JP2010261311A - Variable valve system for internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable valve system for an internal combustion engine, reducing the degree of the variance of learning values of valve timing due to the clearance of a phase fixing mechanism. <P>SOLUTION: The variable valve system includes: a valve timing variable mechanism 40 for changing the valve timing VT of an intake valve; a phase fixing mechanism 50 for fixing the valve timing VT at a middle angle VTmdl; and a learning means for setting as the learning value for the middle angle VTmdl the valve timing VT calculated based on a sensor output in a state with the valve timing VT fixed by the phase fixing mechanism 50. In the case where the valve timing VT is fixed by the phase fixing mechanism 50 during the drive of the valve timing variable mechanism 40 based on an advance angle command of the valve timing VT, the valve timing VT calculated based on the sensor output is set as a learning value VTG. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  In the present invention, a variable valve mechanism that changes the valve timing of an intake valve or an exhaust valve as an engine valve, a phase fixing mechanism that fixes the valve timing to a specific angle, and valve timing is fixed by the phase fixing mechanism. The present invention relates to a variable valve operating apparatus for an internal combustion engine comprising learning means for setting a valve timing calculated based on a sensor output under a state as a learning value for a specific angle.

  In the above variable valve operating apparatus, the relative rotation phase between the input side rotating body and the output side rotating body is fixed to a predetermined phase by fitting the lock pin into the lock hole when the engine operation is stopped. The timing is fixed at an intermediate angle corresponding to this phase. As a result, since the valve timing is fixed at the intermediate angle at the next engine start, the internal combustion engine can be started with good startability (see Patent Document 1).

JP 2001-159330 A

  By the way, the relative rotational phase between the input side rotating body and the output side rotating body when the valve timing is fixed at the intermediate angle differs depending on the valve timing variable mechanism due to dimensional tolerances, etc. It can be said that it is desirable to learn the intermediate angle of the valve timing in order to fit the lock hole appropriately.

  On the other hand, even when the lock pin is fitted in the lock hole, it has been confirmed that the valve timing slightly fluctuates due to the clearance formed between the outer peripheral surface of the lock pin and the wall surface of the lock hole. For this reason, even if the intermediate timing of the valve timing is learned, the learning value of the intermediate angle obtained by each learning varies, and the valve timing is fixed to the intermediate angle by reflecting the learning value. There is a concern that it may lead to a decrease in stability of control.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide an internal combustion engine that can reduce the degree of variation in the learning value of the valve timing caused by the clearance of the phase locking mechanism. The object is to provide a variable valve gear.

In the following, means for achieving the above object and its effects are described.
(1) The invention according to claim 1 is a variable valve mechanism for changing a valve timing of an intake valve or an exhaust valve as an engine valve, a phase locking mechanism for fixing the valve timing to a specific angle, and this phase locking. In a variable valve operating apparatus for an internal combustion engine, comprising learning means for setting the valve timing calculated based on a sensor output under a state where the valve timing is fixed by a mechanism as a learning value for the specific angle. The learning means calculates the valve timing calculated based on the sensor output when the variable valve mechanism is driven based on the valve timing advance command and the valve timing is fixed by the phase fixing mechanism. Is set as the learning value.

  When the variable valve mechanism is being driven based on the valve timing advance command, and when the change in valve timing is stagnant, the variable valve mechanism is in a state of being driven to advance, but the operation of the mechanism is phase-locked. The state is fixed by the mechanism, and the clearance on the advance side of the phase fixing mechanism is filled. In the above invention, since the valve timing calculated based on the sensor output under such a state is set as the learning value, the variation in the learning value of the valve timing caused by the clearance of the phase locking mechanism is The degree can be reduced. It should be noted that, during the driving of the variable valve mechanism based on the advance angle command, the actual valve timing is changed to the advance side by the drive of the variable valve mechanism, and the valve timing is Both of the states in which the actual valve timing does not change to the advance side are included although the drive state is to advance.

  (2) The invention according to claim 2 is the variable valve operating apparatus for the internal combustion engine according to claim 1, wherein the learning means has a fixing request which is a request to fix the valve timing to the specific angle. After the advance angle command is transmitted based on the setting, the learning is performed while the variable valve mechanism is being driven based on the advance angle command and the valve timing is fixed by the phase fixing mechanism. The gist is to set the value.

  According to the present invention, since the learning value is set when the valve timing is changed based on the fixed request, it is avoided to change the valve timing only for the learning value setting. Will be able to.

  (3) The invention according to claim 3 is the variable valve operating apparatus for an internal combustion engine according to claim 1 or 2, wherein the learning means is a request for fixing the valve timing to the specific angle. When the valve timing is on the advance side with respect to the specific angle at the time when the request is set, the valve timing is changed to the retard side with respect to the specific angle, and the variable motion based on the advance angle command thereafter. The gist is that the learning value is set while the valve mechanism is being driven and when the valve timing is fixed by the phase fixing mechanism.

  According to the present invention, since the learning value is set when the valve timing is changed based on the fixed request, it is avoided to change the valve timing only for the learning value setting. Will be able to.

  (4) The invention according to claim 4 is a variable valve mechanism for changing a valve timing of an intake valve or an exhaust valve as an engine valve, a phase fixing mechanism for fixing the valve timing to a specific angle, and this phase fixing. In a variable valve operating apparatus for an internal combustion engine, comprising learning means for setting the valve timing calculated based on a sensor output under a state where the valve timing is fixed by a mechanism as a learning value for the specific angle. The learning means calculates the valve timing calculated based on the sensor output when the variable valve mechanism is being driven based on the valve timing retardation command and the valve timing is fixed by the phase fixing mechanism. Is set as the learning value.

  When the variable valve mechanism is being driven based on the valve timing retard command, and when the change in valve timing is stagnant, the variable valve mechanism is in a state of attempting to drive to the retard side, but the operation of the mechanism is phase locked. The state is fixed by the mechanism, and the retard angle side clearance of the phase fixing mechanism is filled. In the above invention, since the valve timing calculated based on the sensor output under such a state is set as the learning value, the variation in the learning value of the valve timing caused by the clearance of the phase locking mechanism is The degree can be reduced. It should be noted that “during the operation of the variable valve mechanism based on the retard angle command” means that the actual valve timing is changed to the retard side due to the drive of the variable valve mechanism, and the variable valve mechanism is the valve timing Both of the states in which the actual valve timing does not change to the retard side are included although the drive state is to retard the angle.

  (5) The invention according to claim 5 is the variable valve operating apparatus for the internal combustion engine according to claim 4, wherein the learning means has a fixing request which is a request to fix the valve timing to the specific angle. The learning is performed when the variable valve mechanism based on the retard command is being driven and the valve timing is fixed by the phase fixing mechanism after the retard command is transmitted based on the setting. The gist is to set the value.

  According to the present invention, since the learning value is set when the valve timing is changed based on the fixed request, it is avoided to change the valve timing only for the learning value setting. Will be able to.

  (6) The invention according to claim 6 is the variable valve operating apparatus for the internal combustion engine according to claim 4 or 5, wherein the learning means is a request for fixing the valve timing to the specific angle. When the valve timing is on the retard side with respect to the specific angle at the time when the request is set, the valve timing is changed to the advance side with respect to the specific angle, and the variable motion based on the retard command thereafter. The gist is that the learning value is set while the valve mechanism is being driven and when the valve timing is fixed by the phase fixing mechanism.

  According to the present invention, since the learning value is set when the valve timing is changed based on the fixed request, it is avoided to change the valve timing only for the learning value setting. Will be able to.

  (7) The invention according to claim 7 is the variable valve operating apparatus for an internal combustion engine according to any one of claims 1 to 6, wherein when there is a request to increase the engine rotational speed, the phase locking mechanism is used. The gist is that fixing the valve timing to the specific angle is prohibited.

  When a request to increase the engine speed occurs after the valve timing is fixed by the phase fixing mechanism, and when a request to change the valve timing is generated at the same time, it is necessary to first unlock the valve timing. . For this reason, there is a concern that the responsiveness to the valve timing change request may be lowered. In view of this point, the above invention prohibits the fixing of the valve timing when there is a request to increase the engine rotation speed, so that the above-described deterioration in responsiveness can be accurately suppressed. Become.

  (8) The invention according to claim 8 is a variable valve mechanism for changing a valve timing of an intake valve or an exhaust valve as an engine valve, a phase fixing mechanism for fixing the valve timing to a specific angle, and this phase fixing. Learning means for setting, as a learning value, the valve timing calculated based on a sensor output in a state where the valve timing is fixed by a mechanism, and the variable valve mechanism is transmitted from a crankshaft. An input-side rotating body that rotates by force and an output-side rotating body that rotates together with the camshaft of the engine valve by the force transmitted from the input-side rotating body. An advance chamber and a retard chamber that are partitioned from each other are formed between the bodies, and the phase fixing mechanism includes the input-side rotating body and the input-side rotating body. A restricting body that is provided on an accommodation-side rotating body that is one of the force-side rotating bodies and that operates between a protruding position that protrudes from the containing-side rotating body and an accommodation position that is accommodated in the containing-side rotating body; In the variable valve operating apparatus for an internal combustion engine, including a restriction hole provided in an engagement-side rotator which is the other of the side rotator and the output-side rotator and into which the restrictor is fitted. The gist of the invention is that the valve timing calculated based on the sensor output is set as the learning value when the regulating body in the protruding position is pressed against the wall surface on the advance side of the regulating hole. Yes.

  According to this invention, when the regulating body is pressed against the wall on the advance side of the regulation hole, that is, when the clearance on the advance side of the phase fixing mechanism is filled, it is based on the sensor output. Since the valve timing calculated in this way is set as the learning value, the degree of variation in the learning value of the valve timing caused by the clearance of the phase locking mechanism can be reduced.

  (9) The invention according to claim 9 is the variable valve operating apparatus for an internal combustion engine according to claim 8, wherein the phase locking mechanism is configured such that a part of the regulating body at the protruding position is fitted into the regulating hole. The valve timing is fixed at the specific angle, and the valve timing is released when a part of the restricting body at the housing position is detached from the restricting hole. The gist is that the regulating body is pressed against the wall on the advance side of the regulation hole by driving the variable valve mechanism based on the advance timing command of the valve timing when the body is in the protruding position. .

  (10) The invention according to claim 10 is a variable valve mechanism for changing a valve timing of an intake valve or an exhaust valve as an engine valve, a phase fixing mechanism for fixing the valve timing to a specific angle, and this phase fixing. Learning means for setting, as a learning value, the valve timing calculated based on a sensor output in a state where the valve timing is fixed by a mechanism, and the variable valve mechanism is transmitted from a crankshaft. An input-side rotating body that rotates by force and an output-side rotating body that rotates together with the camshaft of the engine valve by the force transmitted from the input-side rotating body. An advance chamber and a retard chamber are formed between the bodies, and the phase fixing mechanism includes the input side rotating body and A regulating body that is provided on the accommodation-side rotator that is one of the output-side rotators and operates between a protruding position that protrudes from the accommodation-side rotator and an accommodation position that is accommodated in the accommodation-side rotator, and In the variable valve operating apparatus for an internal combustion engine, including a restriction hole provided in an engagement-side rotator that is the other of the input-side rotator and the output-side rotator, and into which the restrictor is fitted. The valve timing calculated based on the sensor output is set as the learning value when the regulating body at the protruding position is pressed against the wall surface on the retard side of the regulating hole. It is said.

  According to the present invention, when the restricting body is pressed against the retarding wall surface of the restricting hole, that is, when the retarding side clearance of the phase locking mechanism is filled, the sensor output is used. Since the valve timing calculated in this way is set as the learning value, the degree of variation in the learning value of the valve timing caused by the clearance of the phase locking mechanism can be reduced.

  (11) The invention according to claim 11 is the variable valve operating apparatus for the internal combustion engine according to claim 10, wherein the phase locking mechanism is configured such that a part of the regulating body at the protruding position is fitted into the regulating hole. The valve timing is fixed at the specific angle, and the valve timing is released when a part of the restricting body at the housing position is detached from the restricting hole. The gist is that the regulating body is pressed against the wall surface on the retarding side of the regulating hole by driving the variable valve mechanism based on the retarding command of the valve timing when the body is in the protruding position. Yes.

  (12) A twelfth aspect of the present invention is the variable valve operating apparatus for an internal combustion engine according to any one of the eighth to eleventh aspects, wherein the phase fixing mechanism is provided on the housing-side rotating body and operates. It is configured to include a fixed chamber in which the oil supply / discharge state is operated, and the relative rotation phase between the input-side rotator and the output-side rotator is a specific phase corresponding to the specific angle. And when the hydraulic oil supply / discharge state with respect to the fixed chamber is set to the first supply / discharge state, the restricting body is held at the protruding position, and the relative relationship between the input-side rotating body and the output-side rotating body is When the specific rotational phase is at the specific phase and the hydraulic oil supply / discharge state with respect to the fixed chamber is set to the second supply / discharge state, the restricting body is held in the storage position. It is a summary.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view schematically showing a configuration of an internal combustion engine provided with the device according to a first embodiment that embodies a variable valve operating device for an internal combustion engine of the present invention. Regarding the variable valve timing mechanism of the embodiment, (A) is a plan view showing the planar structure, (B) is a sectional view showing a sectional structure along the line DD in FIG. 2 (A), and (C) is a diagram. Sectional drawing which shows what expanded the cross-sectional structure in alignment with the EE line | wire of 2 (A) on the plane. The schematic diagram which shows typically the structure of the lubricating oil path between these about the lubricating device and valve timing variable mechanism of the embodiment. Regarding the variable valve timing mechanism of the embodiment, (A) shows the relationship between the operation mode of the first oil control valve and the lubricating oil supply / discharge state of the advance chamber and retard chamber, and (B) shows the second oil control valve. (C) is a table showing the relationship between the operation mode of each valve and the operation of the variable valve timing mechanism. FIG. 3 is a schematic view schematically showing the sectional structure of the housing and the vane rotor along the line EE in FIG. 2A on the flat surface of the variable valve timing mechanism of the same embodiment. FIG. 3 is a schematic view schematically showing the sectional structure of the housing and the vane rotor along the line EE in FIG. 2A on the flat surface of the variable valve timing mechanism of the same embodiment. The enlarged view which shows the relationship between a lock pin and a lock hole about the valve timing variable mechanism of the embodiment. FIG. 3 is a schematic view schematically showing the sectional structure of the housing and the vane rotor along the line EE in FIG. 2A on the flat surface of the variable valve timing mechanism of the same embodiment. The flowchart which shows the process sequence about the "phase fixing process" performed by the electronic controller of the embodiment. In the variable valve timing mechanism according to the second embodiment that embodies the variable valve operating apparatus for an internal combustion engine of the present invention, the sectional structure of the housing and the vane rotor along the line EE in FIG. The schematic diagram which shows this typically. The flowchart which shows the process sequence about the "phase fixing process" performed by the electronic controller of the embodiment. (A) shows the operation mode of the third oil control valve and the lubrication oil supply / discharge states of the advance chamber, the retard chamber, and the intermediate chamber according to the third embodiment of the variable valve device for the internal combustion engine of the present invention. (B) is a table showing the relationship between the operation mode of the third oil control valve and the operation of the variable valve timing mechanism. The figure which shows the summary of the learning aspect of 1st Embodiment of this invention, and the learning aspect of other embodiment. The figure which shows the summary of the learning aspect of 2nd Embodiment of this invention, and the learning aspect of other embodiment.

(First embodiment)
With reference to FIGS. 1 to 9, a variable valve operating apparatus for an internal combustion engine according to the present invention will be described as a first embodiment which is embodied as a variable valve operating apparatus for changing the valve timing of an intake valve.

  As shown in FIG. 1, the engine 10 includes an engine body 20 that obtains power through combustion of a mixture of intake air and fuel, a variable valve timing mechanism 40 that changes the valve timing of the intake valve 31, an engine body 20 and A lubricating device 60 for supplying lubricating oil to the variable valve timing mechanism 40 and an electronic control device 80 for controlling these devices in an integrated manner are provided.

  The engine body 20 is provided with a cylinder block 21 that burns an air-fuel mixture of the fuel supplied through the injector 27 and the intake air supplied through the intake device in the combustion chamber 23. The cylinder block 21 is provided with a cylinder 24 that forms a combustion chamber 23, a piston 25 that reciprocates within the cylinder 24, and a crankshaft 26 that rotates with the reciprocation of the piston 25.

  An oil pan 61 that stores lubricating oil supplied to each part of the engine 10 is attached to the lower portion of the cylinder block 21. Further, a cylinder head 22 on which valve-operated parts are arranged is attached to the upper part of the cylinder block 21.

  The cylinder head 22 is provided with an intake valve 31 that opens and closes the combustion chamber 23 with respect to the intake port, and an exhaust valve 33 that opens and closes the combustion chamber 23 with respect to the exhaust port. An intake camshaft 32 is provided above the intake valve 31 to push it down by the intake cam. Further, an exhaust camshaft 34 is provided above the exhaust valve 33 to push it down by the exhaust cam.

  The lubricating device 60 supplies the lubricating oil in the oil pan 61 to each lubricating portion of the engine body 20 through the lubricating oil passage 70. An oil pump 62 that pumps up the lubricating oil from the oil pan 61 and discharges it is provided in the middle of the lubricating oil passage 70. The lubricating oil discharged by the oil pump 62 passes through the lubricating oil passage 70 and is supplied to each part of the engine 10, and a part of the lubricating oil is valve timingd via the first oil control valve 63 or the second oil control valve 64. The variable mechanism 40 is supplied. The lubricating oil after flowing through each part of the engine 10 and the lubricating oil discharged from the variable valve timing mechanism 40 are returned to the oil pan 61 again. In the present embodiment, a variable valve operating device is configured including the variable valve timing mechanism 40, the lubricating device 60, and the electronic control device 80.

  The electronic control unit 80 grasps the engine operating state, the vehicle running state, and the driver's request based on signals from various sensors such as the crank position sensor 81 and the cam position sensor 82, and then performs the following control. Various controls are performed. That is, the valve timing of the intake valve 31 (hereinafter referred to as “throttle control” for adjusting the intake flow rate by the throttle valve, injection control for adjusting the fuel injection amount of the injector 27, and control of the first oil control valve 63 and the second oil control valve 64). , “Valve timing VT”) for adjusting various kinds of control such as valve timing control.

  The crank position sensor 81 outputs a signal corresponding to the rotation angle of the crankshaft 26. The cam position sensor 82 outputs a signal corresponding to the rotation angle of the intake camshaft 32.

  In the valve timing control, a target value of the valve timing VT (hereinafter referred to as “target valve timing VTT”) is set based on the engine operating state (engine rotational speed NE and engine load EL), and the crank position sensor 81 and the cam position sensor. The oil control valve 63 is operated so that the valve timing VT calculated based on the output of 82 matches the target valve timing VTT.

  The configuration of the variable valve timing mechanism 40 will be described with reference to FIG. 2A shows a planar structure of the variable mechanism 40 in a state where the cover 44 shown in FIG. 2B is removed from the housing main body 42. FIG. The rotation direction of the intake camshaft 32 and the sprocket 43 is defined as a rotation direction X. The intake camshaft 32 always rotates in this rotational direction X.

  As shown in FIG. 2A, the variable valve timing mechanism 40 is synchronized with the housing rotor 41 that rotates in synchronization with the crankshaft 26 and the end of the intake camshaft 32 to synchronize with the shaft 32. And a rotating vane rotor 45.

  The housing rotor 41 is connected to the crankshaft 26 so as to rotate in synchronization with the shaft 26, and the housing main body 42 that is assembled inside the sprocket 43 and rotates together with the sprocket 43. , And a cover 44 attached to the main body 42.

The vane rotor 45 is disposed in a space in the housing main body 42 and is accommodated in a space formed by the main body 42 and the cover 44.
The housing body 42 is provided with three partition walls 41A that protrude toward the vane rotor 45 in the radial direction. The vane rotor 45 is provided with three vanes 46 that project toward the housing body 42 and divide the three vane 46 accommodating chambers between the partition walls 41A into an advance chamber 47 and a retard chamber 48, respectively.

  The advance chamber 47 is located behind the vane 46 in the rotational direction X of the intake camshaft 32 in one vane 46 housing chamber, and the lubrication device 60 supplies lubricating oil to the variable valve timing mechanism 40. The volume changes according to The retarding chamber 48 is located in front of the vane 46 in the rotational direction X of the intake camshaft 32 in one vane 46 housing chamber, and the valve timing variable mechanism 40 by the lubricating device 60 is the same as the advance chamber 47. The volume changes according to the supply state of the lubricating oil to the.

  The variable valve timing mechanism 40 changes the valve timing VT by changing the relative rotation phase of the vane rotor 45 with respect to the housing rotor 41 (hereinafter referred to as “rotation phase P”) based on the above configuration. The change of the valve timing VT by the variable mechanism 40 is specifically performed as follows.

  When the vane rotor 45 rotates with respect to the housing rotor 41 in the advance side, that is, in the rotational direction X of the intake camshaft 32 by supplying the lubricant oil to the advance chamber 47 and discharging the lubricant oil from the retard chamber 48, the valve The timing VT changes to the advance side. When the vane rotor 45 rotates to the maximum advance side with respect to the housing rotor 41, that is, when the rotation phase P of the vane rotor 45 is at the most forward phase in the rotation direction X (hereinafter, “most advanced angle phase PH”). The valve timing VT is set to the most advanced timing (hereinafter, “most advanced angle VTmax”). As the most advanced angle phase PH, a position where the vane 46 abuts against the partition wall 41A on the retard chamber 48 side or a position where the vane 46 is near the partition wall 41A on the retard chamber 48 side is set.

  By discharging the lubricating oil from the advance chamber 47 and supplying the lubricant oil to the retard chamber 48, the vane rotor 45 rotates to the retard side, that is, the rear side in the rotational direction X of the intake camshaft 32 with respect to the housing rotor 41. The valve timing VT changes to the retard side. When the vane rotor 45 rotates to the maximally retarded side with respect to the housing rotor 41, that is, the rotational phase P of the vane rotor 45 is at the most rearward phase in the rotational direction X (hereinafter, “most retarded phase PL”). The valve timing VT is set to the most retarded timing (hereinafter, “most retarded angle VTmin”). Here, the position at which the vane 46 abuts against the partition wall 41A on the advance chamber 47 side or the position where the vane 46 is near the partition wall 41A on the advance chamber 47 side is set as the most retarded phase PL.

  The variable valve timing mechanism 40 regulates the rotation of the vane rotor 45 with respect to the housing rotor 41 regardless of the hydraulic pressure of the advance chamber 47 and the retard chamber 48 so that the valve timing VT is set to the most advanced angle VTmax and the most retarded angle VTmin. Is provided with a phase locking mechanism 50 for locking at a specific timing (hereinafter referred to as “intermediate angle VTmdl”). A timing suitable for starting the engine 10 is set as the intermediate angle VTmdl. That is, when comparing the case where the valve timing VT is set to the intermediate angle VTmdl and the case where the valve timing is set to the timing on the retard side at the time of starting the engine, the former seems to ensure higher startability. become.

  The details of the structure of the phase locking mechanism 50 will be described with reference to FIGS. 2 (B) and 2 (C). 2B is a sectional structure of the variable valve timing mechanism 40 along the line DD in FIG. 3A, and FIG. 2C is the same as the line EE in FIG. 3A. The cross-sectional structure of the variable mechanism 40 developed on a plane is shown.

  The phase fixing mechanism 50 operates based on the supply of lubricating oil from the lubricating device 60, and when the rotational phase P is at a rotational phase corresponding to the intermediate angle VTmdl (hereinafter referred to as "intermediate phase PM"), the housing rotor 41 The relative rotation phase between the rotor and the vane rotor 45 is fixed, and the valve timing VT is held at the intermediate angle VTmdl.

  Specifically, the phase locking mechanism 50 includes a lock pin 51 provided on the vane 46, an intermediate chamber 52 provided on the vane 46 and supplied with lubricating oil by the lubricating device 60, and a lock pin provided on the vane 46. A lock spring 53 that pushes 51 in one direction and a lock hole 54 provided in the housing rotor 41 are configured.

  Based on the relationship between the force of the lubricating oil in the intermediate chamber 52 and the force of the lock spring 53, the lock pin 51 protrudes from the vane 46 (hereinafter referred to as “projection direction ZA”) and retracted into the vane 46 (hereinafter referred to as “removal direction ZA”) , “Accommodating direction ZB”). The hydraulic pressure in the intermediate chamber 52 acts on the lock pin 51 in the accommodating direction ZB, and the force of the lock spring 53 acts on the lock pin 51 in the protruding direction ZA. Hereinafter, with respect to the position of the lock pin 51, a position protruding from the vane 46 and fitted into the lock hole 54 is referred to as a “projecting position”, and a position retracted into the vane 46 and accommodated in the vane 46 is referred to as an “accommodating position”. .

  The lock groove 55 is formed as a groove having a depth smaller than that of the lock hole 54 and along the locus in the circumferential direction of the lock pin 51 from the lock hole 54 to a predetermined position on the retard side. . That is, under the relationship with the rotational phase P of the vane rotor 45, from the intermediate phase PM to a predetermined phase between the intermediate phase PM and the most retarded phase PL (hereinafter, “retard angle phase PML”). Is formed over.

  When the lubricating oil is supplied to the intermediate chamber 52 by the lubricating device 60 and the intermediate chamber 52 is filled with the lubricating oil, that is, the supply / discharge state of the lubricant to / from the intermediate chamber 52 is the “second supply / discharge state”. At this time, due to the force in the housing direction ZB due to the lubricating oil in the intermediate chamber 52, a force for moving the lock pin 51 in the housing direction ZB is generated. When the force in the accommodation direction ZB acts on the lock pin 51 under the protruding position of the lock pin 51, the lock pin 51 is detached from the lock hole 54 and accommodated in the vane 46. Thereby, the fixing of the housing rotor 41 and the vane rotor 45 by the engagement of the lock pin 51 and the lock hole 54 is released, and the rotation of the vane rotor 45 with respect to the housing rotor 41 is allowed.

  On the other hand, when the lubricating oil is discharged from the intermediate chamber 52 by the lubricating device 60 and the intermediate chamber 52 is not filled with the lubricating oil, that is, when the lubricating oil supply / discharge state with respect to the intermediate chamber 52 is in the “first supply / discharge state”. The force in the protruding direction ZA by the lock spring 53 exceeds the force in the housing direction ZB by the lubricating oil in the intermediate chamber 52. As a result, a force for moving the lock pin 51 in the protruding direction ZA is generated. Under this state, when the rotational phase P is at the intermediate phase PM, that is, when the circumferential positions of the lock pin 51 and the lock hole 54 coincide with each other, the lock pin 51 protrudes from the vane 46 and locks. It fits into the hole 54. As a result, the housing rotor 41 and the vane rotor 45 are fixed to each other through the engagement between the lock pin 51 and the lock hole 54, so that their relative rotational phases are maintained at the intermediate phase PM.

  Also, the lubricating oil is discharged from the intermediate chamber 52 by the lubricating device 60 so that the intermediate chamber 52 is not filled with the lubricating oil, and the rotational phase P of the vane rotor 45 is on the retard side with respect to the retard phase PML. Originally, when the rotational phase P reaches the retarded phase PML by driving the vane rotor 45 toward the advance side, the tip of the lock pin 51 is fitted into the lock groove 55. In this state, when the vane rotor 45 is further driven to the advance side, the lock pin 51 moves on the lock groove 55 toward the lock hole 54, and the rotational phase P of the vane rotor 45 reaches the intermediate phase PM. Sometimes the lock pin 51 is fitted in the lock hole 54.

  With reference to FIG. 3, the lubricating oil distribution structure between the lubricating device 60 and the variable valve timing mechanism 40 will be described. In addition, the figure has shown typically the structure of the oil path between these apparatuses.

  The variable valve timing mechanism 40 includes three hydraulic chambers, that is, a plurality of advance chambers 47 and a plurality of advance chambers 47 in which the supply and discharge states of the lubricating oil are switched by the first oil control valve 63 and the second oil control valve 64, respectively. A retardation chamber 48 and an intermediate chamber 52 are provided.

  The lubricating device 60 includes an oil pan 61 that stores lubricating oil, an oil pump 62 that pumps up and discharges the lubricating oil in the oil pan 61, each oil control valve 63 that switches the flow path of the lubricating oil, and a variable valve timing mechanism 40. And a lubricating oil passage 70 for supplying lubricating oil to the engine body 20.

  The lubricating oil passage 70 includes a supply oil passage 71, a discharge oil passage 72, an advance chamber oil passage 73, a retard chamber oil passage 74, and an intermediate chamber oil passage 75. The supply oil passage 71 supplies lubricating oil from the oil pump 62 to each of the oil control valves 63 and 64. The drain oil passage 72 circulates the lubricating oil from the oil control valves 63 and 64 to the oil pan 61. The advance chamber oil passage 73 circulates lubricating oil between the first oil control valve 63 and each advance chamber 47. The retard chamber oil passage 74 circulates lubricating oil between the first oil control valve 63 and each retard chamber 48. The intermediate chamber oil passage 75 circulates lubricating oil between the second oil control valve 64 and the intermediate chamber 52.

  The advance chamber oil passage 73 and the retard chamber oil passage 74 directly connect the first oil control valve 63 and the advance chamber 47 and the retard chamber 48, respectively. The intermediate chamber oil passage 75 directly connects the second oil control valve 64 and the intermediate chamber 52. That is, the first oil control valve 63 and the second oil control valve 64 are each configured as a valve that independently controls the supply / discharge state of the lubricating oil in the corresponding hydraulic chamber.

  Referring to FIG. 4, the relationship between the operation mode of first oil control valve 63 and the supply / discharge state of lubricating oil in advance chamber 47 and retard chamber 48 (FIG. 4A), second oil control valve The relationship between the 64 operation modes and the supply / discharge state of the lubricating oil in the intermediate chamber 52 (FIG. 4B), the operation modes and the variable valve timing mechanism 40 (denoted as VVT in the drawing), and the lock pin 51 The relationship with the operation mode (FIG. 4C) will be described.

  The first oil control valve 63 changes its own operation mode to the operation mode A1 by changing the position of the spool 63B relative to the sleeve 63A (hereinafter, “control position of the spool 63B”) to any one of the control position A1 to the control position A3. The operation mode A3 is set to a corresponding one, thereby switching the connection state between the supply oil passage 71 and the discharge oil passage 72, the advance chamber oil passage 73, and the retard chamber oil passage 74. The control position of the spool 63B is changed in the order of the control position A1 to the control position A3 as the spool 63B moves from one side to the other side with respect to the sleeve 63A. The following (A) to (C) show the operation of the variable valve timing mechanism 40 in each control mode.

  (A) When the control position of the spool 63B is at the control position A1, the operation mode of the first oil control valve 63 is set to the operation mode A1. At this time, the advance chamber oil passage 73 and the supply oil passage 71 are connected, and the retard chamber oil passage 74 and the discharge oil passage 72 are connected. Thereby, the lubricating oil from the oil pump 62 flows in the order of the supply oil passage 71 and the advance chamber oil passage 73 and is supplied to the advance chamber 47. Further, the lubricating oil in the retarding chamber 48 flows in the order of the retarding chamber oil passage 74 and the discharge oil passage 72 and is returned to the oil pan 61. In this operation mode A1, the variable valve timing mechanism 40 is maintained in a state of attempting to change the rotational phase P of the vane rotor 45 to the advance side.

  (B) When the control position of the spool 63B is at the control position A2, the operation mode of the first oil control valve 63 is set to the operation mode A2. At this time, the advance chamber oil passage 73 is disconnected from the supply oil passage 71 and the discharge oil passage 72. Thereby, the flow of the lubricating oil from the oil pump 62 to the advance chamber 47 via the first oil control valve 63 and the lubrication to the oil pan 61 from the advance chamber 47 via the first oil control valve 63. Any oil flow is blocked. Also, the flow of lubricating oil from the oil pump 62 to the retarding chamber 48 via the first oil control valve 63 and the lubricating oil to the oil pan 61 from the retarding chamber 48 via the first oil control valve 63. Any flow is interrupted. In this operation mode A2, the variable valve timing mechanism 40 is maintained in a state in which the rotational phase P of the vane rotor 45 is maintained.

  (C) When the control position of the spool 63B is at the control position A3, the operation mode of the first oil control valve 63 is set to the operation mode A3. At this time, the advance chamber oil passage 73 and the discharge oil passage 72 are connected, and the retard chamber oil passage 74 and the supply oil passage 71 are connected. As a result, the lubricating oil in the advance chamber 47 flows in the order of the advance chamber oil passage 73 and the discharge oil passage 72 and is returned to the oil pan 61. Further, the lubricating oil from the oil pump 62 flows in the order of the supply oil passage 71 and the retard chamber oil passage 74 and is supplied to the retard chamber 48. In this operation mode A3, the variable valve timing mechanism 40 is maintained in a state of attempting to change the rotational phase P of the vane rotor 45 to the retard side.

  The second oil control valve 64 changes its own operation mode to the operation mode B1 by changing the position of the spool 64B relative to the sleeve 64A (hereinafter, “control position of the spool 64B”) to either the control position B1 or the control position B2. And the corresponding one of the operation modes B2, thereby switching the connection state of the supply oil passage 71, the discharge oil passage 72, and the intermediate chamber oil passage 75. The control position of the spool 64B is changed to either the control position B1 or the control position B2 as the spool 64B moves from one side to the other side with respect to the sleeve 64A. The following (A) and (B) show the operation of the variable valve timing mechanism 40 in each control mode.

  (A) When the control position of the spool 64B is at the control position B1, the operation mode of the second oil control valve 64 is set to the operation mode B1. At this time, the intermediate chamber oil passage 75 and the supply oil passage 71 are connected. Thereby, the lubricating oil from the oil pump 62 flows in the order of the supply oil passage 71 and the intermediate chamber oil passage 75 and is supplied to the intermediate chamber 52. In this operation mode B1, since the phase fixing mechanism 50 is in a state of trying to move the lock pin 51 to the accommodation position, the rotation phase P of the vane rotor 45 is in any phase regardless of the phase. The valve timing VT is not fixed at the intermediate angle VTmdl.

  (B) When the control position of the spool 64B is at the control position B2, the operation mode of the second oil control valve 64 is set to the operation mode B2. At this time, the intermediate chamber oil passage 75 and the discharge oil passage 72 are connected. As a result, the lubricating oil in the intermediate chamber 52 flows in the order of the intermediate chamber oil passage 75 and the discharge oil passage 72 and is returned to the oil pan 61. In this operation mode B2, since the phase fixing mechanism 50 is in a state of trying to move the lock pin 51 to the protruding position, the rotational phase P of the vane rotor 45 becomes the intermediate phase PM, so that the valve is passed through the mechanism 50. The timing VT is fixed to the intermediate angle VTmdl.

  A control mode of the variable valve timing mechanism 40 will be described with reference to FIGS. 5 and 6 schematically show a cross-sectional structure of the variable valve timing mechanism 40 taken along the line E-E in FIG. 2A on a plane.

  In the valve timing control, when the valve timing VT is changed between the most advanced angle VTmax and the most retarded angle VTmin, that is, the rotational phase P of the vane rotor 45 is shown from the most advanced angle phase PH shown in FIG. When the phase is changed up to the most retarded phase PL shown in FIG. 5 (B), the lock pin 51 is maintained in the accommodation position.

  Even when the valve timing VT is at the intermediate angle VTmdl, that is, when the rotational phase P of the vane rotor 45 is at the intermediate phase PM, the lock pin 51 is accommodated in the vane 46 as the lubricating oil is supplied to the intermediate chamber 52. As long as this is done, as shown in FIG. 5C, the rotational phase P is not fixed to the intermediate phase PM. When a force in the protruding direction ZA is applied to the lock pin 51 as the lubricating oil is discharged from the intermediate chamber 52, the lock pin 51 is driven by the force of the lock spring 53 as shown in FIG. Protrudes from the vane 46 and is fitted into the lock hole 54, whereby the vane rotor 45 is held at the intermediate phase PM.

  On the other hand, as shown in FIG. 6A, the valve timing VT is on the retard side with respect to the intermediate angle VTmdl, and in the protruding direction ZA with respect to the lock pin 51 as the lubricating oil is discharged from the intermediate chamber 52. When the lock pin 51 is moved to a position corresponding to the lock groove 55 by driving the vane rotor 45 toward the advance side in the state where the force is applied, the lock pin 51 protrudes from the vane 46 and the tip portion thereof is It is inserted into the lock groove 55. That is, as the rotational phase P of the vane rotor 45 changes from the rotational phase P shown in FIG. 6A to the rotational phase P shown in FIG. It is abutted against the bottom.

  With the tip of the lock pin 51 in the lock groove 55, the lock pin 51 also moves on the advance side as the vane rotor 45 continues to be advanced. When the rotational phase P of the vane rotor 45 reaches the intermediate phase PM as shown in FIG. 6C, the side surface of the lock pin 51 is abutted against the wall surface forming the lock hole 54, and the lock pin 51 is moved to the vane 46. Projecting to the maximum, and fitted into the lock hole 54.

With reference to FIG. 6, the manner in which the valve timing VT is fixed to the intermediate angle VTmdl by the phase fixing mechanism 50 when the engine is started will be described.
In order to ensure good engine startability through control of the variable valve timing mechanism 40, it is required that the valve timing VT is already held at the intermediate angle VTmdl when the start operation of the engine 10 is started. Therefore, in the engine 10, when an engine stop request accompanying an ignition switch switching operation occurs during engine operation, the valve timing VT is fixed by the phase fixing mechanism 50 in preparation for the next engine start. That is, the valve timing VT is fixed to the intermediate angle VTmdl by the phase fixing mechanism 50 before the operation of the engine 10 is stopped based on the engine stop request, and thereafter the operation of the engine 10 is stopped based on the engine stop request (hereinafter, referred to as the engine stop request). “Engine normal stop”).

  Furthermore, when the engine operation state shifts to the idle operation state, there is a high possibility that an engine stop request will be generated after that, so that the valve timing VT is fixed based on the presence of the idle operation request. In this case, when a request for shifting from the idle operation state to the normal engine operation state occurs, the fixing of the valve timing VT by the phase fixing mechanism 50 is released based on this request. On the other hand, when an engine stop (hereinafter referred to as “engine emergency stop”) that does not occur based on an ignition switch switching operation such as an engine stall occurs, the above-described valve timing VT before the engine normal stop is not fixed. Therefore, there is a problem of a decrease in startability at the next engine start.

  In this regard, according to the phase fixing mechanism 50 of the variable valve timing mechanism 40, the valve timing VT is fixed to the intermediate angle VTmdl as follows when the engine is started after the emergency stop of the engine.

  Here, as shown in FIG. 6 (A), when the engine 10 is started, the starting operation of the engine 10 is started in a state where the rotational phase of the vane rotor 45 is on the retarded side with respect to the intermediate phase PM due to the emergency stop of the engine. Suppose.

  In this case, when the lock pin 51 moves to a position corresponding to the lock groove 55 by the advance driving of the vane rotor 45 due to the fluctuation of the torque of the intake camshaft 32, the lock pin 51 protrudes from the vane 46 and The leading end is inserted into the lock groove 55. That is, as the rotational phase of the vane rotor 45 changes from the rotational phase shown in FIG. 6A to the rotational phase shown in FIG. 6B, the tip of the lock pin 51 strikes the bottom surface of the lock groove 55. Hit. Then, with the tip of the lock pin 51 in the lock groove 55, the lock pin 51 also moves on the advance side as the vane rotor 45 continues to be driven to the advance side. When the rotational phase P of 45 reaches the intermediate phase PM, the lock pin 51 protrudes to the maximum extent from the vane 46 and fits into the lock hole 54.

  By the way, the rotational phase P of the vane rotor 45 when the valve timing VT is fixed at the intermediate angle VTmdl, that is, the rotational phase P when the lock pin 51 is fitted into the lock hole 54 is variable due to dimensional tolerances or the like. Different for each mechanism 40.

  Therefore, in the valve timing control according to the present embodiment, the intermediate angle VTmdl calculated by each of the sensors 81 and 82 in a state where it is confirmed that the valve timing VT is fixed by the phase fixing mechanism 50 is used as the learning value VTG. And the learning value VTG is used to change the valve timing VT to the intermediate angle VTmdl.

  On the other hand, as shown in FIG. 7A, even when the lock pin 51 is fitted in the lock hole 54, the lock hole 51 and the outer peripheral surface of the lock pin 51 (hereinafter referred to as “pin outer peripheral surface 51F”) are formed. It has been confirmed that the rotational phase P of the vane rotor 45, that is, the valve timing VT slightly varies due to the clearance 56 formed between the wall surface (hereinafter referred to as “hole wall surface 54 </ b> F”).

  For example, in the first learning, as shown in FIG. 7B, the valve timing VT in a state where the advance side of the pin outer peripheral surface 51F is in contact with the hole wall surface 54F is set as the learning value VTG. 7C, the valve timing VT in a state where the retard side of the pin outer peripheral surface 51F is in contact with the hole wall surface 54F may be set as the learning value VTG. Furthermore, the learning value VTG of the valve timing VT is set at one of the position of the lock pin 51 shown in FIG. 7B and the position of the lock pin 51 shown in FIG. There is also.

  For this reason, even if learning of the intermediate angle VTmdl of the valve timing VT is performed, the learning value VTG of the intermediate angle VTmdl obtained by each learning varies, and the valve timing reflects the learning value VTG. There is concern that the stability of the control for fixing the VT to the intermediate angle VTmdl may be reduced. That is, in order to make the update mode of the learned value VTG for the intermediate angle VTmdl more stable, simply setting the valve timing VT with the lock pin 51 fitted in the lock hole 54 as the learned value VTG. It can be said that it is insufficient.

  Here, for example, as shown in FIG. 7A, the lock pin 51 is fitted in the lock hole 54 and a clearance 56 is formed between the advance side of the pin outer peripheral surface 51F and the hole wall surface 54F. Under the state, when the vane rotor 45 is driven to the advance side with respect to the housing rotor 41, the advance side of the pin outer peripheral surface 51F and the hole wall surface 54F come into contact with each other to fill the clearance 56 (see FIG. 7 (B)). In this state, the advance side of the pin outer peripheral surface 51F and the hole wall surface 54F are in contact with each other as long as the force to drive the vane rotor 45 toward the advance side with respect to the housing rotor 41 is continuously applied. The state will also be maintained.

  In the present embodiment, in view of the above, when the lock pin 51 is fitted in the lock hole 54 and the vane rotor 45 is continuously driven to the advance side with respect to the housing rotor 41 ( Hereinafter, the valve calculated based on the outputs of the sensors 81 and 82 when the lock pin 51 in the protruding position is pressed against the wall surface on the advance side of the lock hole 54. The timing VT (intermediate angle VTmdl) is set as the learning value VTG.

  As for the abutting state of the phase locking mechanism 50, when the variable valve timing mechanism 40 is driven based on the advance angle command and the change in the valve timing VT is stagnant, that is, the vane rotor 45 tries to drive to the advance angle side. When it is estimated that the operation of the mechanism is fixed by the phase fixing mechanism 50 even though it is in a state, it is determined that it is in the abutting state.

  Here, “being driven by the variable valve timing mechanism 40 based on the advance command” means that the vane rotor 45 is driven to the advance side with respect to the housing rotor 41 and the valve timing VT is changed to the advance side. The vane rotor 45 includes both the state in which the rotation phase P of the vane rotor 45 does not change to the advance side. In such a drive state of the variable valve timing mechanism 40, a command to maintain the operation mode A1 is transmitted to the first oil control valve 63 with the lock pin 51 fitted in the lock hole 54. It is realized by doing.

With reference to FIG. 8, the update mode of the learning value VTG described above will be described.
As shown in FIG. 8A, the valve timing VT is on the retard side with respect to the intermediate angle VTmdl, and a request to fix the valve timing VT to the intermediate angle VTmdl (hereinafter, “fixing request”) is set. At this time, the vane rotor 45 is driven to the advance side based on the fixing request. When the lock pin 51 is moved to a position corresponding to the lock groove 55 by driving the vane rotor 45, as shown in FIG. 8B, the lock pin 51 protrudes from the vane 46 and the tip portion is locked. It is inserted into the groove 55.

  As shown in FIG. 8C, when the rotational phase P of the vane rotor 45 reaches the intermediate phase PM, the lock pin 51 protrudes to the maximum extent from the vane 46 and is fitted into the lock hole 54. In this state, when the vane rotor 45 is driven further toward the advance side with respect to the housing rotor 41, the advance side of the pin outer peripheral surface 51F contacts the hole wall surface 54F as shown in FIG. The abutting state of the fixing mechanism 50 is maintained, and the change in the valve timing VT becomes stagnant. According to the valve timing control, the valve timing VT at this time is set as a new learning value VTG.

In order to realize the abutting state of the phase locking mechanism 50, the following (a) or (b) is given as an example of the transmission mode of the advance angle command for driving the vane rotor 45 to the advance side.
(A) Using the advance command set for the advance of the valve timing VT based on the fixing request, the command is continuously transmitted even after the lock pin 51 is fitted into the lock hole 54.
(B) After the lock pin 51 is fitted in the lock hole 54, a new advance command is transmitted separately from the advance command based on the fixing request.

  With reference to FIG. 9, the details of the “phase fixing process” that defines the processing procedure for fixing the valve timing VT by the phase fixing mechanism 50 will be described. This process is executed by the electronic control unit 80 during the operation of the engine 10, and after reaching the end step, each process from step S110 is repeated. In the drawing, the first oil control valve 63 is represented as “first OCV”, and the second oil control valve 64 is represented as “second OCV”.

  In this processing, in step S110, it is determined whether or not a request for fixing the valve timing VT is set, in step S120, whether or not the valve timing VT at that time is at the intermediate angle VTmdl, and in step S130. Then, it is determined whether or not the valve timing VT at that time is on the retard side with respect to the intermediate angle VTmdl. Then, any one of the following processes (A) to (C) is performed according to the determination results of steps S110 to S130. The fixing request is set or canceled in the following manner in the control separately executed by the electronic control unit 80. That is, when it is determined that there is an engine start request, an engine stop request, and an idle operation request, a fixed request is set based on this. Further, when it is determined that there is a request for changing the valve timing VT, the fixing request is canceled based on this.

  (A) When it is determined in step S110 that there is a fixing request and the intermediate angle VTmdl is in step S120, the operation mode of the first oil control valve 63 is set to operation mode A2 in step S140, and the second oil control The operation mode of the valve 64 is set to the operation mode B2. That is, a command for maintaining the valve timing VT is transmitted to the first oil control valve 63 and a command for moving the lock pin 51 to the protruding position is transmitted to the second oil control valve 64.

  (B) When it is determined in step S110 that there is a fixing request and in step S130 it is on the retard side with respect to the intermediate angle VTmdl, in step S150, the operation mode of the first oil control valve 63 is set to operation mode A1. The operation mode of the second oil control valve 64 is set to the operation mode B2. That is, a command to advance the valve timing VT is transmitted to the first oil control valve 63, and a command to move the lock pin 51 to the protruding position is transmitted to the second oil control valve 64.

  (C) When it is determined in step S110 that there is a fixing request and in step S130 it is on the retard side with respect to the intermediate angle VTmdl, in step S160, the operation mode of the first oil control valve 63 is set to operation mode A3. The operation mode of the second oil control valve 64 is set to the operation mode B2. That is, a command to retard the valve timing VT is transmitted to the first oil control valve 63 and a command to move the lock pin 51 to the protruding position is transmitted to the second oil control valve 64.

  Then, after executing any one of the processes (A) to (C), when it is determined in step S170 that the lock pin 51 is fitted in the lock hole 54, the first oil control valve 63 is determined in step S180. Is set to the operation mode A1, and the operation mode of the second oil control valve 64 is set to the operation mode B2. Further, when these operation modes are already set for the oil control valves 63 and 64, they are maintained. That is, a command to advance the valve timing VT is transmitted to the first oil control valve 63, and a command to move the lock pin 51 to the protruding position is transmitted to the second oil control valve 64.

  The determination mode in step S170 differs as follows according to the process executed immediately before (any of steps S140 to S160). That is, when the immediately preceding process is step S140, the fact that the time from the execution of the process until the lock pin 51 moves to the protruding position has elapsed and the lock pin 51 has been fitted into the lock hole 54. judge. When the immediately preceding process is step S150 or S160, the valve timing VT has reached the intermediate angle VTmdl, and the time from the execution of the process until the lock pin 51 moves to the protruding position has elapsed. Accordingly, it is determined that the lock pin 51 is fitted in the lock hole 54.

  Here, when a positive determination is not obtained as a result of the determination process of step S170 even after a certain period of time has elapsed after the execution of the processes of steps S140 to S160, the valve timing VT based on the sensors 81 and 82 is the intermediate angle VTmdl. Although (learned value VTG) is indicated, it is presumed that the lock pin 51 cannot move toward the protruding position due to a shift in the position of the lock pin 51 and the lock hole 54. Therefore, when such a situation occurs, an operation of gradually advancing or retarding the valve timing VT is performed. Then, when it is determined through this operation that the lock pin 51 is fitted in the lock hole 54, the process proceeds to step S180.

  Next, when it is estimated in step S190 that the phase locking mechanism 50 is in an abutting state, in step S200, the valve timing VT (intermediate angle VTmdl) calculated based on the outputs of the sensors 81 and 82 at that time is calculated. It is set as a new learning value VTG that replaces the learning value VTG that has been set so far. Whether or not the phase locking mechanism 50 is in an abutting state is confirmed by, for example, the valve timing VT calculated based on the outputs of the sensors 81 and 82 continuously showing a constant value over a certain period. be able to. In the phase fixing process, when a negative determination is made in the determination process of step S110, S170, or S190, the determination process is performed again after a predetermined control period has elapsed.

  In the valve timing control, when a request for setting the valve timing VT to the intermediate angle VTmdl is set based on the engine operating state and the learning value VTG has not yet been set, the intermediate angle VTmdl set as the initial value is set. Set as target valve timing VTT. On the other hand, when the request for setting the valve timing VT to the intermediate angle VTmdl is set based on the engine operating state and the learning value VTG is already set, the learning value VTG is set as the target valve timing VTT.

According to the present embodiment described above, the following effects can be obtained.
(1) In the present embodiment, when the lock pin 51 is fitted in the lock hole 54 and the vane rotor 45 is continuously driven to the advance side with respect to the housing rotor 41, that is, When the lock pin 51 in the protruding position is pressed against the wall surface on the advance side of the lock hole 54, the valve timing VT (intermediate angle VTmdl) calculated based on the outputs of the sensors 81 and 82 is learned. It is set as VTG. As a result, the degree of variation in the learned value of the valve timing caused by the clearance formed between the pin outer peripheral surface 51F and the hole wall surface 54F in the phase fixing mechanism 50 can be reduced.

  (2) In the present embodiment, the learning value VTG is set when the valve timing VT is changed based on the fixing request. As a result, it is possible to avoid changing the valve timing VT only for setting the learning value VTG.

  (3) In this embodiment, when there is a request to increase the engine speed NE, the valve timing VT is prohibited from being fixed. As a result, it is possible to quickly respond to a request to increase the engine speed NE.

(Second Embodiment)
A second embodiment of the present invention will be described with reference to FIGS. 7, 10, and 11.
In the first embodiment, when the learning value VTG is updated, the lock pin 51 is fitted into the lock hole 54 from the state where the vane rotor 45 is on the retard side with respect to the intermediate phase PM, and then the vane rotor 45 is further driven to the advance side. Thus, the advance side of the pin outer peripheral surface 51F is abutted against the hole wall surface 54F. That is, the learning value VTG is updated at the most advanced position among the positions where the lock pin 51 is fitted in the lock hole 54.

  On the other hand, in the present embodiment, the lock pin 51 is fitted into the lock hole 54 from the state where the vane rotor 45 is on the retard side with respect to the intermediate phase PM, and then the vane rotor 45 is driven to the retard side to drive the pin outer peripheral surface 51F. The retard side and the hole wall surface 54F are brought into contact with each other. That is, the learning value VTG is updated at the most retarded position among the positions where the lock pin 51 is fitted in the lock hole 54.

  Here, the amount of change of the valve timing VT when the lock pin 51 is fitted into the lock hole 54, that is, the valve timing VT is changed from the predetermined angle VTA which is on the retard side to the intermediate angle VTmdl to the intermediate angle VTmdl (learned value VTG). When the amount of change in the valve timing VT at the time (hereinafter, “change amount ΔVT at the time of fixation”) is compared between the first embodiment and the present embodiment, the difference in the manner of setting the learning value VTG Therefore, the following difference also occurs for the change amount ΔVT. In other words, according to the first embodiment, the difference between the predetermined angle VTA and the learning value VTG on the advance side of the lock hole 54 is the fixed change amount ΔVT. The difference between the angle VTmin and the learning value VTG on the retard side of the lock hole 54 is the fixed change amount ΔVT.

  Thus, according to the present embodiment, when the learning value VTG is updated, only the difference in the position of the lock pin 51 in the lock hole 54, that is, the clearance 56 shown in FIG. The change amount ΔVT can be made smaller than that in the first embodiment. Note that this embodiment is different from the first embodiment in the above points, and the configuration according to the same embodiment is adopted for the other points, so the same reference numerals are given to common parts. The description is omitted.

With reference to FIG. 10, the update mode of the learning value VTG described above will be described.
As shown in FIG. 10A, the valve timing VT is on the more advanced side than the intermediate angle VTmdl, and a request to fix the valve timing VT to the intermediate angle VTmdl (hereinafter, “fixing request”) is set. At this time, the rotational phase P of the vane rotor 45 is changed to a position where the lock pin 51 is positioned on the retard side with respect to the end of the lock groove 55 on the retard side. In other words, the valve timing VT is retarded until the valve timing VT reaches a timing corresponding to the rotational phase P (hereinafter referred to as “groove-corresponding delay angle VTdtc”).

  Next, the lubricant is discharged from the intermediate chamber 52 and the vane rotor 45 is driven to the advance side while the lock pin 51 is applied with the force in the protruding direction ZA. When the lock pin 51 is moved to a position corresponding to the lock groove 55 by driving the vane rotor 45, the lock pin 51 protrudes from the vane 46 and the tip end is locked as shown in FIG. It is inserted into the groove 55.

  As shown in FIG. 10C, when the rotational phase P of the vane rotor 45 reaches the intermediate phase PM, the lock pin 51 protrudes from the vane 46 to the maximum and is fitted into the lock hole 54. Next, in this state, the vane rotor 45 is driven toward the retard side opposite to the housing rotor 41 so that the delay of the pin outer peripheral surface 51F occurs as shown in FIG. The corner side comes into contact with the hole wall surface 54F and the abutting state of the phase fixing mechanism 50 is maintained, and the change in the valve timing VT is stagnated. According to the valve timing control, the valve timing VT at this time is set as a new learning value VTG.

  With reference to FIG. 11, the details of the “phase fixing process” that defines the processing procedure for fixing the valve timing VT by the phase fixing mechanism 50 will be described. This process is executed by the electronic control unit 80 during the operation of the engine 10, and after reaching the end step, the subsequent processes from step S210 are repeated. In the drawing, the first oil control valve 63 is represented as “first OCV”, and the second oil control valve 64 is represented as “second OCV”.

  In this process, it is determined in step S210 that a request for fixing the valve timing VT has been set, and in step S220, it is determined that the valve timing VT at that time is on the advance side or the intermediate angle with respect to the intermediate angle VTmdl. In step S230, the operation mode of the first oil control valve 63 is set to the operation mode A3, and the operation mode of the second oil control valve 64 is set to the operation mode B1. That is, a command to retard the valve timing VT is transmitted to the first oil control valve 63 and a command to move the lock pin 51 to the accommodation position is transmitted to the second oil control valve 64.

  Next, in step S240, when it is determined that the valve timing VT has reached the groove-corresponding retard angle VTdtc, that is, when it is determined that the lock pin 51 is on the retard side with respect to the retard end of the lock groove 55, step In S250, the operation mode of the first oil control valve 63 is set to the operation mode A1, and the operation mode of the second oil control valve 64 is set to the operation mode B2. That is, a command to advance the valve timing VT is transmitted to the first oil control valve 63, and a command to move the lock pin 51 to the protruding position is transmitted to the second oil control valve 64.

  Next, when it is determined in step S260 that the lock pin 51 is fitted in the lock hole 54, the operation mode of the first oil control valve 63 is set to the operation mode A3 in step S270, and the second oil control valve 64 is set. The operation mode is set to operation mode B2. That is, a command to retard the valve timing VT is transmitted to the first oil control valve 63 and a command to move the lock pin 51 to the protruding position is transmitted to the second oil control valve 64.

  In the determination process of step S260, the lock pin is determined by the fact that the valve timing VT has reached the intermediate angle VTmdl and that the time from the execution of the process of step S250 until the lock pin 51 has moved to the protruding position has elapsed. It is determined that 51 is fitted in the lock hole 54.

  Here, if a positive determination is not obtained as a result of the determination process in step S260 even after a predetermined period has elapsed after the execution of the process in step S250, the valve timing VT based on the sensors 81 and 82 is determined to be the intermediate angle VTmdl (learning). Although the value VTG) is indicated, it is presumed that the lock pin 51 cannot move toward the protruding position due to a shift in the position of the lock pin 51 and the lock hole 54. Therefore, when such a situation occurs, an operation of gradually advancing or retarding the valve timing VT is performed. When it is determined that the lock pin 51 is fitted in the lock hole 54 through this operation, the process proceeds to step S270.

  Next, when it is estimated in step S280 that the phase locking mechanism 50 is in an abutting state, in step S290, the valve timing VT (intermediate angle VTmdl) calculated based on the outputs of the sensors 81 and 82 at that time is calculated. It is set as a new learning value VTG that replaces the learning value VTG that has been set so far. Whether or not the phase locking mechanism 50 is in an abutting state is determined by, for example, the valve timing VT calculated based on the outputs of the sensors 81 and 82 being continuously constant over a certain period. Can be confirmed. In the phase fixing process, when a negative determination is made in the determination process of step S210, S240, S260, or S280, the determination process is performed again after a predetermined control period has elapsed.

According to the present embodiment described above, in addition to the effects (2) and (3) according to the first embodiment, the following effects can be further achieved.
(4) In this embodiment, the lock pin 51 is fitted into the lock hole 54 from the state where the vane rotor 45 is on the retard side with respect to the intermediate phase PM, and then the vane rotor 45 is driven to the retard side to retard the pin outer peripheral surface 51F. The corner side and the hole wall surface 54F are abutted against each other. That is, the learning value VTG is updated at the most retarded position among the positions where the lock pin 51 is fitted in the lock hole 54. Thus, the fixed change amount ΔVT is set to the first change amount ΔVT by the amount corresponding to the difference in the position of the lock pin 51 in the lock hole 54 when the learning value VTG is updated, that is, the clearance 56 shown in FIG. It becomes possible to make it smaller than the embodiment.

(Third embodiment)
A third embodiment of the present invention will be described with reference to FIGS.
In the first embodiment, the supply / discharge state of the lubricating oil for the advance chamber 47 and the retard chamber 48 is controlled by the first oil control valve 63, and the supply / discharge state of the lubricant for the intermediate chamber 52 is the second. The structure controlled by the oil control valve 64 was adopted. On the other hand, in the present embodiment, the supply / discharge state of the lubricating oil in the advance chamber 47, the retard chamber 48, and the intermediate chamber 52 is controlled by a single oil control valve (third oil control valve 65). ing. Note that this embodiment is different from the first embodiment in the above points, and the configuration according to the same embodiment is adopted for the other points, so the same reference numerals are given to common parts. The description is omitted.

  The third oil control valve 65 changes its operation mode from the operation mode C1 to the operation mode C1 by changing the control position of the spool 65B relative to the sleeve 65A (hereinafter, “control position”) to any one of the control position C1 to the control position C5. The mode is set to a corresponding one of the modes C5, thereby switching the connection state between the supply oil passage 71 and the discharge oil passage 72, the advance chamber oil passage 73, the retard chamber oil passage 74, and the intermediate chamber oil passage 75. The control position of the spool 65B is changed in the order of the control position C4 and the control position C1 to the control position C3 and the control position C5 as the spool 65B moves from one to the other with respect to the sleeve 65A. The following (A) to (E) show the operation of the variable valve timing mechanism 40 in each control mode.

  (A) When the control position of the spool 65B is at the control position C1, the operation mode of the third oil control valve 65 is set to the operation mode C1. At this time, the advance chamber oil passage 73 and the supply oil passage 71 are connected, the retard chamber oil passage 74 and the discharge oil passage 72 are connected, and the intermediate chamber oil passage 75 and the supply oil passage 71 are connected. Is done. Thereby, the lubricating oil from the oil pump 62 flows in the order of the supply oil passage 71 and the advance chamber oil passage 73 and is supplied to the advance chamber 47. Further, the lubricating oil in the retarding chamber 48 flows in the order of the retarding chamber oil passage 74 and the discharge oil passage 72 and is returned to the oil pan 61. Further, the lubricating oil from the oil pump 62 flows in the order of the supply oil passage 71 and the intermediate chamber oil passage 75 and is supplied to the intermediate chamber 52.

  In this operation mode C1, since the rotation phase P of the vane rotor 45 is to be changed to the advance side, and the lock pin 51 is held at the accommodation position, the valve timing VT changes to the advance side. .

  (B) When the control position of the spool 65B is at the control position C2, the operation mode of the third oil control valve 65 is set to the operation mode C2. At this time, the advance chamber oil passage 73 and the supply oil passage 71 and the discharge oil passage 72 are blocked, and the retard chamber oil passage 74 and the supply oil passage 71 and the discharge oil passage 72 are blocked. In addition, the intermediate chamber oil passage 75 and the supply oil passage 71 are connected. Thereby, the flow of the lubricating oil from the oil pump 62 to the advance chamber 47 via the third oil control valve 65 and the lubrication to the oil pan 61 from the advance chamber 47 via the third oil control valve 65. Any oil flow is blocked. Further, the flow of lubricating oil from the oil pump 62 to the retarding chamber 48 via the third oil control valve 65 and the lubricating oil to the oil pan 61 from the retarding chamber 48 via the third oil control valve 65. Any flow is interrupted. On the other hand, the lubricating oil from the oil pump 62 is supplied to the intermediate chamber 52 through the supply oil passage 71 and the intermediate chamber oil passage 75 in this order.

  In this operation mode C2, since the rotation phase P of the vane rotor 45 is maintained and the lock pin 51 is held at the accommodation position, the valve timing VT is held at a constant timing.

  (C) When the control position of the spool 65B is at the control position C3, the operation mode of the third oil control valve 65 is set to the operation mode C3. At this time, the advance chamber oil passage 73 and the discharge oil passage 72 are connected, the retard chamber oil passage 74 and the supply oil passage 71 are connected, and the intermediate chamber oil passage 75 and the supply oil passage 71 are connected. Is done. As a result, the lubricating oil in the advance chamber 47 flows in the order of the advance chamber oil passage 73 and the discharge oil passage 72 and is returned to the oil pan 61. Further, the lubricating oil from the oil pump 62 flows in the order of the supply oil passage 71 and the retard chamber oil passage 74 and is supplied to the retard chamber 48. Further, the lubricating oil from the oil pump 62 flows in the order of the supply oil passage 71 and the intermediate chamber oil passage 75 and is supplied to the intermediate chamber 52.

  In this operation mode C3, the rotational phase P of the vane rotor 45 is about to be changed to the retard side, and the lock pin 51 is held at the accommodation position, so that the valve timing VT changes to the retard side. .

  (D) When the control position of the spool 65B is at the control position C4, the operation mode of the third oil control valve 65 is set to the operation mode C4. At this time, the advance chamber oil passage 73 and the supply oil passage 71 are connected, the retard chamber oil passage 74 and the discharge oil passage 72 are connected, and the intermediate chamber oil passage 75 and the discharge oil passage 72 are connected. Is done. Thereby, the lubricating oil from the oil pump 62 flows in the order of the supply oil passage 71 and the advance chamber oil passage 73 and is supplied to the advance chamber 47. Further, the lubricating oil in the retarding chamber 48 flows in the order of the retarding chamber oil passage 74 and the discharge oil passage 72 and is returned to the oil pan 61. Further, the lubricating oil in the intermediate chamber 52 flows in the order of the intermediate chamber oil passage 75 and the discharge oil passage 72 and is returned to the oil pan 61.

  In this operation mode C4, the driving state of the variable valve timing mechanism 40 is maintained in a state where the rotational phase P of the vane rotor 45 is to be changed to the advance side, and the driving state of the phase fixing mechanism 50 is fixed at the valve timing VT. Maintained state to try. Therefore, when the rotational phase P reaches the intermediate phase PM as the vane rotor 45 rotates toward the advance side, the valve timing VT is fixed at the intermediate angle VTmdl.

  (E) When the control position of the spool 65B is at the control position C5, the operation mode of the third oil control valve 65 is set to the operation mode C5. At this time, the advance chamber oil passage 73 and the discharge oil passage 72 are connected, the retard chamber oil passage 74 and the supply oil passage 71 are connected, and the intermediate chamber oil passage 75 and the discharge oil passage 72 are connected. Is done.

  In this operation mode C5, the drive state of the variable valve timing mechanism 40 is maintained in a state where the rotational phase P of the vane rotor 45 is to be changed to the retard side, and the drive state of the phase fixing mechanism 50 is fixed at the valve timing VT. Maintained state to try. For this reason, when the rotational phase P reaches the intermediate phase PM as the vane rotor 45 rotates toward the retard angle side, the valve timing VT is fixed at the intermediate angle VTmdl.

  With reference to FIG. 9, changes from the first embodiment regarding the “phase fixing process” of the present embodiment will be described. Except as described below, processing according to the first embodiment is performed.

  Steps S120 and S140 are omitted. Accordingly, when the valve timing VT is at the intermediate angle VTmdl when the fixing request is set, the valve timing VT is changed to the retard side or the advance side with respect to the intermediate angle VTmdl, and then the lock pin 51 is locked. The operation of fitting into 54 is performed. In step S150, the operation mode of the third oil control valve 65 is set to the operation mode C5. In step S160, the operation mode of the third oil control valve 65 is set to the operation mode C4. In step S180, the operation mode of the third oil control valve 65 is set to the operation mode C4.

(Other embodiments)
Note that the embodiments of the present invention are not limited to the above-described embodiments, and can be modified as shown below, for example. The following modifications are not applied only to the above embodiments, and different modifications can be combined with each other.

  In the first embodiment, the lock pin 51 is fitted into the lock hole 54 in the advance process, retard process or holding state of the valve timing VT, and then the advance side of the pin outer peripheral surface 51F is abutted against the hole wall surface 54F. The learning value VTG is updated under the above condition, but the learning value VTG is not limited to this. For example, instead of the learning mode of the embodiment, it can be changed to any of the following (Modification A) to (Modification C). FIG. 13 shows a summary of the learning mode of the first embodiment and the learning mode of each modification.

  (Modification A) In a state where the lock pin 51 is fitted into the lock hole 54 in the advance process of the valve timing VT, and then the retarded side of the pin outer peripheral surface 51F is abutted against the hole wall surface 54F, the learning value VTG is Update.

  (Modification B) In the process of retarding the valve timing VT, the lock pin 51 is fitted into the lock hole 54, and then the learning value VTG is obtained under the condition where the retard side of the pin outer peripheral surface 51F is abutted against the hole wall surface 54F. Update.

  (Modification C) In a state where the valve timing VT is maintained, the lock pin 51 is fitted into the lock hole 54, and then the learning value VTG is updated under the state where the retarded side of the pin outer peripheral surface 51F is abutted against the hole wall surface 54F. I do.

  In the second embodiment, when the valve timing VT is on the advance side with respect to the intermediate angle VTmdl, the valve timing VT is first changed to the retard side with respect to the intermediate angle VTmdl, and then the advance process of the valve timing VT. The learning value VTG is updated under the condition that the lock pin 51 is fitted into the lock hole 54 and the retarded side of the pin outer peripheral surface 51F is abutted against the hole wall surface 54F. The update mode is not limited to this. For example, instead of the learning mode of the same embodiment, it can be changed to any of the following (Modification D) to (Modification F). FIG. 14 shows a summary of the learning mode of the second embodiment and the learning mode of each modification.

  (Modification D) When the valve timing VT is on the advance side with respect to the intermediate angle VTmdl, the valve timing VT is first changed to the retard side with respect to the intermediate angle VTmdl, and then the lock pin in the advance process of the valve timing VT. 51 is fitted into the lock hole 54, and then the learning value VTG is updated under the condition that the advance side of the pin outer peripheral surface 51F is abutted against the hole wall surface 54F.

  (Modification E) When the valve timing VT is on the retard side with respect to the intermediate angle VTmdl, the valve timing VT is first changed to the advance side with respect to the intermediate angle VTmdl, and then the lock pin is used in the process of retarding the valve timing VT. 51 is fitted into the lock hole 54, and then the learning value VTG is updated under the condition that the advance side of the pin outer peripheral surface 51F is abutted against the hole wall surface 54F.

  (Modification F) When the valve timing VT is on the retard side with respect to the intermediate angle VTmdl, the valve timing VT is first changed to the advance side with respect to the intermediate angle VTmdl, and then the lock pin is used in the process of retarding the valve timing VT. 51 is fitted into the lock hole 54, and then the learning value VTG is updated in a state where the retarded side of the pin outer peripheral surface 51F is abutted against the hole wall surface 54F.

  In the first or third embodiment, the variable valve timing mechanism 40 is provided with the phase fixing mechanism 50 that fixes the valve timing VT to the intermediate angle VTmdl. However, the valve timing VT fixed by the phase fixing mechanism is The intermediate angle VTmdl is not limited to the maximum angle VTmax or the most retarded angle VTmin. In short, any of the most advanced angle VTmax, the most retarded angle VTmin, and the intermediate angle VTmdl can be adopted as the specific valve timing angle fixed by the phase fixing mechanism.

  In the second embodiment, when the fixing request is set under the condition that the valve timing VT is on the advance side with respect to the intermediate angle VTmdl, the lock pin 51 is more than the end of the lock groove 55 on the retard side. The rotational phase P of the vane rotor 45 is changed to a position on the retard side, and then the vane rotor 45 is driven to the advance side to fit the lock pin 51 into the lock hole 54. It can also be changed. That is, the rotation phase P of the vane rotor 45 is changed to a position where the lock pin 51 is located in any one of the lock grooves 55, and then the vane rotor 45 is driven forward to fit the lock pin 51 into the lock hole 54. It can also be.

  In each of the above embodiments, as the configuration of the phase fixing mechanism 50, the vane rotor 45 is provided with the lock pin 51, the intermediate chamber 52, and the lock spring 53, and the housing rotor 41 is provided with the lock hole 54. The configuration of the phase locking mechanism is not limited to this. For example, the lock pin 51, the intermediate chamber 52 and the lock spring 53 can be provided in the housing rotor 41, and the lock hole 54 can be provided in the vane rotor 45.

  In each of the above embodiments, the phase locking mechanism 50 is configured such that the lock pin 51 is maintained in a state in which the lock pin 51 can protrude from the vane 46 when the hydraulic pressure of the intermediate chamber 52 with respect to the lock pin 51 is released. The relationship between the intermediate chamber 52 and the lock spring 53 can be set to be opposite to those in the above embodiments. In other words, the configuration is such that the force in the protruding direction ZA is applied to the lock pin 51 by the hydraulic pressure of the intermediate chamber 52 and the force in the accommodating direction ZB is applied to the lock pin 51 by the force of the lock spring 53. it can.

  In each of the above embodiments, the present invention is applied to the variable valve operating apparatus including the variable valve timing mechanism 40 of the intake valve 31. However, the above described also applies to the variable valve operating apparatus including the variable valve timing mechanism of the exhaust valve. The present invention can be applied in a manner according to each embodiment.

  The configuration of the variable valve operating apparatus to which the present invention is applied, including the configuration of the variable valve timing mechanism 40, the phase locking mechanism 50, and the lubrication device 60, is not limited to the contents exemplified in the above embodiments. That is, the present invention is applied to any variable valve operating apparatus as long as it has a valve timing variable mechanism that changes the valve timing and a phase locking mechanism that fixes the valve timing to a specific intermediate angle. In this case as well, it is possible to achieve the effects similar to the effects of the above embodiments.

  DESCRIPTION OF SYMBOLS 10 ... Engine, 20 ... Engine main body, 21 ... Cylinder block, 22 ... Cylinder head, 23 ... Combustion chamber, 24 ... Cylinder, 25 ... Piston, 26 ... Crankshaft, 27 ... Injector, 31 ... Intake valve, 32 ... Intake cam Shaft 33: Exhaust valve 34 ... Exhaust camshaft 40 ... Valve timing variable mechanism (variable valve mechanism) 41 ... Housing rotor (input side rotating body (engagement side rotating body)) 41A ... Partition wall 42 ... Housing body, 43 ... Sprocket, 44 ... Cover, 45 ... Vane rotor (output side rotating body (accommodating side rotating body)), 46 ... Vane, 47 ... Advance chamber, 48 ... Delay chamber, 50 ... Phase locking mechanism, 51 ... Lock pin (regulator), 51F ... Pin outer peripheral surface, 52 ... Intermediate chamber, 53 ... Lock spring, 54 ... Lock hole (restriction hole), 54F ... Hole wall surface 55: Lock groove (regulation groove), 56: Clearance, 60 ... Lubricating device, 61 ... Oil pan, 62 ... Oil pump, 63 ... First oil control valve, 63A ... Sleeve, 63B ... Spool, 64 ... Second oil control Valve, 64A ... Sleeve, 64B ... Spool, 65 ... Third oil control valve, 65A ... Sleeve, 65B ... Spool, 70 ... Lubricating oil passage, 71 ... Supply oil passage, 72 ... Discharge oil passage, 73 ... Advance chamber oil Road, 74 ... retarding chamber oil passage, 75 ... intermediate chamber oil passage, 80 ... electronic control device, 81 ... crank position sensor, 82 ... cam position sensor.

Claims (12)

A variable valve mechanism for changing the valve timing of an intake valve or an exhaust valve as an engine valve, a phase fixing mechanism for fixing the valve timing to a specific angle, and a state in which the valve timing is fixed by the phase fixing mechanism. A variable valve operating apparatus for an internal combustion engine comprising learning means for setting the valve timing calculated based on a sensor output as a learning value for the specific angle.
The learning means calculates the valve timing calculated based on the sensor output when the variable valve mechanism is driven based on the valve timing advance command and the valve timing is fixed by the phase fixing mechanism. Is set as the learning value. A variable valve operating apparatus for an internal combustion engine, characterized in that: The variable valve operating apparatus for an internal combustion engine according to claim 1,
The learning means is configured to change the variable motion based on the advance angle command after the advance angle command is transmitted based on the setting of a fixed request that is a request for fixing the valve timing to the specific angle. The variable valve operating apparatus for an internal combustion engine, wherein the learning value is set when the valve mechanism is being driven and when the valve timing is fixed by the phase fixing mechanism. The variable valve operating apparatus for an internal combustion engine according to claim 1 or 2,
The learning means specifies the valve timing when the valve timing is on the more advanced side than the specific angle at the time when a fixing request that is a request for fixing the valve timing to the specific angle is set. The learning value is set when the variable valve mechanism is driven based on the advance command and the valve timing is fixed by the phase fixing mechanism. A variable valve operating apparatus for an internal combustion engine characterized by A variable valve mechanism for changing the valve timing of an intake valve or an exhaust valve as an engine valve, a phase fixing mechanism for fixing the valve timing to a specific angle, and a state in which the valve timing is fixed by the phase fixing mechanism. A variable valve operating apparatus for an internal combustion engine comprising learning means for setting the valve timing calculated based on a sensor output as a learning value for the specific angle.
The learning means calculates the valve timing calculated based on the sensor output when the variable valve mechanism is being driven based on the valve timing retardation command and the valve timing is fixed by the phase fixing mechanism. Is set as the learning value. A variable valve operating apparatus for an internal combustion engine, characterized in that: The variable valve operating apparatus for an internal combustion engine according to claim 4,
The learning means transmits the variable motion based on the delay angle command after the delay angle command is transmitted based on the setting of a fixing request that is a request for fixing the valve timing to the specific angle. The variable valve operating apparatus for an internal combustion engine, wherein the learning value is set when the valve mechanism is being driven and when the valve timing is fixed by the phase fixing mechanism. The variable valve operating apparatus for an internal combustion engine according to claim 4 or 5,
The learning means specifies the valve timing when the valve timing is on the more retarded side than the specific angle at the time when a fixing request that is a request for fixing the valve timing to the specific angle is set. The learning value is set when the variable valve mechanism is being driven based on the retard command and when the valve timing is fixed by the phase fixing mechanism. A variable valve operating apparatus for an internal combustion engine characterized by the above. The variable valve operating apparatus for an internal combustion engine according to any one of claims 1 to 6,
The variable valve operating apparatus for an internal combustion engine, wherein the valve timing is not fixed to the specific angle by the phase fixing mechanism when there is a request to increase the engine rotation speed. A variable valve mechanism for changing the valve timing of an intake valve or an exhaust valve as an engine valve, a phase fixing mechanism for fixing the valve timing to a specific angle, and a state in which the valve timing is fixed by the phase fixing mechanism. Learning means for setting the valve timing originally calculated based on the sensor output as a learning value,
The variable valve mechanism includes an input-side rotating body that rotates by a force transmitted from a crankshaft, and an output-side rotating body that rotates together with the camshaft of the engine valve by a force transmitted from the input-side rotating body. An advance angle chamber and a retard angle chamber are formed between the input side rotating body and the output side rotating body.
The phase locking mechanism is provided on the accommodation-side rotator that is one of the input-side rotator and the output-side rotator, and the projection position protruding from the accommodation-side rotator and the accommodation accommodated in the accommodation-side rotator. A restriction body that operates between the position and a restriction hole that is provided in an engagement-side rotation body that is the other of the input-side rotation body and the output-side rotation body and into which the restriction body is fitted. In a variable valve operating apparatus for an internal combustion engine,
The valve timing calculated based on the sensor output is set as the learning value when the restricting body at the projecting position is pressed against the wall surface on the advance side of the restricting hole. A variable valve operating apparatus for an internal combustion engine. The variable valve operating apparatus for an internal combustion engine according to claim 8,
The phase locking mechanism fixes the valve timing to the specific angle by fitting a part of the restricting body at the protruding position into the restricting hole, and a part of the restricting body at the receiving position is The release of the valve timing is released by detachment from the restriction hole, and the same is achieved by driving the variable valve mechanism based on the valve timing advance command when the restriction body is in the protruding position. A variable valve operating apparatus for an internal combustion engine, wherein the restricting body is pressed against a wall surface on the advance side of the restricting hole. A variable valve mechanism for changing the valve timing of an intake valve or an exhaust valve as an engine valve, a phase fixing mechanism for fixing the valve timing to a specific angle, and a state in which the valve timing is fixed by the phase fixing mechanism. Learning means for setting the valve timing originally calculated based on the sensor output as a learning value,
The variable valve mechanism includes an input-side rotating body that rotates by a force transmitted from a crankshaft, and an output-side rotating body that rotates together with the camshaft of the engine valve by a force transmitted from the input-side rotating body. An advance angle chamber and a retard angle chamber are formed between the input side rotating body and the output side rotating body.
The phase locking mechanism is provided on the accommodation-side rotator that is one of the input-side rotator and the output-side rotator, and the projection position protruding from the accommodation-side rotator and the accommodation accommodated in the accommodation-side rotator. A restriction body that operates between the position and a restriction hole that is provided in the engagement-side rotation body that is the other of the input-side rotation body and the output-side rotation body and into which the restriction body is fitted. In a variable valve operating apparatus for an internal combustion engine,
The valve timing calculated based on the sensor output is set as the learning value when the restricting body at the projecting position is pressed against the wall surface on the retard side of the restricting hole. A variable valve operating apparatus for an internal combustion engine. The variable valve operating apparatus for an internal combustion engine according to claim 10,
The phase locking mechanism fixes the valve timing to the specific angle by fitting a part of the restricting body at the protruding position into the restricting hole, and a part of the restricting body at the receiving position is When the variable valve mechanism is being driven based on the command for retarding the valve timing when the restricting body is in the projecting position, the valve timing is fixed by releasing from the restricting hole. The variable valve operating apparatus for an internal combustion engine, wherein the restriction body is pressed against a wall surface on the retard side of the restriction hole. The variable valve operating apparatus for an internal combustion engine according to any one of claims 8 to 11,
The phase locking mechanism includes a fixed chamber that is provided in the accommodation-side rotating body and in which a supply / discharge state of hydraulic fluid is operated, and includes the input-side rotating body and the output-side rotating body. When the relative rotation phase is in a specific phase corresponding to the specific angle and the hydraulic oil supply / discharge state with respect to the fixed chamber is set to the first supply / discharge state, the regulating body is held in the protruding position. When the relative rotational phase of the input side rotating body and the output side rotating body is in the specific phase, and the supply / discharge state of hydraulic oil to / from the fixed chamber is set to the second supply / discharge state, The variable valve operating apparatus for an internal combustion engine, wherein the restricting body is held in the housing position.

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