CN103511016A

CN103511016A - Variably operated valve system for internal combustion engine

Info

Publication number: CN103511016A
Application number: CN201310061000.8A
Authority: CN
Inventors: 中村信
Original assignee: Hitachi Automotive Systems Ltd
Current assignee: Hitachi Astemo Ltd
Priority date: 2012-06-22
Filing date: 2013-02-27
Publication date: 2014-01-15
Also published as: DE102013010507A1; JP2014005756A; US20130340694A1

Abstract

The invention provides a variably operated valve system which inhibits the valve stop control as the lost motion quantity (stroke quantity) of a valve stop mechanism exceeds a predetermined value during the single valve stop process and which can inhibits disconnection of a swing arm relative to a pivot. With the driven rotation of a cam (53), a swing cam (7) is enabled to swing through a transmission mechanism, therefore a pair of swing arms (6) is used to enable each valve (3, 3) to do opening and closing motions. The valve stop mechanism is provided to enable a first hydraulic lash adjuster (10a) which acts as a swing fulcrum by abutting aganist the other end part (6b) of one swing arm to do lost motion movements baed on the internal combustion engine operational state so as to stop one valve. When the lost motion quantity of the valve stop mechanism exceeds a predetermined value, the valve of a control unit (53) is used to stop a forbidden loop control electromagnetic changeover valve (55), so that a limit pin (41) is used to inhibit stop of the valves.

Description

The variable valve gear of internal-combustion engine

Technical field

The present invention relates to a kind of can be according to the variable control of the enforcements such as valve lift amount of internal combustion engine operation state combustion motor valve and can carry out the variable valve gear of the internal-combustion engine that valve stops.

Background technique

As the variable valve gear of existing internal-combustion engine, the known device that has following patent documentation 1 to record.

The valve shut-down mechanism that this variable valve gear possesses the lift amount of the intake valve that makes two, every cylinder and changeable mechanism that operating angle changes continuously and the on-off action of a side intake valve is stopped, in conventional operation range, make side's idle running and the action of a side intake valve is stopped, only make the opposing party's intake valve running, thus, strengthening intake swirl, improve combustion efficiency and combustion performance, on the other hand, in requiring the operation range of engine torque, utilize two valves to turn round, and the roughly the same air inlet charging efficiency that improves of the operating angle that makes two valves.

And, the in the situation that of requiring engine torque to increase, if this requires engine torque less than the peak torque under single valve running, maintain single valve operating condition in single valve operating condition, increase operating angle (lift amount) simultaneously.

Patent documentation 1:(Japan) JP 2010-007636 communique (Fig. 8)

But, in described existing variable valve gear, as previously mentioned, if require engine torque less than the peak torque under single valve running in single valve operating condition, maintain single valve operating condition, therefore, the valve mechanism that valve stops a side expanding at operating angle, when namely lift amount increases, be forced to produce large idle running amount.

Therefore, the attitude that described valve stops the valve mechanism of side becomes unreasonable, an end that makes intake valve carry out the swing arm of on-off action becomes inhomogeneous or local between the pivot of swing fulcrum of this swing arm and contacts with becoming, make to misplace between the two, according to circumstances, an end of swing arm may come off from pivot.

Summary of the invention

The present invention researches and develops in view of the described technical problem of existing variable valve gear, its objective is in the situation that the idle running amount (path increment) of the valve shut-down mechanism in single valve stopped process surpasses specified value, forbid that valve stops controlling, suppress swing arm with respect to the dislocation of pivot and the irregular action such as come off.

The variable valve gear that the invention provides a kind of internal-combustion engine, is characterized in that, possesses: live axle, and from the bent axle of internal-combustion engine to this live axle rotary driving force, this live axle is provided with driving cam in periphery; Two swing cams, it makes the elastic force of two engine valve opposing valve spring of every cylinder and carries out opening action; Transfer mechanism, it converts rotatablely moving of described driving cam oscillating motion to and is delivered to described swing cam; A pair of swing arm, it is arranged between described each swing cam and each engine valve, by the oscillatory forces of described swing cam and the elastic force of described valve spring, makes described each engine valve carry out on-off action; A pair of supporting point part, it becomes the swing fulcrum of this each swing arm; Control mechanism, it,, by the attitude of described transfer mechanism is changed, implements variable control to the lift amount of described each engine valve; In the variable valve gear of this internal-combustion engine, be provided with the valve shut-down mechanism by making at least one party's idle running of described a pair of supporting point part that the driven for opening and closing of the engine valve of one is stopped, and be provided with in the situation that the idle running amount of this valve shut-down mechanism forbids that over specified value the valve that valve stops stops forbidding member.

In addition, according to a further aspect in the invention, provide a kind of variable valve gear of internal-combustion engine, it is characterized in that, be provided with: driving cam, from bent axle transmission to this driving cam rotating force; Engine valve, it arranges two in every cylinder, and the elastic force by valve spring is by closing the valve direction application of force; Swing cam, it makes the elastic force of this each engine valve opposing valve spring and carries out opening action; Transfer mechanism, it converts rotatablely moving of described driving cam oscillating motion to and is delivered to described swing cam; Control mechanism, it,, by the attitude of described transfer mechanism is changed, implements variable control to the lift amount of described each engine valve; A pair of action component, its oscillating motion according to described swing cam swings, and makes described each engine valve carry out on-off action; Valve shut-down mechanism, its absorb one action component oscillating quantity and the on-off action of the engine valve of one is stopped; Valve stops forbidding member, and it forbids that described valve shut-down mechanism absorbs oscillating motion in the situation that the oscillating quantity of described action component surpasses established amount.

In addition, in accordance with a further aspect of the present invention, provide a kind of variable valve gear of internal-combustion engine, it is characterized in that possessing: driving cam, it is rotated by crank-driven; A pair of engine valve, its elastic force by valve spring is by the closing direction application of force; A pair of swing cam, it drives described a pair of engine valve by swinging via a pair of action component; Transfer mechanism, it converts rotatablely moving of described driving cam to oscillating motion and is delivered to described a pair of swing cam; Control mechanism, it changes the acting characteristic of described a pair of engine valve by the attitude of this transfer mechanism is changed; Valve shut-down mechanism, it is arranged at least one party of described a pair of action component, by dallying, make the driving of the engine valve of one stop, in the situation that the valve lift amount of the engine valve of one surpasses specified value, forbid the action that the caused valve of valve shut-down mechanism stops.

According to the present invention, in valve stopped process, in the situation that the idle running amount (path increment) of valve shut-down mechanism over specified value, can be forbidden valve halted state and be avoided coming off of valve mechanism etc.

Accompanying drawing explanation

Fig. 1 means the stereogram of the first mode of execution that valve gear of the present invention is applied to the single-row side of V-type six-cylinder engine;

Fig. 2 is the A-A line sectional view of Fig. 1;

Fig. 3 is the B-B line sectional view of Fig. 1;

(A) in Fig. 4 means the longitudinal section for the first hydraulic lash adjuster of present embodiment, (B) means the longitudinal section of the effect of this first hydraulic lash adjuster;

Fig. 5 is the longitudinal section of the second hydraulic lash adjuster of present embodiment;

Fig. 6 means the schematic diagram of the control oil hydraulic circuit of present embodiment;

(A) in Fig. 7 be the lift amount of the intake valve of present embodiment be controlled as in the situation of L2 close valve time the Action Specification figure of the first hydraulic lash adjuster, the Action Specification figure of the first hydraulic lash adjuster of this while (B) being out valve;

(A) in Fig. 8 be the lift amount of the intake valve of present embodiment be controlled as in the situation of L2 close valve time the Action Specification figure of the second hydraulic lash adjuster, the Action Specification figure of the second hydraulic lash adjuster of this while (B) being out valve;

Fig. 9 is the Action Specification figure that state that the lift amount from the intake valve of present embodiment is controlled as L3 starts to carry out the first hydraulic lash adjuster situation that valve stops controlling;

(A) in Figure 10 be the intake valve of present embodiment be controlled as in the situation of maximum lift (L7) close valve time the Action Specification figure of the first hydraulic lash adjuster, the Action Specification figure of the first hydraulic lash adjuster of this while (B) being out valve;

(A) in Figure 11 be the intake valve of present embodiment be controlled as in the situation of maximum lift (L7) close valve time the Action Specification figure of the second hydraulic lash adjuster, the Action Specification figure of the second hydraulic lash adjuster of this while (B) being out valve;

Figure 12 is the valve lift properties figure of the intake valve of present embodiment;

Figure 13 means the performance plot of the idle running amount of the first hydraulic lash adjuster of present embodiment and the relation of the angle of swing of Control Shaft;

Figure 14 means the performance plot of the lift amount of intake valve of present embodiment and the relation of the angle of swing of Control Shaft;

Figure 15 is the control flow chart for the control unit of present embodiment;

Figure 16 means the schematic diagram of the control oil hydraulic circuit of the second mode of execution;

Figure 17 means the longitudinal section of the first hydraulic lash adjuster of the 3rd mode of execution;

Figure 18 means the longitudinal section of the first hydraulic lash adjuster of the 4th mode of execution.

Description of reference numerals

1 ... cylinder head

1a ... retaining hole

3 ... intake valve (engine valve)

5 ... camshaft

5a ... driving cam

6 ... swing arm

6a ... one end

6b ... the other end

7 ... swing cam

8 ... transfer mechanism

9 ... control mechanism

10a ... the first hydraulic lash adjuster (supporting point part)

10b ... the second hydraulic lash adjuster (supporting point part)

11 ... valve shut-down mechanism

12 ... valve spring

13 ... bearing portion

14 ... roller

24 ... main body

27 ... plunger

27b ... front end head

34 ... hole is used in slip

35 ... lost motion springs

36 ... limting mechanism

38 ... the mobile hole of using

39 ... hole is used in restriction

40 ... holder

41 ... banking pin

42 ... Returnning spring

43 ... oil via hole

44 ... drain boles

54 ... oil pump

55 ... electromagnetic switching valve

Embodiment

The mode of execution of the valve gear of internal-combustion engine of the present invention is described based on accompanying drawing below.It should be noted that, in the present embodiment, expressed be applied to V-type six-cylinder engine, possess the structure that operating angle that combustion motor valve is intake valve and valve lift amount are carried out the changeable mechanism of variable control.Right row consist of #1 cylinder, #3 cylinder and #5 cylinder, and left column consists of #2 cylinder, #4 cylinder and #6 cylinder, but because structure is identical, thus below to one-sided be that right row describe.

(the first mode of execution)

Fig. 1～Fig. 3 represents the first mode of execution of the present invention, possesses: the first intake valve 3 that every cylinder is two and the second intake valve 3, and it opens and closes a pair of suction port 2,2 being formed in cylinder head 1; Live axle 5, it is configured in the upside of #1 cylinder, #3 cylinder and #5 cylinder along internal-combustion engine fore-and-aft direction, and has three driving cam 5a in periphery; A pair of swing cam 7,7, it is rotatably freely supported on the outer circumferential face of this live axle 5, by parts are set, is that each swing arm 6 makes described each intake valve 3 carry out on-off action; Transfer mechanism 8, its rotating force by described each driving cam 5a converts oscillatory forces to and is delivered to described each swing cam 7; Control mechanism 9, it controls operating angle and the lift amount of described each intake valve 3,3 by this transfer mechanism 8; Two supporting point parts (pivot) are i.e. the first hydraulic lash adjuster 10a and the second hydraulic lash adjuster 10b, and it is maintained in cylinder head 1, by described each swing arm 6, the valve clearance between each intake valve 3,3 and each swing cam 7 are adjusted into zero clearance; Three valve shut-down mechanisms 11, according to internal combustion engine operation state, the first hydraulic lash adjuster 10a by one stops the on-off action of the first intake valve 3 of one for it.

In addition, changeable mechanism consists of described live axle 5, swing cam 7, transfer mechanism 8 and control mechanism 9.

Below, for ease of explanation, each structure member in a cylinder, for example #1 cylinder is described.

Described each intake valve 3 remains in cylinder head 1 sliding freely by valve guide bushing 4, and utilizes by elasticity and be connected near be located at each rod end 3a each spring holder 3b and each valve spring 12 between the inside upper surface of cylinder head 1 to the closing direction application of force.

Described live axle 5 is supported with freely described swing cam 7 by camshaft 7a rotation on a plurality of bearing portions 13 of upper end portion that are arranged at cylinder head 1, utilizes timing belt via the not shown timing belt pulley that is arranged on an end, to transmit the rotating force of bent axle.In addition, the axle center Y that every cylinder arranges the described driving cam 5aShi Qi axle center X self-powered moving axis 5 of in the periphery of live axle 5 rises to radial disbalance, and the cam profile of periphery forms common circular.

The concavity lower surface of one end 6a of described each swing arm 6 and the rod end 3a butt of described each intake valve 3, and the lower surface recess 6c of the other end 6b and described each hydraulic lash

adjuster

10a, 10b butt, and make roller 14 take in to be freely configured in by roller axle 14a rotation to be formed in central reception hole.

As shown in Fig. 1 waits, described each swing cam 7 is arranged on camshaft 7a cylindraceous two end part integratedly, and on lower surface, be formed with the camming surface 7b consisting of basic circle Mian, inclined-plane and lift face, this basic circle Mian, inclined-plane and lift face rotate contact on the upper surface of the roller 14 of described swing arm 6 according to the swing position of swing cam 9.

The collar that described camshaft 7a makes to be formed on the axial substantial middle position of outer circumferential face is rotatably freely supported on described a plurality of bearing portion 13 with micro-gap, and utilizes inner peripheral surface rotation to support freely the outer circumferential face of described live axle 5.

Described transfer mechanism 8 possesses: the rocking arm 15 that is configured in the top of live axle 5; Make an end 15a of this rocking arm 15 and the link arm 16 of driving cam 5a interlock; Make the connecting rod 17 of rocking arm 15 the other end 15b and swing cam 7 interlocks.

The base portion of the tubular that the central authorities of described rocking arm 15 have is rotatably freely supported on control cam described later via bearing hole, and an end 15a of described rocking arm 15 utilizes pin 18 rotations to be attached at freely 19 rotations of link arm 16Shang，Er the other end 15b utilization pin and is attached at freely on connecting rod 17 upper end portion.

In the embedding hole 16a that the middle position of the circular base portion of described link arm 16 has, rotate the chimeric cam body that has described driving cam 5a freely, and the protruding terminus of described link arm 16 utilizes described pin 18 to be attached on rocking arm one end 15a.

Described connecting rod 17 underpart is attached at the cam tip of swing cam 7 freely by pin 20 rotations.

In addition,, between described rocking arm 15 the other end 15b and connecting rod 17 upper end portion, be provided with the controlling mechanism 23 of finely tuning the lift amount of each intake valve 3 when the assembling of each structure member.

Described control mechanism 9 is fixed with: Control Shaft 21, and its top position at live axle 5 is rotatably freely supported on identical bearing portion; Control cam 22, its periphery at this Control Shaft 21 is embedded in the bearing hole of described rocking arm 15 sliding freely, becomes the swing fulcrum of rocking arm 15.

Described Control Shaft 21 configures side by side along internal-combustion engine fore-and-aft direction and live axle 5, and actuator as shown in Figure 6 50 is controlled rotation.On the other hand, described control cam 22 is cylindric, and shaft core position is from the axis deviation established amount of Control Shaft 21.

As shown in Figure 6, described actuator 50 forms by motor 51 with as the ball screw framework 52 of reducing gear, motor 51 is fixed on an end of not shown housing, and ball screw framework 52 is arranged on the inside of housing, and the rotary driving force of this motor 51 is delivered to described Control Shaft 21.

Described motor 51 consists of the DC motor of proportional-type, by being controlled clockwise and anticlockwise from the control signal that detects the control unit described later 53 of internal combustion engine operation state.

As shown in Fig. 1～Fig. 5, described the first hydraulic lash adjuster 10a and second each hydraulic lash adjuster 10b possess: have the main body 24 of round-ended cylinder shape, it slides up and down in the columned retaining hole 1a that remains on freely cylinder head 1; Plunger 27, it slides up and down and is accommodated in freely in this main body 24, by the partition wall 25 having integratedly in bottom, in inside, is formed and stores chamber 26; Hyperbaric chamber 28, it is formed in described main body 24 bottom, by be penetratingly formed at intercommunicating pore 25a on described partition wall 25 with described in store chamber 26 and be communicated with; One-way valve 29, it is arranged on the inside in this hyperbaric chamber 28, and hydraulic oil Jin Xiang hyperbaric chamber 28 directions that store described in permission in chamber 26 flow into.In addition, in the inside of described cylinder head 1, be formed with the tap hole 1b that the hydraulic oil being detained in described retaining hole 1a is discharged to outside.

On the outer circumferential face of described main body 24, be formed with the first groove 24a cylindraceous, and on the perisporium of this first groove 24a, be radially formed through the first via hole 31, this first via hole 31 will be formed on the inside of described cylinder head 1 and the oily path 30 and main body 24 internal communication that downstream is opened wide to described the first groove 24a.

In addition, as shown in Fig. 4 A, B, the bottom 24b side of the main body 24 of the first hydraulic lash adjuster 10a side is extended setting downwards and is formed roughly cylindric than the main body 24 of the second hydraulic lash adjuster 10b side.

Described oily path 30 is communicated with the main oil gallery 30a that the lubricant oil in being formed on cylinder head 1 is supplied with use, and lubricant oil is pressed to this main oil gallery 30a from the oil pump 54 shown in Fig. 6.

Described plunger 27 is formed with the second groove 27a cylindraceous on the outer circumferential face of axial substantial middle, and on the perisporium of this second groove 27a, is radially formed through the alternate path hole 32 that is communicated with described the first via hole 31 and stores chamber 26.In addition, the front-end face of the front end head 27b of plunger 27 be guarantee and the lower surface recess 6c of the spherical shape of the other end 6b of swing arm 6 between good sliding form spherical shape.

In addition the circular backstopping assembly 33 that, this plunger 27 utilizes setting-in to be fixed on main body 24 upper end portion limits its maximum overhang.

The axial width of described the second groove 27a forms greatlyr, thus, plunger 27 with respect to main body 24 slide up and down arbitrarily position, described the second groove 27a is communicated with described the first via hole 31 all the time with alternate path hole 32.

Described one-way valve 29 consists of holder 29c and the second disc spring 29d of check ball 29a, the first disc spring 29b, cup-shaped, check ball 29a opens and closes the lower openings edge (valve seat) of described intercommunicating pore 25a, the first disc spring 29b to this check ball 29a to the closing direction application of force, holder 29c keeps this first disc spring 29b, the second disc spring 29d elasticity is arranged between the inner bottom surface of diapire 24c and the circular upper end portion of holder 29c of main body 24, to holder 29c to the partition wall 25 direction application of forces and to the plunger 27 integral body application of force upward.

And, in the basic circle interval of swing cam 7, if the stretching out of the described plunger 27 causing along with the active force of described the second disc spring 29d mobile (move top), in hyperbaric chamber 28, become low pressure, the hydraulic oil being supplied in retaining hole 1a from described oily path 30 will be flowed into and be stored chamber 26 by the first via hole 31, the second groove 27a and alternate path hole 32 from the first groove 24a, and further resist the elastic force of the first disc spring 29b and press off check ball 29a, hydraulic oil is flowed in hyperbaric chamber 28.

Thus, the other end 6b of plunger 27 jack-up swing arm all the time 6, is adjusted to zero clearance with contacting of swing cam 7 by the gap between the rod end 3a of an end 6a of swing cam 7 and swing arm 6 and each intake valve 3 by roller 14.

And in the lift interval of described swing cam 7, because below load acts on plunger 27, so the hydraulic pressure in hyperbaric chamber 28 rises, the oil in hyperbaric chamber 28 spills from plunger 27 and main body 24 gap, plunger 27 decline slightly (leaking down).

If it is interval again to enter the basic circle of swing cam 7, as mentioned above, by utilizing the active force of described the second disc spring 29d that described plunger 27 is produced, stretch out mobile (move top), Jiang Gebu gap is adjusted to zero clearance.

Described the first hydraulic lash adjuster 10a and the second hydraulic lash adjuster 10b both sides have such gap adjustment function.

As shown in Fig. 4 A, B, described valve shut-down mechanism 11 consists of with hole 34, lost motion springs 35 and limting mechanism 36 columned slip, slide and be only arranged on described the first hydraulic lash adjuster 10a side with hole 34, form continuously with the bottom side of described retaining hole 1a, lost motion springs 35 is elastically mounted between this slip Yong Kong34 bottom surface and the lower surface of main body 24, to described the first hydraulic lash adjuster 10a side direction application of force that makes progress, the idle running of described the first hydraulic lash adjuster 10a of limting mechanism 36 restriction.

Described slip is set to identical with the internal diameter of described Bao Shi hole 1a with the internal diameter in hole 34, described main body 24 is retained as can start continuously direction up and down from described retaining hole 1a to slide.

Described lost motion springs 35 is formed by disc spring, and it makes progress the side direction application of force and make the front end 27a of described plunger 27 and the other end 6b lower surface elasticity butt of described swing arm 6 described main body 24 bottom surface.

In addition, described main body 24 is configured in pin 37 mobile positions, the maximum top of restriction of described cylinder head 1 inside by interting.; described pin 37 configures along the direction perpendicular to axis towards described main body 24 in cylinder head 1; and front end 37a is configured in described the first groove 24a in the mode that can slide and can be projected into described the first groove 24a inside; thereby by move the butt of the lower ora terminalis of the described front end 37a that occurs and the first groove 24a along with the top of main body 24, the maximum top sliding position of restriction main body 24.

Therefore, described the first hydraulic lash adjuster 10a is along with the swing of swing arm 6, elastic force by described lost motion springs 35 is at described retaining hole 1a and between sliding with hole 34, stroke occurs up and down and dally, thus, lost the function as the swing fulcrum of described swing arm 6, the on-off action of the first intake valve 3 is stopped.

Described limting mechanism 36 is mainly by the mobile hole 38 of using, hole 39 is used in restriction, holder 40, banking pin 41 and Returnning spring 42 form, it is mobile that with hole 38, the inner radial along the bottom 24b of described main body 24 is penetratingly formed, with hole 39, on the interior edge of described cylinder head 1, the direction perpendicular to retaining hole 1a axis forms in restriction, it is distolateral that holder 40 is fixed on the described mobile inside one with hole 38, banking pin 41 is arranged on the described mobile inside with hole 38 sliding freely, can move with hole 38 and move in the scope with hole 39 to described restriction from this, Returnning spring 42 elasticity are arranged between this banking pin 41 rear end and described holder 40, described banking pin 41 is used to the hole 39 direction application of forces to limiting.

Described restriction is consistent from the axial and described mobile hole 38 of using when described main body 24 is limited to maximum top position by described pin 37 with hole 39, its internal diameter forms with described mobile roughly the same with hole 38, and signal hydraulic from being formed on oily via hole 43 in cylinder head 1, to be imported into one distolateral.

At this, the restriction of the sense of rotation of described main body 24 can easily be realized by such mode,, increase slightly the overhang of described pin 37, in the described first groove 24a of described main body 24, the slit of length direction is set, and this slit is engaged with described pin 37 front ends simultaneously.Or, also other rotation restricting units can be arranged between cylinder head 1 and described main body 24.

It is cylindric that described holder 40 has formed lid, in bottom, be penetratingly formed the spiracle 40a that is useful on the smooth and easy movement of guaranteeing banking pin 41, and as shown in Figure 4 B, its axial length is set to following length: at described banking pin 41, be accommodated in completely mobile with that time in hole 38, the front-end edge butt of banking pin 41 rear end and this holder 40 and limit and further retreat movement.

Described banking pin 41 forms filled circles column, and its external diameter forms more mobile with hole 38 with limit that internal diameter with hole 39 is slightly little guarantees sliding smoothly than described.In addition, this banking pin 41 utilizes the compression face of front end 41a to bear from described oily via hole 43 and is supplied to the hydraulic pressure hole 39 for restriction, resisting thus the elastic force of described Returnning spring 42 then retires moving, make front end mobile with in hole 38 with extracting and be accommodated in hole 39 from restriction, thereby lift restrictions.

As shown in Figure 6, from described oil pump 54, by the hydraulic pressure of force feed, via electromagnetic switching valve 55, as signal hydraulic, be supplied to described oily via hole 43(restriction and use hole 39).

Described electromagnetic switching valve 55 utilizes the elastic force of solenoidal electromagnetic force and disc spring that the guiding valve that is arranged on sliding freely the inside of not shown valve body is switched to and opens, cuts out this two-stage, it is to control electric current and be communicated with pump drain passageway and oily via hole 43 or the mode of closing pump drain passageway and being communicated with described oily via hole 43 and drain passage 44 is carried out switching controls to passing into or do not pass into described solenoid from controlling the identical control unit 53 of the driving of described motor 51, thus, signal hydraulic is controlled as big or small two-stage.

The information signal of described control unit 53 based on from various sensors such as crankshaft sensor, Air flow meter, cooling-water temperature sensor, throttle angle sensors detects internal combustion engine operation state (internal combustion engine operation condition), and by this internal combustion engine operation state with from the information signal of not shown rotational position sensor that detects the current rotational position of described Control Shaft 21, drive and control described motor 51, control the rotational position of described Control Shaft 21.Thus, the lift amount of each

intake valve

3,3 and operating angle are changed.

In addition, this control unit 53 has by described electromagnetic switching valve 55 and forbids that the valve of described valve shut-down mechanism 11 idle running stops forbidding that member is that valve stops forbidding loop.This valve stops forbidding that the angle of swing θ of loop based on described Control Shaft 21 carries out being communicated with by described electromagnetic switching valve 55 control of described oily via hole 43 and drain passage 44.Thus, described banking pin 41 moves by hole 39 directions to restriction by the elastic force of Returnning spring 42, make the front end 41a of banking pin 41 snap in restriction with in hole 39, thereby make described main body 24(the first hydraulic lash adjuster 10a) be locked in cylinder head 1, forbid the first hydraulic lash adjuster 10a idle running.

For utilizing described valve to stop to forbid the rotary angle position of described Control Shaft 21 of the driving of circuit controls electromagnetic switching valve 55, can at random set according to internal combustion engine operation state etc., but in the present embodiment, set Control Shaft 21 for for the rotary angle position of θ 3, so that the lift amount of the first intake valve 3 and the second intake valve 3 is the L3 shown in Figure 12.

That is to say, path increment M by the idle running with described the first hydraulic lash adjuster 10a becomes the rotary angle position θ of the described Control Shaft 21 of corresponding relation to detect the path increment M of the idle running of described the first hydraulic lash adjuster 10a, at this θ, surpass the θ 3 corresponding with lift amount L3 at the moment, described the first hydraulic lash adjuster 10a is not limited in the situation of pin 41 lockings, cut-out flows to the control electric current of described electromagnetic switching valve 55 and oily via hole 43 is communicated with drain passage 44, utilizes described banking pin 41 to lock forcibly the first hydraulic lash adjuster 10a.In addition,, if surpassing 3 that times of described θ, described banking pin 41 is locked, becomes two valve lift operating states, maintains this state.

(action of variable valve gear)

Below, the action of the variable valve gear of present embodiment is described.

For example, from the idle running of internal-combustion engine to low rotation speed area, by making motor 51 be rotated driving from the control electric current of control unit 53 output, this torque is delivered to described Control Shaft 21 via ball screw framework 52.If drive this Control Shaft 21 rotations to a direction, as shown in Fig. 7 A, B, Fig. 8 A, B, control cam 22 and also to a direction rotation and axle center, around Control Shaft 21 axle center, with same Radius, rotate, wall thickness moves away from live axle 5 to upper right side direction as shown in figure.Thus, the pivot point of rocking arm 15 the other end 15b and connecting rod 17 (connection pin 19) with respect to live axle 5 upwards side direction move, therefore, each swing cam 7 makes cam tip side by pull-up forcibly by connecting rod 17.

Therefore, if driving cam 5a rotates and passes through an end 15a of link arm 16 jack-up rocking arms 15, its lift amount is delivered to each swing cam 7 and each swing arm 6 via connecting rod 17, the spring counter-force of each intake valve 3 opposing valve spring 12 and drive valve, its lift amount for example L1～L3 as shown in figure 12 becomes fully little like that.

For example, internal-combustion engine is transitioned into the situation of middle and high rotary area from the slow-speed of revolution, if motor 51 makes ball screw framework 52 rotate to equidirectional by the control current reversal from control unit 53, as shown in Figure 10 A, B, Figure 11 A, B, along with this rotation, Control Shaft 21 makes to control cam 22 to other direction rotation, and axle center downward direction moves.

Therefore, the current integral body of rocking arm 15 moves to live axle 5 directions, and utilizes the other end 15b by connecting rod 17, to push the cam tip of swing cam 7 downwards, makes these each swing cam 7 integral body to counter clockwise direction, rotate established amount from the position shown in Fig. 7, Fig. 8.Therefore, as shown in Figure 10, Figure 11, the camming surface 7b of each swing cam 7 is mobile to cam tip side (lift portion side) with respect to the butt position of roller 14 outer circumferential faces of each swing arm 6.

Therefore, if when the opening action of intake valve 3, driving cam 5a rotation via an end 15a of link arm 16 jack-up rocking arms 15, each intake valve 3 is driven valve via the elastic force of each swing arm 6 each valve spring 12 of opposing, its valve lift amount changes continuously until become the maximum L7 shown in Figure 10～Figure 12, and along with the rising of rotation become greater to L4～L7 always.Thus, can improve air inlet charging efficiency, seek the raising of output power.

(action of valve shut-down mechanism)

And, described from idle running to low rotation speed area in, the lift amount of each

intake valve

3,3 becomes in the situation in little lift amount region of the L1～L3 shown in Figure 12, especially wanting to seek to improve under the specific operating condition of combustion efficiency, from described control unit 53, to electromagnetic switching valve 55 outputs, control electric current, make large discharge hydraulic pressure from oil pump 54, by oily via hole 43, be imported into restriction with in hole 39 as signal hydraulic.

Therefore, the elastic force that is subject to the banking pin 41 opposing Returnning springs 42 of this large signal hydraulic is then retired moving, and front end 41a is extracted with hole 39 from restriction, removes the first hydraulic lash adjuster 10a with respect to the locking of cylinder head 1.

Therefore, as shown in Figure 4 B, the first hydraulic lash adjuster 10a integral body can dally, the elastic force by described lost motion springs 35 at retaining hole 1a with in sliding with hole 34 repeatedly up and down direction move and become idling conditions.Therefore, the first intake valve 3 becomes the valve state that closes (valve halted state).

; until become valve halted state; described swing cam 7 is all being opened valve stroke position and is being changed to the maximum of Fig. 7 B from the zero lift shown in Fig. 7 A (closing valve) position; even if suppose that lift amount L2 drives valve; and when becoming valve and stop; described swing cam 7 swings to greatest extent, and the first hydraulic lash adjuster 10a is also the path increment idle running with the M2 shown in Fig. 7 B, to the valve halted state transition of in fact not carrying out valve lift.The position that the open angle α (with reference to Fig. 7 B) forming between the first swing arm 6 of this moment and the first hydraulic lash adjuster 10a becomes peak lift at swing cam 7 becomes the α 2 shown in Figure 13, but this does not become excessive open angle.

Therefore,, even if described swing cam 7 becomes peak lift (maximum is opened valve events), also can obtain valve smoothly and stop action.

On the other hand, as shown in Fig. 8 A, B, because the second hydraulic lash adjuster 10b side is as the common swing fulcrum performance function relative with the second swing arm 6, so the second intake valve 3 still carries out on-off action with lift amount L2, therefore, can strengthen intake swirl, seek the improvement of combustion efficiency and burning.

Then, for example internal-combustion engine rotational speed is further risen, require torque to uprise and again to two valve lift operating state transition, increase lift amount and described Control Shaft 21 simultaneously further and to clockwise direction rotation, become the situation of θ 3, the situation that namely lift amount of two

intake valves

3,3 becomes the L3 shown in Figure 12 is investigated.The requirement of supposing combustion efficiency from this state again uprises and to valve, stops the situation of transition, and as shown in Figure 9, the open angle being formed between the first swing arm 6 and the first hydraulic lash adjuster 10a becomes α 3, becomes the state that opening degree is very large.

Therefore, the front end head 27b of the first hydraulic lash adjuster 10a becomes inhomogeneous with respect to the contact of the lower surface recess 6c of the other end 6b of the first swing arm 6.

; conventionally; the contact of the front end head 27b of hydraulic lash adjuster 10a in the sphere portion of roller 14 sides is balance with contacting in sphere portion at roller 14 opposition sides; and the lower surface recess 6c that stably keeps the other end 6b of the first swing arm 6; if but described α 3 becomes large; the contact in the sphere portion of roller 14 sides is moved upward, and the contacting part in the sphere portion of roller opposition side moves downwards.

If the load from roller 14 acts on this, the load that the contacting part of the sphere portion of roller 14 sides that have been moved upward bears increases terrifically, and balance is broken, and easily becomes local contact.

Consequently, except move the top of contacting part forward end head 27b, also easily because the load of roller 14 etc. misplaces contact, easily there is the first swing arm 6 to the phenomenon of valve opposition side skew, according to circumstances, the lower surface recess 6c of the other end 6b of the first swing arm 6 may depart from from the 27b of front end portion.Yet, under the level of this α 3, be also converged in allowed band at last, if but surpass this α 3, the actual possibility that described break-off occurs will uprise.

So, in the lift amount that time that surpasses this L3, cut-out stops forbidding that from the valve of described control unit 53 loop stream is to the control electric current of electromagnetic switching valve 55, make oily via hole 43 and drain passage 44 be communicated with and restriction is discharged in oil sump 45 with the hydraulic pressure in hole 39 and oily via hole 43, change low-pressure state into.

Thus, as shown in Figure 4 A, described banking pin 41 moves by hole 39 directions to restriction by the elastic force of Returnning spring 42, the first hydraulic lash adjuster 10a rises mobile and is further risen mobile by described pin 37 restrictions in the basic circle region of described swing cam 7, mobile with hole 38 and restriction with hole 39 consistent that time, the front end 41a of banking pin 41 snap in limit with hole 39 interior and the first hydraulic lash adjuster 10a is locked in cylinder head 1.

Therefore, at this constantly, the idle running of the first hydraulic lash adjuster 10a is limited.

Single-point line shown in Figure 13 represents the angle of swing θ of Control Shaft 21 and the dependency relation that valve stops the idle running amount (running length M) in situation, and the dotted line in Figure 14 (and solid line of dotted line prolongation) represents the dependency relation of the angle of swing θ of Control Shaft 21 and the lift amount L of the intake valve 3 in lift motion situation.

That is to say, as shown in figure 13, the idle running amount (running length M) of the first hydraulic lash adjuster 10a becomes dependency relation with the angle of swing θ of described Control Shaft 21, in addition, as shown in figure 14, the angle of swing θ of described Control Shaft 21 also becomes dependency relation with the lift amount L of intake valve 3, therefore, the information signal of described control unit 53 based on from rotation angle sensor, surpasses 3 that times of θ in the angle of swing of Control Shaft 21, cuts off forcibly the electric current that leads to described electromagnetic switching valve 55.

While representing these actions in Figure 13 and Figure 14, become each solid line such, but surpass M3 that time in described idle running amount, namely the lift amount at intake valve 3 surpasses L3 that time, mechanically forbids the idle running action of the first hydraulic lash adjuster 10a.Thus, the first intake valve 3 also carries out on-off action together with the second intake valve 3, implements the internal combustion engine drive of utilizing two valves to carry out.

So, lift amount at described intake valve 3 surpasses L3 that time, the idle running of the first hydraulic lash adjuster 10a disappears, therefore inhomogeneous by between the lower surface recess 6c of the other end 6b side of the first swing arm 6 and the front end head 27b of the plunger 27 of the first hydraulic lash adjuster 10a, avoids local butt.Therefore, the lower surface recess 6c of the first swing arm 6 can for example not come off from the front end head 27b of plunger 27, can obtain all the time working state smoothly.

In addition, in the angle of swing of the further rising of for example internal-combustion engine rotational speed and Control Shaft 21, comparing θ 3 further increases, thereby cause the idle running amount of the first hydraulic lash adjuster 10a further to surpass situation (each intake valve 3 in M3 region, 3 lift amount further surpasses the situation of the L3 of Figure 12) under, the non-power status of maintenance from control unit 53 to electromagnetic switching valve 55, not to hole 39 lead-in signal hydraulic pressure for restriction, therefore, the state not dallying of the first hydraulic lash adjuster 10a continues, bring into play in the same manner as the function that swings fulcrum with the second hydraulic lash adjuster 10b.

In other words, until the angle of swing that the idle running quantitative change of described the first hydraulic lash adjuster 10a is M3(Control Shaft 21 becomes θ 3), the first hydraulic lash adjuster 10a allows to dally, but surpassing M3 at the moment, the first hydraulic lash adjuster 10a makes valve stop being prohibited and idle running is limited and becomes changeless state, as common swing fulcrum performance function.

Figure 15 represents that the valve based on described control unit 53 stops forbidding the concrete control flow in loop.

; in step 1; information signal based on from described various sensor class elements; read current internal combustion engine operation state; in step 2; according to described internal combustion engine operation state, from the control mapping of predefined control mapping, for example internal-combustion engine rotational speed and load, read the target lift amount of the first intake valve 3 and the second intake valve 3.This time, the target lift amount of supposing the second intake valve 3 is L2, and the target lift amount of the first intake valve 3 is zero (valve stops), and the current lift amount of the first intake valve 3 and the second intake valve 3 is all near L3.

In step 3, whether the target lift amount of differentiating the first intake valve 3 of described the first hydraulic lash adjuster 10a side is zero, in differentiation, is zero, in the situation that namely valve stops, being transitioned into step 4.In this step 4, whether the actual lift amount that the angle θ obtaining according to the angular sensor from described Control Shaft 21 differentiates each

intake valve

3,3 has changed to below L3, differentiates for being in the situation below L3, is transitioned into step 5.

In this step 5, carry out to described electromagnetic switching valve 55 output opening signals or stay open the processing of signal.That is to say, owing to being below L3, so supply with signal hydraulic to restriction with hole 39, be transitioned into the idle running of the first hydraulic lash adjuster 10a, or maintenance is dallied and becomes single valve halted state.(this time,, to described electromagnetic switching valve 55 output opening signals, be transitioned into idle running.）

Then, in step 6, carry out controlling motor 51 and controlling the processing of the angle of swing θ of Control Shaft 21 to target lift amount, reset.

In described step 3, differentiation is in the non-vanishing situation of the target lift amount of the first intake valve 3, or in step 4, the actual lift amount of differentiating for each

intake valve

3,3 surpasses in the situation of L3, is transitioned into step 7.

In this step 7, carry out the processing (this time, keeping shutdown signal) to electromagnetic switching valve 55 output shutdown signals or maintenance shutdown signal.

That is to say, in the situation that surpassing L3, cut-out is cut off with the supply of the signal hydraulic in hole 39 or maintenance to restriction, elastic force by Returnning spring 42 makes banking pin 41 snap in restriction with in hole 39 or keep snapping in, and makes the first hydraulic lash adjuster 10a be locked in cylinder head 1 or keeps locking.Thus, the first intake valve 3 makes valve stop being prohibited, and utilizes and take the first hydraulic lash adjuster 10a as swinging the on-off action (lift motion) of the first swing arm 6 enforcements of fulcrum.Therefore, as previously mentioned, can be by forbidding the excessive idle running of the first hydraulic lash adjuster 10a, avoid the irregular action that caused with respect to part contact of front end head 27b etc. by the lower surface recess 6c of first swing arm the other end 6b, obtain operating state smoothly.

In addition, in the present embodiment, the condition of forbidding forcibly the idle running of described the first hydraulic lash adjuster 10a is that this idle running amount is while surpassing M3 (when the target lift of the first intake valve 3 surpasses L3), but in described control mapping, when also can be as follows: even also do not make the first intake valve 3 stop transition to valve lower than the lift amount of L3, the first intake valve 3 and the second intake valve 3 all carry out lift motion control.

At the favourable little operating angle of the toxic emission when to starting a cold engine etc. (for example, little lift amount L2), in situation while all needing to overcome the cold car of burning torque of internal-combustion engine friction, preferably there is not idle running and make two

intake valves

3,3 carry out on-off action, therefore, even if lift amount is less than L3, also forbid possibly idle running.

Surpassing described lift amount L3 and idle running M3 that time is only to become for forbidding forcibly the benchmark of idle running, in controlling mapping, according to operating condition, while being less than the lift amount of L3, also can not carry out the transition (to the transition of idle running action) stopping to valve and carry out two valve events.

On the other hand, also can be according to internal-combustion engine state, to forcing to forbid that the described benchmark of idle running is that the setting of the value of L3, M3 itself is changed.For example, in internal-combustion engine high speed area, due to small separation easily occurring between each parts of valve mechanism, so more easily there is swing arm 6 with respect to the dislocation of pivot and the irregular action such as come off, can be also therefore that the value of L3, M3 is set littlely by benchmark.

Below, supplementary notes present embodiment is with respect to the superior part of disclosed formerly technology in described prior art (TOHKEMY 2010-007636 communique).

That is, as shown in Fig. 4 of this communique, described prior art is fixed in cylinder head main body, by making plunger idle running itself carry out valve, stops.

Specifically, by reducing effect in the hydraulic fluid pressure of main body, increase the idle running amount of plunger, carry out valve and stop, but in the process midway reducing at hydraulic fluid pressure, idle running amount can not instantaneously increase, existence becomes the moment of unsettled middle idle running amount, and the lifting curve in this situation is unstable, and the action of valve mechanism becomes irregular, it is not only unfavorable for the inhibition of irregular action to worry there will be, the engine performance phenomenon such as unstable that also becomes.

To this, in the present embodiment, by the connection, the connection that utilize banking pin to carry out, to remove and alternatively select lift motion state and valve halted state (idling conditions), the lifting curve in the middle of not existing, does not therefore have described misgivings.

In addition, the main body of described prior art is fixed in cylinder head, plunger itself is dallied, therefore, the Returnning spring of jack-up plunger has spring function (micro-stroke) and the spring function (large stroke) for plunger is dallied for carrying out adjusting in the gap of hydraulic lash adjuster concurrently.Therefore, make spring-load reduce if pay attention to gap adjustment, the followability variation while dallying, if increasing conversely spring-load ，Ze gap adjustment can not carry out well, causes the pump that the excessive protuberance of plunger occurs to rise phenomenon.

To this, in the present embodiment, owing to can being provided for respectively spring 29d and the spring 35 for dallying of gap adjustment, so there is no such misgivings.

In addition, if low from the hydraulic fluid pressure of oil pump, as previously mentioned, described prior art becomes valve and stops, and therefore, while not looking to the internal-combustion engine larry from the hydraulic pressure of oil pump or while startup, becomes valve halted state.Therefore, deficiency of air when starting, exists due to the not enough problem that causes startability variation of torque.

To this, in the present embodiment, in the situation that there is no as previously mentioned signal hydraulic effect, become two valve events, therefore there is no such misgivings, can access good startability.

(the second mode of execution)

Figure 16 represents the second mode of execution, as valve, stops forbidding that member has also added mechanical structure.

That is, a part for described oily via hole 43 is formed with: a pair of oilhole 43a, the 43b that in the bearing portion 13 of the described Control Shaft 21 of supporting, along the direction perpendicular to Control Shaft 21 axis, run through.On the other hand, in described Control Shaft 21 inside, along in the direction perpendicular to its axis, be formed through the intercommunicating pore 46 being suitably communicated with described each oilhole 43a, 43b.At this intercommunicating pore 46 two end part, be formed with circular-arc oil groove 46a, 46b.

In the situation that the rotary angle position of Control Shaft 21 is θ 2(L2), as shown in solid line in figure, described intercommunicating pore 46 is communicated with two oilhole 43a, the 43b of described oily via hole 43 via described two oil groove 46a, 46b, and if the rotary angle position of Control Shaft 21 is for surpassing θ 3(L3) angular orientation, shown in dotted line, two oil groove 46a, 46b dislocation, described intercommunicating pore 46 was cut off with two oilhole 43a, being communicated with of 43b.

Therefore, in the situation that internal-combustion engine rotational speed is that the angle of swing of low rotation speed area and Control Shaft 21 lift amount in each

intake valve

3,3 of θ 1～θ 3(is L1～L3) region, as shown by the solid line, become the state that described oily via hole 43 and intercommunicating pore 46 are communicated with, signal hydraulic is fed into restriction with in hole 39, if and become the 3(L3 over θ) angle of swing, shown in dotted line, utilize the outer circumferential face of Control Shaft 21 to seal two

oilhole

43a, 43b, intercommunicating pore 46 was mechanically cut off with being communicated with of oily via hole 43.

Therefore, certainly can obtain the action effect same with described the first mode of execution, especially, in the present embodiment, even if for example described control unit 53 breaks down and makes electromagnetic switching valve 55 cause abnormal operation, make abnormal signal hydraulic be fed into the upstream side of oily via hole 43, also utilize described Control Shaft 21 to cut off path, therefore, surpassing θ 3(L3) in the situation that, must limit the idle running of the first hydraulic lash adjuster 10a and forbid that valve stops.

(the 3rd mode of execution)

Figure 17 represents the 3rd mode of execution, in the retaining hole 1a of the cylinder head 1 of the first hydraulic lash adjuster 10a side, be pressed into and be fixed with the holding member that has round-ended cylinder shape 47 that described the first hydraulic lash adjuster 10a can be slided up and down, and be provided with integratedly jut 47b at the middle position of the diapire 47a of this holding member 47 internal surface.

This jut 47b sets its height by this way,, when described the first hydraulic lash adjuster 10a idle running, idle running amount shown in described Figure 13 is even surpass slightly M3, this jut 47b also with the main body 24 bottom surface butt of the first hydraulic lash adjuster, restriction is idle running stroke further.

In addition, on the perisporium of described holding member 47, be formed with the access 47c that is communicated with described the first groove 24a and oily path 30, in diapire 47a side, be formed with spiracle 47d.

So, in the present embodiment, can utilize described jut 47b mechanically to limit the idle running stroke of the first hydraulic lash adjuster 10a and suppress excessive idle running, therefore can further avoid effectively the first swing arm 6 to contact with the part of the front end head 27b of plunger 27.

In addition, this holding member 47 adopts the aluminium normally with cylinder head 1() different iron type materials, thus, can improve for the limiting holes of described banking pin slip and with the wearability in the slip hole of main body 24 slips of hydraulic lash adjuster 10a etc.Certainly, such holding member 47 can be applied to the first mode of execution to remove the form of jut 47b.

(the 4th mode of execution)

Figure 18 represents the 4th mode of execution, and basic structure is identical with the first mode of execution, but comprise the lift amount changeable mechanism of described each

swing cam

7,7 whole with described each mode of execution mirror configuration oppositely.

Thus, swing cam 7 swings lift by clockwise direction in figure and makes

swing arm

6,6,

intake valve

3,3 open valve stroke.

In the present embodiment, while comparing with the structure shown in Fig. 9 of the first mode of execution, the idle running direction of the swing lift direction of swing cam 7 and the first hydraulic lash adjuster 10a is in the same way, so the cam tip of swing cam 7 and swing arm 6 are difficult to interfere in course of action.

In addition, swing cam 7 approaches the first hydraulic lash adjuster 10a side with the roller 14 point of contact of swing arm 6, just pushes near the central authorities of swing arm 6, and therefore the butt of the first hydraulic lash adjuster 10a and swing arm 6 becomes well, is difficult to come off.This is because the contact of the front end head 27b of the first hydraulic lash adjuster 10a in the sphere portion of roller 14 sides is balance with contacting in sphere portion at roller opposition side.

So, in the present embodiment, can access the good butt state of the first hydraulic lash adjuster 10a and swing arm 6, and can suppress the interference between parts.

The structure that the invention is not restricted to described each mode of execution, for example, as internal-combustion engine, not only can be applied to described V-type six cylinders, can also be applied to V-type eight cylinders, with these single-row suitable in-line four cylinder or other internal-combustion engines.

In addition, also can make the cam profile of described two

swing cams

7,7 different, thus, in the region of the high both sides' of engine load valve event, can maintain air inlet charging efficiency, can also realize the burning being caused by small eddy current and improve simultaneously.As engine valve, except described intake valve 3, can also be applied to exhaust valve side, in this situation, owing to can strengthening the eddy current of waste gas, so can improve the toxic emission conversion performance of catalyzer.

In addition, although show a side who makes in a pair of engine valve, carry out the mode of execution that valve stops, also can being applied to two valves and all carrying out the so-called cylinder that valve stops and stopping.And, as the parts that dally, except hydraulic lash adjuster, can be also the parts without gap function.

In addition, valve shut-down mechanism can also be arranged in the first swing arm 6, in this situation, if on the master pendulum arm shown in Japanese Unexamined Patent Application Publication 2009-503345 for example, arrange can displacement (idle running) roller part, and this roller part and master pendulum arm are switched to connection or non-connection.In this situation, also can suppress to occur to depart from or interfere because excessive idle running makes the butt of roller part and swing cam, or visit irrational attitudes such as the end when idle running, thereby realize action smoothly.

In addition, can also be applied to the tappet formula valve mechanism without hydraulic lash adjuster recorded in TOHKEMY 2010-270633.In this situation, as long as use the valve shut-down mechanism that is built in valve tappet shown in Japanese kokai publication sho 63-16112.And, can also be applied to two valve shut-down mechanisms.

Technological thought for the invention beyond the described claim of holding from described mode of execution, is described as follows.

The variable valve gear of (technological scheme a) internal-combustion engine as described in technological scheme 1, is characterized in that,

Described valve shut-down mechanism there is retaining hole that described supporting point part can be kept movably and to described supporting point part the force application component to the described swing arm direction application of force,

By resisting the active force of described force application part, make described supporting point part move to dally.

The variable valve gear of (technological scheme b) internal-combustion engine as described in technological scheme a, is characterized in that,

Described supporting point part is hydraulic lash adjuster.

The variable valve gear of (technological scheme c) internal-combustion engine as described in technological scheme 1, is characterized in that,

Described valve shut-down mechanism is only arranged on the side in described a pair of supporting point part,

Described idle running amount is specified value when following, allows to utilize described valve shut-down mechanism only to make corresponding engine valve stop.

According to the present invention, can stop making eddy current effect to become large by single valve, seek the raising of combustion efficiency.

The variable valve gear of (technological scheme d) internal-combustion engine as described in technological scheme 1, is characterized in that,

Described valve shut-down mechanism is arranged on the both sides of described a pair of supporting point part,

Described idle running amount is established amount when following, allows to utilize described valve shut-down mechanism that both sides' engine valve is stopped.

According to the present invention, by making both sides' engine valve stop changing into cylinder halted state, can make the closure of the cylinder that do not stop significantly open, therefore can reduce pumping loss.

The variable valve gear of (technological scheme e) internal-combustion engine as described in technological scheme c, is characterized in that,

Described a pair of swing cam forms.

The variable valve gear of (technological scheme f) internal-combustion engine as described in technological scheme a, is characterized in that,

Described swing fulcrum is by being arranged on the recess of the spherical shape in described swing arm and being arranged on described supporting point part and the protuberance of the spherical shape engaging with described recess forms.

The variable valve gear of (technological scheme g) internal-combustion engine as described in technological scheme a, is characterized in that,

Described valve stops forbidding that member mechanically forbids the idle running of described supporting point part when idle running amount surpasses specified value.

The variable valve gear of (technological scheme h) internal-combustion engine as described in technological scheme a, is characterized in that,

Described Control Shaft has the control cam with respect to this axle center bias,

Described transfer mechanism is interspersed in described control cam, and the rotation by this control cam changes attitude.

The variable valve gear of (technological scheme i) internal-combustion engine as described in technological scheme g, is characterized in that,

The restriction of described idle running is in the mobile range of described supporting point part, to utilize jut to limit the movement of described supporting point part.

The variable valve gear of (technological scheme j) internal-combustion engine as described in technological scheme g, is characterized in that,

Described valve stop forbidding member by be arranged on the inwall of described supporting point part and described retaining hole mobile with hole and restriction with hole and across described mobile with hole and restriction with hole in and the banking pin that can arrange movably form, and control: by make described banking pin across move with hole with limit the state that configures to lock described supporting point part with hole; Described banking pin is accommodated in described mobile with in hole and the state that described supporting point part can be dallied.

The variable valve gear of (technological scheme k) internal-combustion engine as described in technological scheme j, is characterized in that,

Described valve stops forbidding that member possesses: force application part, and it is arranged on the mobile with in hole of described supporting point part, and described banking pin is used to the hole direction application of force to limiting; Oil hydraulic circuit, it supplies with hydraulic pressure, and this hydraulic pressure is resisted the active force of this force application part and by hole direction, is pushed described banking pin to the mobile of described supporting point part.

The variable valve gear of (technological scheme 1) internal-combustion engine as described in technological scheme k, is characterized in that,

Described oil hydraulic circuit has: be arranged on the oily via hole on the bearing portion of described Control Shaft; Diametric(al) along described Control Shaft runs through the intercommunicating pore that forms and be suitably communicated with described oily via hole,

Described Control Shaft is when the angle of swing of stipulating is following, and described oily via hole and intercommunicating pore are communicated with, and when described Control Shaft surpasses the angle of swing of regulation, cuts off described connection.

The variable valve gear of (technological scheme m) internal-combustion engine as described in technological scheme k, is characterized in that,

If the idle running amount than the regulation of described supporting point part is little, so that described banking pin is resisted described force application part, mobile mode is supplied with hydraulic pressure, if surpass the idle running amount of regulation, the active force by described force application part makes banking pin move by hole direction to restriction.

The variable valve gear of (technological scheme n) internal-combustion engine as described in technological scheme a, is characterized in that,

Described swing arm and supporting point part angulation when the idle running amount of described supporting point part is specified value deducts the angle after 90 °, than described swing arm and supporting point part when the maximum lift of intake valve is controlled drive valve time the angulation angle that deducts after 90 ° little.

According to the present invention, the undesirable level of the attitude of the described swing arm of opening valve position when the undesirable level of the attitude of the swing arm in the time of can making idle running amount be specified value is controlled than maximum lift is good, can make valve stop action more smooth and easy.

The variable valve gear of (technological scheme o) internal-combustion engine as described in technological scheme a, is characterized in that,

Described valve stops forbidding that member has limiting part, and this limiting part, when the idle running amount of supporting point part surpasses specified value, limits idle running to described supporting point part to the swing arm direction application of force.

The variable valve gear of (technological scheme p) internal-combustion engine as described in technological scheme k, is characterized in that,

Described valve stops forbidding that member stops forbidding that by valve loop forms, and this valve stops forbidding that loop is when idle running amount surpasses specified value, makes control unit by the electromagnetic switching valve of described oil hydraulic circuit, cut off the supply of hydraulic pressure.

The variable valve gear of (technological scheme q) internal-combustion engine as described in technological scheme p, is characterized in that,

The specified value of the idle running amount of described regulation can at random be set according to the operating condition of described internal-combustion engine.

According to the present invention, can set arbitrarily described forbidden idle running amount, thus, and for example, in high speed area, the irregular action in the time of can effectively suppressing valve and stop.

Claims

1. a variable valve gear for internal-combustion engine, is characterized in that, possesses:

Live axle, transmits rotary driving force from the bent axle of internal-combustion engine to this live axle, and this live axle is provided with driving cam in periphery;

Two swing cams, it makes the elastic force of two engine valve opposing valve spring of every cylinder and carries out opening action;

Transfer mechanism, it converts rotatablely moving of described driving cam oscillating motion to and is delivered to described swing cam;

A pair of swing arm, it is arranged between described each swing cam and each engine valve, by the oscillatory forces of described swing cam and the elastic force of described valve spring, makes described each engine valve carry out on-off action;

A pair of supporting point part, it becomes the swing fulcrum of this each swing arm;

Control mechanism, it,, by the attitude of described transfer mechanism is changed, implements variable control to the lift amount of described each engine valve;

In the variable valve gear of this internal-combustion engine,

Be provided with the valve shut-down mechanism by making at least one party's idle running of described a pair of supporting point part that the driven for opening and closing of the engine valve of one is stopped,

And be provided with in the situation that the idle running amount of this valve shut-down mechanism surpasses specified value and forbid that the valve that valve stops stops forbidding member.

2. a variable valve gear for internal-combustion engine, is characterized in that, is provided with:

Driving cam, from bent axle transmission to this driving cam rotating force;

Engine valve, it arranges two in every cylinder, and the elastic force by valve spring is by closing the valve direction application of force;

Swing cam, it makes the elastic force of this each engine valve opposing valve spring and carries out opening action;

A pair of action component, its oscillating motion according to described swing cam swings, and makes described each engine valve carry out on-off action;

Valve shut-down mechanism, its absorb one action component oscillating quantity and the on-off action of the engine valve of one is stopped;

Valve stops forbidding member, and it forbids that described valve shut-down mechanism absorbs oscillating motion in the situation that the oscillating quantity of described action component surpasses established amount.

3. a variable valve gear for internal-combustion engine, is characterized in that, possesses:

Driving cam, it is rotated by crank-driven;

A pair of engine valve, its elastic force by valve spring is by the closing direction application of force;

A pair of swing cam, it drives described a pair of engine valve by swinging via a pair of action component;

Transfer mechanism, it converts rotatablely moving of described driving cam to oscillating motion and is delivered to described a pair of swing cam;

Control mechanism, it changes the acting characteristic of described a pair of engine valve by the attitude of this transfer mechanism is changed;

Valve shut-down mechanism, its at least one party who is arranged on described a pair of action component is upper, by dallying, makes the driving of the engine valve of one stop,

In the situation that the valve lift amount of the engine valve of one surpasses specified value, forbid the action that the caused valve of valve shut-down mechanism stops.

4. the variable valve gear of internal-combustion engine as claimed in claim 1, is characterized in that,

5. the variable valve gear of internal-combustion engine as claimed in claim 4, is characterized in that,

6. the variable valve gear of internal-combustion engine as claimed in claim 5, is characterized in that,

7. the variable valve gear of internal-combustion engine as claimed in claim 6, is characterized in that,

8. the variable valve gear of internal-combustion engine as claimed in claim 6, is characterized in that,

9. the variable valve gear of internal-combustion engine as claimed in claim 4, is characterized in that,

10. the variable valve gear of internal-combustion engine as claimed in claim 4, is characterized in that,