the vane rotor 14 is urged by the advance elastic member 19 toward the advance side with respect to the housing rotor 11 in the rotational phase between the main lock phase Pm and the sub lock phase Ps. Therefore, the vane rotor 14 that receives the urging action of the advance angle elastic member 19 during the cold start of the internal combustion engine has the rotational phase with respect to the housing rotor 11 up to the sub-lock phase Ps in combination with the action of the variable torque (negative torque). Can change quickly. According to this, since the time required from the start of cranking for generating the fluctuating torque in the internal combustion engine at the time of cold start until the rotation phase is locked at the secondary lock phase Ps can be shortened, particularly after the cold stop It is possible to improve the reliability of the cold startability.

(Other embodiments)
Although one embodiment of the present invention has been described above, the present invention is not construed as being limited to the embodiment, and can be applied to various embodiments without departing from the gist of the present invention. it can.

  Specifically, as a first modification of the above-described embodiment, as long as the rotation phase closes the intake valve 9 at a timing later than the timing at which the piston 8 in the cylinder 7 reaches the bottom dead center BDC, the most retarded phase. The main lock phase Pm on the more advanced side may be employed. Further, as a second modification of the above embodiment, the sub lock member 170 may be supported by the housing rotor 11, while the sub lock hole 172 may be formed in the vane rotor 14. Furthermore, as a third modification of the above-described embodiment, in addition to a metal spring other than the coil spring, for example, rubber members or the like may be employed for the elastic members 163, 173, and 166.

  As a fourth modification of the above embodiment, an electric pump that can start supplying hydraulic oil at any time may be employed for the pump 4. Here, in the case of the modified example 4, instead of holding the lock amount Ql when the internal combustion engine is stopped, the lock amount Ql is realized by introducing hydraulic oil from the pump 4 when the internal combustion engine is warmly started. May be.

  As the fifth modification of the above embodiment, the advance elastic member 19 may not be provided. Further, as the sixth modification of the embodiment, the allowable elastic member 166 may not be provided. Furthermore, as a seventh modified example of the above-described embodiment, the resultant force of the restoring force of the allowable elastic member 166 and the restoring force of the advance elastic member 19 (in the case of further combining with the modified examples 5 and 6, either restoring force) Is set to be larger than the peak torques of the positive and negative torques, and at the time of cold start, the movable member 164 is pressed against the advance stopper 165b by the resultant force, and the rotational phase at the sub lock phase Ps. Locking may be achieved. Here, in the case of the modified example 7, the “sub-locking means” constituted by the elements 166, 19, 164, 165 b may be combined with the sub-locking mechanism 17 as the “sub-locking means”, or the sub-locking mechanism 17. May not be provided.

  As a modification 8 of the above embodiment, the movable member 164 is held at the lock position Ll by balancing the restoring force of the allowable elastic member 166 and the pressing force of the pressing member 182 instead of the locking action by the retard stopper 165a. May be. Further, as a ninth modification of the above-described embodiment, an advance stopper 165b may be provided so as to lock the pressing member 182 instead of the movable member 164. Furthermore, as a tenth modification of the above-described embodiment, the movable member 164 and the pressing member 182 may be integrally formed instead of being formed separately. Furthermore, as a modification 11 of the above-described embodiment, the direct drive of the movable member 164 or the drive of the movable member 164 by the pressing member 182 may be realized by various drive sources such as a linear solenoid.

  As a twelfth modification of the above embodiment, when the internal combustion engine stops in response to an engine switch SW off command, the rotation phase is locked to the sub-lock phase Ps, and then the internal combustion engine responds to the engine switch SW on command. When the engine is started, the rotational phase lock at the phase Ps may be realized as it is. Alternatively, as a thirteenth modification of the above embodiment, when the internal combustion engine stops in response to the idle stop command of the idle stop system ISS, the rotation phase is locked to the sub lock phase Ps, and then the idle stop system ISS is restarted. When the internal combustion engine is started in response to the command, the rotational phase lock at the phase Ps may be realized as it is.

  As a fourteenth modification of the above-described embodiment, as shown in FIG. 19, hydraulic oil from the pump 4 is supplied to the lock release chambers 161 and 171 in the introduction lock region Rli that is realized before the preparatory process when the internal combustion engine is stopped. It may be introduced. Here, in the case of the modified example 14, the hydraulic oil in the lock release chambers 161 and 171 is discharged in the holding lock region Rlh that shifts from the introduction lock region Rli after the preparation process when the internal combustion engine is stopped. As a fifteenth modification of the above embodiment, as shown in FIG. 20, a retard angle region Rr may be realized instead of the exhaust lock region Rlo when the internal combustion engine is cold started. Here, in the case of the modified example 15, since the hydraulic oil supply from the pump 4 is substantially stopped at the time of cold start, the main lock member 160 maintains the fitting into the main lock hole 162 as in the above embodiment, The movable member 164 and the vane rotor 14 can be driven relative to the housing rotor 11.

1 valve timing adjusting device, 2 camshaft, 4 pump, 7 cylinder, 8 piston, 9 intake valve, 11 housing rotor, 13 rear plate, 14 vane rotor, 16 main lock mechanism, 17 sub lock mechanism, 18 lock control system, 19 Advance angle elastic member, 60 control valve, 80 control circuit, 160 main lock member, 162 main lock hole, 164 movable member, 165 support groove, 165b advance angle stopper, 166 allowable elastic member, 170 sub lock member, 172 sub lock hole , 180 control mechanism, 181 control passage, 182 pressing member 183 control chamber, Ll lock position, Lp permissible position, Pm main lock phase, Ps sub lock phase, Ql lock amount, Qp permissible amount, Rlh holding lock region, Rli introduction lock Area, Rlo discharge lock area, Ts set temperature

Claims (7)

In the valve timing adjusting device for adjusting the valve timing of the intake valve (9) for opening and closing the cylinder (7) of the internal combustion engine by the pressure of the hydraulic fluid,
A housing rotor (11) that rotates in conjunction with a crankshaft of the internal combustion engine;
A vane rotor (14) that rotates in conjunction with the camshaft (2) of the internal combustion engine and receives a pressure of the hydraulic fluid in the housing rotor to change a rotational phase with respect to the housing rotor;
The rotation phase for closing the intake valve at a timing later than the piston (8) in the cylinder reaches bottom dead center is defined as a main lock phase (Pm), and the main lock phase is set when the internal combustion engine is started. Main locking means (16) for locking the rotational phase reaching
Sub-lock means (17) for locking the rotation phase when the rotation phase advanced from the main lock phase is set to the sub-lock phase (Ps) and changing to the sub-lock phase when the internal combustion engine is started. When,
Lock control means (18) for controlling the operation of the main lock means and the sub lock means,
The main lock means is
A main lock member (160) supported by the vane rotor and reciprocally moved;
A movable member (164) supported by the housing rotor and forming a main lock hole (162), wherein the lock position at which the lock at the main lock phase is achieved by fitting the main lock member into the main lock hole (Ll) and a movable member that reciprocates to an allowable position (Lp) that allows the sub-locking means to lock in the sub-lock phase while maintaining the fitting,
Have
The lock control means includes
The movable member is held at the locked position during a warm start at a temperature equal to or higher than the set temperature (Ts) of the internal combustion engine, while the movable member is moved to the allowable position at a cold start at a temperature lower than the set temperature of the internal combustion engine. The valve timing adjusting device characterized by permitting driving of the valve. The lock control means includes
2. The valve timing adjustment according to claim 1, further comprising: a pressing member (182) that presses the movable member toward the lock position during the warm start and relieves the press during the cold start. apparatus. The lock control means includes
A control chamber (183) for controlling the pressing of the movable member by the pressing member according to the amount of the hydraulic fluid introduced into the interior, wherein the amount of introduction becomes a predetermined lock amount (Ql). In addition, the pressing for holding the movable member at the lock position is performed, and the movable member is driven to the allowable position when the introduction amount is an allowable amount (Qp) smaller than the lock amount. A control room to relieve the pressure for
The control valve (60) for controlling the introduction amount to the lock amount during the warm start, and controlling the introduction amount to the permissible amount during the cold start. The valve timing adjusting device described. The hydraulic fluid is supplied from a supply source (4) driven by the internal combustion engine,
The valve timing adjusting device according to claim 3, wherein the control valve holds the introduction amount at the lock amount as the internal combustion engine stops. The sub-locking means is
A sub-lock member (170) supported by one of the vane rotor and the housing rotor and reciprocating;
5. A sub-lock hole (172) formed on the other of the housing rotor and the vane rotor and configured to achieve locking at the sub-lock phase by fitting of the sub-lock member. The valve timing adjusting device according to any one of the above. The main lock means is
An allowable elastic member (166) for biasing the movable member toward the allowable position by generating a restoring force;
A stopper (165b) for locking the movable member at the allowable position,
6. The valve timing according to claim 5, wherein the main lock member is withdrawn from the main lock hole and the sub-lock member is withdrawn from the sub-lock hole during normal operation after the internal combustion engine is started. Adjustment device.   The advance elastic member (19) for urging the vane rotor toward the advance side with respect to the housing rotor in the rotation phase between the main lock phase and the sub lock phase. The valve timing adjustment apparatus as described in any one of -6.

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