CN103038462B

CN103038462B - Valve timing control apparatus for internal combustion engine and control method thereof

Info

Publication number: CN103038462B
Application number: CN201180037061.XA
Authority: CN
Inventors: 守谷嘉人; 加茂吉朗; 林田笃史; 藤村治仁
Original assignee: Toyota Motor Corp
Current assignee: Toyota Motor Corp
Priority date: 2010-07-30
Filing date: 2011-07-29
Publication date: 2015-04-01
Anticipated expiration: 2031-07-29
Also published as: WO2012014056A1; DE112011102548T5; JP5012973B2; CN103038462A; JP2012031801A; US20130118430A1

Abstract

A variable valve timing mechanism changes a relative rotation phase of a camshaft with respect to a crankshaft to a target phase based on hydraulic pressure supplied to an advance side pressure chamber and a retard side pressure chamber. A lock mechanism is placed in a locked state in which the relative rotation phase is locked at a maximum retard phase when the hydraulic pressure in the advance side pressure chamber and the retard side pressure chamber is low, and that is placed in an unlocked state in which the locked state is released when the hydraulic pressure becomes high. Hydraulic pressure regulations in a first mode that changes the relative rotation phase to a side toward the maximum retard phase (S102) and in a second mode that changes the relative rotation phase to a side away from the maximum retard phase (SI 03) are executed in combination during a period of time from when an operating switch is turned off until the crankshaft stops rotating.

Description

For port timing arrangement for controlling timing and the controlling method thereof of internal-combustion engine

Technical field

The present invention relates to a kind of port timing arrangement for controlling timing for internal-combustion engine, it comprises: variable valve timing timing mechanism, and it sets the opening and closing timing of the engine valve opened and closed according to camshaft changeably relative to the relative rotation phase of bent axle by change camshaft; And locking framework, described relative rotation phase is locked in the limit phase place place of the excursion of described relative rotation phase by it.The invention still further relates to the controlling method of this variable valve timing control gear.

Background technique

Be arranged on opening and closing timing (that is, port timing timing) that vehicle suitably can change engine valve as the internal-combustion engine in automobile has usually thus improve the variable valve timing timing mechanism of the output of motor and effulent etc.

Described variable valve timing timing mechanism comprises: housing, and it is connected to the bent axle of internal-combustion engine with driving; And blade body, it is connected to such as camshaft with driving.Described housing and described blade body are arranged to enclose relative to each other and rotate about the axis.The blade extended in radial directions is formed on described blade body.The inner side of described housing is divided into side pressure room and delay side pressure room in advance by these blades.Carry out pressure controlled working oil and be supplied to each pressure chamber in these pressure chambers.Described blade body is converted to side or delay side in advance relative to the relative rotation phase (that is, described camshaft is relative to the relative rotation phase of described bent axle) of described housing by the hydraulic pressure in pressure chamber be applied on described blade.More particularly, described relative rotation phase is converted to side in advance by the working oil that is fed to described side pressure room in advance and the working oil of discharging from described delay side pressure room.On the other hand, described relative rotation phase is converted to delay side by the working oil of discharging from described side pressure room in advance and the working oil being fed to described delay side pressure room.The port timing timing of described internal-combustion engine is by changing the described relative rotation phase of described camshaft in this way and changing.

And, such as publication number is that the Japanese patent application (JP-A-2009-156217) of 2009-156217 describes a kind of port timing arrangement for controlling timing, it comprises locking framework, the described relative rotation phase of camshaft is mechanically locked in predetermined locking phase (that is, side pole limit phase place [maximum advanced phase] in advance in control range and limit phase place of the delay side pole in control range [maximum delay phase place]) place by this locking framework.This locking framework makes it possible to, when engine start, the port timing timing of described internal-combustion engine is remained on suitable timing place, when engine start, because the rotational speed of oil pump is low, so be difficult to obtain sufficiently high pressure for the supply pressure of working oil.

This locking framework comprises such as: stop pin, and its telescopically is arranged among the receiving hole that is formed in described blade body; Concave shaped portion (that is, locking aperture), the terminal part of stop pin is inserted in this concave shaped portion; And spring, it promotes this stop pin towards this locking aperture, etc.Described locking framework also has the pressure chamber's (that is, lock release pressure chamber) for unlocking.Described side pressure room is in advance communicated with this lock release pressure chamber with described delay side pressure room, and a part of working oil is provided to described lock release pressure chamber.By with the Driving force being applied to the corresponding amount of described hydraulic pressure (that is, described unlocking pressure) on described stop pin in described lock release pressure chamber to promote described stop pin away from described locking aperture.

In this locking framework, the magnitude relationship of the retracted position of described stop pin (that is, lock state and remove the released state of lock state) between the Driving force according to described spring and the Driving force based on described unlocking pressure and selectively changing.

Such as, when by turning off operating switch to stop motor, described port timing arrangement for controlling timing continues to run, and pressure increase in described side pressure room in advance or described delay side pressure room thus the described relative rotation phase of described camshaft is changed over locking phase.Consequently, therefore described relative rotation phase changes over locking phase.Then, predetermined pressure is equal to or less than (namely when described unlocking pressure drops to due to the minimizing of the supply pressure of the gear pump of engine stop in this condition, lock pressure) time, the Driving force of described spring exceedes the Driving force based on described unlocking pressure.Consequently, by making described stop pin move towards described locking aperture from the Driving force of described spring, and the terminal part of described stop pin slips into described locking aperture.Consequently, described locking framework becomes locking, is therefore limited in the relative rotation between described housing with described blade body.

On the other hand, when described internal combustion engine start and described oil pump again entry into service time, the hydraulic pressure being fed to the described working oil of side pressure room and described delay side pressure room in advance from described oil pump increases gradually.When described unlocking pressure becomes than described predetermined pressure height, consequently, the Driving force based on described unlocking pressure becomes larger than the Driving force of described spring.Consequently, the motion of described stop pin, away from described locking aperture, makes the terminal part of described stop pin from described locking aperture out.Consequently, described locking framework becomes unblock, thus makes described housing and described blade body relative to each other to rotate.And, when described locking framework from described lock state be switched to described released state and then the supply pressure of described oil pump raises further time, port timing timing based on the hydraulic pressure in described delay side pressure room and described in advance side pressure room adjustment and change.

When described locking framework is switched to described lock state from described released state, preferably perform this switching (that is, preferably switching time is short) fast.Use said apparatus, described switching time arrives the time spent of locking phase by the described relative rotation phase of described camshaft and described unlocking pressure is reduced to the time that described predetermined pressure spends and determines.

, use said apparatus herein, the described hydraulic pressure shifted to an earlier date in side pressure room and described delay side pressure room is conditioned the described relative rotation phase for changing described camshaft when described internal-combustion engine stops.Therefore, one in use pressure chamber (more specifically, the pressure chamber of working oil is supplied when being used in the side changed to by described relative rotation phase away from locking phase), described working oil is discharged from this pressure chamber, and therefore described hydraulic pressure easily reduces.But use another pressure chamber (more specifically, being supplied the pressure chamber of working oil when being used in the side changed to by described relative rotation phase towards locking phase), working oil is supplied to this pressure chamber, and therefore described hydraulic pressure is not easy to reduce.

Use the described hydraulic pressure had in described side pressure room in advance or one of them pressure chamber, described delay side pressure room to be not easy the device of the structure reduced in this way, described unlocking pressure is not easy to reduce, and therefore contributes to the minimizing preventing switching time like this.Therefore, about this point, use said apparatus to there is the space of improving.

Summary of the invention

In view of foregoing problems, so the port timing arrangement for controlling timing that the invention provides for internal-combustion engine and controlling method thereof, locking framework can be switched to lock state by this device rapidly.

A scheme of the present invention relates to the port timing arrangement for controlling timing for internal-combustion engine, it comprises: variable valve timing timing mechanism, and camshaft is changed over target phase relative to the relative rotation phase of bent axle based on being supplied to the hydraulic pressure of side pressure room and delay side pressure room in advance by it; And locking framework, when described hydraulic pressure is low, described locking framework is placed in the described relative rotation phase lock state locked at the limit phase place place of the excursion of described relative rotation phase, and when described hydraulic pressure uprises, described locking framework is placed in described lock state by the released state removed.This port timing arrangement for controlling timing being used for internal-combustion engine also comprises actuating device, described actuating device is configured to: from the shut-down operation making described internal-combustion engine stop time until during described bent axle time period of stopping the rotation, the combination of described actuating device performs and changes to described relative rotation phase towards the adjustment of the described hydraulic pressure of the first mode of the side of described limit phase place, and described relative rotation phase is changed to the adjustment of described hydraulic pressure of the second pattern of the side away from described limit phase place.

Another scheme of the present invention relates to the controlling method of the port timing arrangement for controlling timing for internal-combustion engine, described port timing arrangement for controlling timing comprises: variable valve timing timing mechanism, and camshaft is changed over target phase relative to the relative rotation phase of bent axle based on being supplied to the hydraulic pressure of side pressure room and delay side pressure room in advance by it; And locking framework, when described hydraulic pressure is low, described locking framework is placed in the described relative rotation phase lock state locked at the limit phase place place of the excursion of described relative rotation phase, and when described hydraulic pressure uprises, described locking framework is placed in described lock state by the released state removed.In this controlling method, from the shut-down operation making described internal-combustion engine stop time until during described bent axle time period of stopping the rotation, combination performs and to be changed to by described relative rotation phase towards the adjustment of the described hydraulic pressure of the first mode of the side of described limit phase place and the adjustment of described hydraulic pressure of the second pattern described relative rotation phase being changed to the side away from described limit phase place.

According to for the described port timing arrangement for controlling timing of internal-combustion engine and the controlling method of this port timing arrangement for controlling timing, when described internal-combustion engine is out of service, when making the described relative rotation phase of described camshaft change over limit phase place when regulating described hydraulic pressure in a first pattern, working oil is discharged from a pressure chamber described side pressure room in advance or described delay side pressure room, makes to reduce described hydraulic pressure.Simultaneously, perform the hydraulic regulation of the second pattern described relative rotation phase being changed to the side away from described limit phase place, working oil is discharged from another pressure chamber (that is, described side pressure room or described delay side pressure room in advance), and described hydraulic pressure reduce.

The hydraulic regulation not only having performed first mode in this way but also the hydraulic regulation performing the second pattern make the described hydraulic pressure in described side pressure room in advance and described delay side pressure room reduce respectively.Therefore, the hydraulic pressure in described in advance side pressure room and described delay side pressure room and therefore described unlocking pressure can reduce fast, and therefore described locking framework can switch to lock state from released state rapidly.

And, in above-mentioned port timing arrangement for controlling timing, described actuating device can perform the hydraulic regulation of described first mode until described relative rotation phase arrives described limit phase place, and when described relative rotation phase arrives described limit phase place, described actuating device can perform the hydraulic regulation of described second pattern.

Use above-mentioned port timing arrangement for controlling timing, when described internal-combustion engine shuts down, perform the first hydraulic regulation of first mode and the described relative rotation phase of described camshaft is changed over limit phase place.Now, working oil from a pressure chamber described side pressure room in advance or described delay side pressure room (more specifically, the pressure chamber of working oil is supplied when described relative rotation phase being changed over the side away from limit phase place) discharge, described hydraulic pressure is reduced.Then, when the described relative rotation phase of described camshaft reaches the limit of phase place, the hydraulic regulation of the second pattern is performed.Now, described hydraulic pressure in the described pressure chamber shifted to an earlier date in side pressure room or described delay side pressure room has been low due to the hydraulic regulation of first mode before this, therefore the described relative rotation phase of described camshaft can not change over the phase place of the side away from limit phase place, and, working oil is discharged from another pressure chamber (described side pressure room or described delay side pressure room in advance), and described hydraulic pressure is reduced.

By this way, the described hydraulic pressure in pressure chamber can suitably reduce.That is, described hydraulic pressure in a pressure chamber in described in advance side pressure room or described delay side pressure room changes over limit phase place along with the described relative rotation phase of described camshaft and reduces, and after the described relative rotation phase of described camshaft has arrived maximum delay phase place, while the change suppressing described relative rotation phase, the described hydraulic pressure in another pressure chamber (described side pressure room or described delay side pressure room in advance) reduces.

And, in above-mentioned port timing arrangement for controlling timing, described actuating device can start the hydraulic regulation performing described second pattern after described shut-down operation starts, and when described relative rotation phase changes to the phase place away from the described side of described limit phase place, described actuating device can be supspended the described hydraulic regulation of described second pattern and perform the hydraulic regulation of described first mode.

Use above-mentioned port timing arrangement for controlling timing, when the described relative rotation phase of described camshaft can not change over the phase place away from the side of limit phase place, by regulating described hydraulic pressure in a second mode, the described hydraulic pressure in a pressure chamber in described side pressure room in advance or described delay side pressure room will be reduced.And, if when performing the described hydraulic regulation of the second pattern, the described relative rotation phase of described camshaft by change over away from the side of limit phase place phase place time, by regulating described hydraulic pressure in a first pattern, the described hydraulic pressure in another pressure chamber (described side pressure room or described delay side pressure room in advance) is reduced.By this way, the described hydraulic pressure in described side pressure room in advance and the described hydraulic pressure in described delay side pressure room all can reduce.

And, in above-mentioned port timing arrangement for controlling timing, when when performing the described hydraulic regulation of described second pattern, described relative rotation phase does not change to the state continuance predetermined time section of the phase place of the described side away from described limit phase place, described actuating device can stop the described hydraulic regulation of described second pattern and perform the described hydraulic regulation of described first mode in predetermined time section.

Even if by the hydraulic regulation of first mode, a pressure chamber in described in advance side pressure room or described delay side pressure room (more specifically, be supplied the pressure chamber of working oil when described relative rotation phase changes over the side away from limit phase place) in described hydraulic pressure enough low and the described relative rotation phase of described camshaft can not be changed over the phase place of the side away from limit phase place, its (such as, described hydraulic pressure) may be enough low and make described locking framework switch to lock state.

About this point, use above-mentioned port timing arrangement for controlling timing, after described hydraulic pressure in a pressure chamber in described side pressure room in advance or described delay side pressure room has become enough low and the described relative rotation phase of described camshaft can not have been changed over the phase place away from the side of limit phase place, alternately perform the hydraulic regulation of first mode and the hydraulic regulation of the second pattern, thus make the described described hydraulic pressure of side pressure room and the described hydraulic pressure of described delay side pressure room in advance reduce all fully.

And, in port timing arrangement for controlling timing described above, described limit phase place can be the limit phase place of the delay side of described relative rotation phase, can to be working oil from described side pressure room in advance discharge described first mode and working oil is supplied to the shaping modes of described delay side pressure room, and described second pattern can be working oil is supplied to described side pressure room in advance and the working oil shaping modes of discharging from described delay side pressure room.

Further, above-mentioned port timing arrangement for controlling timing can also comprise hydraulic control valve, and described hydraulic control valve regulates the amount being fed to the described working oil of side pressure room or described delay side pressure room in advance according to the dutycycle of the drive singal of input.And described first mode can by being set as 0% and to realize and described second pattern can by being set as 100% and realize by described dutycycle by described dutycycle.

And in above-mentioned port timing arrangement for controlling timing, described shut-down operation can be in response to operating switch and be operated to stop the shut-down operation of the running of described internal-combustion engine.

According to for the described port timing arrangement for controlling timing of internal-combustion engine and above-mentioned controlling method thereof, after the running of operation element switch for the described internal-combustion engine of stopping, the described described hydraulic pressure shifted to an earlier date in side pressure room and described delay side pressure room can reduce fast thus make to complete the switching of described locking framework from released state to lock state fast.

Accompanying drawing explanation

Feature to exemplary embodiment of the present invention, advantage and technology and industrial significance are described below in conjunction with accompanying drawing, wherein identical reference character represents identical element, and wherein:

Fig. 1 is the schematic diagram of the structure of port timing arrangement for controlling timing according to the first exemplary embodiment of the present invention;

Fig. 2 is the sectional view of the structure of locking framework according to the first exemplary embodiment;

Fig. 3 is another sectional view of the structure of described locking framework;

The flow chart of control program when Fig. 4 shows the engine stop according to the first exemplary embodiment;

The timing chart of the example of the mode of control program when Fig. 5 A, Fig. 5 B, Fig. 5 C, Fig. 5 D and Fig. 5 E are the execution engine stops according to the first exemplary embodiment;

The flow chart (part 1) of control program when Fig. 6 shows the engine stop according to the second exemplary embodiment of the present invention;

The flow chart (part 2) of control program when Fig. 7 shows engine stop; And

The timing chart of the example of the mode of control program when Fig. 8 A, Fig. 8 B, Fig. 8 C, Fig. 8 D and Fig. 8 E are the execution engine stops according to the second exemplary embodiment.

Embodiment

Hereinafter, be described in detail to the port timing arrangement for controlling timing of the first exemplary embodiment according to the present invention.

Fig. 1 is the view of the configuration of the structure of variable valve timing timing mechanism relevant to the port timing arrangement for controlling timing of the first exemplary embodiment and the oil hydraulic circuit of control gear.As shown in Figure 1, variable valve timing timing mechanism 10 has the housing 12 of roughly ring-type and the blade body 14 be contained in housing 12.Blade body 14 is connected to the camshaft 16 of the suction valve (not shown) driving internal-combustion engine in the mode making blade body 14 and rotate together with camshaft 16.And housing 12 is connected to the cam pulley 18 with the bent axle (not shown) synchronous rotary of internal-combustion engine in the mode making housing 12 and rotate together with cam pulley 18.Fig. 1 convexity wheel shaft 16 turns clockwise.

Be arranged on the periphery of blade body 14 at the upper multiple blades 20 extended of radial direction (direction such as, intersected with the spin axis of blade body 14).And the multiple grooves 22 extended in the circumference of housing 12 are formed in the inner circumferential of housing 12.The each of blade 20 is arranged in a corresponding groove 22.Side pressure room 24 and delay side pressure room 26 are divided by the blade 20 of groove 22 inside and are formed in advance.In FIG, show two blades 20 and two grooves 22, but its number suitably can change.

Side pressure room 24 and delay side pressure room 26 are all connected to hydraulic control valve 28 separately via suitable fluid passage in advance.The working oil carried from the engine-driving oil pump 30 being connected to bent axle with driving is supplied to this hydraulic control valve 28.Hydraulic control valve 28 can be used as according to the valve of the amount executing alive dutycycle to regulate the working oil being fed to side pressure room 24 or delay side pressure room 26 in advance.Hydraulic control valve 28 is based on the dutycycle of the drive singal inputted from electronic control module (ECU) 32 and start, and working oil is fed to and shifts to an earlier date side pressure room 24 or postpone in side pressure room 26, or from working oil is discharged in side pressure room 24 or delay side pressure room 26 in advance.And the relative rotation phase of the blade 20 in groove 22 is according to the side pressure room 24 in advance formed on the both sides of blade 20 and postpone the differing from of pressure (such as, hydraulic pressure) of the working oil in side pressure room 26 and be set to predetermined phase place.Consequently, blade body 14 rotates relative to housing 12, and therefore the relative rotation phase of camshaft 16 changes relative to cam pulley 18, and the opening and closing timing (that is, port timing timing) of suction valve is changed.

Adjustment that drive singal dutycycle (comprises 0% and 100%) in the scope of 0% to 100%.Regulate the hydraulic pressure of each pressure chamber in pressure chamber 24 and pressure chamber 26 make relative rotation phase dutycycle close to 100% time change to side in advance more rapidly.And, regulate the hydraulic pressure of each pressure chamber in pressure chamber 24 and pressure chamber 26 make relative rotation phase dutycycle close to 0% time change to more rapidly and postpone side.

The execution of this port timing timing control is discussed in more detail below.Represent the parameter of engine operating state, the rotatable phase of the camshaft 16 such as detected by cam angle sensor and engine speed NE and the rotatable phase of bent axle detected by crankshaft angle sensor, be imported into electronic control module 32.

Electronic control module 32 calculates suitable port timing timing according to the engine operating state based on these parameters, and calculates the target phase of the relative rotation phase of camshaft 16 according to calculated suitable port timing timing.Electronic control module 32 also can calculate the current relative rotation phase of camshaft 16 according to the relation between the rotatable phase of bent axle and the rotatable phase of camshaft 16.

Then, if target phase is different from current phase place, then electronic control module 32 hydraulic control control valve 28 operation thus discharge working oil from advance side pressure room 24 or the pressure chamber postponed in side pressure room 26, and working oil is fed to another pressure chamber.More specifically, when current relative rotation phase is the phase place of delay side of target phase, the operation of electronic control module 32 hydraulic control control valve 28 thus supply working oil to side pressure room 24 in advance and self-dalay side pressure room 26 discharge working oil and make relative rotation phase change to and shift to an earlier date side.In the first exemplary embodiment, this hydraulic regulation pattern serves the effect of the second pattern relative rotation phase being changed to the side away from limit phase place.On the other hand, if when current relative rotation phase is the phase place of in advance side of target phase, the operation of electronic control module 32 hydraulic control control valve 28 thus discharge working oil from side pressure room 24 in advance and working oil is fed to and postpone side pressure room 26 and make relative rotation phase change to and postpone side.In the first exemplary embodiment, this hydraulic regulation pattern serves and changes to relative rotation phase towards the effect of the first mode of the side of limit phase place.Difference between the side pressure room 24 in advance produced according to the operation due to hydraulic control control valve 28 by this way and the hydraulic pressure postponing in side pressure room 26, to be rotated relative to housing 12 by blade body 14 and regulates port timing timing.

When owing to regulating the hydraulic pressure in pressure chamber 24 and pressure chamber 26 to make current relative rotation phase coupling target phase by this way, the operation of electronic control module 32 hydraulic control control valve 28 thus stop supply working oil to side pressure room 24 in advance and postpone side pressure room 26 and from working oil is discharged in side pressure room 24 and delay side pressure room 26 in advance.Consequently, side pressure room 24 and the pressure postponed in side pressure room 26 keep substantially equal in advance, therefore maintain the relative rotation phase of blade body 14.

Use this variable valve timing timing mechanism 10, blade body 14 can rotate relative to housing 12 in a scope (excursion), this scope be from blade 20 near the phase place of a sidewall surfaces of groove 22 to the phase place of blade 20 near the opposing sidewalls of groove 22.Hereinafter, when blade body 14, relatively the most delay side that rotated to of housing 12 is (namely, rear side in the sense of rotation of camshaft 16), i.e. during the control limit phase place of the delay side of excursion, the relative rotation phase of camshaft 16 will be called maximum delay phase place.When the operation of hydraulic control valve 28 is no longer controlled by electronic control module 32, this phase place is set to initial phase, namely, as phase place during engine stop.In contrast, when blade body 14, the most in advance side that rotates to of housing 12 is (namely relatively, front side in the sense of rotation of camshaft 16), i.e. during the control limit phase place of the in advance side of excursion, the relative rotation phase of camshaft 16 will be called maximum advanced phase.

By this way, use the port timing arrangement for controlling timing according to the first exemplary embodiment, by the hydraulic pressure that the operation of hydraulic control control valve 28 adjusts in advance side pressure room 24 and postpones in side pressure room 26, the relative rotation phase of camshaft 16 is suitably changing in the scope of maximum advanced phase from maximum delay phase place.Can be changed by the relative rotation phase changing camshaft 16 and be driven the port timing timing of the suction valve opened and closed by the rotation of camshaft 16.

And the variable valve timing timing mechanism 10 according to the first exemplary embodiment is provided with locking framework 34, when hydraulic pressure is low, such as, when ato unit, the relative rotation of locking framework 34 limit blade main body 14.To be described this locking framework 34 now.

The rank shape receiving hole 36 extended in parallel with the axial direction of camshaft 16 is formed in a blade of blade 20.Stop pin 38 telescopically is arranged in receiving hole 36.

As shown in the sectional view of Fig. 2 and Fig. 3, stop pin 38 moves between the position shown in the position shown in Fig. 2 and Fig. 3 on the axial direction of camshaft 16, and the outer surface of stop pin 38 slides in receiving hole 36 inner peripheral surface.And, promote stop pin 38 by disc spring 40 towards housing 12.Shape portion, the rank 38a with wide diameter is formed on the end of this stop pin 38, and the lock release pressure chamber 42 in space is formed between shape portion, the rank 36a of rank shape portion 38a and receiving hole 36 in the form of a ring.This lock release pressure chamber 42 is connected to via the delay side liquid passage 44 be formed in blade 20 and postpones side pressure room 26, makes the hydraulic pressure postponed in side pressure room 26 can be passed to lock release pressure chamber 42.

Meanwhile, locking aperture 48 is concave shaped portion, and it is formed in housing 12, and when the relative rotation phase (that is, the relative rotation phase of blade body 14) of camshaft 16 is for maximum delay phase place, stop pin 38 can be inserted in described concave shaped portion.As shown in Figure 2, blade body 14 is mechanically connected to housing 12, and is therefore inserted in locking aperture 48 by the Driving force by means of disc spring 40 by the terminal part of stop pin 38, and the relative rotation of blade body 14 is limited (that is, locked).

The space formed by the terminal part of locking aperture 48 and stop pin 38 is used as lock release pressure chamber 50.This lock release pressure chamber 50 is connected to side pressure room 24 in advance via the side liquid passage 46 be in advance formed in the slidingsurface of blade 20 and housing 12, makes the pressure shifted to an earlier date in side pressure room 24 can be passed to lock release pressure chamber 50.

Lock release pressure chamber 42 acts on the direction that pressure is making stop pin 38 be separated from locking aperture 48 of the working oil in lock release pressure chamber 50.Therefore, when the internal combustion engine is stopped, the relative rotation phase of blade body 14 arrives maximum delay phase place.And in a state in which, when side pressure room 24 and the pressure postponed in side pressure room 26 reduce to make the pressure in lock release pressure chamber 42 and lock release pressure chamber 50 reduce fully in advance, stop pin 38 is moved by the Driving force of disc spring 40.Consequently, the terminal part of stop pin 38 inserts locking aperture 48, as shown in Figure 2, the relative rotation of blade body 14 is locked.

The device of the first exemplary embodiment is provided with operating switch 52, battery 54 and relay 56.When internal combustion engine start with when stopping, operating switch 52 is operated.Battery 54 is for supplying power to various electric component, and relay 56 to be fed to from battery 54 between the state of hydraulic control valve 28 and electronic control module 32 and the state stopping supplying electric power at electric power based on the command signal of electronic control module 32 and to switch.

In the first exemplary embodiment, when internal-combustion engine stops in response to the operation turning off operating switch 52, relay 56 to keep the electric power being fed to hydraulic control valve 28 and electronic control module 32 in predetermined time section, and is continued through the control that electronic control module 32 operates hydraulic control valve 28 by start.And in the process stopping internal-combustion engine, the operation of hydraulic control valve 28 is that the in check relative rotation phase of camshaft 16 that makes arrives maximum delay phase place substantially.Consequently, by locking framework 34, the relative rotation phase of camshaft 16 is locked in maximum delay phase place.

On the other hand, when internal-combustion engine starts in response to the operation of connecting operating switch 52, side pressure room 24 and the pressure increase in one or two pressure chamber postponed in side pressure room 26 in advance.When the hydraulic pressure in the lock release pressure chamber 42 being connected to side pressure room 24 and delay side pressure room 26 in advance and lock release pressure chamber 50 increases fully, the side that stop pin 38 is making it be separated with locking aperture 48 moves upward, as shown in Figure 3, make relatively to rotate to be unlocked.

By this way, in the first exemplary embodiment, when the hydraulic pressure when an engine is stopped and and then after engine start in pressure chamber 24 and pressure chamber 26 is low, the maximum delay phase place place that is relatively rotated in of blade body 14 is locked.But once oil pump 30 can supply enough working oils, the relative rotation of blade body 14 is unlocked, make it possible to perform port timing timing control.

In the first exemplary embodiment, when electric power is not fed to hydraulic control valve 28 or when drive singal is not input to hydraulic control valve 28, the working state of hydraulic control valve 28 is working staties that oil pump 30 is communicated with delay side pressure room 26.Therefore, time when hydraulic control valve 28 is at engine start not by start, working oil is supplied from oil pump 30 towards delay side pressure room 26, and now, applies pilot pressure in the direction making stop pin 38 be separated from locking aperture 48.Then, working oil controls to be fed to side pressure room 24 thus reliably apply hydraulic pressure to lock release pressure chamber 42 and lock release pressure chamber 50 in advance by the operation of hydraulic control valve 28, reliably increases and the locking of locking framework 34 is reliably discharged to make pressure.

, be used in the port timing arrangement for controlling timing in the first exemplary embodiment herein, when the internal combustion engine is stopped, locking framework 34 is switched to lock state from released state (that is, relieving state).Preferably, there is the time (that is, switching time) that this switching spends short.Such as, reason is wherein as follows.

That is, even if the relative rotation phase of camshaft 16 is phase places of side in advance when turning off operating switch 52, locking framework 34 still can be switched to lock state, and therefore before turning off operating switch 52 (usually when empty), the scope of back to back controlled relative rotation phase is wider due to shorter switching time.Therefore can say, the degrees of freedom of the control structure of setting port timing timing control can increase within shorter switching time.Also make shorter switching time locking framework 34 after operating switch 52 is by operation, earlier can be switched to lock state, therefore also earlier can stop the power supply of hydraulic control valve 28 for this switching and electronic control module 32.

In the first exemplary embodiment, in order to shorten this switching time, the operation replacing hydraulic control control valve 28 is to make stopping the engine stopping operation of motor until the relative rotation phase of time period inner camshaft 16 that bent axle stops the rotation arrives maximum delay phase place simply after starting, to perform control below by turning off the operation of operating switch 52.That is, combination performs and changes over towards the first mode of the side of maximum delay phase place (particularly by the relative rotation phase of camshaft 16, the dutycycle of drive singal is the pattern of 0%) in hydraulic control valve 28 operation control, and the operation relative rotation phase of camshaft 16 being changed over the hydraulic control valve 28 in second pattern (particularly, the dutycycle of drive singal is the pattern of 100%) of the side away from maximum delay phase place controls.

Therefore, when internal-combustion engine stop and the operation of hydraulic control control valve 28 in a first pattern time, working oil is discharged from side pressure room 24 in advance, and the hydraulic pressure in side pressure room 24 is in advance reduced.On the other hand, when internal-combustion engine stop and the operation of hydraulic control control valve 28 in a second mode time, working oil is discharged from delay side pressure room 26, and the hydraulic pressure postponed in side pressure room 26 is reduced.

By this way, according to the first exemplary embodiment, by via controlling to regulate hydraulic pressure to the operation of hydraulic control valve 28 in a first mode and a second mode respectively, the pressure shifted to an earlier date in side pressure room 24 can be made to reduce respectively with the pressure postponed in side pressure room 26.Therefore, when the internal combustion engine is stopped, pressure in advance in side pressure room 24 (namely, in advance side unlocking pressure) and delay side pressure room 26 in pressure (namely, postpone side unlocking pressure) can reduce more rapidly, make locking framework 34 than implementing to be switched to lock state from released state more rapidly to the device that the operation of hydraulic control valve 28 controls in a first pattern simply.

Hereinafter, 4 control relevant program (that is, control program during engine stop) be described in detail to operating to described hydraulic control valve 28 this when an engine is stopped by reference to the accompanying drawings.From turn off operating switch 52 with after stopping internal-combustion engine until during the predetermined amount of time of section T1 after a predetermined time, program (that is, series of steps) shown in flow chart is performed by electronic control module 32 using the interrupt routine performed in predetermined period.In the first exemplary embodiment, during this engine stop, control program is an example of the program performed by actuating device.

As shown in Figure 4, in this procedure, first the dutycycle outputting to the drive singal of hydraulic control valve 28 is set to 0% (step S102) until the relative rotation phase of camshaft 16 arrives maximum delay phase place (that is, the "No" in step S101).That is, now, the operation performing the hydraulic control valve 28 of first mode controls to make working oil to discharge from advance side pressure room 24 and working oil is supplied to and postpones side pressure room 26.Herein, when the difference between actual relative rotation phase and maximum delay phase place is less than predetermined value, the relative rotation phase that can determine camshaft 16 has arrived maximum delay phase place.

Then this step is repeated until the relative rotation phase of camshaft 16 arrives maximum delay phase place.When the relative rotation phase of camshaft 16 arrives maximum delay phase place (that is, the "Yes" in step S101), the dutycycle outputting to the drive singal of hydraulic control valve 28 is set to 100% (step S103).That is, now, the operation performing the hydraulic control valve 28 of the second pattern controls to make working oil to be supplied in advance side pressure room 24 and working oil to discharge from delay side pressure room 26.

Then, the operation of the hydraulic control valve 28 when drive singal dutycycle is 100% controls to continue to be performed until the endurance that this operation controls reaches predetermined time section T2 (that is, the "No" in step S104).This predetermined amount of time T2 is such and obtain: obtain in advance and be enough to by the hydraulic pressure that postpones in side pressure room 26 (namely, postpone side unlocking pressure) be reduced to predetermined pressure P1 (namely, the pressure that locking framework 34 can be unlocked) under the amount of time, and this time to be stored in electronic control module 32.

Predetermined amount of time T2 is reached (namely when the endurance that drive singal dutycycle is the operation control of the hydraulic control valve 28 of 100%, "Yes" in step S104) time, stop supplying electric power to hydraulic control valve 28, make the operation of hydraulic control valve 28 stop (step S105).

Hereinafter, composition graphs 5A to Fig. 5 E is described the operation of control program during execution engine stop and effect.Fig. 5 A to Fig. 5 E is the example of the mode of control program when implementing engine stop.In Fig. 5 A to Fig. 5 E, Fig. 5 A shows the mode that electric power is fed to electronic control module 32, Fig. 5 B shows the change of engine speed NE, Fig. 5 C shows the change of the relative rotation phase of camshaft, Fig. 5 D shows the change of unlocking pressure, and Fig. 5 E shows the change of drive singal dutycycle.

As shown in Figure 5A, when turn off operating switch 52 in case time point t11 stop internal-combustion engine time, from now until after a predetermined time section T1 (that is, from time point t11 to time point t16) electric power continuous be fed to electronic control module 32.

And, because now internal-combustion engine operation control as stoppings such as fuel injection control and ignition timing controls, so engine speed NE (Fig. 5 B) after this reduction and along with this reduction, the supply pressure of oil pump 30 also reduces gradually.

In addition, at this moment, the dutycycle (Fig. 5 E) being input to the drive singal of hydraulic control valve 28 is set to 0%.Therefore, the hydraulic pressure postponed in side pressure room 26 increases, and along with this increase, hydraulic pressure in lock release pressure chamber 42 (namely, postpone side unlocking pressure (Fig. 5 D)) also increase, make the relative rotation phase (Fig. 5 C) of camshaft 16 towards maximum delay phase change.Also at this moment, the hydraulic pressure in advance in side pressure room 24 reduces, and along with this reduction, the hydraulic pressure (that is, shifting to an earlier date side unlocking pressure) in lock release pressure chamber 50 also reduces.By this way, in the first exemplary embodiment, when the internal combustion engine is stopped, first the relative rotation phase of camshaft 16 is towards maximum delay phase change, and along with this change, the hydraulic pressure in advance in side pressure room 24 reduces.

Then after a while at time point t12 place, side unlocking pressure drops to predetermined pressure P2 (more specifically, locking framework 34 can be switched to the pressure of lock state from released state) below in advance.In addition, after a while at time point t13 place, when the relative rotation phase of camshaft 16 arrives maximum delay phase place, the dutycycle being input to the drive singal of hydraulic control valve 28 is switched to 100%.Consequently, the hydraulic pressure postponed in side pressure room 26 reduces, and along with this reduction, the hydraulic pressure (that is, postponing side unlocking pressure) in lock release pressure chamber 42 also reduces.

Now, working oil is supplied to side pressure room 24 in advance, and therefore the relative rotation phase of camshaft 16 unnecessarily can change to side in advance.But, hydraulic pressure in advance in side pressure room 24 (namely, in advance side unlocking pressure) enough low due to the hydraulic regulation of the first mode of (time point t11 is to time point t13) before this, and engine speed NE is low, so the supply pressure of oil pump 30 is low.Therefore, the hydraulic pressure in advance in side pressure room 24 can not become so high, so now the relative rotation phase of camshaft 16 can not change to side in advance.

After a while at time point t14 place, postpone side unlocking pressure and drop to predetermined pressure P1 (more specifically, locking framework 34 can be switched to the hydraulic pressure of lock state from released state) below.That is, now, in advance side unlocking pressure drops to below predetermined pressure P2 and postpones side unlocking pressure and drops to below predetermined pressure P1, so stop pin 38 is inserted in locking aperture 48 by the Driving force of disc spring 40 (Fig. 2), locking framework 34 is locked.

As shown in Figure 5, after a while at time point t15 place, when in drive singal dutycycle be 100% hydraulic control valve 28 operation control endurance reach predetermined amount of time T2 time, stop the power supply to hydraulic control valve 28.

In addition, after a while at time point t16 place, when elapsed time amount reaches predetermined amount of time T1 after turning off operating switch 52, the power supply to electronic control module 32 is turned off.This predetermined amount of time T1 is such and obtain: the result based on test and simulation obtains control program when being enough to by performing engine stop in advance and locking framework 34 is switched to the amount of the time of lock state from released state, and is stored in electronic control module 32 this time.

By this way, control program when using engine stop according to the first exemplary embodiment, perform the hydraulic regulation of first mode until the relative rotation phase of camshaft 16 arrives maximum delay phase place, and when relative rotation phase arrives maximum delay phase place, perform the hydraulic regulation of the second pattern.Therefore, the hydraulic pressure in pressure chamber 24 and pressure chamber 26 can reduce aptly.That is, hydraulic pressure in advance in side pressure room 24 changes to maximum delay phase place along with the relative rotation phase of camshaft 16 and reduces, and after the relative rotation phase of camshaft 16 has arrived maximum delay phase place, the hydraulic pressure postponed in side pressure room 26 reduces and suppresses the change of relative rotation phase simultaneously.Therefore, when the internal combustion engine is stopped, shift to an earlier date side pressure room 24 and the hydraulic pressure postponed in side pressure room 26 and therefore shift to an earlier date side unlocking pressure and delay side unlocking pressure, both all can reduce fast, so locking framework 34 can switch to lock state from released state rapidly.

As mentioned above, according to the first exemplary embodiment, effect described below can be obtained.

(1) from shutoff operating switch 52 after until engine speed NE becomes the time period between 0, combination performs the relative rotation phase of camshaft 16 to change over and controls towards the operation of the hydraulic control valve 28 of the first mode of the side of maximum delay phase place, and the relative rotation phase of camshaft 16 is changed over the operation control of hydraulic control valve 28 of the second pattern of the side away from maximum delay phase place.Therefore, when the internal combustion engine is stopped, shift to an earlier date side pressure room 24 and the hydraulic pressure postponed in side pressure room 26 and therefore shift to an earlier date side unlocking pressure and delay side unlocking pressure, can reduce more rapidly, compared with the device using the operation simply performing the hydraulic control valve 28 of first mode to control, so locking framework 34 can switch to lock state from released state more rapidly.

(2) hydraulic regulation of side pressure room 24 and delay side pressure room 26 is in advance performed in a first pattern until the relative rotation phase of camshaft 16 arrives maximum delay phase place, and when the relative rotation phase of camshaft 16 arrives maximum delay phase place, perform the hydraulic regulation of side pressure room 24 and delay side pressure room 26 in advance in a second mode.Therefore, the hydraulic pressure in pressure chamber 24 and pressure chamber 26 can reduce aptly.That is, hydraulic pressure in advance in side pressure room 24 changes to maximum delay phase place with the relative rotation phase of camshaft 16 and reduces, and after the relative rotation phase of camshaft 16 has arrived maximum delay phase place, the hydraulic pressure postponed in side pressure room 26 reduces and suppresses the change of relative rotation phase simultaneously.

(3) after operating switch 52 is operated to stop internal-combustion engine, side pressure room 24 and the hydraulic pressure postponed in side pressure room 26 can reduce fast to complete the switching of locking framework 34 from released state to lock state fast in advance.

Next, be described to the port timing arrangement for controlling timing of the second exemplary embodiment according to the present invention.

According to variable valve timing timing mechanism and the structure being arranged on the locking framework in port timing arrangement for controlling timing of the second exemplary embodiment, and the structure of peripheral unit is identical with the structure shown in above-mentioned Fig. 1 to Fig. 3, so will the description of these structures be omitted.And, the process of control program when the port timing arrangement for controlling timing according to the second exemplary embodiment and the difference of port timing arrangement for controlling timing according to the first exemplary embodiment are only for performing engine stop.

Hereinafter, the flow chart in composition graphs 6 and Fig. 7 is described the process of control program when being used for performing the engine stop according to the second exemplary embodiment.Shutoff operating switch 52 with after stopping internal-combustion engine until within the time period of predetermined time section T3, program (that is, series of steps) shown in these flow charts performs using as the interrupt routine performed in predetermined period by electronic control module 32.In the second exemplary embodiment, during this engine stop, control program is an example of the program performed by actuating device.

As shown in Figure 6, in this procedure, when shutoff operating switch 52 is so that when stopping internal-combustion engine (such as, the "Yes" in step S201), first the dutycycle outputting to the drive singal of hydraulic control valve 28 is set to 100% (step S202).That is, when turning off operating switch 52, the operation first starting the hydraulic control valve 28 of second pattern that performs controls, and make working oil be supplied to side pressure room 24 in advance, and working oil is discharged from delay side pressure room 26.

Then, the operation of the hydraulic control valve 28 when dutycycle is 100% control the condition A that is described below and condition B (that is, step 203 to step 205 judging all as under the condition of "Yes" in steps) continue under the condition that all meets.Condition A has been set to the relative rotation phase of camshaft 16 after 100% in dutycycle not change to side (step S204) in advance.Condition B is less than predetermined time section T4 (such as a few tens of milliseconds) (step S205) endurance that dutycycle is set to 100%.

When change to due to the relative rotation phase of camshaft 16 when being set to 100% in dutycycle in advance side thus no longer meet above-mentioned condition A (that is, in step S204 being "No") time, dutycycle is switched to 0% (step S206).In this case, dutycycle is that the operation of the hydraulic control valve 28 of 0% controls to continue until the endurance that dutycycle is set to 0% reaches predetermined time section T5 (such as a few tens of milliseconds) (namely, it is "No" in step S201, be "No" in step S203, and be "No" in step S207).After this, repeat this step, and (that is, in step S207 be "Yes") when the endurance that dutycycle is set to 0% is equal to, or greater than predetermined amount of time T5, dutycycle turns back to 100% (step S208).

By this way, use this program, perform following process: when be set to due to drive singal dutycycle 100% and make the relative rotation phase of camshaft 16 change in advance side time, dutycycle is temporarily switched to 0% and keeps this state in predetermined amount of time T2, and dutycycle turns back to 100% after this.That is, in this case, the operation of the hydraulic control valve 28 of the second pattern controls to be process is-then temporarily-suspended, and the operation performing the hydraulic control valve 28 of first mode controls, and working oil is discharged and working oil is supplied to and postpones side pressure room 26 from side pressure room 24 in advance.

Then, even if when drive singal dutycycle be set as the relative rotation phase of 100% camshaft 16 will no longer change in advance side time (, it is "No" in step S201, it is "Yes" in step S203, and be "Yes" in step S204), judge whether the endurance that dutycycle is set to 100% has reached predetermined amount of time T4 (step S205).

If the endurance that dutycycle is set to 100% is less than predetermined amount of time T4 (being "Yes" in step S205), then the operation of the hydraulic control valve 28 when dutycycle is 100% controls to continue.Then, when the endurance being set 100% when dutycycle reaches predetermined amount of time T4 (that is, in step S205 being "No"), dutycycle is switched to 0% (step S206).Then, the operation of the hydraulic control valve 28 when dutycycle is 0% controls to continue, until the endurance that dutycycle is set to 0% reaches predetermined amount of time T5 (being "No" in step S207).(that is, in step S207 be "Yes") when the endurance that dutycycle is set to 0% is equal to, or greater than predetermined amount of time T5, dutycycle turns back to 100% (step S208).

By this way, use this program, even if when the relative rotation phase that drive singal dutycycle is set to 100% camshaft 16 will no longer change in advance side time, alternately and to repeat dutycycle in operation control and predetermined amount of time T5 that dutycycle in predetermined amount of time T4 is the hydraulic control valve 28 of 100% be that the operation of the hydraulic control valve 28 of 0% controls.

Then, as shown in Figure 7, this operation of hydraulic control valve 28 controls to continue until turn off operating switch 52 elapsed time to reach predetermined time section T6 (that is, the "No" in step S209).This predetermined amount of time T6 obtains like this: based on to detect or the result of simulation obtains in advance and is enough to be used in making hydraulic pressure in side pressure room 24 in advance (namely, in advance side unlocking pressure) drop to below predetermined pressure P2 and postpone hydraulic pressure in side pressure room 26 (namely, postpone side unlocking pressure) drop to the amount of the time of below predetermined pressure P1, and this time is stored in electronic control module 32.

Then, when when turning off elapsed time after operating switch 52 and reaching predetermined amount of time T3 (, "Yes" in step S209), stop making hydraulic control valve 28 quit work (step S210) to the power supply of hydraulic control valve 28.This predetermined amount of time T3 obtains like this: the control program when result based on test or simulation obtains the engine stop be enough to by implementing according to the second exemplary embodiment in advance and locking framework 34 is switched to the amount of the time of lock state from released state, and is stored in electronic control module 32 this time.

Hereinafter, composition graphs 8A to Fig. 8 E is described to enforcement according to the operation of control program during the second exemplary embodiment engine stop and effect.Fig. 8 A to Fig. 8 E is the example of the mode of control program when performing engine stop.In Fig. 8 A to Fig. 8 E, Fig. 8 A shows power supply to the mode of electronic control module 32, Fig. 8 B shows the change of engine speed NE, Fig. 8 C shows the change of the relative rotation phase of camshaft, Fig. 8 D shows the change of unlocking pressure, and Fig. 8 E shows the change of drive singal dutycycle.

As shown in Figure 8 A, when turn off operating switch 52 in case time point t21 stop internal-combustion engine time, from that time until after a predetermined time section T3 (that is, from time point t21 to time point t38) electric power continuous be fed to electronic control module 32.

And stop at time point t21 because the operation of internal-combustion engine controls such as fuel injection control and ignition timing control etc., after this engine speed NE (Fig. 8 B) reduces, and along with this reduction, the supply pressure of oil pump 30 also reduces gradually.

In addition, at time point t21 place, the dutycycle (Fig. 8 E) being input to the drive singal of hydraulic control valve 28 is set to 100%.Therefore, the hydraulic pressure after this postponed in side pressure room 26 reduces, and along with this reduction, the hydraulic pressure (that is, postponing side unlocking pressure (Fig. 8 D)) in lock release pressure chamber 42 also reduces.By this way, in the second exemplary embodiment, when the internal combustion engine is stopped, the hydraulic pressure first postponing side pressure room 26 reduces, and therefore postpones side unlocking pressure reduction.

And at time point t21 place, the working state of hydraulic control valve 28 is supplied to side pressure room 24 in advance for making working oil, and therefore the relative rotation phase (Fig. 8 C) of camshaft 16 can change to side in advance.In this example, the relative rotation phase of camshaft 16 has in fact changed to side (time point t21 is to time point t22) in advance.

Therefore, at time point t22 place, drive singal dutycycle temporarily switches to 0% and keeps predetermined amount of time T5 (time point t22 to t23) at 0% place.Then, when the operation that drive singal dutycycle is the hydraulic control valve 28 of 0% controls to continue for predetermined amount of time T5, dutycycle turns back to 100% (time point t23).Therefore, the hydraulic pressure (that is, postponing side unlocking pressure) in delay side pressure room 26 is so can again reduce.

At time point t23 place, the operation being the hydraulic control valve 28 of 0% due to dutycycle in back to back predetermined amount of time T5 before controls, and the hydraulic pressure in side pressure room 24 is in advance reduced, and the supply pressure of oil pump 30 follows the reduction of engine speed NE also to reduce.Therefore, when the operation of the hydraulic control valve 28 now starting first mode controls, the relative rotation phase of camshaft 16 no longer will change to side in advance.Therefore, when now to start dutycycle be the operation of the hydraulic control valve 28 of 100% control time, it is by predetermined hold-time section T4 (time point t23 is to time point t24).

By this way, use this program, from by turn off operating switch 52 with the shut-down operation making described internal-combustion engine and stops time until in described bent axle time period of stopping the rotation, the operation that combination performs the hydraulic control valve 28 of first mode controls and the operation control of hydraulic control valve 28 of the second pattern.Therefore, when the internal combustion engine is stopped, pressure in advance in side pressure room 24 (namely, in advance side unlocking pressure) and delay side pressure room 26 in pressure (namely, postpone side unlocking pressure) can reduce more rapidly, make compared with the device using the operation of the hydraulic control valve 28 performing first mode simply to control, locking framework 34 switches to lock state from released state more rapidly.

More specifically, use this program, when the relative rotation phase of camshaft 16 can not change in advance side time, the operation performing the hydraulic control valve 28 of the second pattern controls, and the hydraulic pressure postponed in side pressure room 26 is reduced.And, if when perform the operation control of hydraulic control valve 28 of the second pattern and the relative rotation phase of camshaft 16 will change in advance side time, the operation performing the hydraulic control valve 28 of first mode controls, and makes the hydraulic pressure reduction in side pressure room 24 in advance.Consequently, the hydraulic pressure in advance in side pressure room 24 and the hydraulic pressure that postpones in side pressure room 26 are all by reduction.

At time point t24 place, the relative rotation phase that the operation of the hydraulic control valve 28 when dutycycle is 100% controls predetermined hold-time section T4 and camshaft 16 do not change in advance side time, then the operation performing hydraulic control valve 28 in such a way controls.That is, alternately and repeatedly implement at predetermined amount of time T5 (namely, time point t24 is to time point t26, time point t28 to time point t29 ..., and time point t34 is to time point t35) interior dutycycle be the hydraulic control valve 28 of 0% operation control and at predetermined amount of time T4 (namely, time point t26 is to time point t28, time point t29 to time point t30 ..., and time point t35 is to time point t36) interior dutycycle be the hydraulic control valve 28 of 100% operation control.Then, time point t25 place in the process that this operation performing hydraulic control valve 28 controls, hydraulic pressure in advance in side pressure room 24 (namely, side unlocking pressure in advance) will below predetermined pressure P2 be dropped to, and at time point t27 place, the hydraulic pressure (that is, postponing side unlocking pressure) postponed in side pressure room 26 will drop to below predetermined pressure P1.

Herein, even if the operation due to the hydraulic control valve 28 of first mode controls make the hydraulic pressure of side pressure room 24 in advance enough low and the relative rotation phase of camshaft 16 can not be changed to side in advance, also can not be enough low to make locking framework 34 be switched to lock state.In this case, if the operation only continuing the hydraulic control valve 28 of execution second pattern controls, working oil will be fed to side pressure room 24 in advance, the hydraulic pressure that when therefore may spend more, chien shih shifts to an earlier date in side pressure room 24 reduces fully, and when therefore may spend more, chien shih locking framework 34 switches to lock state from released state.

About this point, in the second exemplary embodiment, the relative rotation phase of camshaft 16 can not be changed to shifting to an earlier date hydraulic pressure in side pressure room 24 enough low after shifting to an earlier date side, the operation alternately performing the operation control of the hydraulic control valve 28 of first mode and the hydraulic control valve 28 of the second pattern controls.Consequently, the hydraulic pressure shifted to an earlier date in side pressure room 24 all can reduce fully with the hydraulic pressure postponed in side pressure room 26.

Then, at time point t37 place, when after turning off operating switch 52, elapsed time section reaches predetermined amount of time T6, electric power stops being fed to hydraulic control valve 28.In addition, after a while at time point t38 place, when after turning off operating switch 52, elapsed time section reaches predetermined amount of time T3, electric power stops being fed to electronic control module 32.

As mentioned above, according to the second exemplary embodiment, the effect described in (4) and (5) below can also be obtained except the effect that above-mentioned (1) and (3) describe.

(4) operation being the hydraulic control valve 28 starting to perform the second pattern as the result turning off operating switch 52 controls.And, when the relative rotation phase of camshaft 16 change in advance side time, the operation of the hydraulic control valve 28 of the second pattern controls to supspend and the operation implementing the hydraulic control valve 28 of first mode controls.Therefore, when the relative rotation phase of camshaft 16 will not change in advance side time, the operation implementing the hydraulic control valve 28 of the second pattern controls the hydraulic pressure postponed in side pressure room 26 can be reduced.In addition, if when the operation of the hydraulic control valve 28 of second pattern of enforcement controls, when the relative rotation phase of camshaft 16 will change to and shift to an earlier date side, the operation performing the hydraulic control valve 28 of first mode will control, and the hydraulic pressure of side pressure room 24 in advance can be reduced.Consequently, the hydraulic pressure shifted to an earlier date in side pressure room 24 all can reduce with the hydraulic pressure postponed in side pressure room 26.

(5) after this, controlled by the operation of the hydraulic control valve 28 of first mode, hydraulic pressure in advance in side pressure room 24 becomes enough low and the relative rotation phase of camshaft 16 can not be changed to side in advance, and the operation alternately performing the operation control of the hydraulic control valve 28 of first mode and the hydraulic control valve 28 of the second pattern controls.Consequently, the hydraulic pressure shifted to an earlier date in side pressure room 24 all can reduce fully with the hydraulic pressure postponed in side pressure room 26.

(other exemplary embodiment)

Above-mentioned exemplary embodiment also can be modified as follows.In the first above-mentioned exemplary embodiment, from when turning off operating switch 52 until the relative rotation phase of camshaft 16 arrived in the time period of maximum delay phase place, the dutycycle being input to the drive singal of hydraulic control valve 28 is set to 0%.But alternatively, in this time period, target phase can be set to maximum delay phase place.Use this structure simultaneously, in this time period, can perform to be in the operation of the relative rotation phase of camshaft 16 towards the hydraulic control valve 28 of the pattern of the side of maximum delay phase change is controlled.

In the first exemplary embodiment, can set and arrive the timing after the timing of maximum delay phase place at the relative rotation phase of camshaft 16 a little, such as, the timing etc. of the relative rotation phase that can set camshaft 16 section after a predetermined time after having arrived maximum delay phase place, is switched to the timing of 100% as drive singal dutycycle after turning off operating switch 52.And, as long as by making the relative rotation phase of camshaft 16 reliably change to maximum delay phase place from the pressure of suction valve etc., the relative rotation phase of camshaft 16 arrives the timing before maximum delay phase place, such as, the relative rotation phase of camshaft 16 has arrived slightly close to timing etc. of the phase place of side in advance of maximum delay phase place, can be set to this timing.

In the first exemplary embodiment, be switched to after 100% in drive singal dutycycle, alternately and repeatedly to perform operation control that predetermined amount of time (< T2) interior dutycycle is the hydraulic control valve 28 of 100% and predetermined amount of time (< T2) interior dutycycle be that the operation of the hydraulic control valve 28 of 0% controls, instead of in predetermined amount of time T2, keep drive singal dutycycle to be 100%.

In the second exemplary embodiment, as long as the hydraulic pressure shifted to an earlier date in side pressure room 24 can suitably reduce, the step S205 in Fig. 6 can be omitted.Use this structure, can following steps be omitted: though when perform dutycycle be the operation of the hydraulic control valve 28 of 100% control the relative rotation phase of camshaft 16 also will no longer change in advance side time, alternately and repeatedly to perform dutycycle in operation control and predetermined amount of time T5 that dutycycle in predetermined amount of time T4 is the hydraulic control valve 28 of 100% be that the operation of the hydraulic control valve 28 of 0% controls.In this case, can continue to perform the operation control that dutycycle is the hydraulic control valve 28 of 100%.

In the foregoing example embodiment, from when turn off operating switch 52 time until engine speed NE become 0 time period in, drive singal dutycycle can be set smaller than the percentage of 100% and drive singal dutycycle be set as 100%.That is, working oil is fed to side pressure room 24 in advance and working oil thus the operation postponing the hydraulic control valve 28 of the pattern that side pressure room 26 is discharged control as long as can perform, drive singal dutycycle can be set as lower than 100%.

In the foregoing example embodiment, from when turn off operating switch 52 time until engine speed NE become 0 time period in, drive singal dutycycle can be set greater than the percentage of 0%, and drive singal dutycycle be set as 0%.That is, to be discharged from advance side pressure room 24 by working oil and the operation that working oil is fed to the hydraulic control valve 28 of the pattern postponing side pressure room 26 controls as long as can perform, drive singal dutycycle can be set as higher than 0%.

In the foregoing example embodiment, predetermined amount of time (that is, T1 and T2 in the first exemplary embodiment, and the T3 to T6 in the second exemplary embodiment) also can set according to the desired value of work oil viscosity or viscosity changeably.The temperature of working oil or the temperature of engine coolant etc. can use as the desired value of work oil viscosity.Herein, if make the viscosity-modifying of working oil due to change in time or temperature variation etc., then result is that the reduction speed of hydraulic pressure in advance in side pressure room 24 and the reduction speed of hydraulic pressure that postpones in side pressure room 26 also will change.About this point, according to above-mentioned structure, control program when can perform engine stop according to the change of reduction speed of this change along with work oil viscosity, makes locking framework 34 suitably can switch to lock state from released state.

The present invention also can be applied to the port timing arrangement for controlling timing being provided with locking framework, camshaft is locked in the limit phase place (that is, maximum advanced phase) of the side in advance of the excursion of relative rotation phase by this locking framework relative to the relative rotation phase of bent axle.In the structure shown here, working oil to be discharged and the shaping modes that working oil is fed in advance side pressure room can be first mode from postponing side pressure room, and working oil is fed to and postpones side pressure room and working oil can be the second pattern from the shaping modes that side pressure room is discharged in advance.

The present invention is not limited to the port timing arrangement for controlling timing of the port timing timing changing suction valve, and is applicable to the port timing arrangement for controlling timing of the port timing timing changing outlet valve.

Claims

1. for a port timing arrangement for controlling timing for internal-combustion engine, comprising: variable valve timing timing mechanism, camshaft is changed over target phase relative to the relative rotation phase of bent axle based on being supplied to the hydraulic pressure of side pressure room and delay side pressure room in advance by it; And locking framework, when described hydraulic pressure is low, described locking framework is placed in the described relative rotation phase lock state locked at the limit phase place place of the excursion of described relative rotation phase, and when described hydraulic pressure uprises, described locking framework is placed in described lock state by the released state removed, and it is characterized in that described port timing arrangement for controlling timing also comprises:

Actuating device, it is configured to: from the shut-down operation making described internal-combustion engine stop time until during described bent axle time period of stopping the rotation, the combination of described actuating device performs and changes to described relative rotation phase towards the adjustment of the described hydraulic pressure of the first mode of the side of described limit phase place, and described relative rotation phase is changed to the adjustment of described hydraulic pressure of the second pattern of the side away from described limit phase place.

2. port timing arrangement for controlling timing according to claim 1, it is characterized in that, described actuating device performs the hydraulic regulation of described first mode until described relative rotation phase arrives described limit phase place, and when described relative rotation phase arrives described limit phase place, described actuating device performs the hydraulic regulation of described second pattern.

3. port timing arrangement for controlling timing according to claim 1, it is characterized in that, described actuating device starts the hydraulic regulation performing described second pattern after described shut-down operation starts, and when described relative rotation phase changes to the phase place away from the side of described limit phase place, described actuating device is supspended the described hydraulic regulation of described second pattern and is performed the hydraulic regulation of described first mode.

4. port timing arrangement for controlling timing according to claim 3, it is characterized in that, when when performing the described hydraulic regulation of described second pattern, described relative rotation phase does not change to the state continuance predetermined time section of the phase place of the side away from described limit phase place, then described actuating device stops the described hydraulic regulation of described second pattern and performs the described hydraulic regulation of described first mode in predetermined time section.

5. port timing arrangement for controlling timing according to any one of claim 1 to 4, it is characterized in that, described limit phase place is the limit phase place on the delay side of described relative rotation phase, to be working oil from described side pressure room in advance discharge described first mode and working oil is supplied to the shaping modes of described delay side pressure room, and described second pattern is working oil is supplied to described side pressure room in advance and the working oil shaping modes of discharging from described delay side pressure room.

6. port timing arrangement for controlling timing according to any one of claim 1 to 4, characterized by further comprising: hydraulic control valve, it regulates the amount being fed to the described working oil of side pressure room or described delay side pressure room in advance according to the dutycycle of drive singal of input, wherein said first mode by described dutycycle is set as 0% and realization and described second pattern by described dutycycle being set as 100% and realize.

7. port timing arrangement for controlling timing according to any one of claim 1 to 4, is characterized in that, described shut-down operation is in response to operating switch and is operated to stop the shut-down operation of the running of described internal-combustion engine.

8. the controlling method for the port timing arrangement for controlling timing of internal-combustion engine, described port timing arrangement for controlling timing comprises: variable valve timing timing mechanism, and camshaft is changed over target phase relative to the relative rotation phase of bent axle based on being supplied to the hydraulic pressure of side pressure room and delay side pressure room in advance by it; And locking framework, when described hydraulic pressure is low, described locking framework is placed in the described relative rotation phase lock state locked at the limit phase place place of the excursion of described relative rotation phase, and when described hydraulic pressure uprises, described locking framework is placed in described lock state by the released state removed, and it is characterized in that:

From the shut-down operation making described internal-combustion engine stop time until during described bent axle time period of stopping the rotation, combination performs and to be changed to by described relative rotation phase towards the adjustment of the described hydraulic pressure of the first mode of the side of described limit phase place and the adjustment of described hydraulic pressure of the second pattern described relative rotation phase being changed to the side away from described limit phase place.