JP2010242714A - 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 including a function of limiting a change range of a valve timing and a function of fixing the valve timing and capable of suppressing complications in a structure for achieving these functions. <P>SOLUTION: This variable valve gear includes: a variable valve mechanism for operating a relative phase which is a relative rotational phase between a housing rotor and a vane rotor, between a most delayed angle phase and a most advanced angle phase; a restriction pin driven among a first projecting position with the range of the relative phase provided in the vane rotor and in which the restriction pin is projected from the vane rotor based on the supply/discharge state of working oil, a second projecting position in which the restriction pin is projected at a place different from the first, and a storage position in which the restriction pin is stored in the vane rotor; a phase restriction mechanism provided in the housing rotor for performing restriction by a restriction hole and a restriction groove in which the restriction pin projected from the vane rotor is fitted; and a hydraulic control mechanism. The supply/discharge state of the working oil with respect to the variable valve gear and the phase restriction mechanism is controlled by a single hydraulic control valve. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention provides a variable valve mechanism for operating a relative phase, which is a relative rotational phase between an input rotator and an output rotator, between a most retarded phase and a most advanced angle phase, and a range of the relative phase. The present invention relates to a variable valve operating apparatus for an internal combustion engine that includes a phase limiting mechanism that controls, a variable valve operating mechanism, and a hydraulic control mechanism that controls a supply and discharge state of hydraulic oil with respect to the phase limiting mechanism.

  As a variable valve operating apparatus for an internal combustion engine, an apparatus having a variable valve lift amount mechanism that varies the maximum valve lift amount of the intake valve and a variable valve timing mechanism that varies the valve timing of the intake valve has been proposed.

  In such a variable valve system, when the maximum valve lift amount of the intake valve is increased by the variable valve lift amount mechanism, a so-called valve stamp in which the intake valve and the piston interfere due to the advance angle of the valve timing occurs. There is also.

  In view of this, the variable valve operating apparatus of Patent Document 1 is provided with a restriction mechanism that restricts the drive range of the variable valve timing mechanism in order to avoid such a valve stamp. In this restriction mechanism, when the intake valve cam is switched from a low-speed cam with a small maximum valve lift amount to a high-speed cam with a large maximum valve lift amount, the restriction pin of the vane rotor (output rotator) is moved to the housing rotor (input rotator). By inserting the vane rotor into the restriction groove, the advancement of the vane rotor beyond the advance restriction phase is restricted. As a result, when the maximum valve lift amount of the intake valve is set to be large, it is avoided that the valve timing is advanced to the point where the valve stamp is caused.

  On the other hand, as a mechanism for regulating the drive range of the variable valve timing mechanism, in addition to the above, a pin protruding from the vane rotor is fitted into the hole of the housing rotor to fix the rotational phase of the vane rotor with respect to the housing rotor. A lock mechanism that fixes the valve timing at a predetermined timing is also known (for example, Patent Document 2).

JP 2000-328911 A JP 2002-317610 A

  By providing the above-described regulation mechanism for limiting the rotation range of the vane rotor and the lock mechanism for fixing the rotation phase of the vane rotor, it is possible to achieve avoidance of the valve stamp and ensuring engine startability. Practicality as a timing variable mechanism can be further enhanced.

  However, when both the restriction mechanism and the lock mechanism are employed in the variable valve operating device, it is necessary to form the pin and groove of the restriction mechanism and the pin and hole of the lock mechanism in each of the vane rotor and the housing rotor. Complicating the configuration of the apparatus is inevitable.

  The present invention has been made in view of such circumstances, and its purpose is to provide a function of limiting the change range of the valve timing and a function of fixing the valve timing, and a complicated structure for realizing these functions. An object of the present invention is to provide a variable valve operating apparatus for an internal combustion engine that can suppress the shift to the internal combustion engine.

In the following, means for achieving the above object and its effects are described.
(1) According to the first aspect of the present invention, the engine valve operates by operating the relative phase, which is the relative rotational phase between the input rotator and the output rotator, between the most retarded angle phase and the most advanced angle phase. A variable valve mechanism that changes the valve timing of the intake valve or the exhaust valve between the most advanced angle and the most retarded angle, a phase regulating mechanism that regulates the range of the relative phase, the variable valve mechanism, and the In the variable valve operating apparatus for an internal combustion engine, the hydraulic control mechanism includes a hydraulic control mechanism that controls a supply and discharge state of the hydraulic oil with respect to the phase restriction mechanism. The supply / discharge state is controlled by a single hydraulic control valve, and the phase restriction mechanism is provided on the output rotator, and is supplied to the output rotator based on the supply / discharge state of hydraulic oil to the restriction mechanism. A regulatory body that moves The control body includes a control hole and a control groove that are provided in the input rotary body and into which the control body protruding from the output rotary body is fitted, and the control body protrudes from the output rotary body. 1 is driven between a projecting position, a second projecting position projecting from the output rotating body to a position different from the projecting position, and a housing position housed in the output rotating body, The restriction hole is for inserting the restriction body at the first projecting position when the relative phase is at a predetermined fixed phase, and the restriction groove has the relative phase from the most retarded angle phase. When the regulating body at the second projecting position is fitted when it is within a predetermined regulating phase range smaller than the range up to the most advanced angle phase, and when the regulating body is fitted into the regulating hole The relative phase is When the valve timing is fixed at a specific angle by being fixed to a phase, and the restricting body is fitted in the restricting groove, the range of change of the relative phase is limited to the restricting phase range, thereby the valve timing. The change range is limited to a predetermined intermediate range smaller than the range from the most retarded angle to the most advanced angle.

  According to the present invention, since the relative phase is fixed and the relative phase change range is restricted by one restricting body, it is possible as compared with the case where the fixing and restricting are performed by two restricting bodies. The structure of the variable valve mechanism can be simplified. In addition, since a single hydraulic control valve controls the supply / discharge state of hydraulic fluid to the variable valve mechanism and the phase restriction mechanism, it is compared with the case where the same supply / discharge state is controlled by a plurality of hydraulic control valves. As a result, the oil passage structure can be simplified. As described above, according to the present invention, it is possible to provide a function for limiting the change range of the valve timing and a function for fixing the valve timing, and it is possible to suppress the complexity of the structure for realizing these functions.

  (2) The invention according to claim 2 is the variable valve operating apparatus for the internal combustion engine according to claim 1, wherein the hydraulic control mechanism supplies hydraulic oil between the hydraulic control valve and the variable valve mechanism. As an oil passage to be circulated, an advance chamber oil passage connecting the hydraulic control valve and the advance chamber of the variable valve mechanism, and a delay connecting the hydraulic control valve and the retard chamber of the variable valve mechanism. The gist of the invention is to provide a corner chamber oil passage, and a working chamber oil passage connecting the hydraulic control valve and the working chamber of the phase restriction mechanism.

  According to this invention, the hydraulic oil is circulated to the advance chamber, the retard chamber, and the working chamber by the advance chamber oil passage, the retard chamber oil passage, and the working chamber oil passage connected to the hydraulic control valve, respectively. ing. That is, on the variable valve mechanism side of the hydraulic control valve, since the oil passages connected to the advance chamber, the retard chamber, and the working chamber are independent, the hydraulic oil is supplied to the advance chamber or the retard chamber. Regardless, the operating state of the phase restriction mechanism can be switched.

  (3) The invention according to claim 3 is the variable valve operating apparatus for the internal combustion engine according to claim 1 or 2, wherein the phase restriction mechanism pushes the restriction body toward the first projecting position. The regulating body is placed in the housing position by the relationship between the force of the spring that imparts the regulating body to the regulating body and the hydraulic pressure of the working chamber that imparts a force pushing the regulating body toward the second projecting position to the regulating body. And the first projecting position and the second projecting position.

According to the present invention, the force toward the first projecting position or the second projecting position is applied to the restricting body based on the magnitude relationship between the hydraulic pressure of the working chamber and the spring force. As the chamber hydraulic pressure is released, it is possible to maintain a state in which the regulating body can be moved to the first protruding position.
(4) The invention as set forth in claim 4 is the variable valve operating apparatus for an internal combustion engine according to claim 2 or 3, wherein the phase regulating mechanism is configured such that the hydraulic oil in the working chamber is discharged. The force toward the second projecting position exceeds the force toward the second projecting position, and the force toward the second projecting position when the working oil is supplied to the working chamber is the force toward the first projecting position. The gist is that it exceeds the above.
(5) The invention according to claim 5 is the variable valve operating apparatus for an internal combustion engine according to any one of claims 2 to 4, wherein the hydraulic control valve includes the advance chamber, the retard chamber, As an operation mode for setting the supply / discharge state of the working oil to the working chamber, a mode A1 for discharging the working oil from the advance chamber, supplying the working oil to the retard chamber, and supplying the working oil to the working chamber. Mode A2 for supplying hydraulic oil to the advance chamber, discharging hydraulic oil from the retard chamber and supplying hydraulic oil to the hydraulic chamber, and supplying hydraulic oil to the advance chamber and the delay The gist of the present invention is to provide a mode B for discharging the hydraulic oil from the corner chamber and discharging the hydraulic oil from the working chamber.

According to the present invention, when the mode A1 is selected, maintenance of the state in which the restricting body can project from the output rotating body toward the second projecting position and the retardation of the valve timing are performed together. When the mode A2 is selected, the maintenance of the state in which the regulating body can project from the output rotating body toward the second projecting position and the advance timing of the valve timing are performed together. When mode B is selected, the maintenance of the state in which the restricting body can protrude from the output rotating body toward the first protruding position and the advance timing of the valve timing are performed together.
(6) According to a sixth aspect of the present invention, in the variable valve operating apparatus for an internal combustion engine according to the fifth aspect, the hydraulic control valve is configured to supply hydraulic fluid supplied to the advance chamber in the mode B. The gist is to make the flow rate smaller than the flow rate of the hydraulic oil supplied to the advance chamber in the mode A2.

  According to the present invention, the valve timing advance speed when the force toward the first protruding position is applied to the regulating body and the valve when the force toward the second protruding position is applied to the regulating body. When comparing the timing advance speed, the former can be made smaller.

  (7) The invention according to claim 7 is the variable valve operating apparatus for an internal combustion engine according to any one of claims 2 to 4, wherein the hydraulic control valve includes the advance chamber, the retard chamber, As an operation mode for setting the supply / discharge state of the working oil to the working chamber, a mode A1 for discharging the working oil from the advance chamber, supplying the working oil to the retard chamber, and supplying the working oil to the working chamber. Mode A2 for supplying hydraulic oil to the advance chamber, discharging hydraulic oil from the retard chamber and supplying hydraulic oil to the hydraulic chamber, and discharging hydraulic oil from the advance chamber and the delay The gist is to provide a mode C for supplying hydraulic oil to the corner chamber and discharging hydraulic oil from the hydraulic chamber.

  According to the present invention, when the mode A1 is selected, maintenance of the state in which the restricting body can project from the output rotating body toward the second projecting position and the retardation of the valve timing are performed together. When the mode A2 is selected, the maintenance of the state in which the regulating body can project from the output rotating body toward the second projecting position and the advance timing of the valve timing are performed together. When mode C is selected, the maintenance of the state in which the regulating body can project from the output rotating body toward the first projecting position and the retardation of the valve timing are performed together.

  (8) According to an eighth aspect of the present invention, in the variable valve operating apparatus for an internal combustion engine according to the seventh aspect, the hydraulic control valve is configured to supply hydraulic oil supplied to the retard chamber in the mode C. The gist is to make the flow rate smaller than the flow rate of the hydraulic oil supplied to the retardation chamber in the mode A1.

  According to this invention, the retarding speed of the valve timing when the force toward the first protruding position is applied to the regulating body, and the valve when the force toward the second protruding position is applied to the regulating body. The former can be made smaller with respect to the retarding speed of timing.

  (9) The invention according to claim 9 is the variable valve operating apparatus for an internal combustion engine according to any one of claims 2 to 4, wherein the hydraulic control valve includes the advance chamber and the retard chamber. As an operation mode for setting the supply / discharge state of the working oil to the working chamber, a mode A1 for discharging the working oil from the advance chamber, supplying the working oil to the retard chamber, and supplying the working oil to the working chamber. Mode A2 for supplying hydraulic oil to the advance chamber and discharging hydraulic oil from the retard chamber and supplying hydraulic oil to the hydraulic chamber; and supplying the hydraulic oil to the advance chamber and the advance The gist of the present invention is to provide a mode D for stopping the discharge of the hydraulic oil from the corner chamber, discharging the hydraulic oil from the retard chamber, and discharging the hydraulic oil from the hydraulic chamber.

  According to the present invention, when the mode A1 is selected, maintenance of the state in which the restricting body can project from the output rotating body toward the second projecting position and the retardation of the valve timing are performed together. When the mode A2 is selected, the maintenance of the state in which the regulating body can project from the output rotating body toward the second projecting position and the advance timing of the valve timing are performed together. When mode D is selected, maintaining the state in which the restricting body can protrude from the output rotating body toward the first protruding position and prohibiting the change toward the retarded side of the valve timing are performed together. become.

  (10) The invention according to claim 10 is the variable valve operating apparatus for an internal combustion engine according to any one of claims 2 to 4, wherein the hydraulic control valve includes the advance chamber and the retard chamber. As an operation mode for setting the supply / discharge state of the working oil to the working chamber, a mode A1 for discharging the working oil from the advance chamber, supplying the working oil to the retard chamber, and supplying the working oil to the working chamber. Mode A2 for supplying hydraulic oil to the advance chamber, discharging hydraulic oil from the retard chamber and supplying hydraulic oil to the hydraulic chamber, and discharging hydraulic oil from the advance chamber and the delay The gist of the present invention is to provide a mode E for stopping the supply of the hydraulic oil to the corner chamber and the discharge of the hydraulic oil from the retard chamber and discharging the hydraulic oil from the working chamber.

  According to the present invention, when the mode A1 is selected, maintenance of the state in which the restricting body can project from the output rotating body toward the second projecting position and the retardation of the valve timing are performed together. When the mode A2 is selected, the maintenance of the state in which the regulating body can project from the output rotating body toward the second projecting position and the advance timing of the valve timing are performed together. When mode E is selected, maintaining the state in which the restricting body can protrude from the output rotating body toward the first protruding position and prohibiting the change of the valve timing toward the advance side are performed. become.

  (11) The invention according to claim 11 is the variable valve operating apparatus for an internal combustion engine according to any one of claims 5 to 10, wherein the hydraulic control valve includes the advance chamber, the retard chamber, As an operation mode for setting the supply / discharge state of hydraulic oil to / from the hydraulic chamber, the supply of hydraulic oil to the advance chamber and the discharge of hydraulic oil from the advance chamber are stopped and the hydraulic oil to the retard chamber is stopped. The mode A3 further includes a mode A3 for stopping the supply of the oil and the discharge of the hydraulic oil from the retard chamber and supplying the hydraulic oil to the hydraulic chamber.

  According to the present invention, when the mode A3 is selected, the state in which the restricting body can protrude from the output rotating body toward the second protruding position and the maintenance of the valve timing are performed together.

  (12) According to a 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, a most retarded angle phase is set as the fixed phase. The gist is that the most retarded angle is set as the angle.

  (13) The invention according to claim 13 is the variable valve operating apparatus for an internal combustion engine according to any one of claims 1 to 12, wherein the restriction phase range is the maximum from the most retarded angle side with respect to the most advanced angle phase. A range up to either the retarded phase or the more advanced side is set, that is, the most retarded angle or the more advanced angle from a predetermined valve timing that is more retarded than the most advanced angle as the intermediate range. The gist is that a range up to a predetermined valve timing on either side is set.

  According to this invention, when the restricting body is fitted in the restricting groove, the output rotating body is restricted from rotating to the advance side beyond the advance angle restricting phase with respect to the input rotating body. When the output rotating body rotates to the retard side, the rotation is allowed until the most retarded phase is reached.

  (14) The invention according to claim 14 is the variable valve operating apparatus for an internal combustion engine according to any one of claims 1 to 13, wherein the variable valve operating apparatus sets a maximum valve lift amount of the engine valve. A variable valve lift amount mechanism to be changed is further provided, and the phase restriction mechanism is configured to change the relative phase based on the maximum valve lift amount of the engine valve being set to a value larger than a reference lift amount. The gist of the invention is that the valve timing change range is limited to the intermediate range by limiting the range to the regulation phase range.

  According to the present invention, with respect to the phase restriction mechanism that restricts the output rotator from being advanced or retarded beyond the restriction phase with respect to the input rotator, the operation of housing the restrictor in the output rotator It becomes possible to suppress obstruction by the relative rotation of.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view showing a cross-sectional structure of an internal combustion engine equipped with the apparatus according to a first embodiment of a variable valve device for an internal combustion engine of the present invention. (A) is a top view which shows the planar structure about the valve timing variable mechanism of the embodiment, (b) is sectional drawing which shows the cross-section along a DA-DA line. The schematic diagram which shows the hydraulic pressure supply path | route about the valve timing variable mechanism of the embodiment. FIG. 3 is a schematic diagram schematically showing the sectional structure of the housing and the vane rotor along the DB-DB line in FIG. FIG. 3 is a schematic diagram schematically showing the sectional structure of the housing and the vane rotor along the DB-DB line in FIG. The schematic diagram which shows typically the cross-section when the operation mode is in a 1st mode about the hydraulic control valve of the embodiment. The schematic diagram which shows typically the cross-section when the operation mode is in a 2nd mode about the hydraulic control valve of the embodiment. The schematic diagram which shows typically the cross-section when the operation mode is in a 3rd mode about the hydraulic control valve of the embodiment. The schematic diagram which shows typically the cross-section when the operation mode is in the 4th mode about the hydraulic control valve of the embodiment. The schematic diagram which shows typically the cross-section when the operation mode is in the 5th mode about the hydraulic 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 about the hydraulic control valve of the embodiment. The map which shows an example of the control aspect of the valve timing and the maximum valve lift amount of an intake valve by the variable valve apparatus of the embodiment. The flowchart which shows the treatment procedure about "advance angle regulation control processing" performed by the electronic control apparatus of the embodiment. The schematic diagram which shows typically a cross-section when the operation mode of a hydraulic control valve exists in 1st mode about 2nd Embodiment which actualized the variable valve apparatus of the internal combustion engine of this invention. The schematic diagram which shows typically the cross-section when the operation mode is in a 2nd mode about the hydraulic control valve of the embodiment. The schematic diagram which shows typically the cross-section when the operation mode is in a 3rd mode about the hydraulic control valve of the embodiment. The schematic diagram which shows typically the cross-section when the operation mode is in the 4th mode about the hydraulic control valve of the embodiment. The schematic diagram which shows typically the cross-section when the operation mode is in a 6th mode about the hydraulic 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 about the hydraulic control valve of the embodiment. The flowchart which shows the treatment procedure about "advance angle regulation control processing" performed by the electronic control apparatus of the embodiment.

(First embodiment)
With reference to FIGS. 1 to 13, a first embodiment in which the variable valve device for an internal combustion engine of the present invention is embodied as a variable valve device for changing the valve opening / closing characteristics of an intake valve will be described.

  As shown in FIG. 1, the internal combustion engine 1 includes an engine body 10 that burns a mixture of intake air and fuel, a variable valve operating device 3 that changes the valve opening / closing characteristics of the intake valve 21, and an engine body 10. A hydraulic control mechanism 70 that supplies lubricating oil to each lubricating part and a control device 100 that comprehensively controls various devices including these devices are provided.

  A combustion chamber 14 for burning the air-fuel mixture is formed in the cylinder block 11 of the engine body 10. The linear motion of the piston 15 accompanying the combustion of the air-fuel mixture is converted into the rotational motion of the crankshaft 16.

  An oil pan 12 for storing lubricating oil supplied to each part of the internal combustion engine 1 is attached to the lower part of the cylinder block 11. A cylinder head 13 on which valve-operated parts are arranged is attached to the upper part of the cylinder block 11.

  The cylinder head 13 includes an intake valve 21 that opens and closes the combustion chamber 14 with respect to the intake passage, an intake camshaft 22 that drives the valve in the valve opening direction, an exhaust valve 25 that opens and closes the combustion chamber 14 with respect to the exhaust passage, and An exhaust camshaft 26 that drives the valve in the valve opening direction and a variable valve gear 3 that changes the valve opening / closing characteristics of the intake valve 21 are provided.

  An oil pump 17 that pumps up and discharges the lubricating oil of the oil pan 12 is connected to the crankshaft 16. Lubricating oil discharged by the oil pump 17 is supplied to each part of the internal combustion engine 1, and a part thereof is supplied to the variable valve operating apparatus 3 (valve timing variable mechanism 40) via the hydraulic control mechanism 70. Further, the lubricating oil after flowing through each part of the internal combustion engine 1 and the lubricating oil discharged from the variable valve gear 3 are returned to the oil pan 12 again.

  The variable valve operating apparatus 3 includes a variable valve timing mechanism 40 that changes the valve timing of the intake valve 21 (hereinafter referred to as “valve timing INVT”) and a maximum valve lift amount of the intake valve 21 (hereinafter referred to as “maximum valve lift amount”). INVL ") and a variable valve lift amount mechanism 30 are provided.

  The variable valve lift amount mechanism 30 has a maximum valve lift amount INVL as an upper limit maximum valve lift amount (hereinafter referred to as “upper limit valve lift amount INVLmax”) and a lower limit maximum valve lift amount (hereinafter referred to as “lower limit valve lift amount INVLmin”). Change continuously between. Further, the working angle of the intake valve 21, that is, the rotation angle of the crankshaft 16 during the period from when the intake valve 21 is opened to when the intake valve 21 is closed is also changed in accordance with the change in the maximum valve lift amount INVL.

  The variable valve lift mechanism 30 is provided between the rocker arm 23 that contacts the upper end of the intake valve 21 and the intake camshaft 22, and is configured by an arm assembly 32 that is swingably supported with respect to the cylinder head 13. . One end of the rocker arm 23 is supported by a lash adjuster 24, and the other end is in contact with the intake valve 21.

  The arm assembly 32 includes an input arm 33 to which rotation is input by the intake cam 22 </ b> C of the intake camshaft 22, an output arm 34 that swings the rocker arm 23, and a control shaft 31 that moves in the axial direction with respect to the arm assembly 32. ing. When the control shaft 31 moves in the axial direction with respect to the arm assembly 32 by driving the actuator, the relative rotational phase between the input arm 33 and the output arm 34 is changed. When the input arm 33 and the output arm 34 rotate in a direction that narrows the interval in the circumferential direction, the maximum valve lift amount INVL decreases accordingly. On the other hand, when the input arm 33 and the output arm 34 rotate in a direction that increases the circumferential interval, the maximum valve lift amount INVL increases accordingly.

  In the present embodiment, the variable valve operating device 3 is configured including the variable valve timing mechanism 40, the hydraulic control mechanism 70, the variable valve lift amount mechanism 30, and the electronic control device 110.

  The control device 100 includes various sensors that monitor engine operating conditions, that is, various sensors including a crank position sensor 111 and a cam position sensor 112, and an electronic control device 110 that controls the operation of each device based on the outputs of these sensors. And are provided. The crank position sensor 111 is provided in the vicinity of the crankshaft 16 and outputs a signal corresponding to the rotation angle of the shaft 16. The cam position sensor 112 is provided in the vicinity of the intake camshaft 22 and outputs a signal corresponding to the rotation angle of the shaft 22.

  The electronic control unit 110 includes a valve timing control for adjusting the valve timing INVT, a valve lift control for adjusting the maximum valve lift amount INVL, and an opening / closing characteristic cooperative control for adjusting the valve timing INVT and the maximum valve lift amount INVL in a coordinated manner. Perform various controls.

  In this open / close characteristic cooperative control, the target values of the valve timing INVT and the maximum valve lift amount INVL (hereinafter referred to as “target angle INVTT” and “target maximum lift”, respectively) based on the engine operating state (engine load and engine speed). Amount INVLT "). Then, the valve timing variable mechanism 40 and the valve lift amount variable mechanism 30 are set so that the valve timing INVT and the maximum valve lift amount INVL calculated on the basis of the outputs of the crank position sensor 111 and the cam position sensor 112 coincide with the respective target values. Control is performed.

  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 30 with the cover 44 shown in FIG. 2B removed from the housing body 42. FIG. Hereinafter, the rotation direction of the camshaft 22 and the sprocket 43 is referred to as a rotation direction RA.

  As shown in FIG. 2A, the variable valve timing mechanism 40 is synchronized with the shaft 22 by being fixed to the housing rotor 41 that rotates in synchronization with the crankshaft 16 and the end of the intake camshaft 22. And a rotating vane rotor 45.

  The housing rotor 41 is connected to the crankshaft 16 via a timing chain (not shown) and rotates in synchronization with the shaft 16. The housing rotor 41 is provided inside the sprocket 43 and rotates integrally with the sprocket 43. The main body 42 and a cover 44 (see FIG. 2B) attached to the housing main body 42 are configured.

The vane rotor 45 is accommodated in the space when the cover 44 (see FIG. 2B) is attached to the housing body 42 by being disposed in the space inside the housing body 42.
The housing body 42 is provided with three partition walls 41A that protrude toward the vane rotor 45 in the radial direction. The vane rotor 45 is provided with three vanes 46 that project toward the housing body 42 and divide the three vane storage chambers 47 between the partition walls 41A into an advance chamber 48 and a retard chamber 49, respectively.

  The advance chamber 48 is located behind the vane 46 in the rotation direction RA of the intake camshaft 22 in one vane storage chamber 47 and is in a state of supplying lubricating oil to the variable valve timing mechanism 40 by the hydraulic control mechanism 70. The volume changes accordingly. The retard chamber 49 is positioned in front of the vane 46 in the rotational direction RA of the intake camshaft 22 in one vane accommodating chamber 47, and is similar to the advance chamber 48 with respect to the valve timing variable mechanism 40 by the hydraulic control mechanism 70. The volume changes according to the supply state of the lubricating oil.

  The variable valve timing mechanism 40 changes the valve timing INVT by changing the rotational phase of the vane rotor 45 with respect to the housing rotor 41 (hereinafter, “rotational phase P of the vane rotor 45”) based on the above configuration. The change of the valve timing INVT by the variable mechanism 30 is specifically performed as follows.

  When the vane rotor 45 rotates with respect to the housing rotor 41 in the advance side, that is, in the rotational direction RA of the intake camshaft 22 by supplying the lubricant to the advance chamber 48 and discharging the lubricant from the retard chamber 49, the valve The timing INVT changes to the advance side. When the vane rotor 45 is rotated to the maximum advance side with respect to the housing rotor 41, that is, when the rotational phase P of the vane rotor 45 is at the maximum advance phase PMAX, the valve timing INVT is the most advanced timing (hereinafter, referred to as the timing of the advancement side) “Most advanced angle INVTmax”). As the most advanced angle phase PMAX, a position where the vane 46 is abutted against the partition wall 41A on the retard chamber 49 side or a position where the vane 46 is in the vicinity of the partition wall 41A is set.

  By discharging the lubricating oil from the advance chamber 48 and supplying the lubricant oil to the retard chamber 49, the vane rotor 45 rotates toward the retard side, that is, the rear side in the rotational direction RA of the intake camshaft 22 with respect to the housing rotor 41. The valve timing INVT changes to the retard side. When the vane rotor 45 rotates to the retard angle side with respect to the housing rotor 41 to the maximum, that is, when the rotational phase P of the vane rotor 45 is at the most retarded angle phase PMIN, the valve timing INVT is the most retarded timing (hereinafter, “Most retarded angle INVTmin”). As the most retarded phase PMIN, a position where the vane 46 abuts against the partition wall 41A on the advance chamber 48 side or a position where the vane 46 is in the vicinity of the partition wall 41A is set.

  The flow of the lubricating oil between each of the advance chamber 48 and the retard chamber 49 and the hydraulic control mechanism 70 is blocked, that is, the lubricant oil is held in each of the advance chamber 48 and the retard chamber 49. Thus, when the relative rotation between the housing rotor 41 and the vane rotor 45 is disabled, the valve timing INVT is maintained at that timing.

  The variable valve timing mechanism 40 is provided with a phase restricting mechanism 50 that restricts the rotation range of the vane rotor 45 relative to the housing rotor 41 more than the range from the most retarded angle phase PMIN to the most advanced angle phase PMAX.

  The phase regulating mechanism 50 has a function of regulating the rotation of the vane rotor 45 relative to the housing rotor 41 regardless of the hydraulic pressure of the advance chamber 48 and the retard chamber 49, and fixing the valve timing INVT to the most retarded angle INVTmin. According to this function, when the rotational phase P of the vane rotor 45 is at the most retarded angle phase PMIN, the housing rotor 41 and the vane rotor 45 are engaged with each other to keep the valve timing INVT at the most retarded angle INVTmin.

  Regardless of the hydraulic pressure in the advance chamber 48 and the retard chamber 49, the rotation range of the vane rotor 45 relative to the housing rotor 41 is restricted, and the change range of the valve timing INVT is set to a specific timing on the retard side with respect to the most advanced angle INVTmax. (Hereinafter referred to as “advance angle regulation angle INVTmdl”) and the most retarded angle INVTmin. According to this function, the rotation phase P of the vane rotor 45 rotates more to the advance side than the corresponding rotation phase between the most retarded angle INVTmin and the advance angle restriction angle INVTmdl (hereinafter, “advance angle restriction phase PMDL”). Limit that. That is, the rotation range of the vane rotor 45 with respect to the housing rotor 41 is reduced more than the range from the most advanced angle phase PMAX to the most retarded angle phase PMIN, and the change range of the valve timing INVT is set between the most retarded angle INVTmin and the advanced angle regulating angle INVTmdl. Limit in between.

  The advance angle regulation angle INVTmdl is set to the most advanced valve timing among valve timings that can suppress the occurrence of the valve stamp when the maximum valve lift amount INVL becomes the regulation lift amount INVLX. . That is, when the valve timing INVT is on the retard side with respect to the advance angle regulating angle INVTmdl, the occurrence of the valve stamp is suppressed regardless of the maximum valve lift amount INVL.

With reference to FIG.2 (b), the structure of the phase control mechanism 50 is explained in full detail. FIG. 2B shows a cross-sectional structure taken along the line DA-DA in FIG.
As shown in FIG. 2 (b), the phase regulating mechanism 50 is supplied and discharged with lubricating oil by a regulating pin 60 provided in the storage chamber 46A of the vane 46 and a hydraulic control mechanism 70 (see FIG. 1). And a spring 53 that is provided in the spring chamber 54 in the storage chamber 46A and pushes the restriction pin 60 in one direction, and a restriction hole 51 and a restriction groove 52 provided in the housing rotor 41. Yes. The restriction hole 51 is provided on the cover wall surface 44 </ b> A of the cover 44, and the restriction groove 52 is provided on the sprocket wall surface 43 </ b> A of the housing main body 42 at a location facing the restriction hole 51.

  The restriction pin 60 is a main body of which one end is fitted into the restriction hole 51, and the other tip is fitted into the restriction groove 52. It is comprised by the division body 62 to which the pressure of this acts. Then, based on the relationship between the force of the lubricating oil in the working chamber 55 and the force of the spring 53, the position accommodated in the vane 46 (hereinafter referred to as “accommodating position P0”) and the vane 46 toward the sprocket wall surface 43A. It moves between the protruding position (hereinafter, “second protruding position P2”) and the position protruding from the vane 46 toward the cover wall surface 44A (hereinafter, “first protruding position P1”).

  The hydraulic pressure in the working chamber 55 acts on the regulation pin 60 in the direction of the sprocket wall surface 43A. The force of the spring 53 acts on the restriction pin 60 in the direction of the cover wall surface 44A. Hereinafter, the direction from the housing position P0 and the first projecting position P1 to the second projecting position P2 is referred to as a “second projecting direction Z2,” and the direction from the housing position P0 and the second projecting position P2 to the first projecting position P1 is defined. It is referred to as “first projecting direction Z1”.

  When the lubricating oil is discharged from the working chamber 55 by the hydraulic control mechanism 70, that is, when the lubricating oil supply / discharge state with respect to the working chamber 55 is in the discharging state, the force in the first protruding direction Z1 by the spring 53 is the working chamber 55. This exceeds the force in the second protruding direction Z2 by the lubricating oil. As a result, a force is generated on the restriction pin 60 so as to operate it in the first protruding direction Z1. In this state, when the rotational phase P of the vane rotor 45 is at the most retarded angle phase PMIN, that is, when the circumferential positions of the regulating pin 60 and the regulating hole 51 coincide with each other, the regulating pin 60 is moved to the vane. It protrudes from 46 and is fitted into the restriction hole 51. As a result, the housing rotor 41 and the vane rotor 45 are fixed to each other through the engagement between the restriction pin 60 and the restriction hole 51, so that their relative rotational phases are held at the most retarded angle phase PMIN.

  On the other hand, when the lubricating oil is supplied to the working chamber 55 by the hydraulic control mechanism 70 and the working chamber 55 is filled with the lubricating oil, that is, when the supply / discharge state of the lubricating oil to the working chamber 55 is in the supply state, the working chamber 55 The force in the second protruding direction Z2 due to the lubricating oil exceeds the force in the first protruding direction Z1 due to the spring 53. As a result, a force is generated on the restriction pin 60 so as to operate it in the second protruding direction Z2. And when the force of the 2nd protrusion direction Z2 acts with respect to the control pin 60 in the state in which the control pin 60 was inserted in the control hole 51, the control pin 60 will detach | leave from the control hole 51 and sprocket wall surface 43A. I hit it. Thereby, the fixing of the housing main body 42 and the vane rotor 45 by the engagement between the restriction pin 60 and the restriction hole 51 is released, and the rotation of the vane rotor 45 with respect to the housing main body 42 is allowed.

  Further, in this case, when the rotational phase P of the vane rotor 45 is within the range from the advance angle restriction phase PMDL to the most retarded angle phase PMIN, that is, when the restriction pin 60 is at a position corresponding to the restriction groove 52, the restriction pin 60 Protrudes from the vane 46 in the second protruding direction Z2 and is fitted into the restriction groove 52. Thus, the range of the relative rotational phase between the housing main body 42 and the vane rotor 45 is limited to the range from the advance angle regulation phase PMDL to the most retarded angle phase PMIN.

  With reference to FIG. 3, the flow mode of the lubricating oil between the variable valve timing mechanism 40 and the hydraulic control mechanism 70 will be described. In addition, the figure has shown typically the structure of the oil path between these apparatuses.

  The hydraulic control mechanism 70 includes an advance chamber oil passage 71 that supplies or discharges lubricant to the advance chamber 48, a retard chamber oil passage 72 that supplies or discharges lubricant to the retard chamber 49, and the lubricant. Working chamber oil passage 73 for supplying or discharging the passage, supply oil passage 74 for supplying lubricating oil to each of the oil passages 71 to 73, discharge oil passage 75 for discharging the lubricating oil from each of the oil passages 71 to 73, and valves The hydraulic control valve 80 is configured to control the supply / discharge state of the lubricating oil with respect to the timing variable mechanism 40. The supply oil passage 74 is provided with an oil pump 17 that discharges the lubricating oil of the oil pan 12.

  The hydraulic control valve 80 switches the connection state between the supply oil passage 74 and the discharge oil passage 75, the advance chamber oil passage 71, the retard chamber oil passage 72, and the working chamber oil passage 73, so The supply state of the lubricating oil to the corner chamber 49 and the working chamber 55 is changed.

  When the advance chamber oil passage 71 is connected to the supply oil passage 74 and the retard chamber oil passage 72 is connected to the discharge oil passage 75 by the control of the hydraulic control valve 80, the advance chamber oil passage 71 is connected via the advance chamber oil passage 71. Lubricating oil is supplied to the advance chamber 48 and the lubricant in the retard chamber 49 is discharged through the retard chamber oil passage 72. At this time, the vane rotor 45 rotates toward the advance phase with respect to the housing rotor 41, and the valve timing INVT changes toward the advance side.

  When the advance chamber oil passage 71 is connected to the discharge oil passage 75 and the retard chamber oil passage 72 is connected to the supply oil passage 74 by the control of the hydraulic control valve 80, the advance chamber oil passage 71 is connected via the advance chamber oil passage 71. Lubricating oil in the advance chamber 48 is discharged and supplied to the retard chamber 49 via the retard chamber oil passage 72. At this time, the vane rotor 45 rotates toward the retard phase with respect to the housing rotor 41, and the valve timing INVT changes toward the retard side.

  When there is a request to project the regulating pin 60 in the second projecting direction Z2, that is, when there is a request to fit the regulating pin 60 into the regulating groove 52, the hydraulic control valve 80 is driven to cause the working chamber oil path 73 to be supplied to the supply oil path 74. And the lubricating oil is supplied to the working chamber 55. On the other hand, when there is a request to project the regulation pin 60 in the first projecting direction Z1, that is, when there is a request to fit the regulation pin 60 into the regulation hole 51, the hydraulic control valve 80 is driven so that the working chamber oil passage 73 is discharged oil. The lubricating oil is discharged from the working chamber 55 connected to the passage 75.

With reference to FIG.4 and FIG.5, the operation | movement aspect of the phase control mechanism 50 is demonstrated.
4 and 5 schematically show a development of the sectional structure of the variable valve timing mechanism 40 along the DB-DB line in FIG. 2A on a plane.

  As shown in FIG. 4A, when the rotational phase P of the vane rotor 45 is at the most retarded phase PMIN and the lubricating oil in the working chamber 55 is discharged, the regulating pin 60 is moved from the vane 46 in the first protruding direction. By projecting in the Z1 direction and being at the first projecting position P1, the front end portion on the cover 44 side (hereinafter referred to as “first front end portion 61A”) is in a state of being fitted into the restriction hole 51. As a result, the relative rotational phase between the vane rotor 45 and the housing rotor 41 is fixed, and the valve timing INVT is fixed to the most retarded angle INVTmin.

  If the lubricating oil is supplied to the working chamber 55 when the variable valve timing mechanism 40 is in the state of FIG. 4A, the movement of the regulating pin 60 based on the supply of the lubricating oil causes the variable valve timing mechanism 40 to move. The operating state shifts to the state shown in FIG.

  As shown in FIG. 4B, when the rotational phase P of the vane rotor 45 is at the most retarded phase PMIN and the hydraulic pressure is supplied to the working chamber 55, the regulating pin 60 is moved from the vane 46 in the second protruding direction Z2. By projecting in the direction and moving to the second projecting position P <b> 2, the tip portion on the sprocket 43 side (hereinafter, “second tip portion 61 </ b> B”) is in a state of being fitted into the regulation groove 52. Then, as the vane rotor 45 advances from the state of FIG. 4B, the operation state of the variable valve timing mechanism 40 shifts to the state of FIG.

  As shown in FIG. 4C, when the rotational phase P of the vane rotor 45 is between the most retarded angle phase PMIN and the advanced angle regulating phase PMDL and the hydraulic pressure is supplied to the working chamber 55, the regulating pin 60 Projecting from the vane 46 in the second projecting direction Z2 and in the second projecting position P2, the second tip 61B is fitted in the restricting groove 52. Then, as the vane rotor 45 further advances from the state of FIG. 4C, the operation state of the valve timing variable mechanism 40 shifts to FIG.

  As shown in FIG. 5A, when the vane rotor 45 advances to the most retarded phase PMIN with the restriction pin 60 fitted in the restriction groove 52, the restriction pin 60 and the end face of the restriction groove 52 The further advance angle of the vane rotor 45 is restricted by the engagement. At this time, the valve timing INVT is maintained at the advance angle regulation angle INVTmdl. That is, when the regulation pin 60 is fitted in the regulation groove 52, the range of relative rotation between the vane rotor 45 and the housing rotor 41 is limited to the range from the most retarded angle phase PMIN to the advanced angle regulation phase PMDL, and the valve It is restricted that the timing INVT is advanced from the advance restriction angle INVTmdl.

  If the lubricating oil in the working chamber 55 is discharged when the operation state of the variable valve timing mechanism 40 is in the state shown in FIG. 5A, the valve timing can be changed by the movement of the restriction pin 60 based on the discharge of the lubricating oil. The operating state of the mechanism 40 shifts to the state shown in FIG.

  As shown in FIG. 5B, when the rotational phase of the vane rotor 45 is in the advance angle regulation phase PMDL and the lubricating oil in the working chamber 55 is discharged, the regulation pin 60 is moved from the vane 46 in the first protruding direction Z1. Although it is in a state of projecting to the cover wall 44 </ b> A, it is held at the housing position P <b> 0 because it hits the cover wall surface 44 </ b> A. Thereby, the relative rotation phase of the vane rotor 45 and the housing rotor 41 toward the advance side or the retard side is allowed.

  If the vane rotor 45 moves to the advance side when the operating state of the variable valve timing mechanism 40 is in the state of FIG. 5B, the rotational phase P of the vane rotor 45 exceeds the advance angle regulation phase PMDL. Accordingly, the operating state of the variable valve timing mechanism 40 shifts to the state shown in FIG.

  As shown in FIG. 5 (c), when the regulation pin 60 is accommodated in the vane 46, the vane rotor 45 is allowed to advance to the most advanced angle phase PMAX. When the rotational phase of the vane rotor 45 is on the more advanced side than the advance angle restricting phase PMDL, the restricting pin 60 is held at the housing position P0 regardless of the supply / discharge state of the lubricating oil to the working chamber 55.

  The structure of the hydraulic control valve 80 and its operation mode will be described with reference to FIGS. 6 to 10 each show a cross-sectional structure along the axial direction of the hydraulic control valve 80, and show cross-sectional structures when in different operation modes. Moreover, the arrow in each figure shows the flow of lubricating oil.

  The hydraulic control valve 80 includes a single sleeve 81 provided with a plurality of ports, and a single spool 82 provided in the sleeve 81. When the spool 82 moves relative to the sleeve 81, the communication state (mode) of the plurality of ports is switched to change the supply state of the lubricating oil to the advance chamber 48, the retard chamber 49, and the working chamber 55. To do. Switching between these modes, that is, driving the spool 82 with respect to the sleeve 81 is performed by changing the DUTY ratio of an electric actuator (not shown) that drives the spool 82.

  The sleeve 81 includes a first supply port 86A and a second supply port 86B connected to the supply oil passage 74, and a first discharge port 87A and a second discharge port 87B and a third discharge port connected to the discharge oil passage 75. 87C, an advance port 83 connected to the advance chamber oil passage 71, a retard port 84 connected to the retard chamber oil passage 72, and an operation port 85 connected to the working chamber oil passage 73 are provided. It has been.

  The spool 82 corresponds to the first partition 82A corresponding to the first discharge port 87A, the second partition 82B corresponding to the advance port 83, the third partition 82C corresponding to the retard port 84, and the operation port 85. A fourth partition wall 82D and a fifth partition wall 82E are provided. Based on the setting of the positional relationship between the partition walls of the spool 82 and the ports of the sleeve 81, the ports on the supply oil passage 74 and the discharge oil passage 75 side and the ports on the valve timing variable mechanism 40 side are next. Communicate like

  That is, the advance port 83 communicates with only one of the first supply port 86A and the first discharge port 87A. The retard port 84 communicates with only one of the first supply port 86A and the second discharge port 87B. Further, the operation port 85 is connected to only one of the second supply port 86B and the third discharge port 87C.

  In the hydraulic control valve 80 having such a structure, the operation mode can be set to any one of the first mode to the fifth mode in accordance with the position of the spool 82 in the axial direction with respect to the sleeve 81.

  As shown in FIG. 6, when the position of the spool 82 with respect to the sleeve 81 is in the first position, and the operation mode is in the first mode, the communication state of each port is maintained as follows. That is, the advance port 83 communicates with the first discharge port 87A and is blocked from the first supply port 86A by the second partition wall 82B. Further, the retard port 84 communicates with the first supply port 86A and is blocked with the second discharge port 87B by the third partition wall 82C. Further, the operation port 85 communicates with the third discharge port 87C and is blocked from the second supply port 86B by the fourth partition wall 82D. Further, a part of the first discharge port 87A is blocked by the first partition wall 82A.

  In the first mode, since the ports are in communication with each other, the lubricating oil in the advance chamber 48 flows in the order of the advance chamber oil passage 71, the advance port 83, the first discharge port 87A, and the discharge oil passage 75. Then, the oil is returned to the oil pan 12. Further, the lubricating oil from the oil pump 17 flows in the order of the supply oil passage 74, the first supply port 86 </ b> A, the retard port 84, and the retard chamber oil passage 72 and is supplied to the retard chamber 49. Further, the lubricating oil from the working chamber 55 flows through the working chamber oil passage 73, the working port 85, the third discharge port 87 </ b> C, and the discharge oil passage 75 in this order and is returned to the oil pan 12.

  As shown in FIG. 7, when the position of the spool 82 with respect to the sleeve 81 is in the second position, and the operation mode is in the second mode, the communication state of each port is maintained as follows. That is, the advance port 83 communicates with the first discharge port 87A and is blocked from the first supply port 86A by the second partition wall 82B. Further, the retard port 84 communicates with the first supply port 86A and is blocked with the second discharge port 87B by the third partition wall 82C. Further, the operation port 85 communicates with the second supply port 86B and is blocked from the third discharge port 87C by the fourth partition wall 82D.

  In the second mode, since the ports are in communication with each other, the lubricating oil in the advance chamber 48 flows in the order of the advance chamber oil passage 71, the advance port 83, the first discharge port 87A, and the discharge oil passage 75. Then, the oil is returned to the oil pan 12. Further, the lubricating oil from the oil pump 17 flows in the order of the supply oil passage 74, the first supply port 86 </ b> A, the retard port 84, and the retard chamber oil passage 72 and is supplied to the retard chamber 49. Further, the lubricating oil from the oil pump 17 flows in the order of the supply oil passage 74, the second supply port 86 </ b> B, the operation port 85, and the operation chamber oil passage 73 and is supplied to the operation chamber 55.

  As shown in FIG. 8, when the position of the spool 82 with respect to the sleeve 81 is in the third position, and the operation mode is in the third mode, the communication state of each port is maintained as follows. That is, the advance port 83 is blocked from the first supply port 86A and the first discharge port 87A by the second partition wall 82B. Further, the retard port 84 is blocked from the first supply port 86A and the second discharge port 87B by the third partition wall 82C. Further, the operation port 85 communicates with the second supply port 86B and is blocked from the third discharge port 87C by the fourth partition wall 82D.

  In the third mode, since the ports are in communication with each other, the flow of the lubricating oil from the oil pump 17 to the advance chamber 48 via the hydraulic control valve 80 and the hydraulic control valve 80 from the advance chamber 48 are changed. Any flow of the lubricating oil to the oil pan 12 is blocked. The flow of the lubricating oil from the oil pump 17 to the retarding angle chamber 49 via the hydraulic control valve 80 and the flow of the lubricating oil from the retarding angle chamber 49 to the oil pan 12 via the hydraulic control valve 80 are both. Blocked. On the other hand, for the working chamber 55, the lubricating oil from the oil pump 17 is supplied to the working chamber 55 through the supply oil passage 74, the second supply port 86 </ b> B, the working port 85, and the working chamber oil passage 73 in this order.

  As shown in FIG. 9, when the position of the spool 82 with respect to the sleeve 81 is in the fourth position, and the operation mode is in the fourth mode, the communication state of each port is maintained as follows. That is, the advance port 83 communicates with the first supply port 86A and is blocked from the first discharge port 87A by the second partition wall 82B. Further, the retard port 84 communicates with the second discharge port 87B and is blocked by the third partition wall 82C from the first supply port 86A. Further, the operation port 85 communicates with the second supply port 86B and is blocked from the third discharge port 87C by the fourth partition wall 82D.

  In the fourth mode, since the ports are in communication with each other, the lubricating oil from the oil pump 17 flows in the order of the supply oil passage 74, the first supply port 86A, the advance port 83, and the advance chamber oil passage 71. Then, it is supplied to the advance chamber 48. Further, the lubricating oil in the retarding chamber 49 flows in the order of the retarding chamber oil passage 72, the retarding port 84, the second discharge port 87 B, and the discharge oil passage 75, and is returned to the oil pan 12. Further, the lubricating oil from the oil pump 17 flows in the order of the supply oil passage 74, the second supply port 86 </ b> B, the operation port 85, and the operation chamber oil passage 73 and is supplied to the operation chamber 55.

  As shown in FIG. 10, when the position of the spool 82 with respect to the sleeve 81 is in the fifth position, and the operation mode is in the fifth mode, the communication state of each port is maintained as follows. That is, the advance port 83 communicates with the first supply port 86A and is blocked from the first discharge port 87A by the second partition wall 82B. Further, the retard port 84 communicates with the second discharge port 87B and is blocked by the third partition wall 82C from the first supply port 86A. Further, the operation port 85 communicates with the third discharge port 87C and is blocked with the second supply port 86B by the fifth partition wall 82E.

  In the fifth mode, since the ports are in communication with each other, the lubricating oil from the oil pump 17 flows in the order of the supply oil passage 74, the first supply port 86A, the advance port 83, and the advance chamber oil passage 71. Then, it is supplied to the advance chamber 48. Further, the lubricating oil in the retarding chamber 49 flows in the order of the retarding chamber oil passage 72, the retarding port 84, the second discharge port 87 B, and the discharge oil passage 75, and is returned to the oil pan 12. Further, the lubricating oil from the working chamber 55 flows through the working chamber oil passage 73, the working port 85, the third discharge port 87 </ b> C, and the discharge oil passage 75 in this order and is returned to the oil pan 12.

  FIG. 11 shows the relationship between each operation mode of the hydraulic control valve 80 and the mode of supply of lubricating oil to the advance chamber 48, the retard chamber 49 and the working chamber 55, and each operation mode of the hydraulic control valve 80 and the variable valve timing mechanism 40. A summary of the relationship between the rotation direction of the vane rotor 45 and the relationship between each operation mode of the hydraulic control valve 80 and the directing direction of the restriction pin 60 is shown. Further, the relationship between each operation mode of the hydraulic control valve 80 and the DUTY ratio is also shown.

  As shown in the figure, the hydraulic control valve 80 uses a DUTY ratio X in the range of 20 to 80% of the DUTY ratio when controlling the normal valve timing INVT. When the operation of fitting the restriction pin 60 into the restriction hole 51 is performed, an area of 0 to 20% that is not used during normal control is used, and when the advance angle exceeds the advance angle restriction angle INVTmdl, it is not used during normal control. Use 80-100% area.

  The first mode corresponds to the mode C described in the claims, the second mode corresponds to the mode A1 described in the claims, the third mode corresponds to the mode A3 described in the claims, and the fourth mode. Corresponds to mode A2 in the claims, and the fifth mode corresponds to mode B in the claims.

With reference to FIG. 12, an example of the control mode of the phase restriction mechanism 50 based on the valve timing INVT and the maximum valve lift amount INVL will be described.
In the open / close characteristic cooperative control, the valve open / close characteristic required value VTVL determined by the target angle INVTT and the target maximum lift amount INVLT is in any of the valve open / close characteristic regions determined by the valve timing INVT and the maximum valve lift amount INVL. Based on this, the phase restriction mechanism 50 is controlled. Here, the valve opening / closing characteristic region is divided into the following regions A to F.

  Region A shows a valve opening / closing characteristic region in which the maximum valve lift amount INVL is larger than the regulated lift amount INVLX and the valve timing INVT is on the retard side with respect to the advance angle regulating angle INVTmdl.

  Region B shows a valve opening / closing characteristic region in which the maximum valve lift amount INVL is larger than the regulated lift amount INVLX and the valve timing INVT is on the advance side with respect to the advance angle regulated angle INVTmdl.

  Region C shows a valve opening / closing characteristic region in which the maximum valve lift amount INVL is smaller than the regulated lift amount INVLX and the valve timing INVT is on the retard side with respect to the advance angle regulating angle INVTmdl.

  Region D shows a valve opening / closing characteristic region in which the maximum valve lift amount INVL is smaller than the regulated lift amount INVLX and the valve timing INVT is on the advance side with respect to the advance angle regulated angle INVTmdl.

  The region E is an advance angle side and large lift side region of the region B, and a valve opening / closing characteristic region in which a bubble stamp occurs when the maximum valve lift amount INVL and the valve timing INVT are set in the region E. Indicates.

  A region F indicates a basic use region when the valve opening / closing characteristic is changed based on the engine operating state. That is, in a normal engine operating state, the variable valve gear 3 is controlled so that the valve opening / closing characteristics change in the region F based on changes in the engine load, the engine speed, and the like.

When the required value VTVL changes within the region F, the phase restriction mechanism 50 is driven as follows.
When the required value VTVL is in the region A, the restricting pin 60 and the restricting groove 52 are set to the engaged state, whereby the changeable range of the valve timing INVT is between the most retarded angle INVTmin and the advanced angle restricting angle INVTmdl. Limited. In this state, when the rotation phase of the vane rotor 45 reaches the advance angle regulation phase PMDL, the regulation groove 52 restricts the rotation of the vane rotor 45 to the further advance angle side.

  When the region to which the required value VTVL belongs changes from the region A to the region C, the restriction pin 60 and the restriction groove 52 are operated from the engaged state to the released state, whereby the changeable range of the valve timing INVT is from the most retarded angle INVTmin. It is enlarged up to the most advanced angle INVTmax.

  When the region to which the required value VTVL belongs changes from the region C to the region D, the released state of the restriction pin 60 and the restriction groove 52 is maintained, and thereby the changeable range of the valve timing INVT is from the most retarded angle INVTmin to the most advanced angle. Maintained until INVTmax.

  Note that, in the region B, the portion where the valve stamp may be generated is limited to the region E, but here, the variable valve gear 3 so that the actual valve timing INVT and the maximum valve lift amount INVL do not belong to the region B. Is controlled.

  With reference to FIG. 13, the processing procedure of “advance angle restriction control process”, which is a process for causing the rotational phase P to exceed the advance angle restriction phase PMDL, will be described in detail. The “advance restriction control process” is executed by the electronic control device 110. After reaching the end step, the same process is repeated again from step S11 as long as the engine is operating. It is.

  In this process, first, in step S11, it is determined whether or not there is an advance angle regulation request. Here, the advance angle restriction request is set in the following manner in the control separately executed by the electronic control unit 110. That is, when it is confirmed that there is a request for increasing the maximum valve lift amount INVL to be greater than the restriction lift amount INVLX, the restriction request is set based on this.

  When it is determined in step S11 that the advance angle restriction request is present, in next step S12, it is determined whether or not the valve timing INVT at that time is behind the advance angle restriction angle INVTmdl. When it is determined by the determination process in step S12 that the angle is on the retard side from the advance angle regulation angle INVTmdl, the process proceeds to step S13, and the hydraulic control valve 80 is set to one of the second to fourth modes.

  In any of the second to fourth modes, since the lubricating oil is supplied to the working chamber 55 in any mode, the regulation pin 60 projects in the second projecting direction Z2 and is fitted into the regulation groove 52, and the advance angle regulation angle INVTmdl. The advance angle exceeding is restricted.

  If it is determined by the determination processing in step S12 that the angle is not behind the advance angle regulation angle INVTmdl, that is, the angle is on the advance side, the process proceeds to step S14, and the hydraulic control valve 80 is set to the second mode.

  In the second mode, the lubricant oil is supplied to the working chamber 55, the lubricant oil is discharged from the advance chamber 48, and the lubricant oil is supplied to the retard chamber, so that the vane 46 is rotated on the retard side. While moving to P, the restriction pin 60 tends to protrude in the second protruding direction Z2. When the vane 46 exceeds the advance angle restriction phase PMDL, the restriction pin 60 protrudes in the second protrusion direction Z2 and is fitted into the restriction groove 52, and the advance angle exceeding the advance angle restriction angle INVTmdl is restricted.

  Thereafter, the fourth mode is selected when there is a request for advancement of the valve timing INVT, the fourth mode is selected when there is a request for retarding the valve timing INVT, and the second mode is selected when there is a request for holding the valve timing INVT. To do.

  If it is determined in step S11 that there is no advance angle restriction request, the process proceeds to step S15 to determine whether there is an advance angle restriction release request. Here, the advance angle restriction release request is set as a restriction request in the following manner in the control separately executed by the electronic control unit 110. That is, when it is confirmed that there is a request to make the maximum valve lift amount INVL smaller than the regulated lift amount INVLX, the advance angle restriction release request is set based on this.

  If it is determined in step S15 that there is an advance restriction release request, whether or not the valve timing INVT at that time is on the more advanced side than the target angle INVTT that is the target valve timing in step S16. Determine. When it is determined by the determination process in step S16 that the valve timing INVT at that time is on the advance side with respect to the target angle INVTT, the process proceeds to step S17, and the hydraulic control valve 80 is set to the first mode.

  In the first mode, since the lubricating oil is discharged from the working chamber 55, the lubricating oil is supplied to the retarding chamber 49, and the lubricating oil is discharged from the advance chamber 48, the vane 46 rotates on the retard side. While moving to the phase P, the restriction pin 60 tends to protrude in the first protruding direction Z1. Then, the regulation pin 60 tries to project in the first projecting direction Z1, moves to the accommodation position P0 while being abutted against the cover wall surface 44A, and an advance angle exceeding the advance angle regulation angle INVTmdl is allowed.

  When it is determined by the determination process in step S16 that the valve timing INVT at that time is not on the advance side relative to the target angle INVTT, that is, on the delay side, the process proceeds to step S18, and the hydraulic control valve 80 is set to the fifth mode. Set to.

  In the fifth mode, since the lubricating oil is discharged from the working chamber 55, the lubricating oil is supplied to the advance chamber 48, and the lubricating oil is discharged from the retard chamber 49, the vane 46 rotates on the advance side. While moving to the phase P, the restriction pin 60 tends to protrude in the first protruding direction Z1. Then, the regulation pin 60 tries to project in the first projecting direction Z1, moves to the accommodation position P0 while being abutted against the cover wall surface 44A, and an advance angle exceeding the advance angle regulation angle INVTmdl is allowed.

  Thereafter, the fourth mode is selected when there is a request for advancement of the valve timing INVT, the second mode is selected when there is a request for retarding the valve timing INVT, and the third mode is selected when there is a request for holding the valve timing INVT. To do.

If it is determined in step S11 that there is no advance angle restriction request, and it is determined in next step S12 that there is no advance angle restriction release request, this process ends.
According to this embodiment described above, the following effects can be obtained.

  (1) The hydraulic control mechanism 70 of this embodiment controls the supply / discharge state of the lubricating oil to each of the variable valve timing mechanism 40 and the phase restriction mechanism 50 by a single hydraulic control valve 80. The phase restriction mechanism 50 is provided on the vane rotor 45 and is provided on the housing rotor 41 with the restriction pin 60 that moves relative to the vane rotor 45 based on the supply / discharge state of the lubricating oil with respect to the phase restriction mechanism 50. A restriction hole 51 and a restriction groove 52 into which the restriction pin 60 projecting from the hole is fitted are configured.

  The regulation pin 60 is located between the first projecting position P1 projecting from the vane rotor 45, the second projecting position P2 projecting from the vane rotor 45 apart from the projecting position P1, and the housing position P0 housed in the vane rotor 45. Drive with. In the restriction hole 51, the restriction pin 60 at the first protruding position P1 is fitted when the rotational phase P is the most retarded phase PMIN that is a predetermined fixed phase. The restriction groove 52 is fitted with the restriction pin 60 at the second protruding position P2 when the rotational phase P is within a predetermined restriction phase range smaller than the range from the most retarded angle phase PMIN to the most advanced angle phase PMAX.

  When the restriction pin 60 is fitted in the restriction hole 51, the rotational phase P is fixed to the most retarded angle phase PMIN, so that the valve timing INVT is fixed to the most retarded angle INVTmin. When the restriction pin 60 is fitted in the restriction groove 52, the change range of the rotation phase P is limited to the restriction phase range, so that the change range of the valve timing INVT is larger than the range from the most retarded angle INVTmin to the most advanced angle INVTmax. It is limited to a small predetermined intermediate range.

  In other words, since the rotation phase P is fixed and the change range of the rotation phase P is restricted by one restriction pin 60, the valve is compared with the case where the two restriction pins 60 fix and restrict the rotation phase P. The configuration of the timing variable mechanism 40 can be simplified. In addition, since a single hydraulic control valve 80 controls the supply / discharge state of the lubricating oil with respect to the variable valve timing mechanism 40 and the phase restriction mechanism 50, the plurality of hydraulic control valves 80 can control the supply / discharge state. Compared with the case where it performs, simplification of an oil-path structure comes to be achieved. As described above, according to the present embodiment, the function of limiting the change range of the valve timing INVT and the function of fixing the valve timing INVT are provided, and the complexity of the structure for realizing these functions can be suppressed. become.

  (2) The hydraulic control mechanism 70 of the present embodiment is an advancement that connects the hydraulic control valve 80 and the advance chamber 48 as an oil passage through which the lubricating oil flows between the hydraulic control valve 80 and the variable valve timing mechanism 40. A corner chamber oil passage 71, a retard chamber oil passage 72 that connects the hydraulic control valve 80 and the retard chamber 49, and a working chamber oil passage 73 that connects the hydraulic control valve 80 and the working chamber 55 are provided. ing.

  Lubricating oil flows through the advance chamber 48, the retard chamber 49, and the working chamber 55 by the advance chamber oil passage 71, the retard chamber oil passage 72, and the working chamber oil passage 73 connected to the hydraulic control valve 80, respectively. I have to. That is, on the valve timing variable mechanism 40 side of the hydraulic control valve 80, since the oil passages connected to the advance chamber 48, the retard chamber 49, and the working chamber 55 are independent, the advance chamber 48 or the retard chamber 49 is moved to. The operation state of the phase restriction mechanism 50 can be switched regardless of the supply state of the lubricating oil.

  (3) The phase restricting mechanism 50 of the present embodiment includes the force of the spring 53 that applies a force to the restricting pin 60 to push the restricting pin 60 toward the first projecting position P1, and the restricting pin 60 to the second projecting position P2. The restriction pin 60 is driven between the housing position P0 and the first and second protruding positions P1 and P2 in accordance with the relationship with the hydraulic pressure of the working chamber 55 that applies the pressing force to the restriction pin 60. .

  Based on the magnitude relationship between the hydraulic pressure of the working chamber 55 and the force of the spring 53, a force toward the first projecting position P1 or the second projecting position P2 is applied to the restriction pin 60. Specifically, when the lubricating oil in the working chamber 55 is discharged, the force toward the first protruding position P1 exceeds the force toward the second protruding position P2, and the second protruding when the lubricating oil is supplied to the working chamber 55. The force toward the position P2 is greater than the force toward the first protruding position P1. For this reason, it is possible to maintain a state in which the restriction pin 60 can be moved to the first protruding position P1 as the hydraulic pressure in the working chamber 55 is released.

  (4) The hydraulic control valve 80 of the present embodiment has the second mode, the fourth mode, and the fifth mode as operation modes for setting the supply and discharge states of the lubricating oil to the advance chamber 48, the retard chamber 49, and the working chamber 55. A mode is provided. In the second mode, the lubricant oil is discharged from the advance chamber 48, the lubricant oil is supplied to the retard chamber 49, and the lubricant oil is supplied to the working chamber 55. In the fourth mode, the lubricating oil is supplied to the advance chamber 48, the lubricating oil is discharged from the retard chamber 49, and the lubricating oil is supplied to the working chamber 55. In the fifth mode, the lubricant oil is supplied to the advance chamber 48, the lubricant oil is discharged from the retard chamber 49, and the lubricant oil is discharged from the working chamber 55.

  When the second mode is selected, maintaining the state in which the restriction pin 60 can protrude from the vane rotor 45 toward the second protrusion position P2 and the retardation of the valve timing INVT are performed together. When the fourth or mode is selected, the state in which the regulation pin 60 can project from the vane rotor 45 toward the second projecting position P2 and the advance angle of the valve timing INVT are performed together. Further, when the fifth mode is selected, the state in which the restriction pin 60 can protrude from the vane rotor 45 toward the first protrusion position P1 and the advance angle of the valve timing INVT are performed together.

  (5) The hydraulic control valve 80 of the present embodiment further discharges the lubricant from the advance chamber 48 as an operation mode for setting the supply / discharge state of the lubricant to the advance chamber 48, the retard chamber 49, and the working chamber 55. And a first mode for supplying the lubricating oil to the retarding chamber 49 and discharging the lubricating oil from the working chamber 55.

  When the first mode is selected, the state in which the regulation pin 60 can project from the vane rotor 45 toward the first projecting position P1 and the retardation of the valve timing INVT are performed together.

  (6) The hydraulic control valve 80 according to the present embodiment further includes a third mode as an operation mode for setting the supply / discharge state of the lubricating oil with respect to the advance chamber 48, the retard chamber 49, and the working chamber 55. . In the third mode, the supply of the lubricant oil to the advance chamber 48 and the discharge of the lubricant oil from the advance chamber 48 are stopped, and the supply of the lubricant oil to the retard chamber 49 and the lubricant oil from the retard chamber 49 are stopped. Discharging is stopped and lubricating oil is supplied to the working chamber 55.

  When the third mode is selected, the state in which the restriction pin 60 can protrude from the vane rotor 45 toward the second protrusion position P2 and the maintenance of the valve timing INVT are performed together.

  (7) In the present embodiment, a range from the retard side to the most retarded angle INVTmin phase or the more advanced side than the most advanced angle INVTmax phase is set as the restriction phase range. That is, a range from a predetermined valve timing INVT that is on the more retarded side than the most advanced angle INVTmax to a predetermined valve timing INVT that is either on the most retarded angle INVTmin or more advanced than this is set as an intermediate range.

  When the restriction pin 60 is fitted in the restriction groove 52, the vane rotor 45 is restricted from rotating to the advance side beyond the advance angle restriction phase with respect to the housing rotor 41, while the vane rotor 45 is slow. When rotating to the corner side, the rotation is allowed until the most retarded angle INVTmin phase is reached.

  (8) The variable valve operating apparatus 3 of the present embodiment further includes a variable valve lift amount mechanism 30 that changes the maximum valve lift amount INVL of the intake valve 21. Then, the phase restriction mechanism 50 restricts the change range of the rotation phase P to the restriction phase range based on the fact that the maximum valve lift amount INVL of the intake valve 21 is set to a value larger than the restriction lift amount INVLX. The change range of the valve timing INVT is limited to an intermediate range.

  Regarding the phase restriction mechanism 50 that restricts the vane rotor 45 from being advanced or retarded beyond the advance angle restriction phase PMDL with respect to the housing rotor 41, the operation of accommodating the restriction pin 60 in the vane rotor 45 is performed by the housing rotor and the vane rotor 45. It becomes possible to suppress obstruction by relative rotation.

(Second Embodiment)
With reference to FIGS. 14-20, 2nd Embodiment which actualized the variable valve apparatus 3 of the internal combustion engine of this invention is described. This embodiment is a sixth mode in which the supply state of the lubricating oil to the advance chamber 48 in the fifth mode of the first embodiment is changed from the supply state to the stop state, and the structure of the hydraulic control valve is adjusted accordingly. And the operation is changed. Hereinafter, details of changes from the first embodiment will be described. In addition, about the structure which is common in said 1st Embodiment, the description regarding this is abbreviate | omitted suitably.

  With reference to FIGS. 14-19, the structure of the hydraulic control valve 90 of this embodiment and its operation mode are demonstrated. 14 to 19 show cross-sectional structures along the axial direction of the hydraulic control valve 90, and show the cross-sectional structures when in different operation modes. Moreover, the arrow in each figure shows the flow of lubricating oil.

  The hydraulic control valve 90 includes a single housing 91 provided with a plurality of ports, and a single spool 92 provided in the housing 91. When the spool 92 moves relative to the housing 91, the communication state (mode) between the plurality of ports is switched to change the supply state of the lubricating oil to the advance chamber 48, the retard chamber 49, and the working chamber 55. To do. Note that switching between these modes is executed by changing the DUTY ratio of a motor (not shown) as an actuator connected to the hydraulic control valve 90.

  The housing 91 includes a first supply port 96A and a second supply port 96B connected to the supply oil passage 74, and a first discharge port 97A, a second discharge port 97B and a third discharge port connected to the discharge oil passage 75. 97C, an advance port 93 connected to the advance chamber oil passage 71, a retard port 94 connected to the retard chamber oil passage 72, and an operation port 95 connected to the working chamber oil passage 73 are provided. It has been.

  The spool 92 includes a first partition 92A corresponding to the first discharge port 97A, a second partition 92B, a third partition 92C and a fourth partition 92D corresponding to the advance port 93 and the retard port 94, and an operation port. Corresponding fifth partition walls 92E and sixth partition walls 92F are provided. Then, based on the setting of the positional relationship between each partition wall of the spool 92 and each port of the housing 91, each port on the supply oil passage 74 and the discharge oil passage 75 side and each port on the valve timing variable mechanism 40 side are next. It corresponds as follows.

  That is, the advance port 93 communicates with only one of the first supply port 96A and the first discharge port 97A. The retard port 94 communicates with only one of the first supply port 96A and the second discharge port 97B. The operation port 95 is connected to only one of the second supply port 96B and the third discharge port 97C.

  In the hydraulic control valve 90 having such a structure, the operation mode can be set to any one of the first mode to the fourth mode and the sixth mode according to the position of the spool 92 in the axial direction with respect to the housing 91.

  As shown in FIG. 14, when the position of the spool 92 with respect to the housing 91 is in the first position, and the operation mode is in the first mode, the communication state of each port is maintained as follows. That is, the advance port 93 communicates with the first discharge port 97A and is blocked from the first supply port 96A by the second partition wall 92B. Further, the retard port 94 communicates with the first supply port 96A, and is blocked with the second discharge port 97B by the fourth partition wall 92D. Further, the operation port 95 communicates with the third discharge port 97C and is blocked from the second supply port 96B by the fifth partition wall 92E. Further, a part of the first discharge port 97A is closed by the first partition wall 92A.

  As shown in FIG. 15, when the position of the spool 92 with respect to the housing 91 is in the second position, and the operation mode is in the second mode, the communication state of each port is maintained as follows. That is, the advance port 93 communicates with the first discharge port 97A and is blocked from the first supply port 96A by the second partition wall 92B. Further, the retard port 94 communicates with the first supply port 96A, and is blocked with the second discharge port 97B by the fourth partition wall 92D. Further, the operation port 95 communicates with the second supply port 96B, and is disconnected from the third discharge port 97C by the fifth partition wall 92E.

  As shown in FIG. 16, when the position of the spool 92 with respect to the housing 91 is in the third position, and the operation mode is in the third mode, the communication state of each port is maintained as follows. That is, the advance port 93 is blocked by the second partition wall 92B from the first supply port 96A and the first discharge port 97A. Further, the retard port 94 is blocked from the first supply port 96A and the second discharge port 97B by the fourth partition wall 92D. Further, the operation port 85 communicates with the second supply port 96B and is blocked by the fifth partition wall 92E from the third discharge port 97C.

  As shown in FIG. 17, when the position of the spool 92 with respect to the housing 91 is in the fourth position, and the operation mode is in the fourth mode, the communication state of each port is maintained as follows. In other words, the advance port 93 communicates with the first supply port 96A and is blocked from the first discharge port 97A by the first partition 92A. Further, the retard port 94 communicates with the second discharge port 97B, and is blocked from the first supply port 96A by the fourth partition wall 92D. Further, the operation port 95 communicates with the second supply port 96B, and is disconnected from the third discharge port 97C by the fifth partition wall 92E.

  In the first mode to the fourth mode, the supply state of the lubricating oil to the advance chamber 48, the retard chamber 49, and the working chamber 55 is changed from the first mode to the fourth mode of the first embodiment through each port. It is maintained in the same state as each.

  As shown in FIG. 18, when the position of the spool 92 with respect to the housing 91 is in the sixth position, and the operation mode is in the sixth mode, the communication state of each port is maintained as follows. In other words, the advance port 93 is blocked from the first supply port 96A by the third partition 92C, and is blocked from the first discharge port 97A by the second partition 92B. Further, the retard port 94 communicates with the second discharge port 97B, and is blocked from the first supply port 96A by the fourth partition wall 92D. Further, the operation port 95 communicates with the third discharge port 97C and is blocked by the sixth partition wall 92F from the second supply port 96B.

  In the sixth mode, since the ports are in communication with each other, the flow of the lubricating oil from the oil pump 17 to the advance chamber 48 through the hydraulic control valve 90 and the hydraulic control valve 90 from the advance chamber 48 are turned on. Any flow of the lubricating oil to the oil pan 12 is blocked. Further, the lubricating oil in the retarding chamber 49 is circulated to the oil pan 12 through the retarding chamber oil passage 72, the retarding port 94, the second discharge port 97 </ b> B, and the discharge oil passage 75 in this order. Further, the lubricating oil from the working chamber 55 flows in the order of the working chamber oil passage 73, the working port 95, the third discharge port 97 </ b> C, and the discharge oil passage 75 and is circulated to the oil pan 12.

  FIG. 19 shows the relationship between each operation mode of the hydraulic control valve 80 and the mode of supply of lubricating oil to the advance chamber 48, the retard chamber 49 and the working chamber 55, and each operation mode of the hydraulic control valve 80 and the variable valve timing mechanism 40. A summary of the relationship between the rotation direction of the vane rotor 45 and the relationship between each operation mode of the hydraulic control valve 80 and the directing direction of the restriction pin 60 is shown. Further, the relationship between each operation mode of the hydraulic control valve 80 and the DUTY ratio is also shown.

  As shown in the figure, the hydraulic control valve 80 uses a DUTY ratio X in the range of 20 to 80% of the DUTY ratio when controlling the normal valve timing INVT. When the operation of fitting the restriction pin 60 into the restriction hole 51 is performed, an area of 0 to 20% that is not used during normal control is used, and when the advance angle exceeds the advance angle restriction angle INVTmdl, it is not used during normal control. Use 80-100% area.

  The first mode corresponds to the mode C described in the claims, the second mode corresponds to the mode A1 described in the claims, the third mode corresponds to the mode A3 described in the claims, and the fourth mode. Corresponds to mode A2 in the claims, and the sixth mode corresponds to mode D in the claims.

  Referring to FIG. 20, the processing procedure of “advance angle restriction control process”, which is a process for causing rotational phase P to exceed advance angle restriction phase PMDL, will be described in detail. The “advance restriction control process” is executed by the electronic control unit 110, and once reaching the end step, the same process is repeated again from step S21 as long as the engine is operating. It is.

  In this process, first, in step S21, it is determined whether or not there is an advance angle regulation request. Here, the advance angle restriction request is set in the following manner in the control separately executed by the electronic control unit 110. That is, when it is confirmed that there is a request for increasing the maximum valve lift amount INVL to be greater than the restriction lift amount INVLX, the restriction request is set based on this.

  If it is determined in step S21 that the advance angle restriction request is present, it is determined in next step S22 whether or not the valve timing INVT at that time is on the retard side with respect to the advance angle restriction angle INVTmdl. When it is determined by the determination process in step S22 that the angle is on the retard side from the advance restriction angle INVTmdl, the process proceeds to step S23, and the hydraulic control valve 80 is set to one of the second to fourth modes.

  In any of the second to fourth modes, since the lubricating oil is supplied to the working chamber 55 in any mode, the regulation pin 60 projects in the second projecting direction Z2 and is fitted into the regulation groove 52, and the advance angle regulation angle INVTmdl. The advance angle exceeding is restricted.

  If it is determined by the determination processing in step S22 that there is no retard angle from the advance angle regulation angle INVTmdl, ie, it is on the advance angle side, the process proceeds to step S24, and the hydraulic control valve 80 is set to the second mode.

  In the second mode, the lubricant oil is supplied to the working chamber 55, the lubricant oil is discharged from the advance chamber 48, and the lubricant oil is supplied to the retard chamber, so that the vane 46 is rotated on the retard side. While moving to P, the restriction pin 60 tends to protrude in the second protruding direction Z2. When the vane 46 exceeds the advance angle restriction phase PMDL, the restriction pin 60 protrudes in the second protrusion direction Z2 and is fitted into the restriction groove 52, and the advance angle exceeding the advance angle restriction angle INVTmdl is restricted.

  Thereafter, the fourth mode is selected when there is a request for advancement of the valve timing INVT, the second mode is selected when there is a request for retarding the valve timing INVT, and the third mode is selected when there is a request for holding the valve timing INVT. To do.

  If it is determined in step S21 that there is no advance angle restriction request, the process proceeds to step S25 to determine whether there is an advance angle restriction release request. Here, the advance angle restriction release request is set as a restriction request in the following manner in the control separately executed by the electronic control unit 110. That is, when it is confirmed that there is a request to make the maximum valve lift amount INVL smaller than the regulated lift amount INVLX, the advance angle restriction release request is set based on this.

  If it is determined in step S25 that there is an advance angle restriction release request, whether or not the valve timing INVT at that time is on the more advanced side than the target angle INVTT that is the target valve timing in step S26. Determine. When it is determined by the determination processing in step S26 that the valve timing INVT at that time is on the advance side with respect to the target angle INVTT, the process proceeds to step S27, and the hydraulic control valve 80 is set to the first mode.

  In the first mode, since the lubricating oil is discharged from the working chamber 55, the lubricating oil is discharged from the advance chamber 48, and the lubricating oil is supplied to the retard chamber 49, the vane 46 rotates on the retard side. While moving to the phase P, the restriction pin 60 tends to protrude in the first protruding direction Z1. Then, the regulation pin 60 tries to project in the first projecting direction Z1, moves to the accommodation position P0 while being abutted against the cover wall surface 44A, and an advance angle exceeding the advance angle regulation angle INVTmdl is allowed.

  When it is determined by the determination processing in step S26 that the valve timing INVT at that time is not on the advance side relative to the target angle INVTT, that is, on the delay side, the process proceeds to step S28, and the hydraulic control valve 80 is set to the sixth mode. Set to.

  In the sixth mode, the lubricating oil is discharged from the working chamber 55, the supply and discharge of the lubricating oil to the advance chamber 48 is stopped, and the lubricating oil is discharged from the retard chamber 49. Therefore, the vane 46 is prohibited from rotating to the retard side, and moves to the advance side based on the lubricating oil supplied to the retard chamber 49 in the advance phase P. Accordingly, the regulation pin 60 moves in the first projecting direction Z1 while the vane rotor 45 keeps the rotational phase P or moves at a lower speed than when the lubricant is supplied to the advance chamber 48 as in the fourth mode. And try to protrude. Then, the regulation pin 60 tries to project in the first projecting direction Z1, moves to the accommodation position P0 while being abutted against the cover wall surface 44A, and an advance angle exceeding the advance angle regulation angle INVTmdl is allowed.

  Thereafter, the fourth mode is selected when there is a request for advancement of the valve timing INVT, the second mode is selected when there is a request for retarding the valve timing INVT, and the third mode is selected when there is a request for holding the valve timing INVT. To do.

If it is determined in step S21 that there is no advance angle restriction request and it is determined in next step S22 that there is no advance angle restriction release request, this process ends.
According to this embodiment described above, the following effects can be achieved in addition to (1) to (3) and (5) to (8).

  (9) In the present embodiment, the hydraulic control valve 90 has the first mode, the second mode, and the second mode as operation modes for setting the supply / discharge state of the lubricating oil with respect to the advance chamber 48, the retard chamber 49, and the working chamber 55. The third mode, the fourth mode, and the sixth mode are provided. In the first mode, the lubricating oil is discharged from the advance chamber 48, the lubricating oil is supplied to the retard chamber 49, and the lubricating oil is discharged from the working chamber 55. In the second mode, the lubricant oil is discharged from the advance chamber 48, the lubricant oil is supplied to the retard chamber 49, and the lubricant oil is supplied to the working chamber 55. In the third mode, the supply of the lubricant oil to the advance chamber 48 and the discharge of the lubricant oil from the advance chamber 48 are stopped, and the supply of the lubricant oil to the retard chamber 49 and the lubricant oil from the retard chamber 49 are stopped. In the fourth mode in which the discharge is stopped and the lubricating oil is supplied to the working chamber 55, the lubricating oil is supplied to the advance chamber 48, the lubricating oil is discharged from the retard chamber 49, and the lubricating oil is supplied to the working chamber 55. . In the sixth mode, the supply of the lubricant to the advance chamber 48 and the discharge of the lubricant from the advance chamber 48 are stopped, the lubricant is discharged from the retard chamber 49, and the lubricant is discharged from the working chamber 55. .

  When the first mode is selected, the state in which the regulation pin 60 can project from the vane rotor 45 toward the first projecting position P1 and the retardation of the valve timing INVT are performed together. When the second mode is selected, maintaining the state in which the restriction pin 60 can protrude from the vane rotor 45 toward the second protrusion position P2 and the retardation of the valve timing INVT are performed together. When the third mode is selected, the state in which the restriction pin 60 can protrude from the vane rotor 45 toward the second protrusion position P2 and the maintenance of the valve timing INVT are performed together. When the fourth mode is selected, maintaining the state in which the regulation pin 60 can project from the vane rotor 45 toward the second projecting position P2 and the advance angle of the valve timing INVT are performed together. When the sixth mode is selected, maintaining the state in which the restriction pin 60 can protrude from the vane rotor 45 toward the first protrusion position P1 and prohibiting the change toward the retard side of the valve timing INVT are performed. Will come to be.

  (10) When the advance angle restriction release request is set and the valve timing INVT at that time is on the retard side with respect to the target angle INVTT, the advance is made by advancing with the restriction pin 60 moved to the accommodation position P0. The angle can be advanced beyond the angle regulation phase PMDL. However, unless the restriction pin 60 is moved to the accommodation position P0 before reaching the advance angle restriction phase PMDL, the restriction pin 60 and the restriction groove 52 may come into contact with each other and the advance angle restriction phase PMDL may not be exceeded. is there.

  In the present embodiment, the sixth mode is selected when the advance angle restriction release request is set and the valve timing INVT at that time is on the retard side with respect to the target angle INVTT. In the sixth mode, the regulation pin 60 is accommodated in the accommodation position P0 as the lubricating oil is discharged, and the vane 46 maintains the rotational phase P or enters the advance angle chamber 48 as the lubricating oil is supplied to the retard angle chamber 49. It moves at a smaller speed toward the advance side than when lubricating oil is supplied. For this reason, when exceeding the advance angle regulation phase PMDL, it is possible to suppress the regulation pin 60 from reaching the advance angle regulation phase PMDL before moving to the accommodation position P0.

(Other embodiments)
The embodiment of the present invention is not limited to the above-described embodiment, and can be carried out, for example, in the following manner.

  In the second embodiment, the supply / discharge state of the lubricating oil in the working chamber 55 and the advance chamber 48 is switched when the fourth mode is switched to the sixth mode, but the fourth mode and the sixth mode are switched. In the meantime, a new mode of the lubricating oil supply mode for the advance chamber 48, the retard chamber 49, and the working chamber 55 may be provided as in the fifth mode of the first embodiment. In other words, the timing at which the supply of the lubricating oil to the advance chamber 48 is stopped may not coincide with the timing at which the lubricating oil starts to be discharged from the working chamber 55.

  In the first embodiment, in the fifth mode, the lubricating oil is supplied to the advance chamber 48, the lubricating oil is discharged from the retard chamber 49, and the lubricating oil is discharged from the working chamber 55. The flow rate of the lubricating oil supplied to the corner chamber 48 may be smaller than the flow rate of the lubricating oil supplied to the advance chamber when in the fourth mode. In such a configuration, the advance speed of the valve timing INVT when the force toward the first protruding position P1 is applied to the restriction pin 60 and the force toward the second protrusion position P2 are applied to the restriction pin 60. When comparing the advance speed of the valve timing INVT at the time, the former can be made smaller.

  In each of the above embodiments, the first mode is such that the lubricating oil is discharged from the advance chamber 48, the lubricating oil is supplied to the retard chamber 49, and the lubricating oil is discharged from the working chamber 55. Even if the lubricating oil is discharged from the advance chamber, the supply of the lubricating oil to the retard chamber and the discharge of the lubricant from the retard chamber are stopped, and the mode is changed to the seventh mode in which the lubricant is discharged from the working chamber. Good. Moreover, you may make it take the structure which provides a 1st mode between the said 7th mode and a 2nd mode. When the seventh mode is selected, maintaining the state where the restriction pin 60 can protrude from the vane rotor 45 toward the first protrusion position P1 and prohibiting the change of the valve timing INVT toward the advance side are performed. It becomes like this.

  In the first mode in each of the above embodiments, the flow rate of the lubricating oil supplied to the retarding chamber 49 may be made smaller than the flow rate of the lubricating oil supplied to the retarding chamber 49 in the second mode. Good. In such a configuration, the retarding speed of the valve timing INVT when a force toward the first protruding position P1 is applied to the restriction pin 60 and a force toward the second protrusion position P2 are applied to the restriction pin 60. With respect to the retarding speed of the valve timing INVT, the former can be made smaller.

  In each of the above-described embodiments, the phase regulating mechanism 50 that fixes the rotational phase of the vane rotor 45 to the most retarded angle phase PMIN is used. However, a predetermined value between the most retarded angle phase PMIN and the most advanced angle phase PMAX is used. It is also possible to employ a phase restriction mechanism 50 that fixes the intermediate phase.

  In each of the above embodiments, a region with a DUTY ratio of 20 to 80% is used during normal operation, and a region outside this region is used in the first mode and the fifth or sixth mode. However, the DUTY ratio and each mode This is not limited to this and can be changed as appropriate.

  In each of the embodiments described above, the phase restriction mechanism 50 determines whether the advance angle restriction phase PMDL corresponding to the advance angle restriction angle INVTmdl on the retard side with respect to the most advance angle INVTmax and the most retarded angle phase PMIN corresponding to the most delay angle INVTmin. Although the rotational phase of the vane rotor 45 with respect to the housing rotor 41 is regulated in between, the regulation range by the phase regulation mechanism 50 is not limited to this. For example, the rotational range of the vane rotor 45 is set to a range between the phase on the retard side of the most advanced angle phase PMAX and the phase on the more retarded side than this and the phase on the more advanced side than the most retarded angle phase PMIN. It can also be restricted.

  In each of the above embodiments, the present invention is applied to the variable valve operating apparatus 3 that changes the valve timing INVT of the intake valve 21, but the present invention is similarly applied to a variable valve operating apparatus that changes the valve timing of the exhaust valve 25. can do. In the exhaust valve, there is a concern that a valve stamp may occur in the retarded phase. That is, in this case, when the maximum valve lift amount of the exhaust valve exceeds a predetermined valve lift amount, the phase restriction mechanism that restricts the rotation of the vane rotor to the retard side exceeding the retard angle regulation phase is engaged with the regulation pin. The configuration is as follows. As a result, in the variable valve timing mechanism, the vane rotor is restricted from rotating beyond the rotation phase corresponding to the retard angle restriction phase, so that the collision between the exhaust valve and the piston is avoided.

  In each of the above embodiments, the restriction pin 60 is pushed toward the second protruding direction Z2 when the lubricating oil is supplied to the working chamber 55. However, when the lubricating oil is supplied to the working chamber 55, The restriction pin 60 may be pushed toward the first protruding direction Z1. At this time, each operation | movement of the control pin 60 can be performed by changing the supply-and-discharge state of the lubricating oil with respect to the working chamber 55 in each said embodiment.

  In each of the above embodiments, the present invention is applied to a variable valve apparatus that is provided with both a variable valve timing mechanism and a variable valve lift amount mechanism. Can also be applied.

  In this case, although the control of the restriction pin based on the maximum valve lift amount INVL is not performed by omitting the valve lift amount variable mechanism, the restriction of the valve timing INVT by the restriction pin is restricted based on other requirements. Can be done. For example, when the upper limit value of the retard amount of the valve timing INVT is set in the control so as to limit the size of the valve overlap to a value larger than a predetermined period, this limit of the valve overlap should be assisted. It is conceivable to keep the regulating pin in a protruding state.

  According to this configuration, normally, the valve timing INVT is retarded beyond the upper limit value of the retard amount in terms of control, but for some reason, the valve timing INVT exceeds the upper limit value and the retard angle is retarded. It may be changed to the side. At this time, when the upper limit value of the retard amount is set to an advance side with respect to the restriction angle corresponding to the retard restriction phase, the valve timing INVT exceeds the upper limit value of the retard amount as described above. Even so, retarding beyond the regulation angle is limited by the regulation pin.

  As described above, when the configuration in which the restriction pin is maintained in the protruding state with respect to the restriction groove is adopted, when the valve timing INVT exceeds the upper limit value of the retard amount, the amount exceeding this is regulated by the restriction pin. It is smaller than the case without it. In other words, even in a configuration in which the valve lift amount variable mechanism is omitted, it is meaningful to regulate the valve timing INVT by the regulation pin.

  And about what operates a regulation pin based on the demand different from the demand from the maximum valve lift amount including the composition illustrated above, according to the modification to which the present invention is applied, As in the above embodiment, the configuration of the phase restriction mechanism can be simplified.

  -After all, any variable valve operating system that has a phase regulating mechanism that limits the range of relative rotation between the housing and the vane rotor more than the range from the most retarded phase to the most advanced angle phase. The present invention can be applied, and even in that case, an effect according to the effect of the above-described embodiment can be achieved.

  DESCRIPTION OF SYMBOLS 1 ... Internal combustion engine, 10 ... Engine main body, 11 ... Cylinder block, 12 ... Oil pan, 13 ... Cylinder head, 14 ... Combustion chamber, 15 ... Piston, 16 ... Crankshaft, 17 ... Oil pump, 21 ... Intake valve, 22 ... intake camshaft, 22C ... intake cam, 23 ... rocker arm, 24 ... lash adjuster, 25 ... exhaust valve, 26 ... exhaust camshaft, 3 ... variable valve gear, 30 ... variable valve lift mechanism, 31 ... control shaft, 32 ... Arm assembly, 33 ... Input arm, 34 ... Output arm, 40 ... Variable valve timing mechanism (variable valve mechanism), 41 ... Housing rotor (input rotating body), 41A ... Partition wall, 42 ... Housing body, 43 ... Sprocket 43A ... Sprocket wall surface, 44 ... Cover, 44A ... Cover wall surface, 45 ... Vanero (Rotating output body), 46 ... vane, 46A ... storage chamber, 47 ... vane storage chamber, 48 ... advance chamber 48 ... retard chamber, 50 ... phase regulating mechanism, 51 ... regulating hole 51 ... regulating groove, 53 ... Spring, 54 ... Spring chamber, 55 ... Working chamber, 60 ... Restriction pin (regulator), 61 ... Pin body, 61A ... First tip, 61B ... Second tip, 62 ... Partition, 70 ... Hydraulic control mechanism 71 ... Advancing chamber oil passage, 72 ... Delay chamber oil passage, 73 ... Working chamber oil passage, 74 ... Supply oil passage, 75 ... Drain oil passage, 80 ... Hydraulic control valve, 81 ... Sleeve, 82 ... Spool, 82A ... first partition, 82B ... second partition, 82C ... third partition, 82D ... fourth partition, 82E ... fifth partition, 83 ... advance port, 84 ... retard port, 85 ... actuation port, 86A ... 1 supply port, 86B ... 2nd supply port, 87A ... 1st discharge port, 87B ... 2nd discharge 87C ... third discharge port, 90 ... hydraulic control valve, 91 ... sleeve, 92 ... spool, 92A ... first partition, 92B ... second partition, 92C ... third partition, 92D ... fourth partition, 92E ... Fifth partition, 92F ... Sixth partition, 93 ... Advance port, 94 ... Delay port, 95 ... Operating port, 96A ... First supply port, 96B ... Second supply port, 97A ... First discharge port, 97B ... Second discharge port, 100... Control device, 110... Electronic control device, 111... Crank position sensor, 112.

Claims (14)

By operating the relative phase, which is the relative rotational phase between the input rotator and output rotator, between the most retarded angle phase and the most advanced angle phase, the valve timing of the intake valve or exhaust valve as the engine valve is maximized. A variable valve mechanism that changes between an advance angle and a most retarded angle, a phase restriction mechanism that restricts the range of the relative phase, and a supply and discharge state of hydraulic fluid to the variable valve mechanism and the phase restriction mechanism are controlled. In a variable valve operating apparatus for an internal combustion engine comprising a hydraulic control mechanism for
The hydraulic control mechanism controls the supply / discharge state of hydraulic oil to each of the variable valve mechanism and the phase restriction mechanism with a single hydraulic control valve,
The phase restriction mechanism is provided in the output rotator and moves with respect to the output rotator based on a supply / discharge state of hydraulic oil to the restriction mechanism, and the output rotator is provided in the input rotator and outputs the output. It is configured including a regulation hole and a regulation groove into which the regulation body protruding from the rotating body is fitted,
The restricting body is accommodated in the output rotating body, a first protruding position protruding from the output rotating body, a second protruding position protruding from the output rotating body at a different location from the protruding position, and the output rotating body. It is driven between the storage position,
The restriction hole is to be fitted with the restriction body at the first protruding position when the relative phase is at a predetermined fixed phase,
The restricting groove is fitted with the restricting body at the second projecting position when the relative phase is within a predetermined restricting phase range smaller than a range from the most retarded phase to the most advanced angle phase. Is,
When the restriction body is fitted in the restriction hole, the valve timing is fixed at a specific angle by fixing the relative phase to the fixed phase,
When the restriction body is fitted in the restriction groove, the change range of the relative phase is limited to the restriction phase range, so that the change range of the valve timing is more than the range from the most retarded angle to the most advanced angle. A variable valve operating apparatus for an internal combustion engine, wherein the variable valve operating apparatus is limited to a small predetermined intermediate range. The variable valve operating apparatus for an internal combustion engine according to claim 1,
The hydraulic control mechanism is an advance chamber that connects the hydraulic control valve and an advance chamber of the variable valve mechanism as an oil passage through which hydraulic oil flows between the hydraulic control valve and the variable valve mechanism. An oil passage, a retarding chamber oil passage connecting the hydraulic control valve and the retarding chamber of the variable valve mechanism, and a working chamber oil passage connecting the hydraulic control valve and the working chamber of the phase restriction mechanism. A variable valve operating apparatus for an internal combustion engine, comprising: The variable valve operating apparatus for an internal combustion engine according to claim 1 or 2,
The phase restricting mechanism includes a spring force that applies a force to the restricting body to push the restricting body toward the first projecting position, and a force to push the restricting body toward the second projecting position. The internal combustion engine is configured to drive the regulating body between the housing position, the first projecting position, and the second projecting position based on a relationship with a hydraulic pressure of a working chamber applied to the regulating body. Variable valve gear for engine. The variable valve operating apparatus for an internal combustion engine according to claim 2 or 3,
In the phase regulating mechanism, when the hydraulic oil in the working chamber is discharged, the force toward the first projecting position exceeds the force toward the second projecting position, and the hydraulic oil is supplied to the working chamber. The variable valve operating apparatus for an internal combustion engine, characterized in that the force toward the second protruding position is sometimes greater than the force toward the first protruding position. The variable valve operating apparatus for an internal combustion engine according to any one of claims 2 to 4,
The hydraulic control valve is an operation mode for setting a supply / discharge state of hydraulic oil to the advance chamber, the retard chamber, and the working chamber.
Mode A1 for discharging hydraulic oil from the advance chamber, supplying hydraulic oil to the retard chamber, and supplying hydraulic oil to the hydraulic chamber;
A mode A2 for supplying hydraulic oil to the advance chamber and discharging hydraulic oil from the retard chamber and supplying hydraulic oil to the hydraulic chamber;
A variable valve operating apparatus for an internal combustion engine, comprising: mode B for supplying hydraulic oil to the advance chamber, discharging hydraulic oil from the retard chamber, and discharging hydraulic oil from the hydraulic chamber. The variable valve operating apparatus for an internal combustion engine according to claim 5,
The hydraulic control valve makes the flow rate of hydraulic oil supplied to the advance chamber in mode B smaller than the flow rate of hydraulic oil supplied to the advance chamber in mode A2. A variable valve operating apparatus for an internal combustion engine. The variable valve operating apparatus for an internal combustion engine according to any one of claims 2 to 4,
The hydraulic control valve is an operation mode for setting a supply / discharge state of hydraulic oil to the advance chamber, the retard chamber, and the working chamber.
Mode A1 for discharging hydraulic oil from the advance chamber, supplying hydraulic oil to the retard chamber, and supplying hydraulic oil to the hydraulic chamber;
Mode A2 for supplying hydraulic oil to the advance chamber, discharging hydraulic oil from the retard chamber, and supplying hydraulic oil to the hydraulic chamber;
A variable valve operating apparatus for an internal combustion engine, comprising: mode C for discharging hydraulic oil from the advance chamber, supplying hydraulic oil to the retard chamber, and discharging hydraulic oil from the hydraulic chamber. The variable valve operating apparatus for an internal combustion engine according to claim 7,
The hydraulic control valve makes the flow rate of the hydraulic oil supplied to the retarding chamber in the mode C smaller than the flow rate of the hydraulic oil supplied to the retarding chamber in the mode A1. A variable valve operating apparatus for an internal combustion engine. The variable valve operating apparatus for an internal combustion engine according to any one of claims 2 to 4,
The hydraulic control valve is an operation mode for setting a supply / discharge state of hydraulic oil to the advance chamber, the retard chamber, and the working chamber.
Mode A1 for discharging hydraulic oil from the advance chamber, supplying hydraulic oil to the retard chamber, and supplying hydraulic oil to the hydraulic chamber;
A mode A2 for supplying hydraulic oil to the advance chamber and discharging hydraulic oil from the retard chamber and supplying hydraulic oil to the hydraulic chamber;
A mode D for stopping the supply of the hydraulic oil to the advance chamber and the discharge of the hydraulic oil from the advance chamber, discharging the hydraulic oil from the retard chamber, and discharging the hydraulic oil from the working chamber; A variable valve operating apparatus for an internal combustion engine. The variable valve operating apparatus for an internal combustion engine according to any one of claims 2 to 4,
The hydraulic control valve is an operation mode for setting a supply / discharge state of hydraulic oil to the advance chamber, the retard chamber, and the working chamber.
Mode A1 for discharging hydraulic oil from the advance chamber, supplying hydraulic oil to the retard chamber, and supplying hydraulic oil to the hydraulic chamber;
A mode A2 for supplying hydraulic oil to the advance chamber and discharging hydraulic oil from the retard chamber and supplying hydraulic oil to the hydraulic chamber;
A mode E for discharging the hydraulic oil from the advance chamber, stopping the supply of the hydraulic oil to the retard chamber, and discharging the hydraulic oil from the retard chamber, and discharging the hydraulic oil from the operation chamber; A variable valve operating apparatus for an internal combustion engine. The variable valve operating apparatus for an internal combustion engine according to any one of claims 5 to 10,
The hydraulic control valve is an operation mode for setting a supply / discharge state of hydraulic oil to the advance chamber, the retard chamber, and the working chamber.
Stop supplying hydraulic oil to the advance chamber and discharging hydraulic oil from the advance chamber, stop supplying hydraulic oil to the retard chamber and discharging hydraulic oil from the retard chamber, and A variable valve operating apparatus for an internal combustion engine, further comprising a mode A3 for supplying hydraulic oil to the working chamber. The variable valve operating apparatus for an internal combustion engine according to any one of claims 1 to 11,
A variable valve operating apparatus for an internal combustion engine, wherein a most retarded angle phase is set as the fixed phase, that is, a most retarded angle is set as the specific angle. The variable valve operating apparatus for an internal combustion engine according to any one of claims 1 to 12,
A range from the most retarded angle phase to the most retarded angle phase or any more advanced angle side than the most advanced angle phase is set as the restriction phase range, that is, the intermediate range is retarded from the most advanced angle. A variable valve operating apparatus for an internal combustion engine, characterized in that a range from a predetermined valve timing at a predetermined angle to a predetermined valve timing at either the most retarded angle or an advanced angle side is set. The variable valve operating apparatus for an internal combustion engine according to any one of claims 1 to 13,
The variable valve operating apparatus further includes a variable valve lift amount mechanism for changing the maximum valve lift amount of the engine valve,
The phase restriction mechanism restricts the change range of the relative phase to the restriction phase range based on the maximum valve lift amount of the engine valve being set to a value larger than a reference lift amount. The variable valve operating apparatus for an internal combustion engine is characterized in that the change range is limited to the intermediate range.

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