JP2010242535A - Variable valve gear for internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable valve gear for an internal combustion engine capable of supplying lubricating oil to an advance chamber and a delay chamber when a restriction mechanism is in a fixed state. <P>SOLUTION: This variable valve gear includes a valve timing variable mechanism 40 for changing a valve timing of an intake valve between a most advanced angle and a most delayed angle, an intermediate lock mechanism 50 for fixing the valve timing at a specific intermediate angle between the most advanced angle and the most delayed angle, and a lubricating device for controlling the supply state of the lubricating oil with respect to each of the advance chamber 46 and the delay chamber 47 of the valve timing variable mechanism 40 and an intermediate chamber 52A of the intermediate lock mechanism 50. The valve timing is fixed to the intermediate angle when an intermediate lock pin 51 is at a projecting position based on the lubricating oil being supplied to the intermediate chamber 52A. When the intermediate lock pin 51 is at the projecting position, the advance chamber 46 and the delay chamber 47 are communicated with each other by a communication mechanism. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a variable mechanism that changes the valve timing of an intake valve or an exhaust valve between a most advanced angle and a most retarded angle, and a specific intermediate angle that is between the most advanced angle and the most retarded angle. The present invention relates to a variable valve operating apparatus for an internal combustion engine, which includes a regulation mechanism fixed to a cylinder, and a drive mechanism for controlling a supply state of lubricating oil to each of an advance chamber and a retard chamber of the variable mechanism and an intermediate chamber of the regulation mechanism.

  In the conventional variable valve device described above, including the variable valve device described in Patent Document 1, the rotation phase of the vane rotor with respect to the housing is fixed by fitting the restrictor body of the vane rotor into the restriction hole of the housing when the engine operation is stopped. Like to do. Thereby, 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.

JP 2001-50064 A

  By the way, when the engine is stopped, the advance chamber and retard chamber lubricating oil of the variable mechanism flows out of the mechanism, so that the advance chamber and retard chamber are sufficiently filled with the lubricant when the engine is started next time. There is no state. For this reason, in order to change the valve timing after the engine start is completed, it is necessary to first fill the advance chamber and the retard chamber with the lubricating oil.

  On the other hand, in an internal combustion engine having an intermediate lock mechanism, the valve timing is maintained at an intermediate angle at least until the engine start is completed, that is, a request to change the valve timing is not set. The timing when the supply of the lubricating oil to the retard chamber is started is after the completion of the engine start.

  On the other hand, in the variable valve system of Patent Document 1, since the lubricating oil can be supplied only to one of the advance chamber and the retard chamber while the valve timing is maintained at the intermediate angle, the engine Lubricant is supplied to one of the advance angle chamber and the retard angle chamber during start-up, and after the start of the engine is completed, the lubricant is supplied to the other of the advance angle chamber and the retard angle chamber after releasing the fixing of the valve timing to the intermediate angle. I am doing so. Thereby, compared with the conventional variable valve operating apparatus in which the supply of the lubricating oil to the advance chamber and the retard chamber is started after the start is completed, the variable valve apparatus disclosed in Patent Document 1 has the advance chamber during the engine start. In addition, since the lubricating oil can be supplied to one of the retarding chambers, the time when the valve timing can be changed can be advanced.

  However, even in the apparatus of Patent Document 1, the timing when the valve timing can be changed after the completion of the engine start is after the other chamber is filled with the lubricating oil. It is hard to say that you can. Such a problem is not limited to the variable valve device of Patent Document 1, but can be said to be generally common to variable valve devices that fix the valve timing to an intermediate angle by a regulating mechanism.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a variable motion of an internal combustion engine that can supply lubricating oil to an advance chamber and a retard chamber when the regulating mechanism is in a fixed state. It is to provide a valve device.

In the following, means for achieving the above object and its effects are described.
(1) The invention according to claim 1 is a variable mechanism that changes the valve timing of an intake valve or an exhaust valve as an engine valve between a most advanced angle and a most retarded angle, and the valve timing of the engine valve is maximized. A restriction mechanism that fixes to a specific intermediate angle between the advance angle and the most retarded angle, and a lubricant for each of the advance angle chamber of the variable mechanism, the delay angle chamber of the variable mechanism, and the intermediate chamber of the restriction mechanism A drive mechanism that controls a supply state, and the restriction mechanism is configured such that when its operation state is in a fixed state based on the supply state of the lubricating oil to the intermediate chamber being set to the first supply state. When the valve timing of the engine valve is fixed at the intermediate angle and the operating state of the engine is in the released state based on the supply state of the lubricating oil to the intermediate chamber being set to the second supply state, the engine valve In the variable valve operating apparatus for an internal combustion engine that releases the fixing of the valve timing to the intermediate angle, the advance chamber and the retard chamber are communicated with each other by the communication mechanism when the restriction mechanism is in a fixed state. The gist is to be done.

  According to the present invention, since the advance chamber and the retard chamber are communicated with each other when the regulating mechanism is in the fixed state, the drive mechanism supplies lubricant to one of the advance chamber and the retard chamber. As a result, the lubricating oil is supplied to the other chamber. That is, when the engine is started and the valve timing is fixed to the intermediate angle by the regulating mechanism, when the lubricating oil is supplied to one of the advance chamber and the retard chamber, the other chamber similarly Lubricating oil is supplied. Therefore, the lubricating oil can be supplied to the advance chamber and the retard chamber when the regulating mechanism is in the fixed state.

  (2) A second aspect of the present invention is the variable valve operating apparatus for an internal combustion engine according to the first aspect, wherein the advance chamber is formed by the communication mechanism as the regulating mechanism shifts from a fixed state to a released state. And the communication with the retardation chamber is released.

  In the above invention, since the communication between the advance chamber and the retard chamber is released with the transition of the regulation mechanism to the release state, the advance chamber and the retard chamber are communicated only when the regulation mechanism is in the fixed state. Become so.

  (3) A third aspect of the present invention is the variable valve operating apparatus for an internal combustion engine according to the first or second aspect, wherein the variable mechanism rotates on the input side that is rotated by a force transmitted from a crankshaft of the internal combustion engine. And an output side rotator that rotates together with the camshaft of the engine valve by a force transmitted from the input side rotator, and is partitioned between the input side rotator and the output side rotator. The advance angle chamber and the retard angle chamber are provided, and the restriction mechanism is provided in an accommodation chamber of an accommodation-side rotation body that is one of the input-side rotation body and the output-side rotation body. A regulating body that operates between a state of protruding from the chamber and a state of being accommodated in the storage chamber, and the intermediate chamber that is provided as a part of the storage chamber and is supplied with lubricating oil from the drive mechanism. Consists of including It is the gist that there.

  (4) According to a fourth aspect of the present invention, in the variable valve operating apparatus for an internal combustion engine according to the third aspect, the advance chamber and the retard angle are controlled by the communication mechanism when the restricting body is in a protruding state. The gist is that the chamber communicates with each other through the storage chamber.

(5) The invention according to claim 5 is the variable valve operating apparatus for the internal combustion engine according to claim 4, wherein the communication mechanism includes the retard chamber and the housing when the regulating body is in a protruding state. The gist of the present invention is to include a first communication passage that communicates with the chamber and a second communication passage that communicates the advance chamber and the storage chamber when the restricting body protrudes. Yes.

  (6) The invention according to claim 6 is the variable valve operating apparatus for an internal combustion engine according to claim 5, wherein the communication mechanism is provided in the housing chamber and the regulating body is in a protruding state. The intermediate communication path includes an intermediate communication path that connects the first communication path and the second communication path to each other, and the first communication path and the intermediate communication path when the restricting body is in a protruding state. In addition, the gist is that the advance chamber and the retard chamber communicate with each other through a single passage formed by the second communication passage.

  (7) The invention according to claim 7 is the variable valve operating apparatus for an internal combustion engine according to claim 6, wherein the intermediate communication passage is accommodated in the accommodation chamber in a state in which the regulating body protrudes from the accommodation chamber. The position in the intermediate chamber changes between the projecting position and the housed position when being switched between the first communication path and the projecting position. The gist is that it communicates with both of the second communication paths and does not communicate with either the first communication path or the second communication path when in the accommodated position.

  According to the above invention, the intermediate communication path communicates the first communication path and the second communication path when the position in the storage chamber is in the protruding position, and the first communication path and the second communication path when in the storage position. Since it does not communicate with any of the communication paths, the first communication path and the second communication path are communicated only when the intermediate communication path is in the protruding state.

  (8) According to an eighth aspect of the present invention, in the variable valve operating apparatus for an internal combustion engine according to the sixth or seventh aspect, the advance chamber, the retard chamber, and the storage chamber are provided only through the intermediate communication passage. Only when the first communication path and the second communication path are connected to each other by the intermediate communication path, the lubricating oil between the advance chamber, the retard chamber, and the storage chamber The gist is that the distribution of

  (9) The invention according to claim 9 is the variable valve operating apparatus for an internal combustion engine according to any one of claims 3 to 8, wherein the regulating mechanism is configured so that a supply state of the lubricating oil to the intermediate chamber is The restricting body protrudes from the storage chamber based on being set to the first supply state, and the protruding restricting body is the other of the input side rotating body and the output side rotating body. The fixed state in which the valve timing of the engine valve is fixed at the intermediate angle by being fitted into the restriction hole of the side rotating body is maintained, and the supply state of the lubricating oil to the intermediate chamber is the second supply state The release body is released from the restriction hole and is accommodated in the storage chamber based on being set to the release state, and the release state for releasing the fixation of the valve timing to the intermediate angle by the accommodation of the restriction body. It is summarized in that is intended to maintain.

  (10) The invention according to claim 10 is the variable valve operating apparatus for an internal combustion engine according to any one of claims 1 to 9, wherein the valve timing is fixed to an intermediate angle by the restriction mechanism when the engine is started, In addition, the gist is that the lubricating oil is supplied to the advance chamber or the retard chamber while the valve timing is fixed.

  (11) According to the eleventh aspect of the present invention, in the variable valve operating apparatus for the internal combustion engine according to the tenth aspect, the valve timing is maintained at an intermediate angle by the regulating mechanism until the engine start is completed. The gist is to be done.

  (12) According to the twelfth aspect of the present invention, in the variable valve operating apparatus for an internal combustion engine according to any one of the first to eleventh aspects, the variable mechanism by the drive mechanism when the engine starting operation is started. The gist is that the supply mode of the lubricant is set to a supply mode for supplying the lubricant to only one of the advance chamber and the retard chamber.

  (13) The invention according to claim 13 is the variable valve operating apparatus for the internal combustion engine according to claim 12, wherein the drive mechanism supplies lubricating oil to only one of the advance chamber and the retard chamber. The supply mode has a plurality of modes, and the supply mode set when the engine start operation is started is a lubricant for one of the advance chamber and the retard chamber among the plurality of supply modes. The main point is that the supply amount is the largest.

  According to the above invention, since the supply amount of the lubricating oil to one of the advance angle chamber and the retard angle chamber at the time of starting the engine is set to the largest value, the supply amount of the lubricating oil is not set to the largest value. Compared to the case, the lubricating oil can be quickly supplied to one of the advance chamber and the retard chamber.

  (14) The invention according to claim 14 is a variable mechanism that changes a valve timing of an intake valve or an exhaust valve as an engine valve between a most advanced angle and a most retarded angle, and a maximum valve timing of the engine valve. A restriction mechanism that fixes to a specific intermediate angle between the advance angle and the most retarded angle, and a lubricant for each of the advance angle chamber of the variable mechanism, the delay angle chamber of the variable mechanism, and the intermediate chamber of the restriction mechanism A drive mechanism that controls a supply state, and the restriction mechanism is configured such that when its operation state is in a fixed state based on the supply state of the lubricating oil to the intermediate chamber being set to the first supply state. When the valve timing of the engine valve is fixed at the intermediate angle and the operating state of the engine is in the released state based on the supply state of the lubricating oil to the intermediate chamber being set to the second supply state, the engine Ba In the variable valve operating apparatus for an internal combustion engine that releases the fixation of the valve timing to the intermediate angle, the valve timing is fixed to the intermediate angle by the restriction mechanism when the engine is started, and the valve timing is being fixed. The gist is that the lubricating oil is supplied to the advance chamber and the retard chamber.

  According to the above invention, the lubricating oil can be supplied to the advance chamber and the retard chamber when the valve timing is fixed at the intermediate angle. As a result, the valve timing can be quickly changed after the engine start is completed.

  (15) The invention according to claim 15 is the variable valve operating apparatus for an internal combustion engine according to any one of claims 1 to 14, wherein the drive mechanism includes an advance chamber of the variable mechanism and the variable mechanism. The supply state of the lubricating oil to each of the retardation chamber and the intermediate chamber of the restriction mechanism is controlled by a single hydraulic control valve, and lubrication is performed between the hydraulic control valve, the variable mechanism, and the restriction mechanism. As an oil passage through which oil flows, an advance oil passage connecting the hydraulic control valve and the advance chamber, a retard oil passage connecting the hydraulic control valve and the retard chamber, the hydraulic control valve, and the oil passage The gist of the invention is that it comprises an intermediate oil passage connecting the intermediate chambers.

  (16) The invention according to claim 16 is the variable valve operating apparatus for an internal combustion engine according to claim 15, wherein the hydraulic control valve is configured to supply lubricating oil to the advance chamber, the retard chamber, and the intermediate chamber. As an operation mode for setting the supply state, the lubricant is supplied to the advance chamber, the lubricant is discharged from the retard chamber, and the supply state of the lubricant to the intermediate chamber is maintained in the second supply state. Mode A1, Mode A2 for discharging the lubricant from the advance chamber, supplying the lubricant to the retard chamber, and maintaining the supply state of the lubricant to the intermediate chamber in the second supply state, Stop supply of lubricant oil to the advance chamber and discharge of lubricant oil from the advance chamber, stop supply of lubricant oil to the retard chamber, and discharge of lubricant oil from the retard chamber, and The supply state of the lubricating oil to the intermediate chamber is the second supply state. Mode A3 for maintaining, mode A4 for supplying lubricant to the advance chamber, discharging lubricant from the retard chamber, and maintaining the supply state of lubricant to the intermediate chamber in the first supply state; The gist is that the operation mode of the hydraulic control valve is maintained in the mode A4 during engine start.

  (17) The invention according to claim 17 is the variable valve operating apparatus for an internal combustion engine according to claim 15, wherein the hydraulic control valve is configured to supply lubricating oil to the advance chamber, the retard chamber, and the intermediate chamber. As an operation mode for setting the supply state, the lubricant oil is supplied to the retard chamber, the lubricant oil is discharged from the advance chamber, and the supply state of the lubricant oil to the intermediate chamber is maintained in the second supply state. Mode B1, Mode B2 for discharging the lubricating oil from the retarding chamber, supplying the lubricating oil to the advance chamber, and maintaining the supply state of the lubricating oil to the intermediate chamber in the second supply state, Stop supply of lubricant oil to the retard chamber and discharge of lubricant oil from the retard chamber, stop supply of lubricant oil to the advance chamber and discharge of lubricant from the advance chamber, and The supply state of the lubricating oil to the intermediate chamber is the second supply state. Mode B3 for maintaining, mode B4 for supplying lubricating oil to the retarding chamber, discharging lubricating oil from the advance chamber, and maintaining the supply state of the lubricating oil to the intermediate chamber in the first supply state; The gist is that the operation mode of the hydraulic control valve is maintained in the mode B4 during engine start.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view showing a cross-sectional structure of a configuration of an internal combustion engine provided with the apparatus according to a first embodiment that embodies a variable valve operating apparatus for an internal combustion engine of the present invention. (A) The top view which shows the planar structure about the valve timing variable mechanism of the embodiment. (B) Sectional drawing which shows the cross-sectional structure which follows the DD line | wire of FIG. 2 (A) about the valve timing variable mechanism. Sectional drawing which shows the cross-sectional structure which follows the EE line | wire of FIG. 2 (A) 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 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. (A) The table which shows the relationship between the operation mode and the lubricating oil supply aspect with respect to a valve timing variable mechanism about the oil control valve of the embodiment. (B) A table showing the relationship among the operation mode, the operation mode of the variable valve timing mechanism, the operation mode of the intermediate lock pin, and the operation mode of the inter-chamber communication path for the oil control valve. The flowchart which shows the process sequence about "the 1st lubricating oil supply process" performed by the electronic controller of the embodiment. The schematic diagram which shows typically the structure of the lubricating oil path between a lubricating device and a valve timing variable mechanism about 2nd Embodiment which actualized the variable valve apparatus of the internal combustion engine of this invention. (A) About the 1st oil control valve of the embodiment, the table which shows the relationship between the operation mode and the lubricating oil supply aspect with respect to a valve timing variable mechanism. (B) The table which shows the relationship between the operation mode and the lubricating oil supply aspect with respect to a valve timing variable mechanism about the 2nd oil control valve of the embodiment. (C) The table which shows the relationship between the operation mode, the operation mode of the variable valve timing mechanism, the operation mode of the intermediate lock pin, and the operation mode of the inter-chamber communication path for the first oil control valve and the second oil control valve. The flowchart which shows the process sequence about "the 2nd lubricating oil supply process" performed by the electronic controller of the embodiment. The schematic diagram which expands the cross-section of a housing and a vane rotor on a plane, and shows this typically about the modification of the valve timing variable mechanism of each embodiment.

(First embodiment)
With reference to FIGS. 1 to 7, 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 air and fuel, a variable valve timing mechanism 40 that changes the valve timing of the intake valve 31, A lubricating device 70 for supplying lubricating oil to the variable valve timing mechanism 40 and an electronic control device 80 for comprehensively controlling these devices are provided.

  The engine body 20 is provided with a cylinder block 21 that burns a mixture of fuel supplied to the combustion chamber 23 via the injector 27 and air supplied to the combustion chamber 23 through the intake device. The cylinder block 21 is provided with a cylinder 24 that forms a combustion chamber 23. A piston 25 is provided in the cylinder 24. The reciprocating motion of the piston 25 is converted into the rotational motion of the crankshaft 26.

  An oil pan 71 for storing lubricating oil supplied to each part of the engine 10 is attached to the lower part of the cylinder block 21. 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 an intake port for the combustion chamber 23 and an exhaust valve 33 that opens and closes an exhaust port for the combustion chamber 23. An intake camshaft 32 is provided above the intake valve 31 to push it down by the intake cam. An exhaust camshaft 34 is provided above the exhaust valve 33 to push it down by the exhaust cam. The intake camshaft 32 and the exhaust camshaft 34 are drivingly connected to the crankshaft 26 via a timing chain.

  The lubricating device 70 supplies the lubricating oil in the oil pan 71 to each lubricating portion of the engine body 20 through the lubricating oil passage 74. In the middle of the lubricating oil passage 74, an oil pump 72 is provided for pumping lubricating oil from the oil pan 71 and discharging it. The lubricating oil discharged by the oil pump 72 passes through the lubricating oil passage 74 and is supplied to each part of the engine 10, and a part thereof is supplied to the variable valve timing mechanism 40 via the oil control valve 73. Further, 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 71 again. In the present embodiment, the variable valve mechanism is configured including the variable valve timing mechanism 40, the oil control valve 73, and the electronic control unit 80.

  The electronic control unit 80 determines the engine operation state, the vehicle running state, and the driver's request based on signals from various sensors including the accelerator position sensor 81, the throttle position sensor 82, the crank position sensor 83, and the cam position sensor 84. After grasping the above, the following control is performed. That is, a valve for adjusting the valve timing (hereinafter referred to as “valve timing VT”) of the intake valve 31 through throttle control for adjusting the intake flow rate, injection control for adjusting the fuel injection amount by the injector 27, and control of the oil control valve 73. Various controls including timing control are performed.

  The accelerator position sensor 81 outputs a signal corresponding to the depression amount of the accelerator pedal of the vehicle. The throttle position sensor 82 outputs a signal corresponding to the opening of the throttle valve. The crank position sensor 83 outputs a signal corresponding to the rotational speed of the crankshaft 26 (hereinafter referred to as “engine rotational speed NE”). The cam position sensor 84 outputs a signal corresponding to the rotation angle of the crankshaft 26.

  Here, in the valve timing control, a target value of the valve timing VT (hereinafter referred to as “target valve timing VTT”) is calculated based on the engine operating state, and based on the outputs of the crank position sensor 83 and the cam position sensor 84. An occasional valve timing VT is calculated, and the oil control valve 73 is controlled to maintain the actual valve timing VT at the calculated 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 with the cover removed from the housing 41. FIG. In the same figure, an arrow X indicates the rotation direction of the intake camshaft 32 and the variable valve timing mechanism 40. FIG. 2B shows a cross-sectional structure taken along line DD in FIG. 2A developed on a plane.

  The variable valve timing mechanism 40 is connected to the crankshaft 26 via a timing chain so that it rotates in synchronization with the shaft 26 and is fixed to the end of the intake camshaft 32 so that the shaft 32 is fixed. And a vane rotor 44 that rotates in synchronization with each other. Inside the sprocket 42, a housing 41 is provided that rotates in an integrated manner.

  The housing 41 is provided with three partition walls 43 that protrude toward the vane rotor 44 in the radial direction. The vane rotor 44 is provided with three vanes 45 protruding toward the housing 41. A space between adjacent partition walls 43 is partitioned into an advance chamber 46 and a retard chamber 47 by a corresponding vane 45.

  The advance chamber 46 is located on the rear side in the rotational direction of the intake camshaft 32 when the vane 45 is used as a reference, and the volume of the advance chamber 46 changes depending on the supply state of the lubricating oil by the lubricating device 70. It is. One retarding chamber 47 is located on the front side in the rotational direction of the intake camshaft 32 when the vane 45 is used as a reference, and the lubricating oil is supplied by the lubricating device 70 in the same manner as the advance chamber 46. The volume changes according to the above.

  The variable valve timing mechanism 40 changes the valve timing VT by changing the rotational phase of the vane rotor 44 with respect to the housing 41 and the sprocket 42 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 44 rotates to the advance side, that is, the front side in the rotation direction of the intake camshaft 32 with respect to the housing 41 due to the supply of the lubricant oil to the advance chamber 46 and the discharge of the lubricant oil from the retard chamber 47, the valve The timing VT changes to the advance side. When the vane rotor 44 rotates to the maximum advance side with respect to the housing 41, the valve timing VT is set to the most advance side timing (hereinafter referred to as “maximum advance angle VTmax”). Hereinafter, the rotational phase of the vane rotor 44 with respect to the housing 41 at this time is referred to as a “most advanced angle phase PH”. As a position when the vane rotor 44 rotates to the advance side as much as possible, a position where the vane 45 abuts against the partition wall 43 on the retard chamber 47 side or a partition wall on the retard chamber 47 side of the vane 45 is shown. A position in the vicinity of 43 can be set.

  When the vane rotor 44 rotates to the retard side, that is, the rear side in the rotation direction of the intake camshaft 32 with respect to the housing 41 due to the discharge of the lubricant from the advance chamber 46 and the supply of the lubricant to the retard chamber 47, the valve The timing VT changes to the retard side. When the vane rotor 44 rotates to the maximal retard side with respect to the housing 41, the valve timing VT is set to the most retarded timing (hereinafter, “most retarded angle VTmin”). Hereinafter, the rotational phase of the vane rotor 44 with respect to the housing 41 at this time is referred to as “most retarded phase PL”. In addition, as a position when the vane rotor 44 rotates to the retarding side to the maximum, a position where the vane 45 abuts against the partition wall 43 on the advance chamber 46 side or a partition wall on the advance chamber 46 side of the vane 45 is provided. A position in the vicinity of 43 can be set.

  The flow of the lubricating oil between each of the advance chamber 46 and the retard chamber 47 and the lubricating device 70 is blocked, that is, the lubricant oil is held in each of the advance chamber 46 and the retard chamber 47. Thus, when the relative rotation between the housing 41 and the vane rotor 44 is disabled, the valve timing VT is maintained at the current timing.

  The variable valve timing mechanism 40 regulates the rotation of the vane rotor 44 relative to the housing 41 regardless of the hydraulic pressure of the advance chamber 46 and the retard chamber 47, and sets the valve timing VT between the most advanced angle VTmax and the most retarded angle VTmin. An intermediate lock mechanism 50 is provided for fixing 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 at the time of starting the engine and the case where the valve timing is set to the timing on the retard side, the former can ensure higher starting performance. Become.

  The intermediate locking mechanism 50 operates based on the supply of lubricating oil from the lubricating device 70, and the rotational phase of the vane rotor 44 with respect to the housing 41 is at a rotational phase corresponding to the intermediate angle VTmdl (hereinafter referred to as “intermediate phase PM”). In addition, the housing 41 and the vane rotor 44 are fixed to each other to keep the valve timing VT at the intermediate angle VTmdl.

  As shown in FIG. 2B, specifically, the intermediate lock mechanism 50 is provided in the vane 45 to accommodate the intermediate lock pin 51, and the intermediate lock pin 51 provided in the vane 45. A lock spring 53 provided in the vane 45 to push the intermediate lock pin 51 in one direction, an intermediate chamber 52A provided in the storage chamber 52 and supplied with lubricating oil by the lubricating device 70, and provided in the storage chamber 52. A spring chamber 52 </ b> B that accommodates the lock spring 53, an intermediate communication path 52 </ b> C provided in the intermediate lock pin 51, and an intermediate lock hole 54 provided in the housing 41 is configured. The accommodation chamber is formed by an intermediate chamber 52A, a spring chamber 52B, and an intermediate communication path 52C. The intermediate lock pin 51 is provided with a portion having a small diameter (hereinafter, “pin small diameter portion 51A”) and a portion having a large diameter (hereinafter, “pin large diameter portion 51B”).

  Based on the relationship between the force of the lubricating oil in the intermediate chamber 52A and the force of the lock spring 53, the intermediate lock pin 51 has a direction projecting from the vane 45 (hereinafter referred to as “projection direction”) and a direction retracting into the vane 45 (hereinafter referred to as “removal direction”) "Accommodating direction"). The hydraulic pressure in the intermediate chamber 52A acts on the intermediate lock pin 51 in the accommodation direction, and the force of the lock spring 53 acts on the intermediate lock pin 51 in the protruding direction. Hereinafter, with respect to the position of the intermediate lock pin 51, the position protruding from the vane 45 and fitted into the intermediate lock hole 54 is referred to as “projection position”, and the position retracted into the vane 45 and accommodated in the vane 45 is “accommodation position”. And

  When lubricating oil is supplied to the intermediate chamber 52A by the lubricating device 70 and the intermediate chamber 52A is filled with the lubricating oil, that is, when the supply state of the lubricating oil to the intermediate chamber 52A is in the second supply state, the intermediate chamber Due to the force in the accommodation direction by the lubricating oil 52A, a force is generated to move the intermediate lock pin 51 in the accommodation direction. Then, when a force in the accommodation direction acts on the intermediate lock pin 51 with the intermediate lock pin 51 in the protruding position, the intermediate lock pin 51 is detached from the intermediate lock hole 54 and accommodated in the vane 45. As a result, the fixing of the housing 41 and the vane rotor 44 by the engagement between the intermediate lock pin 51 and the intermediate lock hole 54 is released, and the rotation of the vane rotor 44 with respect to the housing 41 is allowed.

  On the other hand, when the lubricant is discharged from the intermediate chamber 52A by the lubricating device 70 and the intermediate chamber 52A is not filled with the lubricant, that is, when the supply state of the lubricant to the intermediate chamber 52A is in the first supply state, the lock spring 53 The force in the protruding direction due to the pressure exceeds the force in the accommodating direction due to the lubricating oil in the intermediate chamber 52A. As a result, a force to move the intermediate lock pin 51 in the protruding direction is generated. In this state, when the rotational phase of the vane rotor 44 with respect to the housing 41 is in the intermediate phase PM, that is, when the circumferential positions of the intermediate lock pin 51 and the intermediate lock hole 54 coincide, 51 protrudes from the vane 45 and is fitted into the intermediate lock hole 54. As a result, the housing 41 and the vane rotor 44 are fixed to each other through the engagement between the intermediate lock pin 51 and the intermediate lock hole 54, so that their relative rotational phases are maintained at the intermediate phase PM.

  In the engine 10 having the intermediate lock mechanism 50, the valve timing VT is basically fixed by the intermediate lock mechanism 50 when the engine is stopped this time in order to ensure startability at the next engine start. That is, when an engine stop request based on the switching operation of the ignition switch from on to off is detected, the valve timing VT is set to the intermediate angle VTmdl before starting the engine stop operation based on the request, and the intermediate lock mechanism 50, the rotational phase of the vane rotor 44 is fixed. Then, after the rotation phase is fixed by the intermediate lock mechanism 50, the engine operation is stopped. As a result, the valve timing VT is already maintained at the intermediate angle VTmdl by the intermediate lock mechanism 50 at the next engine start, so that the engine 10 can be started with good startability.

  By the way, since the lubricating oil in the advance chamber 46 and the retard chamber 47 of the variable valve timing mechanism 40 flows out of the variable mechanism 40 while the engine is stopped, in many cases, the advance chamber 46 is used at the next engine start. The retard chamber 47 is not sufficiently filled with the lubricating oil. For this reason, when changing the valve timing VT after the engine start is completed, it is first necessary to fill the advance chamber 46 and the retard chamber 47 with the lubricating oil.

  On the other hand, in the engine 10 provided with the intermediate lock mechanism 50, the valve timing VT is held at the intermediate angle VTmdl at least until the engine start is completed, that is, a request for changing the valve timing VT is not set. Therefore, unless special control is performed, the timing when the supply of the lubricating oil to the advance chamber 46 and the retard chamber 47 is started is after the engine start is completed.

  For this reason, during the period until the advance chamber 46 and the retard chamber 47 are sufficiently filled with the lubricating oil immediately after the engine start is completed, it is not possible to respond to this even if the valve timing VT is advanced or retarded. Become.

  Therefore, in the present embodiment, the variable valve timing mechanism 40 is provided with a communication mechanism that allows the advance chamber 46 and the retard chamber 47 to communicate with each other when the intermediate lock pin 51 is in the protruding position. In other words, this communication mechanism allows the advance chamber 46 and the retard chamber 47 to communicate with each other by forming a single passage when the intermediate lock pin 51 is in the protruding position. When the lubricating oil is supplied to one of the corner chambers 47, the lubricating oil can be supplied to the advance chamber 46 and the retard chamber 47. The communication mechanism includes a vane 45 provided with an intermediate lock pin 51 and an intermediate lock pin 51.

The details of the structure of such a communication mechanism will be described with reference to FIG. FIG. 3 shows a cross-sectional structure developed along a line E-E in FIG.
As shown in FIG. 3, the vane 45 having the intermediate lock pin 51 is provided with an inter-chamber communication passage 60 that communicates the advance chamber 46 and the retard chamber 47 when the intermediate lock pin 51 is in the protruding position. ing. This inter-chamber communication passage 60 is a first communication passage 61 that communicates the retard chamber 47 and the intermediate communication passage 52C as a part of the storage chamber 52, and a first communication passage 61 that communicates the advance chamber 46 and the intermediate communication passage 52C. The two communication paths 62 and the intermediate communication path 52 </ b> C of the intermediate lock pin 51 are configured.

  As shown in FIG. 3A, when the pin large-diameter portion 51B of the pin 51 is located between the first communication path 61 and the second communication path 62 when the intermediate lock pin 51 is in the storage position, When the space between the first communication passage 61 and the second communication passage 62 is blocked by the pin large-diameter portion 51B, the advance chamber 46 and the retard chamber 47 are blocked. At this time, when the lubricant is supplied to one of the advance chamber 46 and the retard chamber 47, the lubricant supplied to one of the first communication passage 61 and the second communication passage 62 is blocked by the intermediate lock pin 51. Therefore, distribution to the other is prohibited.

  On the other hand, as shown in FIG. 3B, when the pin small diameter portion 51A of the pin 51 is located between the first communication path 61 and the second communication path 62 when the intermediate lock pin 51 is in the protruding position. That is, when the first communication path 61, the intermediate communication path 52C, and the second communication path 62 communicate with each other, the advance chamber 46 and the retard chamber 47 communicate with each other. As a result, when the lubricant is supplied to one of the advance chamber 46 and the retard chamber 47, the lubricant supplied to one of the first communication passage 61 and the second communication passage 62 passes through the intermediate communication passage 52C. Will also be distributed and supplied to the other.

  According to the variable valve timing mechanism 40 having such a communication mechanism, the advance chamber 46 and the retard chamber 47 are communicated with each other when the intermediate lock pin 51 is in the protruding position. By supplying the lubricating oil to one of the chamber 46 and the retarding chamber 47, the lubricating oil is also supplied to the other chamber. That is, even when the lubricating oil is supplied to one of the advance chamber 46 and the retard chamber 47 while the valve timing VT is fixed to the intermediate angle VTmdl by the intermediate lock mechanism 50 when the engine is started. Similarly, the lubricating oil is supplied to the other chamber. Accordingly, the lubricating oil can be supplied to the advance chamber 46 and the retard chamber 47 when the valve timing VT is maintained at the intermediate angle VTmdl during engine startup.

  FIG. 4 schematically shows a cross-sectional structure of the variable valve timing mechanism 40. This figure schematically shows a sectional structure of the variable valve timing mechanism 40 taken along the line E-E in FIG.

  When the rotational phase of the vane rotor 44 with respect to the housing 41 is changed between the most advanced angle phase PH shown in FIG. 4A and the most retarded angle phase PL shown in FIG. The pin 51 is maintained in the storage position. Further, even when the rotational phase of the vane rotor 44 is in the intermediate phase PM, as long as the intermediate lock pin 51 is accommodated in the vane 45 as the lubricating oil is supplied to the intermediate chamber 52A, FIG. ), The rotation phase of the vane rotor 44 is not fixed to the intermediate phase PM.

  On the other hand, when the rotational phase of the vane rotor 44 is in the intermediate phase PM, when the lubricating oil is discharged from the intermediate chamber 52A and a force in the protruding direction acts on the intermediate lock pin 51, FIG. As shown in the figure, the intermediate lock pin 51 protrudes from the vane 45 and is fitted into the intermediate lock hole 54 by the urging of the lock spring 53, whereby the vane rotor 44 is held at the intermediate phase PM.

  Here, in FIGS. 4A to 4C, since the intermediate lock pin 51 is maintained in the accommodation position, the pin 51 has a large diameter between the first communication path 61 and the second communication path 62. Blocked by the part 51B. That is, in the accommodation position of the intermediate lock pin 51, the lubricating oil is prohibited from flowing between the advance chamber 46 and the retard chamber 47 regardless of the phase of rotation of the vane rotor 44. On the other hand, in FIG. 4D, when the intermediate lock pin 51 is maintained at the protruding position, the pin small-diameter portion 51A of the pin 51 is located between the first communication path 61 and the second communication path 62. The first communication path 61, the intermediate communication path 52C, and the second communication path 62 are communicated, and the advance chamber 46 and the retard chamber 47 are communicated. That is, at the protruding position of the intermediate lock pin 51, when the rotational phase of the vane rotor 44 is fixed to the intermediate phase PM and the lubricating oil is supplied to one of the advance chamber 46 and the retard chamber 47, The lubricating oil supplied to one of the passage 61 and the second communication passage 62 is circulated and supplied to the other through the intermediate communication passage 52C.

  With reference to FIG. 5, the flow mode of the lubricating oil between the variable valve timing mechanism 40 and the lubricating device 70 will be described. In addition, the figure has shown typically the structure of the oil path between these apparatuses.

  The lubricating device 70 includes an oil pan 71, an oil pump 72, an oil control valve 73, and a lubricating oil passage 74 through which lubricating oil flows between them. Further, as this lubricating oil passage 74, a supply oil passage 75 for supplying lubricating oil from the oil pan 71 to the oil control valve 73 (indicated as OCV in the drawing), and the lubricating oil is recirculated from the oil control valve 73 to the oil pan 71. Lubricating oil is circulated between the oil discharge valve 76, the advance oil passage 77 through which the lubricating oil flows between the oil control valve 73 and each advance chamber 46, and the oil control valve 73 and each retard chamber 47. A retarding oil passage 78 and an intermediate oil passage 79 through which lubricating oil flows between the oil control valve 73 and the intermediate chamber 52A are provided.

  The advance oil passage 77, the retard oil passage 78, and the intermediate oil passage 79 directly connect the oil control valve 73 to the corresponding one of the advance chamber 46, the retard chamber 47, and the intermediate chamber 52A. ing. That is, the intermediate oil passage 79 is formed as an oil passage through which the lubricating oil flows between the oil control valve 73 without passing through either the advance chamber 46 or the retard chamber 47.

  The oil control valve 73 switches the connection state between the supply oil passage 75 and the discharge oil passage 76 and the advance oil passage 77, the retard oil passage 78, and the intermediate oil passage 79, thereby causing the advance chamber 46 and the retard chamber 47. The supply state of the lubricating oil to the intermediate chamber 52A can be set to any one of the first mode to the fifth mode.

  FIG. 6 shows the relationship between the operation modes of the oil control valve 73 and the supply mode of the lubricating oil to the advance chamber 46, the retard chamber 47, and the intermediate chamber 52A (FIG. 6A), and the operation modes and variable valve timing. A summary of the relationship between the mechanism 40 (denoted as VVT in the figure), the operation modes of the intermediate lock pin 51 and the inter-chamber communication path 60 (FIG. 6B) is shown.

  In the first mode, the lubricating oil from the oil pump 72 flows in the order of the supply oil passage 75 and the advance oil passage 77 and is supplied to the advance chamber 46. Further, the lubricating oil in the retarding chamber 47 flows in the order of the retarding oil passage 78 and the discharge oil passage 76 and is returned to the oil pan 71. Further, the lubricating oil from the oil pump 72 flows in the order of the supply oil passage 75 and the intermediate oil passage 79 and is supplied to the intermediate chamber 52A. As a result, the intermediate lock pin 51 becomes the accommodation position, and the first communication passage 61 and the second communication passage 62 are blocked by the pin large-diameter portion 51B of the pin 51 being located, so that the advance chamber 46 is retarded from the advance chamber. The distribution of lubricating oil to 47 is prohibited.

  In the second mode, the lubricating oil in the advance chamber 46 flows in the order of the advance oil passage 77 and the discharge oil passage 76 and is returned to the oil pan 71. Further, the lubricating oil from the oil pump 72 flows in the order of the supply oil passage 75 and the retard oil passage 78 and is supplied to the retard chamber 47. Further, the lubricating oil from the oil pump 72 flows in the order of the supply oil passage 75 and the intermediate oil passage 79 and is supplied to the intermediate chamber 52A. As a result, the intermediate lock pin 51 becomes the accommodation position, and the first communication passage 61 and the second communication passage 62 are blocked by the pin large-diameter portion 51B of the pin 51 being located, so that the advance chamber 46 is retarded from the advance chamber. The distribution of lubricating oil to 47 is prohibited.

  In the third mode, the lubricating oil flows from the oil pump 72 to the advance chamber 46 through the oil control valve 73, and the lubricating oil from the advance chamber 46 to the oil pan 71 through the oil control valve 73. Any flow is interrupted. Further, the flow of the lubricating oil from the oil pump 72 to the retarding chamber 47 through the oil control valve 73 and the flow of the lubricating oil from the retarding chamber 47 to the oil pan 71 through the oil control valve 73 are any. Is also blocked. On the other hand, in the intermediate chamber 52A, the lubricating oil from the oil pump 72 is circulated and supplied in the order of the supply oil passage 75 and the intermediate oil passage 79. As a result, the intermediate lock pin 51 becomes the accommodation position, and the first communication passage 61 and the second communication passage 62 are blocked by the pin large-diameter portion 51B of the pin 51 being positioned, so that the advance chamber 46 and the retard chamber are provided. The distribution of lubricating oil between 47 is prohibited.

  In the fourth mode, the lubricating oil from the oil pump 72 flows in the order of the supply oil passage 75 and the advance oil passage 77 and is supplied to the advance chamber 46. Further, the lubricating oil in the retarding chamber 47 flows in the order of the retarding oil passage 78 and the discharge oil passage 76 and is returned to the oil pan 71. Further, the lubricating oil in the intermediate chamber 52 </ b> A flows in the order of the intermediate oil passage 79 and the discharge oil passage 76 and is returned to the oil pan 71. As a result, the intermediate lock pin 51 is in the protruding position, and the first communication path 61 and the second communication path 62 are communicated by the pin small-diameter portion 51A of the pin 51 being located, that is, the first communication path 61 and The intermediate communication path 52 </ b> C and the second communication path 62 form an inter-chamber communication path 60 that is a single path, allowing the lubricating oil to flow from the advance chamber 46 to the retard chamber 47.

  In the fifth mode, the lubricating oil from the oil pump 72 flows in the order of the supply oil passage 75 and the advance oil passage 77 and is supplied to the advance chamber 46. Further, the lubricating oil in the retarding chamber 47 flows in the order of the retarding oil passage 78 and the discharge oil passage 76 and is returned to the oil pan 71. Further, the lubricating oil in the intermediate chamber 52 </ b> A flows in the order of the intermediate oil passage 79 and the discharge oil passage 76 and is returned to the oil pan 71. Further, the supply amount of the lubricating oil to the advance chamber 46 is larger than the supply amount in the first mode and the fourth mode. That is, the supply amount of the lubricating oil to the advance chamber 46 is the maximum among a plurality of modes. And according to the said mode, the intermediate | middle lock pin 51 becomes a protrusion position similarly to 4th mode, and it communicates because the pin small diameter part 51A of the same pin 51 is located between the 1st communicating path 61 and the 2nd communicating path 62. That is, the first communication passage 61, the intermediate communication passage 52C, and the second communication passage 62 form an inter-chamber communication passage 60 that is a single passage, and the lubricating oil is supplied from the advance chamber 46 to the retard chamber 47. Distribution is allowed.

  With reference to FIG. 7, the details of the processing procedure for the “first lubricating oil supply process”, which is a process for supplying lubricating oil to the advance chamber 46 and the retard chamber 47 at the time of starting, will be described. This process is repeatedly executed by the electronic control unit 80 at predetermined control intervals while the engine 10 is operating.

  In this process, first, when it is determined in step S110 that the ignition switch is switched from OFF to ON, that is, when a start request for the engine 10 is detected, the oil control valve 73 (in the figure) is detected in step S120. Then, the operation mode (indicated as OCV) is set to the fifth mode. Thereby, the supply of the lubricating oil to the advance chamber 46 is started at the maximum supply amount.

  Then, when it is determined in the next step S130 that the engine start has been completed and it is determined in step S140 that the target valve timing VTT is set to be different from the intermediate angle VTmdl, the valve timing VT is determined in step S150. Is changed toward the target valve timing VTT. That is, when the target valve timing VTT is on the advanced side with respect to the intermediate angle VTmdl, the oil control valve 73 is set to the first mode, and when the target valve timing VTT is on the retarded side with respect to the intermediate angle VTmdl, the oil control valve 73 is set. Is set to the second mode.

  When it is determined in step S160 that the ignition switch has been switched from on to off, that is, when a stop request for the engine 10 is detected, the valve timing VT is changed toward the intermediate angle VTmdl in step S170. . That is, when the valve timing VT is on the advance side with respect to the intermediate angle VTmdl, the oil control valve 73 is set to the second mode and the valve timing VT is changed to the position on the retard side with respect to the intermediate angle VTmdl. The control valve 73 is set to the fourth mode or the fifth mode, and the valve timing VT is changed toward the intermediate angle VTmdl. On the other hand, when the valve timing VT is behind the intermediate angle VTmdl, the oil control valve 73 is set to the fourth mode or the fifth mode and the valve timing VT is changed toward the intermediate angle VTmdl. In any case, since the intermediate lock pin 51 is about to move in the protruding direction, when the valve timing VT coincides with the intermediate angle VTmdl, the intermediate lock pin 51 shifts from the storage position to the protruding position. And is fitted into the intermediate lock hole 54.

  Then, when it is determined in step S180 that the valve timing VT is fixed at the intermediate angle VTmdl, the operation of the engine 10 is stopped based on a stop request by an ignition switch switching operation in step S190. Thus, the next engine start is performed in a state where the valve timing VT is fixed to the intermediate angle VTmdl.

According to the present embodiment, the following effects can be achieved.
(1) In the present embodiment, since the advance chamber 46 and the retard chamber 47 communicate with each other when the intermediate lock pin 51 is in the protruding position, the lubrication device 70 supplies lubricating oil to the advance chamber 46. By doing so, the lubricating oil is also supplied to the retard chamber 47. That is, when the engine is started and the valve timing VT is fixed to the intermediate angle VTmdl by the intermediate lock mechanism 50, when the lubricating oil is supplied to the advance chamber 46, the retard chamber 47 is similarly supplied. Lubricating oil is supplied. Accordingly, the lubricating oil can be supplied to the advance chamber 46 and the retard chamber 47 when the intermediate lock pin 51 is in the protruding position.

  (2) In the present embodiment, the advance chamber 46 and the retard chamber 47 communicate with each other when the operation mode of the oil control valve 73 is set to the fourth mode and the fifth mode. By supplying the lubricating oil, the lubricating oil is also supplied to the retarding chamber 47. Accordingly, the lubricating oil can be supplied to the advance chamber 46 and the retard chamber 47 when the operation mode of the oil control valve 73 is set to the fourth mode and the fifth mode.

  (3) In this embodiment, since the supply mode of the lubricating oil to the variable valve timing mechanism 40 at the time of starting the engine is set to the fifth mode, that is, the supply amount of the lubricating oil to the advance chamber 46 is maximum. Since the supply mode is set, the lubricant oil can be supplied to the advance chamber 46 more quickly than when the supply mode in which the supply amount of the lubricant is maximized is not set.

(4) In the present embodiment, the lubricant oil can be supplied to the advance chamber 46 and the retard chamber 47 when the valve timing VT is fixed to the intermediate angle VTmdl. As a result, the valve timing VT can be quickly changed after the engine start is completed.
(Second Embodiment)
With reference to FIGS. 8 to 10, a second embodiment in which the variable valve operating apparatus for an internal combustion engine of the present invention is embodied as a variable valve operating apparatus for changing the valve timing of an intake valve will be described.

  The variable valve operating apparatus of the present embodiment is obtained by adding the following changes to the configuration of the first embodiment. In other words, the variable valve operating apparatus according to the present embodiment includes a first oil control valve 91A and a second oil control valve 91B instead of the lubricating apparatus 70 according to the first embodiment having the single oil control valve 73. A device 90 is provided. The first oil control valve 91A supplies or discharges the lubricating oil to the advance chamber 46 and the retard chamber 47, and the second oil control valve 91B supplies the lubricant to the intermediate chamber 52A. Or a device for discharging is provided. Hereinafter, a detailed change from the configuration of the first embodiment that occurs with this change will be described. In addition, about the structure which is common in the said 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  In the variable valve operating apparatus according to the present embodiment, since the communication mechanism described in the first embodiment is provided in the variable valve timing mechanism 40, a configuration in which two oil control valves are mounted is adopted. In addition, the lubricating oil can be quickly supplied to both the advance chamber 46 and the retard chamber 47.

  With reference to FIG. 8, the flow mode of the lubricating oil between the variable valve timing mechanism 40 and the lubricating device 90 will be described. In addition, the figure has shown typically the structure of the oil path between these apparatuses.

  The lubricating device 90 includes an oil pan 71, an oil pump 72, a first oil control valve 91A (denoted as OCV1 in the drawing) and a second oil control valve 91B (denoted as OCV2 in the diagram), and mutually lubricates between them. And a lubricating oil passage 92 through which oil flows. Further, as the lubricating oil passage 92, a first supply oil passage 93 that supplies lubricating oil from the oil pan 71 to the first oil control valve 91A, and a first oil passage that returns the lubricating oil to the oil pan 71 from the first oil control valve 91A. 1 exhaust oil passage 94, an advance oil passage 97 through which lubricating oil flows between the first oil control valve 91A and each advance chamber 46, and between the first oil control valve 91A and each retard chamber 47. And a retard oil passage 98 through which the lubricating oil flows. A second supply oil passage 95 for supplying lubricating oil from the oil pan 71 to the second oil control valve 91B; a second discharge oil passage 96 for returning the lubricating oil from the second oil control valve 91B to the oil pan 71; An intermediate oil passage 99 is provided between the second oil control valve 91B and the intermediate chamber 52A for flowing lubricating oil.

  The first oil control valve 91A switches the connection state between the first supply oil passage 93 and the first discharge oil passage 94 and the advance oil passage 97 and the retard oil passage 98, whereby the advance chamber 46 and the retard chamber 47. The supply state of the lubricating oil can be set to any one of the first mode to the third mode. Further, the second oil control valve 91B switches the connection state of the second supply oil passage 95, the second discharge oil passage 96, and the intermediate oil passage 99, thereby changing the supply state of the lubricating oil to the intermediate chamber 52A in the first mode or The second mode can be set.

  FIG. 9 shows the relationship between the operation modes of the first oil control valve 91A (indicated as OCV1 in the drawing) and the mode of supply of the lubricating oil to the advance chamber 46 and the retard chamber 47 (FIG. 9A), and the second The relationship between the operation modes of the oil control valve 91B (indicated as OCV2 in the drawing) and the mode of supply of the lubricating oil to the intermediate chamber 52A (FIG. 9B), the operation modes of the first oil control valve 91A and the second The relationship between each operation mode of the oil control valve 91B, the valve timing variable mechanism 40 (denoted as VVT in the drawing), the operation mode of the intermediate lock pin 51, and the inter-chamber communication path 60 (FIG. 9C). A summary is shown.

  9C, in the first mode, the lubricating oil from the oil pump 72 flows in the order of the first supply oil passage 93 and the advance oil passage 97 and is supplied to the advance chamber 46. Further, the lubricating oil in the retarding chamber 47 flows in the order of the retarding oil passage 98 and the first discharge oil passage 94 and is returned to the oil pan 71. Further, the lubricating oil from the oil pump 72 flows in the order of the second supply oil passage 95 and the intermediate oil passage 99 and is supplied to the intermediate chamber 52A. As a result, the intermediate lock pin 51 becomes the accommodation position, and the first communication passage 61 and the second communication passage 62 are blocked by the pin large-diameter portion 51B of the pin 51 being located, so that the advance chamber 46 is retarded from the advance chamber. The distribution of lubricating oil to 47 is prohibited.

  9C, in the second mode, the lubricating oil in the advance chamber 46 flows in the order of the advance oil passage 97 and the first discharge oil passage 94 and is returned to the oil pan 71. Further, the lubricating oil from the oil pump 72 flows in the order of the first supply oil passage 93 and the retard oil passage 98 and is supplied to the retard chamber 47. Further, the lubricating oil in the intermediate chamber 52 </ b> A flows in the order of the intermediate oil passage 99 and the second discharge oil passage 96 and is returned to the oil pan 71. As a result, the intermediate lock pin 51 is in the protruding position, and the first communication path 61 and the second communication path 62 are communicated by the pin small-diameter portion 51A of the pin 51 being located, that is, the first communication path 61 and The intermediate communication path 52 </ b> C and the second communication path 62 form an inter-chamber communication path 60 that is a single path, allowing the lubricating oil to flow from the advance chamber 46 to the retard chamber 47.

  9C, in the third mode, the lubricating oil from the oil pump 72 flows in the order of the first supply oil passage 93 and the advance oil passage 97 and is supplied to the advance chamber 46. Further, the lubricating oil in the retarding chamber 47 flows in the order of the retarding oil passage 98 and the first discharge oil passage 94 and is returned to the oil pan 71. Further, the lubricating oil in the intermediate chamber 52 </ b> A flows in the order of the intermediate oil passage 99 and the second discharge oil passage 96 and is returned to the oil pan 71. As a result, the intermediate lock pin 51 is in the protruding position, and the first communication path 61 and the second communication path 62 are communicated by the pin small-diameter portion 51A of the pin 51 being located, that is, the first communication path 61 and The intermediate communication path 52 </ b> C and the second communication path 62 form an inter-chamber communication path 60 that is a single path, allowing the lubricating oil to flow from the advance chamber 46 to the retard chamber 47.

  9C, in the fourth mode, the flow of the lubricating oil from the oil pump 72 to the advance chamber 46 through the first oil control valve 91A, and the first oil control valve 91A from the advance chamber 46. Any flow of the lubricating oil to the oil pan 71 via the is blocked. Further, the flow of lubricating oil from the oil pump 72 to the retarding chamber 47 through the first oil control valve 91A, and the lubricating oil from the retarding chamber 47 to the oil pan 71 through the first oil control valve 91A. Any flow is interrupted. On the other hand, in the intermediate chamber 52A, the lubricating oil from the oil pump 72 is circulated and supplied in the order of the second supply oil passage 95 and the intermediate oil passage 99. As a result, the intermediate lock pin 51 becomes the accommodation position, and the first communication passage 61 and the second communication passage 62 are blocked by the pin large-diameter portion 51B of the pin 51 being located, so that the advance chamber 46 is retarded from the advance chamber. The distribution of lubricating oil to 47 is prohibited.

  With reference to FIG. 10, the details of the processing procedure of “second lubricating oil supply process”, which is a process for supplying lubricating oil to the advance chamber 46 and the retard chamber 47 at the start, will be described. This process is repeatedly executed by the electronic control unit 80 at predetermined control intervals while the engine 10 is operating.

  In this process, first, when it is determined in step S210 that the ignition switch has been switched from OFF to ON, that is, when a request for starting the engine 10 is detected, in step S220, the first oil control valve 91A ( The operation mode of OCV1 in the figure is set to either the first mode or the second mode, and the operation mode of the second oil control valve 91B (indicated as OCV2 in the figure) is set to the first mode. As a result, the supply of the lubricating oil to either the advance chamber 46 or the retard chamber 47 is started.

  Then, when it is determined in the next step S230 that the engine start has been completed and it is determined in step S240 that the target valve timing VTT is set to be different from the intermediate angle VTmdl, the valve timing VT is determined in step S250. Is changed toward the target valve timing VTT. That is, when the target valve timing VTT is more advanced than the intermediate angle VTmdl, the operation mode of the first oil control valve 91A is set to the first mode, and the operation mode of the second oil control valve 91B is set to the second mode. To do. When the target valve timing VTT is behind the intermediate angle VTmdl, the operation mode of the first oil control valve 91A is set to the second mode, and the operation mode of the second oil control valve 91B is set to the second mode.

  When it is determined in step S260 that the ignition switch has been switched from on to off, that is, when a request to stop the engine 10 is detected, the valve timing VT is changed toward the intermediate angle VTmdl in step S270. . That is, when the valve timing VT is more advanced than the intermediate angle VTmdl, the operation mode of the first oil control valve 91A is set to the second mode, and the operation mode of the second oil control valve 91B is set to the first mode. . When the valve timing VT is behind the intermediate angle VTmdl, the operation mode of the first oil control valve 91A is set to the first mode, and the operation mode of the second oil control valve 91B is set to the first mode. In any case, since the intermediate lock pin 51 is about to move in the protruding direction, when the valve timing VT coincides with the intermediate angle VTmdl, the intermediate lock pin 51 shifts from the storage position to the protruding position. And is fitted into the intermediate lock hole 54.

  When it is determined in step S280 that the valve timing VT is fixed to the intermediate angle VTmdl, the operation of the engine 10 is stopped based on the stop request by the ignition switch switching operation in step S290. Thus, the next engine start is performed in a state where the valve timing VT is fixed to the intermediate angle VTmdl.

According to the variable valve operating apparatus for an internal combustion engine of the present embodiment, in addition to the following effects, effects similar to the effects (1) and (4) of the first embodiment can be achieved.
(5) In this embodiment, since the advance chamber 46 and the retard chamber 47 are communicated with each other when the operation mode of the second oil control valve 91B is set to the first mode, the first oil control valve 91A. When the operation mode is set to the first mode or the second mode, the lubricant is supplied to the advance chamber 46 or the retard chamber 47, so that the lubricant is supplied to the advance chamber 46 and the retard chamber 47. Will be able to supply.

(Other embodiments)
The embodiment of the present invention is not limited to the above-described embodiment, and can be modified as shown below, for example.

  The following operation mode can be further added to the oil control valve 73 of the first embodiment. That is, the sixth mode in which the lubricant is supplied to the advance chamber 46, the supply of the lubricant to the retard chamber 47 and the discharge of the lubricant from the retard chamber 47 is stopped, and the lubricant is discharged from the intermediate chamber 52A. Can also be provided.

  In the first embodiment, the operation mode of the oil control valve 73 is set to the fifth mode when the start request of the engine 10 is detected. However, the operation mode of the oil control valve 73 when the start request is detected. The setting of is not limited to this. That is, the fourth mode can be set.

  In each of the above embodiments, as the communication mechanism, the first communication path 61 and the second communication path 62 are provided inside the vane 45 and the intermediate communication pin 52C is provided in the intermediate lock pin 51. The configuration is not limited to this. For example, as shown in FIG. 11, the communication mechanism includes a first communication path 102 that allows the distal end portion of the intermediate lock pin 101 to be fitted and a retard chamber 47 that communicates with the intermediate communication path 104 and the intermediate communication path 104. The housing 41 may be provided with a second communication passage 103 that communicates with the advance chamber 46. Even when this configuration is adopted, as shown in FIG. 11A, when the intermediate lock pin 101 is in the storage position, the single communication path 102, the intermediate communication path 104, and the second communication path 103 are formed. The advance chamber 46 and the retard chamber 47 communicate with each other through one passage. On the other hand, as shown in FIG. 11B, when the intermediate lock pin 101 is in the projecting position, the intermediate lock pin 101 blocks the first communication path 102, the intermediate communication path 104, and the second communication path 103, so that the advancement proceeds. The space between the corner chamber 46 and the retard chamber 47 is blocked. In short, any configuration may be used as long as the advance chamber and the retard chamber can communicate with each other when the intermediate lock pin is in the protruding position.

  In each of the above-described embodiments, the intermediate lock mechanism 50 has a configuration in which the vane rotor 44 includes the intermediate chamber 52A, the spring chamber 52B, and the intermediate communication passage 52C, the intermediate lock pin 51, the lock spring 53, Although the communication mechanism is provided and the housing 41 is provided with the intermediate lock hole 54, the configuration of the intermediate lock mechanism is not limited to this. For example, the housing chamber 52, the intermediate lock pin 51, the lock spring 53, and the communication mechanism can be provided in the housing 41, and the intermediate lock hole 54 can be provided in the vane rotor 44.

  In each of the above embodiments, when the hydraulic pressure of the intermediate chamber 52A with respect to the intermediate lock pin 51 is released, the pin 51 is maintained in a state in which the pin 51 can protrude from the vane 45, but the intermediate chamber 52A, the lock spring 53, This relationship can also be set to the opposite of the above embodiments. That is, the intermediate lock pin 51 can be moved in the protruding direction by the hydraulic pressure in the intermediate chamber, and the intermediate lock pin 51 can be moved in the accommodation direction by the force of the lock spring 53.

  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 the embodiment.

  The configuration of the variable valve operating apparatus to which the present invention is applied including the configurations of the variable valve timing mechanism 40 and the intermediate lock mechanism 50 are not limited to the contents exemplified in the above embodiments. In short, it is provided with a variable valve timing mechanism that changes the valve timing, an intermediate lock mechanism that fixes the valve timing to a specific intermediate angle by an intermediate lock pin, and a lubrication device that controls the supply state of lubricating oil to these mechanisms. If there is, the present invention can be applied to any variable valve operating apparatus, and in this case also, the operational effects according to the operational effects of the above-described embodiments can be achieved.

  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 ... variable valve timing mechanism, 41 ... housing (input side rotator, (engagement side rotator)), 42 ... sprocket, 43 ... partition wall, 44 ... vane rotor (Output-side rotator), 45 ... vane (accommodating-side rotator), 46 ... advance chamber, 47 ... retard chamber, 50 ... intermediate lock mechanism (regulator), 51 ... intermediate lock pin (regulator), 51A ... Pin small diameter part, 51B ... Pin large diameter part, 52 ... Accommodating chamber, 52A ... Intermediate chamber, 52B ... Spring chamber, 52C ... Intermediate communication path, 53 ... Lock spring, 54 ... Medium Lock hole (regulatory hole), 60 ... inter-chamber communication path, 61 ... first communication path, 62 ... second communication path, 70 ... lubrication device (drive mechanism), 71 ... oil pan, 72 ... oil pump, 73 ... oil Control valve (hydraulic control valve), 74 ... lubricating oil passage, 75 ... supply oil passage, 76 ... discharge oil passage, 77 ... advance oil passage, 78 ... retard oil passage, 79 ... intermediate oil passage, 80 ... electronic control , 81 ... Accelerator position sensor, 82 ... Throttle position sensor, 83 ... Crank position sensor, 84 ... Cam position sensor, 90 ... Lubrication device, 91A ... First oil control valve, 91B ... Second oil control valve, 92 ... Lubrication Oil path 93... First supply oil path 94. First exhaust oil path 95. Second supply oil path 96. Second exhaust oil path 97. Advance oil path 98 98 Delay oil path 99 ... intermediate oil passage, 00 ... communication mechanism, 101 ... intermediate lock pin, 102 ... first communication passage, 103 ... second communication passage, 104 ... intermediate communication passage.

Claims (17)

A variable mechanism that changes the valve timing of the intake valve or exhaust valve as the engine valve between the most advanced angle and the most retarded angle, and the valve timing of the engine valve that is between the most advanced angle and the most retarded angle A regulation mechanism that fixes the intermediate angle of the variable mechanism, and a drive mechanism that controls the supply state of the lubricating oil to each of the advance angle chamber of the variable mechanism, the retard angle chamber of the variable mechanism, and the intermediate chamber of the restriction mechanism,
The regulating mechanism sets the valve timing of the engine valve to the intermediate angle when the operating state of the regulating valve is in a fixed state based on the supply state of the lubricating oil to the intermediate chamber being set to the first supply state. And fixing the valve timing of the engine valve to the intermediate angle when the operation state of the engine valve is in the release state based on the fact that the supply state of the lubricating oil to the intermediate chamber is set to the second supply state In the variable valve operating apparatus for an internal combustion engine that releases the
The variable valve operating apparatus for an internal combustion engine, wherein the advance chamber and the retard chamber are communicated with each other by a communication mechanism when the restriction mechanism is in a fixed state. The variable valve operating apparatus for an internal combustion engine according to claim 1,
The variable valve operating apparatus for an internal combustion engine, wherein the communication between the advance chamber and the retard chamber by the communication mechanism is released when the regulating mechanism shifts from the fixed state to the released state. The variable valve operating apparatus for an internal combustion engine according to claim 1 or 2,
The variable mechanism includes an input side rotating body that rotates by a force transmitted from a crankshaft of an internal combustion engine, 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. The advance angle chamber and the retard angle chamber are provided so as to be partitioned from each other between the input side rotating body and the output side rotating body.
The regulation mechanism is provided in a storage chamber of a storage-side rotary body that is one of the input-side rotary body and the output-side rotary body and between a state of protruding from the storage chamber and a state of being stored in the storage chamber The internal combustion engine is characterized in that it is configured to include a regulating body that operates in the above-described manner and the intermediate chamber that is provided as a part of the storage chamber and is supplied with lubricating oil from the drive mechanism. Variable valve device. The variable valve operating apparatus for an internal combustion engine according to claim 3,
The variable valve operating apparatus for an internal combustion engine, wherein the advance chamber and the retard chamber are communicated with each other through the storage chamber by the communication mechanism when the regulating body is in a protruding state. The variable valve operating apparatus for an internal combustion engine according to claim 4,
The communication mechanism includes a first communication passage that communicates the retard chamber and the storage chamber with each other when the restricting body protrudes, and the advance chamber when the restricting body protrudes. A variable valve operating apparatus for an internal combustion engine, comprising a second communication path that communicates the storage chamber with the storage chamber. The variable valve operating apparatus for an internal combustion engine according to claim 5,
The communication mechanism includes an intermediate communication path that is provided in the storage chamber and connects the first communication path and the second communication path to each other when the restricting body protrudes. And the advance chamber and the retard chamber are connected to each other by a single passage formed by the first communication passage, the intermediate communication passage, and the second communication passage when the restricting body is in a protruding state. A variable valve operating apparatus for an internal combustion engine, characterized in that it communicates. The variable valve operating apparatus for an internal combustion engine according to claim 6,
The intermediate communication passage is switched between a state in which the restricting body protrudes from the storage chamber and a state in which the control body is stored in the storage chamber. Between the first communication path and the second communication path when in the protruding position, and the first communication path and the second communication when in the accommodated position. A variable valve operating apparatus for an internal combustion engine, characterized by not communicating with any of the passages. The variable valve operating apparatus for an internal combustion engine according to claim 6 or 7,
The advance chamber, the retard chamber, and the storage chamber communicate with each other only through the intermediate communication path, that is, when the first communication path and the second communication path are connected to each other by the intermediate communication path. The variable valve operating apparatus for an internal combustion engine, wherein the lubricating oil is allowed to flow between the advance chamber, the retard chamber, and the storage chamber. The variable valve operating apparatus for an internal combustion engine according to any one of claims 3 to 8,
The restricting mechanism causes the restricting body to protrude from the storage chamber based on the supply state of the lubricating oil to the intermediate chamber being set to the first supply state, and the protruding restricting body is the Maintaining the fixed state in which the valve timing of the engine valve is fixed to the intermediate angle by being fitted into the restriction hole of the engaging side rotating body which is the other of the input side rotating body and the output side rotating body, Based on the fact that the supply state of the lubricating oil to the intermediate chamber is set to the second supply state, the restricting body is detached from the restricting hole and accommodated in the accommodating chamber. The variable valve operating apparatus for an internal combustion engine is characterized in that the released state of releasing the fixation of the valve timing to an intermediate angle is maintained. The variable valve operating apparatus for an internal combustion engine according to any one of claims 1 to 9,
A valve timing is fixed to an intermediate angle by the restriction mechanism when the engine is started, and lubricating oil is supplied to the advance chamber or the retard chamber while the valve timing is fixed. Variable valve gear. The variable valve operating apparatus for an internal combustion engine according to claim 10,
The variable valve operating apparatus for an internal combustion engine, wherein the valve timing is maintained at an intermediate angle by the restriction mechanism until the engine start is completed. The variable valve operating apparatus for an internal combustion engine according to any one of claims 1 to 11,
With the start of the engine start operation, the supply mode of the lubricant for the variable mechanism by the drive mechanism is set to a supply mode for supplying the lubricant to only one of the advance chamber and the retard chamber. A variable valve operating apparatus for an internal combustion engine. The variable valve operating apparatus for an internal combustion engine according to claim 12,
The drive mechanism has a plurality of modes as a supply mode for supplying lubricating oil to only one of the advance chamber and the retard chamber,
The supply mode set when the engine start operation is started is characterized in that the supply amount of lubricating oil to one of the advance chamber and the retard chamber is the largest among the plurality of supply modes. A variable valve operating device for an internal combustion engine. A variable mechanism that changes the valve timing of the intake valve or exhaust valve as the engine valve between the most advanced angle and the most retarded angle, and the valve timing of the engine valve that is between the most advanced angle and the most retarded angle A regulation mechanism that fixes the intermediate angle of the variable mechanism, and a drive mechanism that controls the supply state of the lubricating oil to each of the advance angle chamber of the variable mechanism, the retard angle chamber of the variable mechanism, and the intermediate chamber of the restriction mechanism,
The regulating mechanism sets the valve timing of the engine valve to the intermediate angle when the operating state of the regulating valve is in a fixed state based on the supply state of the lubricating oil to the intermediate chamber being set to the first supply state. And fixing the valve timing of the engine valve to the intermediate angle when the operation state of the engine valve is in the release state based on the fact that the supply state of the lubricating oil to the intermediate chamber is set to the second supply state In the variable valve operating apparatus for an internal combustion engine that releases the
The internal combustion engine is characterized in that the valve timing is fixed to an intermediate angle by the restriction mechanism when the engine is started, and that the lubricating oil is supplied to the advance chamber and the retard chamber while the valve timing is fixed. Variable valve gear. The variable valve operating apparatus for an internal combustion engine according to any one of claims 1 to 14,
The drive mechanism controls a supply state of lubricating oil to each of the advance angle chamber of the variable mechanism, the retard angle chamber of the variable mechanism, and the intermediate chamber of the restriction mechanism by a single hydraulic control valve, As an oil passage for flowing lubricating oil between the hydraulic control valve and the variable mechanism and the regulating mechanism, an advance oil passage connecting the hydraulic control valve and the advance chamber, the hydraulic control valve and the retard angle A variable valve operating apparatus for an internal combustion engine, comprising: a retarded oil passage that connects a chamber; and an intermediate oil passage that connects the hydraulic control valve and the intermediate chamber. The variable valve operating apparatus for an internal combustion engine according to claim 15,
The hydraulic control valve is an operation mode for setting a supply state of lubricating oil to the advance chamber, the retard chamber, and the intermediate chamber.
Mode A1 for supplying lubricating oil to the advance chamber and discharging the lubricating oil from the retard chamber and maintaining the supply state of the lubricating oil to the intermediate chamber in the second supply state;
A mode A2 for discharging the lubricating oil from the advance chamber and supplying the lubricating oil to the retard chamber and maintaining the supply state of the lubricant to the intermediate chamber in the second supply state;
Stopping supply of lubricant oil to the advance chamber and discharge of lubricant oil from the advance chamber, stop supply of lubricant oil to the retard chamber, and discharge of lubricant oil from the retard chamber; and Mode A3 for maintaining the supply state of the lubricating oil for the intermediate chamber in the second supply state;
A mode A4 for supplying lubricating oil to the advance chamber and discharging the lubricating oil from the retard chamber and maintaining the supply state of the lubricating oil to the intermediate chamber in the first supply state; and
The variable valve operating apparatus for an internal combustion engine, wherein the operation mode of the hydraulic control valve is maintained in the mode A4 during engine startup. The variable valve operating apparatus for an internal combustion engine according to claim 15,
The hydraulic control valve is an operation mode for setting a supply state of lubricating oil to the advance chamber, the retard chamber, and the intermediate chamber.
Mode B1 for supplying lubricating oil to the retarding chamber, discharging the lubricating oil from the advance chamber, and maintaining the supply state of the lubricating oil to the intermediate chamber in the second supply state;
Mode B2 for discharging the lubricating oil from the retarding chamber and supplying the lubricating oil to the advance chamber and maintaining the supply state of the lubricating oil to the intermediate chamber in the second supply state;
Stopping supply of lubricant oil to the retard chamber and discharge of lubricant oil from the retard chamber, and stop supply of lubricant oil to the advance chamber and discharge of lubricant from the advance chamber; Mode B3 for maintaining the supply state of the lubricating oil for the intermediate chamber in the second supply state;
A mode B4 for supplying lubricating oil to the retarding chamber and discharging the lubricating oil from the advance chamber and maintaining the supply state of the lubricating oil to the intermediate chamber in the first supply state;
The variable valve operating apparatus for an internal combustion engine, wherein the operation mode of the hydraulic control valve is maintained in the mode B4 during engine startup.

Images